01_マイクロ_E_p006_023.qxd 11.11.

10 9:37 AM ページ6

Electromagnetic clutches and brakes

Miki Pulley electromagnetic clutches
and brakes belong to the type of
dry/single plate/coil static system in
the frictional-type electromagnetic
clutches and brakes.
The "Electromagnetic clutches and
brakes" is a generic term used to refer to
the functions such as transmission and
interruption or deceleration and
stoppage of torque by electro-
magnetic action. They are
classified mainly by three in
accordance with the intended
use.
Electromagnetic clutches and brakes

●Electromagnetic clutches and brakes

Electromagnetic micro clutches and brakes

Electromagnetic clutches and brakes

Electromagnetic clutch and brake units

● Electromagnetic micro clutches and

brakes
Ideal for use in small precision equipment such as business
machine, communications equipment or automobile
machinery that has a susceptibility to fluctuations of torque
and responsiveness. The 102 model (clutch) and the 112
model (brake) with the same basic design can be provided as
well as the customizable CYT model (clutch).

● Electromagnetic clutches and

brakes
Compatible with overall general industrial machinery and the
rational design offers good performance.
The 101・CS model (clutch) and the 111 model (brake) with
the same basic design can be provided as well as the CSZ
model (clutch) and the BSZ model (brake) designed to
significantly reduce the assembling time by integrating each
part.

● Electromagnetic clutch and brake

units
Several clutches and brakes can be used when designing a
complex mechanism. Various units are available to eliminate a
troublesome task to combine the required number of each
clutch and brake. A number of models that combined a motor
or a reducer are also available.

6
01_マイクロ_E_p006_023.qxd 11.11.10 9:37 AM ページ7

■ Basic structure and Principle of operation

● Constant-force plate spring
As our basic actuation method of "Electromagnetic clutches and
brakes", we adopt spring drive using a "constant-force plate
spring".
The armature assembly of clutches and brakes consists of two Constant-force plate spring
moving parts an armature and an armature hub. A positive
connection between these two parts (armature and armature
hub) requires transmitting torque and moving the armature in an Force
axial direction.
The "constant-force plate spring" is capable of transmitting
torque and releasing the armature by single piece, which offers Dia.
good performance compared with other methods.
The thin spring is excellent for torque transmission. It is very
strong when loaded in the tangential direction. There is
structurally no backlash. Stable suction and release can be
performed by waving the plate spring to reduce variation of Function of the plate spring Torque to the plate spring
load.

Electromagnetic clutches and brakes

● Clutch ● Brake

Rotor Armature Brake stator

Brake armature

Clutch stator
Constant-force Coil
plate spring Constant-force
Coil plate spring
C-shaped retaining
ring groove Armature hub
Keyway
Lining Air space
Air space Keyway
Lining
C-shaped retaining
Lead wire
ring groove
Lead wire

The clutch consists of three basic elements, the armature assembly, The brake consists of two basic elements, the armature assembly of the
rotor of the rotating part, and stator of the static part. rotating part and the stator of the static part.
The armature assembly is essentially formed of the armature and the The armature of the armature assembly is pulled and attached to the
constant-force plate spring. Only the armature is pulled and attached to stator by energization of a coil, and the damping torque is transferred to
the rotor by energization of a coil, and the torque is transferred from the the rotating body through the plate spring.
driving side to the driven side through the plate spring.

Constant-force Constant-force
plate spring Armature Air gap plate spring Armature Air gap
(Enlarged) Magnetic circuit (Enlarged) (Enlarged) Magnetic circuit (Enlarged)

When applying When released When applying

current/connecting current/braking When released

Operation of clutch Operation of brake

7
01_マイクロ_E_p006_023.qxd 11.11.10 9:37 AM ページ8

Electromagnetic micro clutches and brakes

■ 102 model (electromagnetic micro
clutches)
■ CYT model (customizable
electromagnetic micro clutches)
■ 112 model (electromagnetic micro
brakes)

Clutch and brake torque［N・m］

0 1 2 3
102 Model

CYT Model

112 Model

■ Selection
Select the appropriate shape and size in accordance with the use z Intended use (Requirement functions for
Electromagnetic micro clutches and brakes

condition and the intended use. The friction type clutches and clutches brakes)
brakes are useful since the performance is instantaneously Coupling・Uncoupling, Braking・Holding, Speed change,
exerted. If the clutch and brake is not properly selected the Forward reverse operation, High-frequency operation,
clutch or brake my have performance problems. Fully grasp Positioning・Dividing, Inching, etc.
the following matters when selecting. x Required performance
Torque, Response, Frequency of use, Operating life, Accuracy,
Work volume, etc.

c Load characteristic
Load torque, Load moment of inertia J, Load change, Rotation
speed to be applied, etc.

v Driving side condition

Motor (three phase, single phase, alternating
current, etc.), Engine, Hydraulic・Pneumatic pressure, etc.

■ Model list ◎…Excellence ●…Adjustment ○…Suitable depending on applications △…Customizing

Electromagnetic micro clutches and brakes
Class Micro clutches Micro brakes
Model 102 CYT 112
Type 13 15 11 33 35 31 33M 33B 13 12 11

Appearance

Descriptive page P10∼15 P16∼19 P20∼23

Rotational transmission ● ● ● ● ● ● ● ●
Braking・Holding ● ● ●
Adaptability

Wall mounting ● ● ● ● ● ●
Shaft mounting ● ● ● ● ●
High-velocity revol. (1000min-1 ∼) ● ● ● ● ● ●
Parallel axis input/output ● ● ● ● ● ● ● ● ○
●
Shaft-to-shaft input/output ● ● ○ ●
Characteristic

Compact design ◎ ● ● ◎ ● ● ◎ ◎ ◎ ◎ ●
Easy to mount and use ● ● ○ ● ◎ ○ ● ● ● ○ ●
One-touch mounting △ △
Environmental responsiveness ● ● ● ● ● ● ● ● ● ● ●

8
01_マイクロ_E_p006_023.qxd 11.11.10 9:37 AM ページ9

■ Type・Model Selection 102 model (micro clutches)

● Selection of clutches There are two types of stators; the flange mounted type that
There are two types of stators and three types of armature allows effective space use and the bearing mounted type that
assemblies with different mounting methods, and six combinations of allows easy setting on a shaft. By combining with three types of
those. Select the appropriate type for the configuration of the armature assemblies with different mounting forms (direct
mounting part. mounting), six types can be selected according to the mounting
z Select the place to mount (Selection of conditions.
stators)
q Mount directly on the wall surface
A flange mounted type stator is used. This type is shorter to the
axial direction. Mounting space can be saved.
w Mount on a shaft and apply a piece or a pin to stabilize.
A bearing mounted type stator is used. This type is relatively
easy to mount. The trouble from processing the mounting
portion can be saved.

(1) Mount directly on the wall surface (2) Mount on a shaft

x Select the shaft configuration to mount

(Selection of armature assemblies) CYT model (customizable micro clutches)

Electromagnetic micro clutches and brakes

There are two types of connections between the driving side and the
The stator is a bearing mounted type that allows easy setting on a
driven side.
shaft. The dry-metal type or the ball-bearing type can be
q Couple a mating shaft selected depending on the shaft rotation speed.
Use an armature assembly for the mating shaft. Positioning such as Various custom types such as assembling a pulley and gear in the
centering may become complicated. A coupling flange or a flexible armature type-3 or combing a shaft with it are available.
coupling may be required.
w Wrapping and gear connection of a parallel shaft
Use an armature assembly for through shaft. This method
allows for rational mounting, and is relatively easy.

(1) Directly connect (2) Wrap the parallel shaft.

the mating shaft.

● Selection of brakes
Since a brake is used to brake and maintain the rotating body, 112 model (micro brakes)
the stator part must be properly fixed on the static part. This model is a compact and high-performance brake with the
There are three ways to mount an armature assembly on the same basic design with the micro clutches.
rotating body. Select the appropriate method in accordance with the The optimum condition can be selected from the three types of
configuration of the mounting part. armature assemblies with different mounting forms.
q Mount on the braking shaft
The point for selecting the mounting method from three types is
that determining how to fix on the shaft effectively.
w Mount directly on the rotating body
Since the inertial body that is not fixed on the shaft will not stop
when stopping the shaft, use an armature assembly that can be
directly mounted on the inertial body.

(1) Mount directly on a shaft (2) Mount on a rotating body

9
01_マイクロ_E_p006_023.qxd 11.11.10 9:37 AM ページ10

102 model Electromagnetic

micro clutches
Electromagnetic
clutches and
Clutch
and brake
Spring-
applied Electromagnetic
tooth clutches
Brake motors
Power supplies
for clutches &
and brakes brakes units brakes brakes
Electromagnetic micro clutches

Ideal for use in small precision equipment such as business machines,

communications equipment or automobile machinery that has a
susceptibility to fluctuations of torque and responsiveness. Many
different types are available in order to install in any place. Compact and
lightweight, and easy to mount and use.

■Various types
There are two types of stators; the flange mounted type that allows
effective space use and the bearing mounted type that allows easy
setting on a shaft. By combining with three type of armature
assemblies with different mounting forms (direct mounting/shaft
mounting type), six types can be selected according to the mounting
terms.
■Adapted to the RoHS
Adapted to the Restriction of Hazardous Substances that bans the use of
6 substances such as mercury or lead can be selected as option.

Clutch torque ［N・m］ 0.4 ∼ 2.4

Operational temperature［℃］ −10 ∼ ＋40
Backlash Zero
Electromagnetic micro clutches and brakes

■ 6types
● Stator・Rotor form
The flange mounted type is installed by combining a stator and rotor
together. It allows effective wall space use. The bearing mounted
type has integral structure of stator and rotor, and also has built-in
oil retaining metal bearing. It allows easy setting at the optional
position on a shaft.
Flange mounted type Bearing mounted type

■ With the armature type-3

¡Mainly used for through shaft.
¡Ideal for wrapping and gear drive.
¡The armature type-3 is the type of "direct mounting". Easy to
install to a sprocket or a spur gear.
¡The 102-□-13 uses a wall surface to mount.
¡The 102-□-33 is mounted on a shaft. Armature type-3 102-□-13 102-□-33

■ With the armature type-5

¡Mainly used for through shaft.
¡The armature type-5 is the type of "bearing mounting". Easy to
install to a sprocket or a spur gear.
¡The 102-□-15 uses a wall surface to mount.
¡The 102-□-35 is mounted on a shaft.
Armature type-5 102-□-15 102-□-35

■ With the armature type-1

¡Mainly used for through shaft.
¡The armature type-1 is the type of "shaft mounting".
¡The 102-□-11 uses a wall surface to mount.
¡The 102-□-31 is mounted on a shaft.
Armature type-1 102-□-11 102-□-31

10
01_マイクロ_E_p006_023.qxd 11.11.10 9:37 AM ページ11

■ Outline Structure
Stator Rotor
The micro clutch 102 model consists of the following three parts; the
stator with built-in coil, rotor with lining material, and armature Armature

assembly. Each part is mutually combined in the correct physical Plate spring
relationship, and forms a magnetic circuit.

● Stator and Rotor

¡Flange mounted type
The stator is directly fixed on the static part such as flange, by Key
a mounting flange. The rotor is fixed against the rotating shaft by
a key. The stator and rotor are combined through a narrow air Air gap [a]
gap which becomes a part of the magnetic circuit, and forms Air space Bearing

magnetic poles. Structure of the flange mounted type

¡Bearing mounted type
The stator is integrated with the rotor through the bearing,
and is maintained in the static part of the machine by an Antirotation arm Stator
Rotor
antirotation arm. The rotor is fixed on the rotating shaft by a Armature
setscrew. The stator and rotor form a magnetic pole through the Plate spring
bearing (iron oil-bearing metal).
Setscrew

● Armature assembly
The armature assembly is composed of armature, plate spring
and armature hub. It is combined properly with keeping a certain

Electromagnetic micro clutches and brakes

amount of air gap [a] facing the rotor. The though-shaft armature
assembly is fixed on the shaft by a bearing. The shaft-to-shaft Bearing
Air gap [a]
type armature assembly is fixed on the opposed shaft by a key and
Structure of the bearing mounted type
set screw.

■ Stator・Rotor mounting
● Flange mounted type
¡Centering
For the mounting shaft of the stator and rotor, centering is Retaining ring
H Air gap [a]
performed by "positioning fits" using the stator inside
diameter or the flange outside diameter. Since the inside
diameter is designed to fit into the nominal dimension for the
Bearing Rotor
outside diameter of the ball bearing, correct centering can be
performed by directly using the bearing that supports the
shaft.
¡Setting of axial positional relationship (H measurement)
For the positional relationship between the stator and rotor,
set the H measurement in order that it becomes its specified Stator/Rotor mounting (flange mounted type)
value. If centering is performed by using a ball bearing, use a
retaining ring and strike the rotor edge to determine the H
measurement.

● Bearing mounted type Antirotation arm

¡Centering is not necessary. Antirotation arm
Stator
¡Fix on the shaft
The stator and rotor can be easily fixed on the shaft by a
fixing collar and a setscrew. Fixing collar
¡Maintain the stator
The force acting on the stator is a minimal amount of torque
caused by the supporting bearing friction. To prevent free Setscrew Bearing
rotation of the stator, and to protect a lead wire, maintain an
antirotation arm in the static part of the machine. An Stator/Rotor mounting (bearing mounted type)
antirotation arm must be retained in the suitable form for not
turning into the shaft direction.

11
01_マイクロ_E_p006_023.qxd 11.11.10 9:37 AM ページ12

102-□-1□ type Electromagnetic

micro clutches
Electromagnetic
clutches and
Clutch
and brake
Spring-
applied Electromagnetic
tooth clutches
Brake motors
Power supplies
for clutches &
and brakes brakes units brakes brakes
Electromagnetic micro clutches
/Flange mounted type

■ Specifications
Dynamic Coil（at 20℃） Heat- Maximum Rotating part moment of inertia J Allowable Total amount of Armature Torque Torque
friction rotation engaging energy before air pull in build-up decaying Mass
Model Size torque  Td Voltage Wattage Amperage Resistance resistance speed Armature Rotor energy gap readjustment time time time ［kg］
［N・m］［V］［W］［A］［Ω］ class ［min−1］［kg・m ］［kg・m ］ EeaR［J］ E［
2 2
T J］ t［s］ a t［
p s］ t［d s］

102-02-13 10000 6.75×10−7 0.075

102-02-15 02 0.4 DC24 6 0.25 96 B 500 1.00×10−6 2.45×10−6 1500 2×106 0.009 0.019 0.017 0.081
102-02-11 10000 1.00×10−6 0.079
102-03-13 10000 1.30×10−6 0.096
102-03-15 03 0.6 DC24 6 0.25 96 B 500 1.95×10−6 3.25×10−6 2300 3×106 0.009 0.022 0.020 0.105
102-03-11 10000 1.95×10−6 0.103
102-04-13 10000 4.38×10−6 0.178
102-04-15 04 1.2 DC24 8 0.33 72 B 500 6.15×10−6 1.41×10−5 4500 6×106 0.011 0.028 0.030 0.195
102-04-11 10000 6.15×10−6 0.191
102-05-13 10000 9.08×10−6 0.310
102-05-15 05 2.4 DC24 10 0.42 58 B 500 1.38×10−5 3.15×10−5 9000 9×106 0.012 0.031 0.040 0.335
102-05-11 10000 1.38×10−5 0.325
*Dynamic friction torque (Td) indicates the value when relative velocity is (100min-1).
*Rotating part moment of inertia and mass indicate the values of maximum bore diameter.
*Power supply voltage variation must be within ±10% of the coil voltage.
Electromagnetic micro clutches and brakes

■ Dimensions 102-□-13 (For direct mounting)

Unit［mm］
Shaft bore dimensions
H φC1 h9
Size New JIS standards Previous edition of JIS
□S
4-φ3.4

K M a±0.05
d H7 correspondence standards correspondence
b Z b P9 t b E9 t
φV2
φV1

02 5 ー ー
03 6 2 −0.006
−0.031 0.8 ＋0.3
 0
P.C.D. C2

8 2 −0.006 0.8 ＋0.3

P.C.D. A3±0.05

−0.031  0
φdH7

04
φC4 H8

3 −0.006 1.2 ＋0.3 4 ＋0.050 1.5 ＋0.5

φC3

10
φC5

φA4

φA2
φA1

J −0.031  0 ＋0.020  0
t

10 3 −0.006
−0.031 1.2 ＋0.3
 0 4 ＋0.050
＋0.020 1.5 ＋0.5
 0
05
15 5 −0.012
−0.042 2 ＋0.5
 0 5 ＋0.050
＋0.020 2 ＋0.5
 0
φV3
400

X
45°
P 4-90°
L

Unit［mm］
Radial dimensions Axial direction dimensions CAD
Size
A1 A2 A3 A4 C1 C2 C3 C4 C5 S V1 V2 V3 Z H J K L P M a X File No.
02 31 28 19.5 10.5 39 33.5 11.4 11 8 ー 2-2.1 2-5.3 2-4 4-90° 18 16.5 1.5 20.5 5 1.1 0.1 0.8 102-131
03 34 32 23 12.5 45 38 13.6 13 10 33 3-2.6 3-6 3-4.5 6-60° 22.2 20.2 2 24.5 6.7 1.3 0.15 1.2 102-132
04 43 40 30 18.5 54 47 20 19 15.5 41 3-3.1 3-6 3-5 6-60° 25.4 23.4 2 28.2 7 1.3 0.15 1.5 102-133
05 54 50 38 25.5 65 58 27.2 26 22 51 3-3.1 3-6.5 3-5.5 6-60° 28.1 26.1 2 31.3 8.2 1.5 0.2 1.5 102-134
*The size 02 has a round flange.
*There is no keyway on the rotor of the size 02. Fix on the shaft by press fitting.

■ Ordering information
102- 03 -13 24V 6 DIN
Size Keyway standard New JIS standards correspondence：DIN
Rotor bore diameter (Dimensional sign d) Previous edition of JIS standards correspondence：JIS
*Unnecessary to enter the keyway standard if there is no description (–) in the shaft-bore dimensions table. Specification displayed as diagonal line is not available as a standard product.

12
01_マイクロ_E_p006_023.qxd 11.11.10 9:37 AM ページ13

■ Dimensions 102-□-15 (For through shaft) Unit［mm］

H φC1 h9
Shaft bore dimensions
New JIS standards Previous edition of JIS
Size d1 d2 correspondence
a±0.05 standards correspondence
4-φ3.4
K M □S
H7 H7
b P9 t b E9 t
02 5 5 ー ー

φd2H7
b
03 6 6 2 −0.006
−0.031 0.8 ＋0.3
 0
φd1 H7
P.C.D. C2

2 −0.006 0.8 ＋0.3

t

8 8 −0.031  0

φA3 h7
04
φC4 H8
φC3

φC5

φA2
φA1
J 10 10 3 −0.006
−0.031 1.2 ＋0.3
 0 4 ＋0.050
＋0.020 1.5 ＋0.5
 0

Rotor 10 10 3 −0.006
−0.031 1.2 ＋0.3
 0 4 ＋0.050
＋0.020 1.5 ＋0.5
 0
05 −0.012 ＋0.5 ＋0.050 ＋0.5
keyway 15 15 5 −0.042 2  0 5 ＋0.020 2  0
400

※The d2 of the 5-type armature is a straight bore.

45°
P
L2 N1 4-90°
L1
Unit［mm］
Radial dimensions Axial direction dimensions CAD
Size
A1 A2 A3 C1 C2 C3 C4 C5 S H J K L1 L2 M P N1 a File No.
02 31 28 13 39 33.5 11.4 11 8 ー 18 16.5 1.5 27.5 22.4 1.1 5 4.8 0.1 102-151
03 34 32 14 45 38 13.6 13 10 33 22.2 20.2 2 34.5 26.5 1.3 6.7 7.8 0.15 102-152
04 43 40 18 54 47 20 19 15.5 41 25.4 23.4 2 40.2 30.8 1.3 7 9.1 0.15 102-153
05 54 50 28 65 58 27.2 26 22 51 28.1 26.1 2 43.3 34.3 1.5 8.2 8.8 0.2 102-154
*The size 02 has a round flange.
*There is no keyway on the rotor of the size 02. Fix to the shaft by press fitting.

■ Ordering information

Electromagnetic micro clutches and brakes

03 -15 24V R 6  
102-  DIN A 6
Size Armature bore diameter（Dimensional sign d2）
Rotor bore diameter (Dimensional sign d) Keyway standard New JIS standards correspondence: DIN
Previous edition of JIS standards correspondence: JIS
*It is not necessary to enter the keyway standard if there is no description (–) in the shaft-bore dimensions table.

■ Dimensions 102-□-11 (For shaft-to-shaft) Unit［mm］

Shaft bore dimensions
H φC1 h9
New JIS standards Previous edition of JIS
Size d1 d2 correspondence
a±0.05 □S standards correspondence
4-φ3.4

b H7 H7
K M U b P9 t b E9 t
02 5 5 ー ー
2 −0.006 0.8 ＋0.3
φA3

03 6 6 −0.031  0
φd1 H7

φd2 H7
P.C.D. C2

2 −0.006 0.8 ＋0.3

t

8 8 −0.031  0
04
φC4 H8
φC3

φC5

10 10 3 −0.006 1.2 ＋0.3 4 ＋0.050 1.5 ＋0.5

φA2
φA1

J −0.031  0 ＋0.020  0

10 10 3 −0.006
−0.031 1.2 ＋0.3
 0 4 ＋0.050
＋0.020 1.5 ＋0.5
 0
05
15 15 5 −0.012
−0.042 2 ＋0.5
 0 5 ＋0.050
＋0.020 2 ＋0.5
 0
400

45°
P T
4-90°
L2
L1 m
｡
（120 arrangement）
Unit［mm］
Radial dimensions Axial direction dimensions CAD
Size
A1 A2 A3 C1 C2 C3 C4 C5 S m H J K L1 L2 M P U T a File No.
02 31 28 9.5 39 33.5 11.4 11 8 ー M3 18 16.5 1.5 27.5 22.5 1.1 5 7 2.5 0.1 102-111
03 34 32 12 45 38 13.6 13 10 33 2-M3 22.2 20.2 2 34.5 26.5 1.3 6.7 10 4 0.15 102-112
04 43 40 17 54 47 20 19 15.5 41 2-M3 25.4 23.4 2 40.2 30.8 1.3 7 12 5 0.15 102-113
05 54 50 24 65 58 27.2 26 22 51 2-M4 28.1 26.1 2 43.3 34.3 1.5 8.2 12 5 0.2 102-114
*The size 02 has a round flange.
*There is no keyway on the rotor of the size 02. Fix on the shaft by press fitting.

■ Ordering information
102- 
03 -11 24V R 
6 DIN A 6 DIN Keyway standard
Size New JIS standards correspondence : DIN
Previous edition of JIS standards correspondence : JIS
Rotor bore diameter (Dimensional sign d1)
Armature bore diameter（Dimensional sign d2）
*Unnecessary to enter the keyway standard if there is no
description (–) in the shaft-bore dimensions table. Specification Keyway standard New JIS standards correspondence: DIN
displayed as diagonal line is not available as a standard product. Previous edition of JIS standards correspondence: JIS

13
01_マイクロ_E_p006_023.qxd 11.11.10 9:37 AM ページ14

102-□-3□ type Electromagnetic

micro clutches
Electromagnetic
clutches and
Clutch
and brake
Spring-
applied Electromagnetic
tooth clutches
Brake motors
Power supplies
for clutches &
and brakes brakes units brakes brakes
Electromagnetic micro clutches
/Bearing mounted type

■ Specifications
Dynamic Coil（at 20℃） Heat- Maximum Rotating part moment of inertia J Allowable Total amount of Armature Torque Torque
friction Voltage Wattage Amperage Resistance resistance rotation engaging energy before air pull in build-up decaying Mass
Model Size torque  Td speed Armature Rotor energy gap readjustment time time time ［kg］
2 2
［N・m］［V］［W］［A］［Ω］ class ［min ］［kg・m ］［kg・m ］ EeaR［J］ E［
−1
T J］ t［s］ a t［
p s］ t［d s］

102-02-33 6.75×10−7 0.076

102-02-35 02 0.4 DC24 6 0.25 96 B 500 1.00×10−6 2.75×10−6 1500 2×106 0.009 0.019 0.017 0.082
102-02-31 1.00×10−6 0.080
102-03-33 1.30×10−6 0.101
102-03-35 03 0.6 DC24 6 0.25 96 B 500 1.95×10−6 4.08×10−6 2300 3×106 0.009 0.022 0.020 0.110
102-03-31 1.95×10−6 0.108
102-04-33 4.38×10−6 0.183
102-04-35 04 1.2 DC24 8 0.33 72 B 500 6.15×10−6 1.44×10−5 4500 6×106 0.011 0.028 0.030 0.200
102-04-31 6.15×10−6 0.196
102-05-33 9.08×10−6 0.321
102-05-35 05 2.4 DC24 10 0.42 58 B 500 1.38×10−5 2.90×10−5 9000 9×106 0.012 0.031 0.040 0.346
102-05-31 1.38×10−5 0.336
*Dynamic friction torque (Td) indicates the value when relative velocity is (100min-1).
*Rotating part moment of inertia and mass indicate the values of maximum bore diameter.
*Power supply voltage variation must be within ±10% of the coil voltage.
Electromagnetic micro clutches and brakes

■ Dimensions 102-□-33 (For direct mounting)

Unit［mm］
L2 Shaft bore dimensions
Y2 Size
H d H7
02 5
P.C.D. A3±0.05

m R a±0.05 Y1
（120°arrangement） 03 6
T Z
φV2

8
φV1

04
φd H7

10
G2
G1

10
05
φA2
φA1
φA4

15
φF

φV3
400

P
L1

Unit［mm］
Radial dimensions Axial direction dimensions CAD
Size
A1 A2 A3 A4 F V1 V2 V3 G1 G2 Y1 Y2 Z m H R L1 L2 P N T a File No.
02 31 28 19.5 10.5 14 2-2.1 2-5.3 2-4 16.8 20 3.1 8 4-90° 2-M3 19.5 1.6 25.9 23.5 5 0.8 2.5 0.1 102-331
03 34 32 23 12.5 16 3-2.6 3-6 3-4.5 20 23 3.1 8 6-60° 2-M3 21.9 1.6 28.5 26.2 4.7 1.2 2.3 0.15 102-332
04 43 40 30 18.5 22 3-3.1 3-6 3-5 23 26 3.1 8 6-60° 2-M4 25.1 1.6 33.2 30.4 5 1.5 2.8 0.15 102-333
05 54 50 38 25.5 30 3-3.1 3-6.5 3-5.5 28 31 3.1 8 6-60° 2-M5 27.9 1.6 37.3 34.1 6 1.5 3.3 0.2 102-334

■ Ordering information
03 -33 24V 6
102- 
Size Rotor bore diameter (Dimensional sign d)

14
01_マイクロ_E_p006_023.qxd 11.11.10 9:37 AM ページ15

■ Dimensions 102-□-35 (For through shaft) Unit［mm］

H1
Shaft bore dimensions
Size d1 H7 d2 H7
H2
m R a±0.05 Y2 02 5 5
（120°arrangement） T Y1 03 6 6
8 8
04
10 10

φd2H7
φd1 H7

10 10
G2
G1

05
15 15

φA3h7
φA2
φA1
φF

400

P
L2 N
L1
Unit［mm］
Radial dimensions Axial direction dimensions CAD
Size
A1 A2 A3 F G1 G2 Y1 Y2 m H1 H2 R L1 L2 P N T a File No.
02 31 28 13 14 16.8 20 3.1 8 2-M3 23.5 19.5 1.6 33 27.9 5 4.8 2.5 0.1 102-351
03 34 32 14 16 20 23 3.1 8 2-M3 26.2 21.9 1.6 38.5 30.5 4.7 7.8 2.3 0.15 102-352
04 43 40 18 22 23 26 3.1 8 2-M4 30.4 25.1 1.6 45.2 35.8 5 9.1 2.8 0.15 102-353
05 54 50 28 30 28 31 3.1 8 2-M5 34.1 27.9 1.6 49.3 40.3 6 8.8 3.3 0.2 102-354

■ Ordering information

Electromagnetic micro clutches and brakes

03 -35 24V R 
102-  6 A6
Size Armature bore diameter（Dimensional sign d2）
Rotor bore diameter (Dimensional sign d1)

■ Dimensions 102-□-31 (For shaft-to-shaft) Unit［mm］

H1
Shaft bore dimensions
m1 Y2
H2 a±0.05 New JIS standards Previous edition of JIS
Size d1 d2 correspondence
（120｡arrangement） Y1 standards correspondence
R U H7 H7
T1 b b P9 t b E9 t
02 5 5 ー ー
03 6 6 2 −0.006 0.8 ＋0.3
φd1 H7

−0.031  0
G2

φd2 H7

8 8 2 −0.006 0.8 ＋0.3

G1

−0.031  0
04
10 10 3 −0.006 1.2 ＋0.3 4 ＋0.050 1.5 ＋0.5
φA3
φA2
φA1

−0.031  0 ＋0.020  0
φF

10 10 3 −0.006
−0.031 1.2 ＋0.3
 0 4 ＋0.050
＋0.020 1.5 ＋0.5
 0
05
15 15 5 −0.012
−0.042 2 ＋0.5
 0 5 ＋0.050
＋0.020 2 ＋0.5
 0
400

T2
m2
P ｡
（120 arrangement）
L2
L1
Unit［mm］
Radial dimensions Axial direction dimensions CAD
Size
A1 A2 A3 F G1 G2 Y1 Y2 m1 m2 H1 H2 R L1 L2 P U T1 T2 a File No.
02 31 28 9.5 14 16.8 20 3.1 8 2-M3 M3 23.5 19.5 1.6 33 27.9 5 7 2.5 2.5 0.1 102-311
03 34 32 12 16 20 23 3.1 8 2-M3 2-M3 26.2 21.9 1.6 38.5 30.5 4.7 10 2.3 4 0.15 102-312
04 43 40 17 22 23 26 3.1 8 2-M4 2-M3 30.4 25.1 1.6 45.2 35.8 5 12 2.8 5 0.15 102-313
05 54 50 24 30 28 31 3.1 8 2-M5 2-M4 34.1 27.9 1.6 49.3 40.3 6 12 3.3 5 0.2 102-314

■ Ordering information
102- 
03 -31 24V R 
6 A 6 DIN
Size Keyway standard New JIS standards correspondence: DIN
Previous edition of JIS standards correspondence: JIS
Rotor bore diameter (Dimensional sign d1) Armature bore diameter（Dimensional sign d2）
* It is not necessary to enter the keyway standard if there is no description (–) in the shaft-bore dimensions table.
Specification displayed as diagonal line is not available as a standard product.

15
01_マイクロ_E_p006_023.qxd 11.11.10 9:37 AM ページ16

CYT model Electromagnetic

micro clutches
Electromagnetic
clutches and
Clutch
and brake
Spring-
applied Electromagnetic
tooth clutches
Brake motors
Power supplies
for clutches &
and brakes brakes units brakes brakes
Electromagnetic micro clutches

Excellent for use in small precision equipment such as business

machines, communications equipment or automobile machinery.
The CYT provides excellent stability of torque and quick response.
Various custom types coupled with shafts are available.
The compact design along with high torque capacity is also easy to
mount and use.

■Various custom types

The stator is a bearing mounted type that allows easy setting on a
shaft. The dry-metal type or the ball-bearing type can be selected
depending on the shaft rotation speed.
Various custom types such as assembling a pulley and a gear in the
armature type-3 or combing a shaft are available.
■Adapted to the RoHS
Adapted to the Restriction of Hazardous Substances that bans the use of
6 substances such as mercury or lead can be selected as option.

Clutch torque ［N・m］ 0.4 ∼ 1.0

Operational temperature［℃］ −10 ∼ ＋40
Backlash Zero

■ Structure
Electromagnetic micro clutches and brakes

The micro clutch CYT model consists of the following three parts; the
stator with built-in coil, rotor with lining material, and armature
assembly. Each part is mutually combined in the correct physical
relationship, and forms a magnetic circuit.
The stator is a bearing mounted type that allows easy setting on a
shaft. The dry-metal type or the ball-bearing type can be selected
depending on the shaft rotation speed.
Bearing mounted type Bearing mounted type
（Dry metal type） （Ball bearing type）
● Stator and Rotor
¡Bearing mounted type (Dry metal type)
Stator
The stator is integrated with the rotor through the bearing, Antirotation arm
Rotor
and is maintained in the static part of the machine by an Armature
Plate spring
antirotation arm. The rotor is fixed on the rotating shaft by a
setscrew. The stator and rotor form a magnetic pole through the
bearing (dry metal).
¡Bearing mounted type (Ball bearing type)
The stator is fixed on the shaft through the bearing, and is
maintained in the static part of the machine by an antirotation
Bearing
arm. The stator and rotor are combined through a narrow air gap
（Dry metal）
which becomes a part of the magnetic circuit, and forms Air gap「a」
magnetic poles.
Structure of the bearing mounted type (Dry metal type)
● Armature assembly
¡The armature assembly is composed of armature and plate Automation arm Stator
Rotor
spring. It is combined properly with keeping a certain amount of air Armature
Plate spring
gap [a] facing the rotor, and is fixed on the through shaft by the
bearing.

Bearing
（Ball bearing）

Air gap「a」
Structure of the bearing mounted type (Ball bearing type)

16
01_マイクロ_E_p006_023.qxd 11.11.10 9:37 AM ページ17

■ Stator・Rotor mounting
● Bearing mounted type (Dry metal type) Antirotation arm
¡Centering is not necessary. Antirotation arm
¡Fix on the shaft
The stator can be easily fixed on the shaft by a setscrew. Stator
¡Maintain the stator
The force acting on the stator is a minimal amount of torque
caused by the supporting bearing friction. To prevent free
rotation of the stator, and to protect a lead wire, maintain an
Setscrew
antirotation arm in the static part of the machine. An
antirotation arm must be retained in the suitable form for not
turning into the shaft direction. Dry metal
Stator/Rotor mounting (Dry metal type)
● Bearing mounted type (Ball bearing type)
¡Centering is not necessary.
¡Fix on the shaft Antirotation arm
When mounting the stator, perform positioning for the shaft
Antirotation arm
direction by a retaining ring and a fixing collar. The rotor can be
easily fixed on the shaft by a setscrew or keyway. Stator
¡Maintain the stator
The force acting on the stator is a minimal amount of torque
caused by the supporting bearing friction. To prevent free

Electromagnetic micro clutches and brakes

rotation of the stator, and to protect a lead wire, maintain an
antirotation arm in the static part of the machine. An
antirotation arm must be retained in the suitable form for not Retaining ring
turning into the shaft direction.
Ball bearing

Stator/Rotor mounting (Ball bearing type)

■ Custom examples
Baffle Air gap [a]
Air gap [a] Timing pulley
Gear

Baffle

Bearing mounted type (Dry metal type) Mounting example Bearing mounted type (Dry metal type) Mounting example
Built-in timing pulley

Air gap [a] Baffle

Gear
Air gap [a]
Gear

Baffle

Bearing mounted type (Dry metal type) Mounting example Bearing mounted type (Ball bearing type) Mounting example
Built-in gear

17
01_マイクロ_E_p006_023.qxd 11.11.10 9:37 AM ページ18

CYT model Electromagnetic

micro clutches
Electromagnetic
clutches and
Clutch
and brake
Spring-
applied Electromagnetic
tooth clutches
Brake motors
Power supplies
for clutches &
and brakes brakes units brakes brakes
Electromagnetic micro clutches
/Bearing mounted type

■ Specifications
Dynamic Coil（at 20℃） Heat- Maximum Rotating part moment of inertia J Allowable Total amount of Armature Torque Torque
friction Voltage Wattage Amperage Resistance resistance rotation engaging energy before air pull in build-up decaying Mass
Model Size torque  Td speed Armature Rotor energy gap readjustment time time time ［kg］
［N・m］［V］［W］［A］［Ω］ class ［min−1］ ［kg・m2］［kg・m2］ EeaR［J］ E［ T J］ t［s］ a t［
p s］ t［d s］

CYT-025-33B 025 0.4 DC24 4.5 0.188 128 B 3600 1.00×10−6 1.43×10−6 800 1.0×106 0.014 0.028 0.030 0.07
CYT-03-33B 3600 1.85×10−6 0.13
03 0.5 DC24 5.5 0.23 105 B 1.30×10−6 900 1.5×10 6
0.015 0.030 0.040
CYT-03-33M 500 1.90×10−6 0.11
CYT-04-33B 3600 1.00×10−5 0.26
04 1.0 DC24 5.9 0.25 98 B 5.15×10−6 1900 2.0×106 0.030 0.040 0.040
CYT-04-33M 500 1.05×10−5 0.23
*Dynamic friction torque (Td) indicates the value when relative velocity is (100min-1).
*Rotating part moment of inertia and mass indicate the values of maximum bore diameter.
*Power supply voltage variation must be within ±10% of the coil voltage.

■ Dimensions CYT-□-33M
L1 （Lead wire position）
L2
45°
H a
8±0.2
Electromagnetic micro clutches and brakes

m R
（120°
arrangement） 3.1
T
3-φV1

3-φV2
φd+0.005
+0.06

G2

G1
φA3±0.05
φA2

φA1
φA4
φF
P

3-φV3

0°
200
+20
0
＊
N
The ＊ mark indicates the runout dimensions 6-6
＊

of the rivet head when mounting.

Unit［mm］
Radial dimensions Axial direction dimensions CAD
Size
d A1 A2 A3 A4 F V1 V2 V3 G1 G2 m H R L1 L2 P N T a File No.
6 ー
03 34 32 23 12.5 14 3-2.6 3-5.5 3-6 20 23 M3 21 1.2 28.6 26.2 13 3 2.3 0.2 ±0.05
8 ー
8 ー
04 45 42 30 18.5 18 3-3.1 3-6 3-6 25 27.5 M4 25.3 1.2 35.1 32.4 17.5 3.5 3 0.2 ＋0.05
−0.1
10 ー
*The dimensional sign N and V3 indicate the runout dimensions of the rivet head when mounting.

■ Ordering information

CYT- 
03 -33M 24V 6
Size Rotor bore diameter (Dimensional sign d)

18
01_マイクロ_E_p006_023.qxd 11.11.10 9:37 AM ページ19

■ Dimensions CYT-025-33B
21.9 （Lead wire position）
45°
19.3 0.2±0.1 8±0.2

1.2 3.1

3-φ2.6

φ12.5

+0.3
+0.030

0
2+0.005

0.8

21
18
φ6
10.5

φ23±0.05
+0.3
0 φ30
+0.03
φ6 0

Rotor bore, Keyway

5.5
φ4.5

0°
2.1 6-6
＋20
200  0 10 9.3

■ Ordering information

CYT-025-33B 24V 6

Electromagnetic micro clutches and brakes

■ Dimensions CYT-□-33B
H a 45° （Lead wire position）
8±0.2
R
3.1
3-φV1

3-φV2

b
φd2

+0.3

G2

G1
t0
φA3±0.05

φA2

φA1
φA4
φF

L3 L4
P

+0.06
φd1+0.005
3-φV3

＊ Rotor bore, Keyway

0°
6-6
+20
2000 N
＊

T
L2
L1 The ＊ mark indicates the runout dimensions of the rivet head when mounting.
Unit［mm］
Nominal Radial dimensions Axial direction dimensions Shaft bore dimensions CAD
Size
diameter A1 A2 A3 A4 F V1 V2 V3 G1 G2 H R L1 L2 L3 L4 P N T a d2 d1 b t File No.
6 34 32 23 12.5 15 3-2.6 3-5.5 3-6 20 23 21 1.2 22.2 19.8 10 11.3 13 3 1.5 0.2 ±0.05 6 6 2 ＋0.030
＋0.005 0.8 ＋0.3
 0 ー
03 ＋0.030
8 34 32 23 12.5 16 3-2.6 3-5.5 3-6 20 23 21 1.2 22.2 19.8 10 11.3 13 3 1.5 0.2 ±0.05 8 8 2 ＋0.005 0.8 ＋0.3
 0 ー
8 45 42 30 18.5 19 3-3.1 3-6 3-6 25 28 25.3 1.2 26.8 24.1 12 13 17.5 3.5 0.9 0.2 ＋0.05
−0.1 8 8 2 ＋0.030
＋0.005 0.8 ＋0.3
 0 ー
04
10 45 42 30 18.5 19 3-3.1 3-6 3-6 25 28 25.3 1.2 26.8 24.1 14 11 17.5 3.5 0.9 0.2 ＋0.05
−0.1 10 10 3 ＋0.025
 0 1.2 ＋0.3
 0 ー
*The dimensional sign N and V3 indicate the runout dimensions of the rivet head when mounting.

■ Ordering information

03 -33B 24V 6
CYT- 
Size Nominal diameter

19
01_マイクロ_E_p006_023.qxd 11.11.10 9:37 AM ページ20

112 model Electromagnetic

micro clutches
Electromagnetic
clutches and
Clutch
and brake
Spring-
applied Electromagnetic
tooth clutches
Brake motors
Power supplies
for clutches &
and brakes brakes units brakes brakes
Electromagnetic micro brakes

This model is a compact and high-performance brake with a similar basic

design to the micro clutches.
It is excellent in breaking performance, and also ideal for high-precision
positioning. Due to its design, it fits into many mounting positions of
small precision equipment. It is lightweight and easy to use.

■Three types
The optimum condition can be selected from the three types of
armature assemblies with different mounting forms.
■Adapted to the RoHS
Adapted to the Restriction of Hazardous Substances that bans the use of
6 substances such as mercury or lead can be selected as option.

Brake torque ［N・m］ 0.4 ∼ 2.4

Operational temperature［℃］ −10 ∼ ＋40
Backlash Zero

■ Flange mounted type stator ■ Three types

The stator is a flange mounted type that allows ■ With the armature type-3
easy setting on the wall. Use in combination ¡Wide range of application
Electromagnetic micro clutches and brakes

with three types of assemblies. ¡Direct mounting type that is directly mounted
on a pulley or spur gear.
¡Suitable for braking and holding various
types of rotating bodies. Armature type-3 112-□-13
¡112-□-13
■ With the armature type-2
¡Unique slim type
¡Shaft mounting type. The mounting portion
fits into the inside stator.
¡Shorter to the axial direction.
¡112-□-12 Armature type-2 112-□-12
■ With the armature type-1
¡Easy-to-use general type
¡Shaft mounting type that allows easy setting
on the braking shaft.
¡112-□-11
■ Structure Armature type-1 112-□-11
The micro brake consists of the stator with built-in coil and with
embedded lining material, and the armature assembly.
The stator is fixed on the firm and static portion such as
machine frame, by a mounting flange.
The armature assembly is composed of armature, ring plate Stator
Armature
spring and armature hub. It is combined properly with keeping a
Plate spring
certain amount of air gap [a] facing the stator, and is fixed on the Armature hub
braking shaft (rotating body).

Bearing
● Stator mounting
Retaining ring
Centering is performed by "positioning fits" using the stator
inside diameter or the flange outside diameter. (See the arrow on
the right figure) Since the inside diameter is designed to fit into the
nominal dimension for the outside diameter of the ball bearing,
correct centering can be performed by directly using the bearing Air gap [a]
that supports the armature assembly mounting shaft. In
addition, there is a retaining-ring groove on the inside stator that the
shaft-directional fixation of the bearing outer ring can be
simultaneously performed.

20
01_マイクロ_E_p006_023.qxd 11.11.10 9:37 AM ページ21

■ Mounting Example
● Combination of the 112-□-13 and V ● Using the 112-□-12 at the shaft end
pulley
Armature type-3 Collar

Sprocket
V pulley

Shim
Air gap [a]
Air gap [a]

Use the armature type-3 by directly mounting on the transmission Since the necessary mounting space of the armature type-2 is
device such as V-belt pulley, or the rotating body to break the smallest, the overhung load is no problem if mounting a
inertial force. sprocket on the brake end.
Shaft processing of the brake part is not necessary. Also, the shaft The air gap [a] can be easily set by a collar and shim. The
diameter can be optionally determined. corrections can also be performed simply by adding or reducing the
The air gap [a] can be easily set by a collar and shim. The number of shims.
corrections can also be performed simply by adding or reducing the
number of shims.

Electromagnetic micro clutches and brakes

● Using the 112-□-11 at the shaft end ● Using the 112-□-11 for the vertical
shaft
Armature type-1 Setscrew

Air gap [a]

Armature type-1

Setscrew

Air gap [a]

This model can be mounted on the shaft end of the existing Since there is no limit for the mounting direction, idling torque or
machine with the simplest way. abnormal friction will not occur when mounting on the vertical
The air gap [a] can be easily set by moving the armature type-1 shaft.
and fixing with a setscrew. The air gap [a] can be easily set by moving the armature type-1
and fixing with a setscrew.

21
01_マイクロ_E_p006_023.qxd 11.11.10 9:37 AM ページ22

112 model Electromagnetic

micro clutches
Electromagnetic
clutches and
Clutch
and brake
Spring-
applied Electromagnetic
tooth clutches
Brake motors
Power supplies
for clutches &
and brakes brakes units brakes brakes
Electromagnetic micro brakes
/Flange mounted type

■ Specifications
Dynamic Coil（at 20℃） Heat- Maximum Armature Allowable Total amount of Armature Torque Torque
friction rotation moment engaging energy before air pull in build-up decaying Mass
Model Size torque  Td Voltage Wattage Amperage Resistance resistance speed of inertia2 J energy gap readjustment time time time ［kg］
［N・m］［V］ ［W］ ［A］ ［Ω］ class ［min−1］ ［kg・m ］ EeaR［J］ E［ T J］ t［s］
a t［
p s］ t［d s］

112-02-13 6.75×10−7 0.053

112-02-12 02 0.4 DC24 6 0.25 96 B 10000 1.00×10−6 1500 2×106 0.004 0.010 0.010 0.057
112-02-11 1.00×10−6 0.057
112-03-13 1.30×10−6 0.072
112-03-12 03 0.6 DC24 6 0.25 96 B 10000 1.95×10−6 2300 3×106 0.005 0.012 0.008 0.079
112-03-11 1.95×10−6 0.079
112-04-13 4.38×10−6 0.118
112-04-12 04 1.2 DC24 8 0.33 72 B 10000 6.15×10−6 4500 6×106 0.007 0.016 0.010 0.131
112-04-11 6.15×10−6 0.131
112-05-13 9.08×10−6 0.200
112-05-12 05 2.4 DC24 10 0.42 58 B 10000 1.38×10−5 9000 9×106 0.010 0.023 0.012 0.215
112-05-11 1.38×10−5 0.215
*Dynamic friction torque (Td) indicates the value when relative velocity is (100minー1).
*Rotating part moment of inertia and mass indicate the values of maximum bore diameter.
*Power supply voltage variation must be within ±10% of the coil voltage.
Electromagnetic micro clutches and brakes

■ Dimensions 112-□-13

H φC1h9
a±0.05 □S
4-φ3.4

K
Z
φV1
φV2
P.C.D. C2

P.C.D. A2±0.05

J1
φC4 H8

φA3
φC3

φA1

J2
φV3
400

45°
P
X 4-90°
L

Unit［mm］
Radial dimensions Axial direction dimensions CAD
Size
A1 A2 A3 C1 C2 C3 C4 S V1 V2 V3 Z H K J1 J2 L P X a File No.
02 28 19.5 10.5 39 33.5 11.4 11 ー 2-2.1 2-5.3 2-4 4-90° 13.7 1.5 2.6 1.3 16.1 5 0.8 0.1 112-131
03 32 23 12.5 45 38 13.6 13 33 3-2.6 3-6 3-4.5 6-60° 17 2 3.3 1.3 19.3 6.7 1.2 0.15 112-132
04 40 30 18.5 54 47 20 19 41 3-3.1 3-6 3-5 6-60° 20 2 3.3 1.3 22.8 7 1.6 0.15 112-133
05 50 38 25.5 65 58 27.2 26 51 3-3.1 3-6.5 3-5.5 6-60° 22 2 3.5 1.5 25.2 8 1.6 0.2 112-134
*The size 02 has a round flange.

■ Ordering information
112- 
03 -13 24V
Size

22
01_マイクロ_E_p006_023.qxd 11.11.10 9:37 AM ページ23

■ Dimensions 112-□-12 Unit［mm］

Shaft bore dimensions
H φC1 h9
New JIS standards Previous edition of JIS
4-φ3.4
□S Size
K a±0.05 d H7 correspondence standards correspondence
b b P9 t b E9 t
02 5 ー ー
03 6 2 −0.006
−0.031 0.8 ＋0.3
 0
P.C.D. C2

φd H7
8 2 −0.006
−0.031 0.8 ＋0.3
 0
J1 04
φC4 H8
φC3

φA1
10 3 −0.006
−0.031 1.2 ＋0.3
 0 4 ＋0.050
＋0.020 1.5 ＋0.5
 0
J2

t
10 3 −0.006
−0.031 1.2 ＋0.3
 0 4 ＋0.050
＋0.020 1.5 ＋0.5
 0
05
15 5 −0.012
−0.042 2 ＋0.5
 0 5 ＋0.050
＋0.020 2 ＋0.5
 0
400

U 45°
P
4-90°
L
Unit［mm］
Radial dimensions Axial direction dimensions CAD
Size
A1 C1 C2 C3 C4 S H K J1 J2 L P U a File No.
02 28 39 33.5 11.4 11 ー 13.7 1.5 2.6 1.3 18.1 5 7 0.1 112-121
03 32 45 38 13.6 13 33 17 2 3.3 1.3 21.3 6.7 10 0.15 112-122
04 40 54 47 20 19 41 20 2 3.3 1.3 25.5 7 12 0.15 112-123
05 50 65 58 27.2 26 51 22 2 3.5 1.5 28.2 8 12 0.2 112-124
*The size 02 has a round flange.
*There is no keyway on the rotor of the size 02. Fix on the shaft by press fitting.

■ Ordering information

Electromagnetic micro clutches and brakes

03 -12 24V 6 DIN
112- 
Size Keyway standard New JIS standards correspondence : DIN
Previous edition of JIS standards correspondence : JIS
Armature bore diameter (Dimensional sign d)
*It is not necessary to enter the keyway standard if there is no description (–) in the shaft-bore dimensions table.
Specification displayed as diagonal line is not available as a standard product.

■ Dimensions 112-□-11 Unit［mm］

φC1 h9 Shaft bore dimensions

H a±0.05
4-φ3.4

□S New JIS standards Previous edition of JIS

K U Size
b d H7 correspondence standards correspondence
b P9 t b E9 t
02 5 ー ー
P.C.D. C2

03 6 2 −0.006 0.8 ＋0.3

φd H7

−0.031  0
J1
φC4H8

8 2 −0.006 0.8 ＋0.3

φC3

φA2
φA1

−0.031  0
J2 04
t

10 3 −0.006
−0.031 1.2 ＋0.3
 0 4 ＋0.050
＋0.020 1.5 ＋0.5
 0

10 3 −0.006
−0.031 1.2 ＋0.3
 0 4 ＋0.050
＋0.020 1.5 ＋0.5
 0
05
15 5 −0.012
−0.042 2 ＋0.5
 0 5 ＋0.050
＋0.020 2 ＋0.5
 0
400

T 45°
P
m 4-90°
L2 ｡
（120 arrangement）
L1
Unit［mm］
Radial dimensions Axial direction dimensions CAD
Size
A1 A2 C1 C2 C3 C4 S m H K J1 J2 L1 L2 P U T a File No.
02 28 9.5 39 33.5 11.4 11 ー M3 13.7 1.5 2.6 1.3 23.1 18.1 5 7 2.5 0.1 112-111
03 32 12 45 38 13.6 13 33 2-M3 17 2 3.3 1.3 29.3 21.3 6.7 10 4 0.15 112-112
04 40 17 54 47 20 19 41 2-M3 20 2 3.3 1.3 34.8 25.5 7 12 5 0.15 112-113
05 50 24 65 58 27.2 26 51 2-M4 22 2 3.5 1.5 37.2 28.2 8 12 5 0.2 112-114
*The size 02 has a round flange.

■ Ordering information
03 -11 24V 6 DIN
112- 
Size Keyway standard New JIS standards correspondence: DIN
Previous edition of JIS standards correspondence: JIS
Armature bore diameter (Dimensional sign d)
*It is not necessary to enter the keyway standard if there is no description (–) in the shaft-bore dimensions table.
Specification displayed as diagonal line is not available as a standard product.

23
03_特性_E_p076_097.qxd 11.11.10 11:02 AM ページ76

■ Torque characteristics
● Static friction torque and dynamic 3

friction torque

Dynamic friction torque T d [N・m]

2 Size 05
Clutches and brakes transmit torque by sliding with a certain
relative velocity in the process of coupling and braking. The 1 Size 04

relative velocity gradually becomes smaller, and they are

Size 03
completely connected. The transmittable torque when coupling 0.5

and braking are completed is called "dynamic friction torque" of the Size 02

relative velocity. The static friction torque becomes about the 0.2
same value and the dynamic friction torque changes measurably
with the relative velocity. 0.1
0 1 2 3 4 5 6 7 8
3
X10
Relative sliding velocity [min −1 ]
● Dynamic friction torque
Dynamic friction torque characteristic Micro size 102・112 model
characteristics
The relationship between relative sliding velocity and dynamic

Dynamic friction torque T d [N・m]

3

friction torque is indicated in the right diagram. As indicated in the 2

diagram, the difference between the static friction torque and the
dynamic friction torque is small, which indicates that the effect in 1
Size 04
actual use becomes small. The value shown in the specification is
when the sliding velocity is 100min . -1
Electromagnetic clutches and brakes

0.5
Size 03
Size 025
● Initial torque characteristics 0.2
For the friction type clutches and brakes, the friction surface does not
sufficiently conform when initially used. It may not reach the rated 0.1
0 1 2 3 4 5 6 7 8
torque, which is called initial torque condition. The value of initial X10
3

Relative sliding velocity [min−1 ]

torque is 60 to 70% of the indicated torque, however, it will reach the
Dynamic friction torque characteristic Micro size CYT model
normal value by a short test operation. Please confirm if the
indicated torque is needed from the beginning of use. It may take 500

longer time for a test operation for use by light load or low
Size 25
200
revolution speed.
Dynamic friction torque T d [N・m]

The duration time of the residual torque (remaining torque after Size 20
100

current interruption) is very short due to the plate spring action so that Size 16
50
a particular circuit such as reverse excitation is not necessary for
Size 12
normal use. 20

Size 10
10
● Torque current characteristics Size 08
Size of torque (magnitude of torque) is determined by the formula of 5 Size 06

T= μ (frictional factor) X r (mean radius of frictional surface) X P

2
(suction power).
T＝μ×r×P 1
0 1 2 3 4 5 6 7 8
μ and r are determined at this time, but P changes depending on
Relative sliding velocity [min−1] X10
3

the current magnitude (amount of the current) to apply. A current is

Dynamic friction torque characteristic Normal size 101・111・CS model, etc.
proportional to a voltage that the friction torque varies by
changing the voltage applied to a coil. The relationship between 120

friction torque and excitation current is indicated in the right

diagram. Around the rated current value, torque increases and 100

decreases in proportion to the current. As the current increases

Friction torque [％]

above the rated value, the magnetic flux density reaches a point of 80

saturation in the magnetic circuit. There is no torque increment

after then, and only the calorific power increases. On the other 60

hand, torque decreases as the current decreases.

40
When it becomes closer to the minimum current value to draw
the armature, torque becomes unstable. By decreasing more
20
current, the armature becomes unable to draw and torque fades
away. To generate torque below the suction current, some
0
procedures are needed. Meanwhile, the diagram is for the 0 20 40 60 80 100 120

specified air gap that the characteristic curve changes as the air gap Excitation current [％]

value changes. Torque current characteristic

76
03_特性_E_p076_097.qxd 11.11.10 11:02 AM ページ77

■ Operating characteristics
● Transient characteristics of
clutches and brakes in working
condition
The following figure shows the transient phenomena of torque
and current when the clutch and brake is connected (braking)
and released. It is generally called operating characteristics.
When applying a voltage through the clutch and brake, the
current increases according to the time constant that is
determined by the coil. When the current reaches a certain value, the
armature is suctioned and the friction torque is generated. The
frictional torque increases as the current increases, and reaches the
rated value. As well as when releasing the clutch and brake, the
armature starts separation by the releasing action of the plate
spring as the current decreases, and torque fades away.

Clutch operating characteristics Brake operating characteristics

Operation input

Operation input

Operation input

Operation input
Actuation input

Actuation input

Actuation input

Actuation input
Exciting voltage

Exciting voltage

Electromagnetic clutches and brakes

Time
Time

Initial delay time Initial delay time Initial delay time Initial delay time
（tid） （tid） （tid） （tid）
Excitation current

Excitation current

Armature pull in time（ta） Armature release time（tar） Time

Armature pull in time（ta） Armature release time Time
（tar）
80％ of the rated dynamic friction torque（Ti）
80％ of the rated dynamic friction torque（Ti）
Static
friction Decreasing torque
torque Decreasing torque
（Ts） 10％ of the rated torqueTr）
Torque

Dynamic Static
Torque

Dynamic Load Drag torque friction 10％ of the rated

friction torque friction
torque torque torque（Tr）
torque（Td） （Tdg） Time
（Td） （Ts） Time
Actual engaging time（tae） Torque decaying time（td）
Actual braking time（tab） Torque decaying time（td）
Actual torque build-up time（tap） Release time（tre） Drag torque Actual torque build-up time（tap） Release time（tre）
Torque build-up time（tp） Time to 0 speed
Torque build-up time（tp）
Drive side
Drive side
Driven side Driven side
Rotating
velocity

Rotating
velocity

Driven side Stop

Engaging time（te） Time
Total engaging time（tte） Braking time（tb） Time
Total braking time（ttb）

Ta: Armature pull in time: Time from when Td: Torque decaying time: Time from when Tae: Actual engaging time: Time from when
the current is applied till when the the current is shut off till when the torque is generated by clutch till when
armature is pulled in and torque is torque decreases to 10% of the rated connection is completed.
generated. torque. Tab: Actual braking time: Time from when
Tap: Actual torque build-up time: Time from Tid: Initial delay time: Time from when the torque is generated by brake till when
when torque is generated till when it operation input is on by the clutch and braking is completed.
becomes 80% of the rated torque. brake till when the actuating input or
Tp: Torque build-up time: Time from when releasing input is on for the clutch or
the current is applied till when the brake body.
torque becomes 80% of the rated
torque.

77
03_特性_E_p076_097.qxd 11.11.10 11:07 AM ページ78

■ Operating characteristics
● Control circuit and operating time ● Shorten the coupling・braking time
The standard voltage is DC24V. If there is no DC source, use the The current conforms to the specified time constant, but if
direct current that is obtained by step-down and commutation especially fast rise is required, the operating characteristic can be
(full-wave rectification) of alternating source. (Refer to the section of changed by using an excitation method such as overexcitation.
power supply.) The on-off operation is generally done on the Overexcitation method is the means to quicken the rise by
direct-current side. The following table indicates the operating applying overvoltage to the coil. The following table indicates the
time at the time. The direct-current side operation allows a quick operating time when overexcitation. Refer to the section of power
response, however extremely high surge voltage is generated supply for more detail.
when the current is shut off, which may cause burnout of the
Operating time in the case of clutch overexcitation
contact in the control circuit or a dielectric breakdown of the coil, (Applicable power supply type: BEH)
therefore, a protective device for surge absorption is
Operating time ［s］
recommended. When switching operation is performed on the Clutch size
ta tap tp td
alternating-current side, torque fading time becomes long, which may 101-06 0.008 0.005 0.013 0.005
cause interference with next operation. In such case, take a time lag. 101-08 0.009 0.008 0.017 0.008
The torque rise time is the same as when operation is performed on 101-10 0.010 0.010 0.020 0.011
the direct-current side. 101-12 0.013 0.012 0.025 0.018
101-16 0.018 0.016 0.034 0.023
The following tables indicate each operating time under the
101-20 0.027 0.020 0.047 0.037
transformer step-down and single-phase full-wave rectification 101-25 0.045 0.026 0.071 0.045
method. *The above values correspond to the CS, CSZ model and various clutch and brake units.
Electromagnetic clutches and brakes

■Micro size Operating time in the case of brake overexcitation

(Applicable power supply type: BEH)
Clutch operating time
Operating time ［s］
Operating time［s］ Brake size
Clutch size ta tap tp td
ta tap tp td
111-06 0.005 0.007 0.012 0.004
 
102-02 0.009 0.010 0.019 0.017
111-08 0.005 0.007 0.012 0.005
 
102-03 0.009 0.013 0.022 0.020
111-10 0.007 0.008 0.015 0.007
 
102-04 0.011 0.017 0.028 0.030
111-12 0.009 0.009 0.018 0.007
 
102-05 0.012 0.019 0.031 0.040
111-16 0.014 0.010 0.024 0.011
 
CYT-025 0.014 0.014 0.028 0.030
111-20 0.015 0.025 0.040 0.020
 
CYT-03 0.015 0.015 0.030 0.040
111-25 0.021 0.034 0.055 0.038
 
CYT-04 0.030 0.010 0.040 0.040
*The above values correspond to the BSZ model and various clutch and brake units.

Brake operating time

Ta- Armature pull in time: Time from when the current is applied till
Operating time［s］ when the armature is suctioned and torque is generated.
Brake size
ta tap tp td
Tap- Actual torque build-up time: Time from when torque is
 
112-02 0.004 0.006 0.010 0.010
 
112-03 0.005 0.007 0.012 0.008 generated till when it becomes 80% of the rated torque.
 
112-04 0.007 0.009 0.016 0.010 Tp- Torque build-up time: Time from when the current is applied till
 
112-05 0.010 0.013 0.023 0.012
when it becomes 80% of the rated torque.
Td- Torque decaying time: Time from when the current is shut off
■Standard size till when it decreases to 10% of the rated torque.
Clutch operating time
Operating time ［s］
Clutch size
ta tap tp td
 
101-06 0.020 0.021 0.041 0.020
 
101-08 0.023 0.028 0.051 0.030
 
101-10 0.025 0.038 0.063 0.050
 
101-12 0.040 0.075 0.115 0.065
 
101-16 0.050 0.110 0.160 0.085
 
101-20 0.090 0.160 0.250 0.130
 
101-25 0.115 0.220 0.335 0.210
*The above values correspond to the CS, CSZ model and various clutch and brake units.

Brake operating time

Operating time ［s］
Brake size
ta tap tp td
111-06 0.015 0.018 0.033 0.015
111-08 0.016 0.026 0.042 0.025
111-10 0.018 0.038 0.056 0.030
111-12 0.027 0.063 0.090 0.050
111-16 0.035 0.092 0.127 0.055
111-20 0.065 0.135 0.200 0.070
111-25 0.085 0.190 0.275 0.125
The above values correspond to the BSZ model and various clutch brake units.

78
03_特性_E_p076_097.qxd 11.11.10 11:07 AM ページ79

■ Heat dissipation characteristics

● Allowable engaging or braking Allowable engaging or braking energy of the micro clutches
and brakes
energy（EeaR or EbaR）
When accelerating or decelerating a load by clutch and brake, heat Allowable engaging or braking energy
Model size
（EeaR or EbaR） ［J］
is generated by sliding friction. The amount of heat changes
 102/112-02 1500
according to the use condition. A clutch and brake works best if  102/112-03 2300
the heat can be dissipated. However, if the core temperature  102/112-04 4500
exceeds the operational temperature limit, this may cause an  102/112-05 9000
operation trouble or damage. As stated above, the limit of  CYT-025 800
frictional load by heat is called allowable work.  CYT-03 900
The tolerance is specified for each size. Heat dissipation  CYT-04 1900

depends on the mounting condition, rpm's and environment.

When accelerating or decelerating a large load, heat generation of
the friction surface is greatly increased due to the intensive
slippage. The friction material or armature could be damaged
by single connection. The right table indicates the allowable
work (allowable friction energy) for each size. Despite its
operation frequency, if the work volume is large, apply the value
much below the indicated value. For the standard size, apply
below the limit line of the following diagram.

Electromagnetic clutches and brakes

50×105
When cold starting
(Position where engaging
（   and braking are performed at
near ordinary temperature)
）
5
20×10

10×105

5×105
Allowable engaging or braking energy (EeaR or EbaR)〔J〕

2×105

1×105

50000

20000

Si
ze
10000 25
Si
ze
20
5000 Si
ze
16

Si
ze
12
2000
Si
ze
10
Si
ze
1000 08

Si
500 ze
06

300
10    20      50    100    200     500    1000   2000     5000  10000

Rotating velocity〔minー1〕

79
03_特性_E_p076_097.qxd 11.12.7 0:24 PM ページ80

■ Heat dissipation characteristics

● Allowable engaging or braking
400
energy rate（PeaR or PbaR）

energy rate (PeaR or PbaR) [W〕

Allowable engaging or braking
Clutch
For high-frequency engaging and braking, the heat dissipation Brake
300
must be fully taken into account. The maximum mount of work Size 12

per minute is called allowable work rate, and it is determined for each Size 10
200 Size 12 Size 08
size as indicated in the diagram. For actual use, apply the value Size 06
Size 10
much below the permissible value in consideration of the Size 08
100
changes of condition. Size 06
The diagram shows the value when wall mounting. When it is
0
fixed on the shaft like bearing mounting, 80% of each diagram is 0 1 2 3 4 5 6 7 8
3
equal to the permissible value. Rotating velocity [minー1] ×10

Standard size

500
40 Size 25
energy rate (PeaR or PbaR) [W〕
Allowable engaging or braking

Size 05

energy rate (PeaR or PbaR) [W〕

Allowable engaging or braking
400 Size 20
30 Size 25 Size 16
Size 04
Electromagnetic clutches and brakes

300 Size 20
20 Size 16
Size 03 200
Size 02
10
100
Clutch
0 Brake
0 1 2 3 4 5 6 7 8 0
3
×10 0 500 1000 1500 2000 2500 3000
Rotating velocity [minー1]
Rotating velocity [minー1]

Micro size (Except CYT model) Standard size

80
03_特性_E_p076_097.qxd 11.12.7 0:24 PM ページ81

■ Structural instructions n Relationship between rotor and stator

When using a clutch and brake for machinery, how to maximize the (Model: □-□-1□)
performances and features in design. From the point of view of For the flange mounted type clutches, the positional relationship
design, this section describes some useful factors to improve the between the stator and rotor is very important. If the H
reliability of machinery. measurement shown in the figure below is too small, the stator and
rotor will come into contact with each other. If the H measurement
● Mounting method of stator and rotor shown is too big, the suction power decreases. The following table
zFlange mounted type stator (Model: □-□-1□） indicates the tolerance for each size. The design should be
performed by not exceeding the value. As for the permissible
This stator must be fixed by an accurate positioning for the value of h, follow the JIS standard tolerance.
rotating shaft. For the inner and outer circumferences of the
stator, class of fit (tolerance quality) is set for positioning. For the H
mounting surface, the concentricity and squareness of the
Bearing
positioning diameter must be below the permissible value to the
rotating shaft.
Unit ［mm］
T Size Concentricity （T.I.R.） Squareness（T.I.R.）
A
02 0.05 0.03
A 03 0.05 0.04
Collar
04 0.06 0.04
h
05 0.06 0.05
06 0.08 0.05
Unit［mm］

Electromagnetic clutches and brakes

08 0.08 0.05
10 0.1 0.05 H h
A Clutch size
12 0.1 0.07 Standard value Tolerance Standard value
16 0.12 0.08 102-02 18.0 1.6

20 0.12 0.13 102-03 22.2 2.0

25 0.14 0.13 102-04 25.4 2.0

±0.2
102-05 28.1 2.0
101-06 24.0 2.0
xBearing mounted type stator（Model:□-□-3□） 101-08 26.5 2.5
This stator is subjected to a small amount of torque by a built-in 101-10 30.0 3.0
bearing or sliding bearing. Therefore, maintain an antirotation arm in 101-12 33.5 ±0.3 3.5
101-16 37.5 3.5
the static part of the machine to prevent corotation.
101-20 44.0 4.0
Antirotation arm
±0.4
101-25 51.0 4.0

● Mounting method of armature

zInstallation of the armature type-1
Tighten completely with the attached hexagon socket bolt to fix. If it
comes loose, apply an adhesive thread lock to the threaded part.

Bearing Set screw

cMagnetic shield of stator

When mounting a stator in combination with clutch and brake, the
performance may become unstable by the effect of each other's xInstallation of the armature type-2
magnetism. Also, if there is an instrument or equipment around the
It has a unique configuration that hides the boss in the inside
clutch and brake, it could cause a negative effect such as noise or
stator. By using a C-shaped retaining ring or collar, fix completely as
error. In such a case, appropriate measures to shut off the
the figure below indicates.
magnetism should be taken. Generally, nonmagnetic material is used
for the mounting surface or shaft.

vLead wire protection

If the coated layer is damaged, it could become the source of
troubles such as short circuit or burnout. Therefore, take into
consideration the protection of the lead wire in the design phase.

bRotor mounting Collar Shim

The rotor is a part of the magnetic circuit. Any bore modifications cInstallation of the armature type-5
may cause performance degradation. For rotor bore diameters
Insert directly if the micro size is below 0.5. As well as the
other than the indicated standard bore diameters, contact us for
armature type-2, use a C-shaped retaining ring or collar to fix the end
further information. face.

81
03_特性_E_p076_097.qxd 11.12.7 0:24 PM ページ82

Unit [mm]
vInstallation of the armature type-3 Size Concentricity (T.I.R.) Squareness (T.I.R.)
02 0.1 0.02
Apply a bore processing to screw or a runout processing for the rivet
03 0.1 0.03
head on the mounting surface. Mounting is performed with the
04 0.1 0.04
attached special hexagon socket bolt and disc spring washer. For the
05 0.1 0.04
thread part, apply a small amount of adhesive to prevent 06 0.16 0.04
loosening. (Do not apply too much adhesive, which may disrupt the 08 0.16 0.05
operation if it is attached to the plate spring.) For the mounting 10 0.16 0.05
screw bore, chamfering is not necessary just remove the burr. 12 0.16 0.06
The attached hexagon socket bolt is a special bolt with a low 16 0.16 0.07
head. For the size below 04, the JIS standard cross-recessed 20 0.24 0.11
head screw is attached. The disc spring washer must be used as the 25 0.24 0.11
following figure. The tightening force decreases if it is used in
reverse. For the armature type-3, the concentricity and
squareness of the positioning diameter must be below the
permissible value to the rotating shaft.
A
Screw / Rivet relief bore Do not chamfer (Before tightening) (After tightening)

A
Electromagnetic clutches and brakes

Screw /
Rivet head Apply an adhesive
Armature Plate spring
A
How to mount armature type-3 How to use washer Mounting accuracy

Armature type-3 mounting dimensions Clutch Mounting pitch diameter Mounting angle Mounting screw bore Screw / rivet relief bore
and brake F P Tolerance No. of bores - M M No. of bores - n
m Tolerance (Nominal Pitch Effective screw Bore Depth of counterbore
M size （P.C.D.） ［° ］ ［ ′］ designation) (minimum) (minimum)
diameter B
B
02 19.5 90 2-M2 0.4 4 2-5 2.5
03 23 3-M2.5 0.45 5 3-6 3
±0.05
04 30 60 3-6
F 3-M3 0.5 7 3.5
05 38 3-7
06 46 3-M3 0.5 7 3-7 3.5
08 60 ±5 3-M4 0.7 9 3-8.5 3.5
10 76 3-M5 0.8 11 3-10.5 4
P ±0.05 60
12 95 3-M6 1.0 11 3-12.5 4
n
16 120 3-M8 1.25 16 3-15.5 4.5
20 158 3-M10 1.5 18 3-19 5.5
25 210 ±0.1 45 4-M12 1.75 22 4-22 6

Armature type-3 mounting parts Clutch Hexagon socket special bolt (*cross-recessed head screw) Disc spring washer
and brake
H r size Nominal dimension x Pitch φD H B R φD φd H t
02 *M2×0.4 3.5 1.3 3
03 *M2.5×0.45 4.5 1.7 4 Disc spring washer is not used
D

04 *M3×0.5 5.5 2.0 6

Size 02∼04 05
M3×0.5 5.5 2.0 2.0 6 6 3.2 0.55 0.36
06
B H r 08 2.8 2.5 8 0.7
M4×0.7 7 7 4.25 0.5
10 M5×0.8 8.5 3.5 3.0 10 8.5 5.25 0.85 0.6
12 M6×1.0 10 4.0 4.0 10 10 6.4 1.0 0.7
D

16 M8×1.25 13 5.0 5.0 15 13 8.4 1.2 0.8

Size 05∼ 20 M10×1.5 16 6.0 6.0 18 16 10.6 1.9 1.5
t 25 M12×1.75 18 7.0 8.0 22 18 12.6 2.2 1.8
d

Size 05∼ H

82
03_特性_E_p076_097.qxd 11.12.7 0:24 PM ページ83

● Air gap design and adjustment ● Fit tolerance

Set the air gap [a] between the frictional surfaces (Figure Clutches and brakes perform substantial work in a moment, but
below) in order that it becomes its specified value when high accuracy control is also required at the same time.
released. At this time, adjustable layout should be done for Therefore, the appropriate integration of each part is necessary for
further convenience. As a method of that, the layout with a not generating a friction or vibration. For that purpose, the fit
combination of collar and shim as indicated in the figure below is tolerance is needed to determine in accordance with the use
recommended. (A shim is regularly stocked. Contact us if condition.
necessary.)
zFit tolerance between rotor / armature
zSet the air gap [a] type 1 & 2 / V-belt pulley and shaft
Prepare a slightly shorter collar than the required length R to The standard bore tolerance is H7 class. For the CYT model, a
maintain the air gap [a], and adjust the remaining gap with a shim to special bore diameter tolerance is applied. The shaft dimensional
obtain the specified value. At this time, the collar length is tolerance used is as follows.
determined approximately by the following formula.
L≒R-2a [mm]
L: length of the collar
R: required length to maintain the air gap
a: specified air gap value
Prepare the collar with appropriate length based on the estimated
value. If the layout is done by the above method, the air gap

Electromagnetic clutches and brakes

Load condition Shaft tolerance Remarks
adjustment after a long period of use can be performed simply by
Shaft below 10φ h6  h7 H5 for high accuracy
removing the required number of shims. h6 h6 j6 for motor shaft
Light, normal and js6  js7
Setting of air gap Air gap [a] Clutch and brake
variable load j6 for unit shaft
j6  j7
Heavy load and k6  k7
impact load m6

xFit tolerance between armature type-5

and sprocket / armature type-5 and shaft

Shim
R
Collar

*Refer to the section of technical data for shim dimensions.

Micro size Standard size

xRemove the allowance of the shaft direction

Clutch and brake Armature type-5 Bore tolerance of Shaft
For the clutch and brake also the parts used in combination, the size Boss part tolerance Bore tolerance sprocket, etc. tolerance

performance degradation may occur if there is an allowance in 02∼05 h7 H7 H7 h7 h8

Conforms to Conforms to
the shaft direction after assembling. Therefore, reduce the 06 or more j6 table below H7 table above

allowance as much as possible. For controlling a little amount of

allowance, various types of shims are available. They correspond to
the often-used shaft diameter or bearing outside diameter. In cFit tolerance between ball bearing and
addition, reliable fixing with a spring action can be performed housing
when used in combination with a C-shaped retaining ring. Load condition Bore tolerance Remarks
How to use shims Heavy load N7
Outer-ring
Normal load
rotational load
and variable load M7
Heavy impact load
Heavy load
Unstable load and normal load K7
in direction
Heavy load
and normal load J7
Impact load
Inner-ring
When it does not have impact
rotational load General load H7 from clutch and brake

Shim *Apply to the iron-steel or cast-iron housing. For light-alloy housing, tighter fitting is required.

Shim C-shaped retaining Shim C-shaped retaining

ring ring

83
03_特性_E_p076_097.qxd 11.12.7 0:24 PM ページ84

vFit tolerance between ball bearing and shaft ● Bore diameter and keyway
Load condition Bore tolerance Remarks zBore diameter
H5 for
Outer-ring rotational load h6 The standard bore diameter is determined for each size as
high accuracy
φ18 or less
Light load, normal h5 indicated in the measurement. To apply the bore diameter other
Unstable load
in direction
load and variable load
φ100 or less j6 than the standard, a pilot bore is prepared for the 101 & 111
Inner-ring
Heavy load φ18 or less j5 type rotor and the armature type 1 & 2. Please follow bore
rotational load
and impact load φ100 or less k5 specifications and precautions q∼ r. The bore range is
indicated in the table below.
q The tolerance of bore must be H7 class.
bFit tolerance between bearing and other w When machining a bore care must be taken with respect to the
parts concentricity and perpendicularity of the bore.
As for the shaft with bearing and rotor or V-belt pulley mounted in the e Since the outer part of the rotor is deformed by applying
same part, prioritize the bearing and follow the fit tolerance force, do not chuck when machining.
between ball bearing and shaft. r Remove all cutting oil or wash oil and dry completely before
mounting.

xKey and keyway

Our company specification based on JIS standard is applied for the
keyway of the rotor and armature. (Refer to the page of clutch
Electromagnetic clutches and brakes

and brake standard bore processing specification.)

For the CYT model, a special keyway tolerance (shown in the
measurement table below) is applied. For use of the key and
keyway of the shaft, the JIS standard is suitable. Refer to the
page of the technical data excerpted from JIS B 1301-1996. When
performing a keyway processing on the rotor or armature, follow the
above as well.

Bore diameter processing range for rotor and armature type 1 & 2 Unit [mm]
Clutch and Bore                diameter  
brake size 5 6 8 （8.5） 10 12 （12.5） 15 17 （18.5） 20 （24） 25 28 30 32 35 40 48 50 60 70 75 80
02 R・A Standard bore diameter
03 R・A Processable range
04 R・A
( ) indicates a pilot bore
05 R・A
(Finish process is not performed.)
R
06 A R: Rotor
R A: Armature type 1 & 2
08 A
R
10 A
12 R
A
16 R
A
20 R
A
25 R
A
*The above table does not correspond to the CYT, CSZ and BSZ model.

84
03_特性_E_p076_097.qxd 11.12.7 0:24 PM ページ85

● Environment of the mounting ● Vibration and backlash

When selecting a clutches or brakes careful consideration of Both clutch and brake assemblies are balanced to reduce
the operating environment must be taken. vibration. However, if the device is applied impactive forces
repeatedly, backlash could occur to generate vibration noises.
zTemperature
Perform the layout with no backlash.
The heat-resistant class of clutch and brake is B type, and the
allowable operating temperature is -10oC∼ 40oC. When the
clutch or brake is used at high temperatures, the heat
● Antirust
An antioxidation treatment is applied to the clutches and
generated by actual clutching and braking operations does not
brakes. However, oxidation may be generated depending on
dissipate, this may cause damage to the coil or friction part.
the storage condition or environment. Please attempt to prevent
Even if it is used below -10oC, there is no problem if the
oxidation. A small amount of oxidation is acceptable.
temperature becomes over -10oC by heat generation of the
clutch and brake. However, if the water of crystalline frosts
generated by a longtime stoppage or low-frequency operation is ● Occurrence of sparks
attached on the device, it may cause performance degradation. During the use process of clutches and brakes, sparks may
occur by the friction between the magnetic pole part of the
xHumidity and water drop frictional surface and the armature. Make sure not to use in a
As in the case of temperature, if water drops are attached on the flammable environment.
friction surface, the coefficient of friction decreases temporally
until it dries. Also, water contamination causes oxidation as
● Structural design with
well. Therefore, take appropriate measures such as using a
maintainability

Electromagnetic clutches and brakes

cover.
Maintenance of clutches and brakes is not generally required
cMixing in of a foreign body such as dust or oil for a long period of time.
The friction surface has a susceptibility to foreign body. If any oil By performing maintenance on a ball bearing, for instance, it
is mixed, the coefficient of friction significantly decreases. Metal can be used for a prolonged period. A structural design that can be
dust especially damages the friction surface or rotating part. In easily disassembled and reassembled is recommended. Refer to
addition, an agent could also cause oxidation. For such the instruction manual for more detail.
environment, use of a protective cover is recommended.

vAir ventilation ● Use of micro clutches

If a bearing mounted type micro clutch (oil retaining metal) is
Since the clutch and brake converts the friction work into heat
used, there is a possibility to be regulated by the current-
proper ventilation is required to dissipate the heat build up.
carrying rate or temperature. Contact us for further information.
Forced cooling is a effective way for increasing an allowable
amount of work. Confirm the temperature if the device is used in
the place with poor ventilation. ● Overhung load of the unit
The permissible value of the radial load applied on the shaft is
indicated below. For the through shaft type unit, the permissible
● Maximum rotation speed (RPM)
value slightly changes due to the direction of action of the input-
The maximum rotation speed (rpm) of clutches and brakes is
output load. (The indicated value is when the most stringent
indicated in the specification table. This value is determined by the
condition is applied. The load point is the midpoint of the shaft.)
peripheral velocity of the friction surface. If the speed exceeds the
maximum rpm, this may cause premature wear and premature
Unit: [N]
failure of the clutch or brake. Overspeed applications will not
125 - □ -12 121- □ -10
transmit rated torque. Size 121-□-20
126 - □ - 4B 122 - □ - 20

● Ball bearing
A ball bearing is generally used in combination with clutches
and brakes, and a deep-grooved ball bearing is the most
W W W1 (W2) W1 W1
common. Since dry-type clutches and brakes have a W3 W3
susceptibility to oils and fats attached on the frictional surface, use
a double sealed bearing which does not require lubrication. A
W2 W2 W2
double sealed bearing with contactless rubber seal is effective for
preventing dust. For a compact bearing or rare bearing, a
metallic double sealed type is also available.
05 250 − − −
06 320 300 （320） 140 140
● Mechanical strength
08 480 450 （500） 250 250
Due to the operating characteristics of clutches and brakes,
10 700 700 （800） 450 450
coupling and braking of load can be immediately performed, 12 900 900（1000） 700 700
thus impactive forces may be applied to each part of the 16 1300 1400（1600） 1000 1000
machine, therefore to allow enough strength is important. 20 1800 2000（2500） 1800 1800
(Undue safety design could cause a load torque increase, or 25 2900（3600） 2600 2600
affect the coupling and braking accuracy.) *( ) for load in both directions.

85
03_特性_E_p076_097.qxd 11.12.7 0:24 PM ページ86

■ Control circuit
● Basic configuration of a control cRelay (Control contact)
circuit Since the electromagnetic clutches and brakes have a magnetic coil
When designing an electric circuit to control the clutch and brake, the inside, they must be used within the conditions of the applied relay direct-
selection of control method and control device is very important. The current inductive load. This is because the contact erosion occurs by the
appropriate selection and circuit design stabilize the performance of the surge voltage generated when the electromagnetic clutch and brake is
clutch and brake and strengthen the reliability of the machine. controlled. In the case that the operating life or operation frequency is a
To run the clutch and brake, DC24V (standard specification) power is problem in use, a static relay is required. For details, refer to the
required. There are two methods to run the clutch and brake. One is to section of power supply for electromagnetic clutch and brake control.
use a direct current, and the other is to step down the voltage and rectify
Control point
an alternating current power. Various power supplies for exclusive
use are available. Refer to the section of power supply for more
details. C/B
Commercial Clutch and
power Power supply Control device brake
MC
C/B Power supply

Standard wiring Direct-current switching

● Selection of parts of power supply v Control circuit structural points to

remember
zTransformer qControl of clutch and brake
Adjust the primary side to the power supply voltage. For the When the clutches and brakes are controlled on the alternating-
Electromagnetic clutches and brakes

secondary side, use a transformer that has enough capacity to apply the current side, the armature release time becomes late and high-
rated voltage to the clutch or brake coil. To get a rough idea, choose a frequency operation becomes unable to perform. Therefore, set the
transformer with a capacity of more than 1.25-times the rating control contact on the direct-current side.
capacity of the clutch or brake in temperature of 20oC. In addition, the wPower supply voltage of clutch and brake
secondary side output voltage is generally required to be set in Variation of the exciting voltage must be within ±10％ of the clutch and
accordance with the voltage drop of the rectifier and the impedance of brake rated voltage.
the transformer, however it can be evaluated simply by the formula below eSmooth the exciting voltage
(Formula q and w). A single-phase full-wave rectification is generally used for a clutch
V＋1.4 and brake power supply. If high accuracy is required, a sufficient
V2=−
−−−
−−−
−−− −〔V〕 ………………………………………………q
−−
0.9 result can be obtained by smoothing.
Formula q is a method of single-phase full-wave rectification.
P≧WCB×1.25〔VA〕………………………………………………w
V2: Transformer secondary side Primary Transformer Secondary
side side ＋
voltage [V] Constant
Unstable Stabilized
voltage
V: Direct voltage [V] AC voltage input output
circuit
50/60Hz V2
P: Transformer capacity [VA]
WCB:Clutch (brake) capacity [VA]
Stabilized power supply circuit
xRectifier rProtection of the control contact
The "single-phase full-wave rectification (bridge method)" is When a protection circuit is set for the clutch and brake, the control
adopted from various types of rectification methods. For the contact is also protected. In addition, if a CR absorber is applied
selection, the maximum rated value of the rectifiers must be between the contact points as below, the protection effect
followed. It can be evaluated simply by the formula below. increases. C (condenser) and R (resistance) become approximately as
qDetermination of the reverse withstand voltage VRM below.
VRM=VL・   ・K
2 …………………………………………………e Condenser C [μF] : ratio to contact current is;
VL: Alternate current input voltage [V] C［μF］ 0.5∼1
K: Factor of safety (take 2∼3) =
Protection of rectifier is required if there is a possibility of commingling of
I［A］ 1
more than the withstand voltage of surge. Withstanding voltage: 600 [V]
wDetermination of the average rectified current
Select a rectifier that has more than 1.5-times the clutch or brake Resistance R [Ω]: ratio to contact voltage is;
rated current. In the case of high current, temperature rise becomes a R［Ω］ MC
=1 ＋
problem. Take measures to dissipate the heat and prevent the rise of
E［V］
temperature.
C R
Capacity: 1 [W] D.C C/B

A.C
D.C
input C/B −
Varistor Varistor output
Relay protection circuit

Single-phase full-wave rectification method

86
03_特性_E_p076_097.qxd 11.12.7 0:24 PM ページ87

bDischarge circuit In addition, the effect to control the armature release time or
When a direct exciting current is applied to electromagnetic surge voltage is different depending on the types of discharge
clutches and brakes, the energy is stored in the inside coil. When circuits. For the characteristics of discharge circuits, refer to the table
interrupting the current, surge energy is generated between the coil below. Each discharge circuit has both merits and demerits. We
terminals by the stored energy. This surge energy could reach recommend using a varistor.
more than 1000V by the breaking speed or current, which may
cause a dielectric breakdown of the coil or contact burnout of the
switch. Therefore, to set an appropriate discharge circuit to
prevent these troubles is required.

Circuit diagrams Current decay Characteristics

MC I
＋

Varistor It has a significant effect to reduce a surge voltage.

VR C/B
There is no delay of the armature release time.
− t
MC I
＋ The power consumption of the power section can be
R reduced as well as its resistance capacitance. Since the
Resistor + diode C/B
armature release time becomes slow in a measure,
D
− caution is demanded for high-frequency use.
t

Electromagnetic clutches and brakes

MC I
＋ It is effective to reduce a surge voltage. However, the
armature release time becomes slow, and there is a high
Diode D C/B possibility of occurrence of mutual interference of the
−
clutch and brake. It is not suitable for high-frequency use.
t
MC I
＋
Resistor + condenser R The armature release time becomes faster, but a
C/B
C condenser with high withstanding voltage is required.
− t

■ Applicable power supplies specifications

Rectification Frequency AC input voltage DC input voltage＊1 Capacity Applicable clutch
Model
method ［Hz］ AC［V］ DC［V］ ［W］ and brake size

BES-20-05 Single-phase full-wave 50/60 100/200 24 50 02∼05

BES-20-10 Single-phase full-wave 50/60 100/200 24 50 06∼10

BES-20-16 Single-phase full-wave 50/60 100/200 24 50 12∼16

BES-20-20 Single-phase full-wave 50/60 100/200 24 50 20

BES-40-25 Single-phase full-wave 50/60 100/200 24 100 25

* When using the applied power supply BES, varistor is not required. Refer to the section of power supply for more detail.

87
03_特性_E_p076_097.qxd 11.12.7 0:24 PM ページ88

■ Accessories
The attached components of clutches and brakes are different depending on the model and type. Refer to the accessory list below.
Besides, information in this document is subjected to change without notice.

■Micro size
Varistors Screws＊1 Shims
Model
Model Qty Specifications Qty Inside dia. x outside dia. x thickness Qty
102-02-□1,□5 1 − − −
102/112-02-□3 1 M2×3 2 −
112-02-□1,□2 1 − − −
102-03-□1,□5 1 − − −
102/112-03-□3 1 M2.5×4 3 −
112-03-□1,□2 1 − − −
102-04-□1,□5 1 − − No accessories −
102/112-04-□3 1 M3×6 3 −
112-04-□1,□2 1 − − −
NVD07SCD082
102-05-□1,□5 or equivalent
1 − − −
Low-head bolt M3×6 3 −
102/112-05-□3 1
Disc spring washer for M3 3 −
112-05-□1,□2 1 − − −
Electromagnetic clutches and brakes

CYT-025-□ φ6 1 6.3×8.7×0.1t 3
CYT-03-□  φ6 1 M2.5×4 3 6.3×8.7×0.1t 3
CYT-03-□  φ8 1 8.3×11.7×0.1t 3
CYT-04-□  φ8 1 8.3×11.7×0.1t 3
M3×6 3
CYT-04-□ φ10 1 10.3×13.7×0.1t 3
CSZ/BSZ-05-□ 1 − − No accessories −
* *1 For the size 05, a hexagon socket special bolt is attached. For other sizes, a cross-recessed pan head machine screw is attached.

■Standard size
Varistors Screws Shims Collars
Model
Model Qty Specifications Qty Inside dia. x outside dia. x thickness Qty Inside dia. x outside dia. x thickness Qty
101/CS-06-□1 1 − − − − − −
101/CS-06-□3 
φ12 1 Low-head bolt  M3×6 each 3 12.3×15.7×0.1t 3 − −
101-06-13 
φ15 1 Disc spring washer for M3 each 3 15.3×20.7×0.1t 3 − −
12.3×15.7×0.1t 5
101/CS-06-□5 
φ12 1 − − 12.2×18×5.5 1
12.3×15.7×0.5t 1
NVD07SCD082
φ12,15
111-06-11  or equivalent 1 − − − − − −
111-06-12 
φ12 1 − − 12.3×15.7×0.1t 3 − −
111-06-12 
φ15 1 − − 15.3×20.7×0.1t 3 − −
Low-head bolt  M3×6
111-06-13 1 Disc spring washer for M3 each 3 − − − −

CSZ/BSZ-06-□ 1 − − − − − −
101/CS-08-□1 1 − − − − − −
101/CS-08-□3 
φ15 1 Low-head bolt  M4×8 each 3 15.3×20.7×0.1t 3 − −
101-08-13 
φ20 1 Disc spring washer for M4 each 3 20.3×27.7×0.1t 3 − −
15.3×20.7×0.1t 5
101/CS-08-□5 
φ15 1 − − 15.2×22×5.5 1
15.3×20.7×0.5t 1
NVD07SCD082
φ15,20
111-08-11  or equivalent 1 − − − − − −
111-08-12 
φ15 1 − − 15.3×20.7×0.1t 3 − −
111-08-12 
φ20 1 − − 20.3×27.7×0.1t 3 − −
Low-head bolt  M4×8
111-08-13 1 Disc spring washer for M4 each 3 − − − −

CSZ/BSZ-08-□ 1 − − − − − −

88
03_特性_E_p076_097.qxd 11.12.7 0:24 PM ページ89

■Standard size
Varistors Screws Shims Collars
Model
Model Qty Specifications Qty Inside dia. x outside dia. x thickness Qty Inside dia. x outside dia. x thickness Qty
101/CS-10-□1 1 − − − − − −
101/CS-10-□3 
φ20 1 Low-head bolt M5×10 each 3 20.3×27.7×0.1t 3 − −
101-10-13 
φ25 1 Disc spring washer for M5 each 3 25.3×34.7×0.1t 3 − −
20.3×27.7×0.1t 5
101/CS-10-□5 
φ20 1 − − 20.2×28×5.9 1
NVD07SCD082 20.3×27.7×0.5t 2
φ20,25
111-10-11  or equivalent 1 − − − − − −
111-10-12 
φ20 1 − − 20.3×27.7×0.1t 3 − −
111-10-12 
φ25 1 − − 25.3×34.7×0.1t 3 − −
Low-head bolt M5×10 each 3
111-10-13 1
Disc spring washer for M5
− − − −

101/CS-12-□1 1 − − − − − −
101-12-13 
φ25 1 each 3 25.3×34.7×0.1t 3 − −
Low-head bolt M6×10 each 3
101-12-13 
φ30 1 Disc spring washer for M6 30.3×39.7×0.1t 3 − −
CS-12-33 
φ25 1 each 3 25.3×31.7×0.1t 3 − −
25.3×31.7×0.1t 5
101/CS-12-□5 
φ25 NVD07SCD082 1 − − 25.2×32×7.5 1
or equivalent 25.3×31.7×0.5t 2
φ25,30
111-12-11  1 − − − − − −

Electromagnetic clutches and brakes

111-12-12 
φ25 1 − − 25.3×31.7×0.1t 3 − −
111-12-12 
φ30 1 − − 30.3×39.7×0.1t 3 − −
Low-head bolt M6×10 each 3
111-12-13 1
Disc spring washer for M6
− − − −

101/CS-16-□1 1 − − − − − −
101-16-13 
φ30 1 each 3 30.3×41.7×0.1t 3 − −
Low-head bolt M8×15
101-16-13 
φ40 1 Disc spring washer for M8 each 3 40.3×51.7×0.1t 3 − −
CS-16-33 
φ30 1 each 3 30.3×39.7×0.1t 3 − −
30.3×39.7×0.1t 5
101/CS-16-□5 
φ30 NVD07SCD082 1 − − 30.2×40×11.2 1
30.3×39.7×0.5t 2
or equivalent
φ30,40
111-16-11  1 − − − − − −
111-16-12 
φ30 1 − − 30.3×39.7×0.1t 3 − −
111-16-12 
φ40 1 − − 40.3×51.7×0.1t 3 − −
Low-head bolt M8×15 each 3
111-16-13 1 Disc spring washer for M8 − − − −

101-20-11 1 − − − − − −
101-20-13 
φ40 1 each 3 40.3×51.7×0.1t 3 − −
101-20-13 
φ50 1 Low-head bolt M10×18 each 3 50.3×67.7×0.1t 3 − −
Disc spring washer for M10
CS-20-33 
φ40 1 each 3 40.3×51.7×0.1t 5 − −
40.3×51.7×0.1t 5
101-20-15 
φ40 1 − − 40.2×50×11.7 1
NVD07SCD082 40.3×51.7×0.5t 2
φ40,50
111-20-11  or equivalent 1 − − − − − −
111-20-12 
φ40 1 − − 40.3×51.7×0.1t 3 − −
111-20-12 
φ50 1 − − 50.3×67.7×0.1t 3 − −
Low-head bolt M10×18
111-20-13 1 Disc spring washer for M10 each 3 − − − −

101-25-11 1 − − − − − −
101-25-13 
φ50 1 each 4 50.3×67.7×0.1t 3 − −
Low-head bolt M12×22
101-25-13 
φ60 1 Disc spring washer for M12 each 4 60.3×84.7×0.1t 3 − −
CS-25-33 φ50 1 each 4 50.3×67.7×0.1t 5 − −
50.3×61.7×0.1t 5
101-25-15 
φ50 1 − − 50.2×60×12.2 1
NVD07SCD082 50.3×61.7×0.5t 2
φ50,60
111-25-11  or equivalent 1 − − − − − −
111-25-12 
φ50 1 − − 50.3×67.7×0.1t 3 − −
111-25-12 
φ60 1 − − 60.3×84.7×0.1t 3 − −
Low-head bolt M12×22 each 4
111-25-13 1 Disc spring washer for M12 − − − −

89
03_特性_E_p076_097.qxd 11.12.7 0:24 PM ページ90

■ Selection
● Points for selection xRelationship between torque and RPM
Due to the high controllability, clutches and brakes are used not qDifference of characteristic
only for on-off control but also complex operation. If the size is The shaft in the machine with a high RPM can be rotated by a small
determined simply by its torque, an unexpected trouble may force, but the decelerated low-speed shaft needs a large force to
occur. When selecting the size, a careful examination from rotate. That is, torque is inverse proportion to RPM. This is very
several points of view such as load characteristic or layout of important in selecting a clutch and brake. The size or operating life
the mechanism where the clutch and brake is assembled is changes depending on the RPM of the shaft.
required. This section describes the situational selection
methods, calculation examples and required information.
Motor Load
zMotor and clutch & brake
qRelationship between motor output and torque
Motor HP is indicated by output, but it is indicated by torque in
clutches and brakes.The following relationship is formed between the
wCombination with a speed changer
torque and motor output.
Like a non-stage speed changer, when a clutch and brake is
9550･P used in the mechanism that can change the RPM, the torque
TM＝−
−−−
−−−
−−− − η［N・m］ ……………………………………q
−−
nr requirement during low speed and the responsiveness and
operating life requirement during high speed must be considered in
P: Motor HP ［kW］
advance.
nr: RPM of the clutch and brake shaft ［minー1］
Electromagnetic clutches and brakes

η: Transmission efficiency from the motor to clutch and brake

cUnderstanding of load characteristics
The coupling time or wear life of clutch and brake varies
wDifference of characteristic
depending on the coupling and braking load characteristics.
Motor and clutch & brake have different torque characteristics.
Therefore, to understand the load characteristics is important to
Therefore, if a motor is used as a drive source and the start-and-stop
maintain a consistent operation. However, the load
control of load is performed by a clutch and brake, the selection must
characteristics vary in definition and a complete understanding is
be done in consideration of respective characteristics.
difficult. As it is now, the size is often determined from an
experimental point of view.
A) Motor characteristics
A motor can generate over 200% of the full-load torque at start-up.
qImportance of safety factor
After passing through the maximum torque while accelerating, it
When the size of clutch and brake is determined, the required
drives the load near the full-load torque until stable operation can be
torque is evaluated by multiplying the factor empirically. If the
obtained. When the load increases while running the motor RPM will
driving part is already set, use the factor K empirically depending on
be reduced, the motor momentum will continue to drive the load and
the motor to be used. When the factor is too small, it could cause
the motor will generate additional torque. The following diagram
trouble such as slippage when worsening of the condition.
indicates the relationship between motor torque and rotating
Conversely, if the factor is too big, the motor load increases. An
velocity characteristic.
excessive load may lead to motor problems.

Motor/ Gasoline Diesel engine

Torque

Turbine engine (1∼2 cylinder gasoline engine)

K 2∼2.5 2.5∼2.8 2.8∼3.4

Maximum torque wLoad torque and moment of inertia

In load torque, there are resistance forces in machine and
Starting torque resistance forces added after coupling (such as cutting
resistance). Since load torque is difficult to evaluate the size
Synchronous
Full load speed selection is sometimes calculated incorrectly, this may cause
Start-up torque (slippage
(slippage ratio 0%) torque insufficiency in the case of clutch. The selection must be done
ratio 100%) with due caution. Moment of inertia is also called flywheel effect,
Rotation speed［min−1］
which indicates the amount of power required to stop or start a
rotating object. Overload of clutch and brake can be prevented by
B) Clutch and brake characteristics
reducing the load on the clutch as much as possible. In the
As described in the section of torque characteristics, the upper
design phase apply a measurably larger load for brake. In
limit of coupling and braking torque is determined, and if more of the
addition this will minimize the inertia moment and improve
load torque is applied, it slips on the friction surface. An
responsiveness and operating life. Be sure include the inertia of
appropriate selection can be performed by confirming the
clutch and brake in your inertia calculations.
difference of characteristic in advance. For a wide range of
application, a clutch and brake with a torque value of 200~ 250% of
the full load torque of the motor is recommended.

90
03_特性_E_p076_097.qxd 11.12.7 0:24 PM ページ91

■ Selection
● Simplified selection graph [Selection Example]
This selection graph is applied to a relatively light load and low qWhen the motor output is 0.75 kW and the clutch and brake
frequency and when a motor is used as a drive source. The rotating velocity is 1500min-1, select the size 10 where the
size of clutch and brake can be determined by a simplified way intersecting point is.
if the motor to be used is set appropriately to the load wWhen the motor output is 0.4kW, the clutch and brake rotating
condition, and when there is no complicated mechanism or velocity is 850min-1, and the safety factor is 1.5,
large inertial system to help the drive between the motor and 1.5
0.4［kW］×−
−−−−
−−−− =0.24［kW］
clutch and brake. The safety factor K is 2.5 in this graph. 2.5
If other factors are required, use the value evaluated by evaluate the value as below. The point at intersection of 0.24kw
multiplying the motor output by K/2.5 as kW of the vertical axis. of the vertical axis and 850min-1 is in the range of the size 08.

50

20

Electromagnetic clutches and brakes

40
10 ze
Si
31
ze
Si
5
25
ze
Si
20
ze
Si
Motor output［kW］

2
16
ze
Si

1 12
ze
Si
（0.75）
10
ze
Si
0.5
08
ze
Si
06
z e
（0.24） Si
0.2
05
ze
Si

0.1 04
z e
Si
03
ze
Si
0.05 02
z e
Si

0.02

0.01
30 50 100 200 500 850 1000 1500 2000 5000 10000

Rotation speed［min−1］

* Perform the selection within the range. If the intersecting point is in the dashed line, the amount of work, heat
dissipation or wear could become below the specified level.
For the heavy-line frame of below 100min-1, confirm the required torque by the formula.
*For the size 31 and 40, contact us for further information.

91
03_特性_E_p076_097.qxd 11.12.7 0:24 PM ページ92

● Study of torque vRequired torque（T）

The required torque to drive (brake) the load by condition is as
zFull load torque of motor (TM)
follows.
The full load torque converted to the clutch and brake mounting
qWhen engaged and when J and TR are applied together.
shaft is;
T＝（Ta±TR）K［N･m］………………………………………y

9550･P K is a factor by load condition. Refer to the table below and

TM＝−
−−−
−−−−−−・η［N・m］ ………………………………………q
− select the value empirically. In a case of clutch, the load torque
nr
works on the direction of counteracting the drive so that TR is
P: Motor output [kW] plus (+). In a case of clutch, the load torque works on the
nr: Rotating velocity of the clutch and brake shaft [min-1] direction of enhancing the braking so that TR is minus (-).
η: Transmission efficiency from the motor to clutch and brake wWhen engaged and when J and TR are applied together
T＝TR・K［N･m］……………………………………………………u
xLoad torque (TR)
Load torque is difficult to evaluate by a formula. Therefore, the
eWhen J is mostly applied
value is estimated empirically or evaluated by measuring
directly. T＝Ta・K［N･m］……………………………………………………i
qDetermine form the motor capacity
rIn a case of stational engagement
Assume that the motor is correctly selected for the load
If the clutch is coupled during stationary state and the load is
condition. Use the evaluated value TM of q as its load torque.
accelerated by a motor, the required torque to prevent a slip of
TR＝ TM［N･m］………………………………………………………w clutch during acceleration is;

｛ −J−−−J＋J−（T −T ）＋T ｝
R
Electromagnetic clutches and brakes

wIn a case of direct measurement T＝ −−

− K［N･m］ …………………o
M R R
d R
A correct TR can be determined by actual measurement of load.
For the measurement, use a torque wrench or rotate the shaft Jd: Total amount of J on the driving side from the clutch [kg･m2]
to mount the clutch and brake, and evaluate the product of F JR: Total amount of J on the loading side from the clutch [kg･m2]
(force when the load starts to rotate) and R(length of the arm).

TR＝R・F［N･m］……………………………………………………e Safety factor by load condition: K

Use condition Factor K

Motor Low-frequency use of a small inertial body 1.5
Light High-frequency use of a relatively small inertial body
F: Pull force [N] 2∼2.2
load General use of a standard inertial body
High-frequency use 2.2∼2.4
90°
R: Length of arm [m] Low-frequency use of a small inertial body 2∼2.4
Standard
load General use of a standard inertial body 2.4∼2.6
Drive a large inertial body 2.7∼3.2
：Load side Heavy load Operation that involved impact (Large load fluctuations) 3.5∼4.5
Mounting part of
clutch and brake
Measurement of torque
bConversion of torque to the other shaft
eLoad torque sign
To convert the torque of B shaft to the A shaft
In the formula, the load torque is indicated by a plus-minus (+/-) nB
sign. In a case of clutch, the load torque works on the direction TA＝TB・− −−−−−−［N・m］…………………………………………!0
nA
of counteracting the rotation so that it is subtracted from the
clutch torque Td. In a case of brake, the load torque works on
the direction of enhancing the braking so that it is added to the TA: Torque of A shaft, TB: torque of B shaft
brake torque Td. (It is relatively rare, but it may work the other nA: Rotation speed of A shaft, nB: Rotation speed of B shaft
way. In such a case, change the sign to calculate.) In the
formula, it is indicated as ±TR.

cAcceleration/deceleration torque (Ta)

qThe required torque to accelerate the load is;
A Shaft nA ［minー1］
J・nr
Ta＝−
−−−
−−−−
−−−
−−
−−
−−−
 ［N・m］ ……………………………………r
9.55tae
tae: Actual coupling time of clutch (Acceleration time) [s]
J: Total amount of inertia moment engaged by clutch [kg･m2]
B Shaft nB ［minー1］

wThe required torque to accelerate the load is;

J・nr
Ta＝−
−−−
−−−−
−−−
−−
−−
−−−
 ［N・m］ ……………………………………t
9.55tab
tab: Actual braking time of brake (Deceleration time) [s]
J: Total amount of inertia moment decelerated by brake [kg･m2]

92
03_特性_E_p076_097.qxd 11.12.7 0:24 PM ページ93

● Study of energy wBraking energy rate (Pb)

zEngaging or braking energy(Ee, Eb) Eb･S

Pb＝−
−−−
−−−
−−≪PbaR [W] ………………………………………………!9
The work volume of single coupling or braking by clutch and 60
brake is;
S: Operation frequency [operations/min]
qDuring acceleration, the engaging energy Ee is;
The allowable energy rate PeaR and PbaR are the values under
J･nr2 Td an ideal condition. Therefore, determine Ee and Eb and S in
Ee＝−−−−−−−
−−・− −− −−−
− −−−
−− [J］ ………………………………!1
182 Td−TR
order that they become sufficiently smaller than them.
wDuring deceleration, the braking energy Eb is;
* For the values of EeaR and EbaR, refer to the page of heat dissipation characteristics.
J･nr2 Td
Eb＝−
−−−
−−−
− −・−
−−−
−−−−
−−−［J］…………………………………!2
− cEngaging/braking frequency (Sa)
182 Td＋TR
The allowable operation frequency determined by heat
eNormal/Reverse rotation dissipation Sa is;
The clutch engaging energy when the rotational direction is
60PeaR
switched by clutch is; Sa≪−
−−−
−−−
−−−[operations/min] …………………………………@0
−
Ee
J Td Td
Ee＝− −−
−
182 ｛ 2
− （n1 ＋2･n1･n2）−
−−−−
−
Td＋TR
2
− ＋n2 −−−
−−−−［J］……!3
−
Td−TR ｝ Sa≪−
−
60PbaR
−−
−−−
−−− [operations/min] …………………………………@1
−
n1: Normal rotation velocity [min ] −1 Eb
n2: Reverse rotation velocity[min−1] This allowable frequency is determined only by heat dissipation.
For actual use, consider the operating time also.

Electromagnetic clutches and brakes

Normal rotation
n1
● Study of operating time
zTotal engaging and total braking time (tte, ttb)
0 t
The engaging and braking time of load by clutch and brake is
the sum of the clutch and brake operating time itself and the
n2
Reverse rotation accelerating and decelerating time of load.
qTotal engaging time
tte＝tid＋ta＋tae [s]………………………………………………………@2
rEnergy during slip tid: Initial delay time
2π ta: Armature pull in time [s]
Ee＝−
−−−
−−−・n・t・Td［J］ ……………………………………!4
60 tab: Clutch actual engaging time (Acceleration time )[s]

2π
Eb＝− −
−−−−−・n・t・Td［J］ ……………………………………!5 wTotal braking time
60 ttb＝tid＋ta＋tab [s] ………………………………………………………@3
t : Slipping time [s]
tid: Initial delay time
n: Rotating velocity to slip min−1]
ta: Armature pull in time [s]
Td: Dynamic torque at n [min-1][ N･m]
tab: Brake actual braking time [s]
tae and tab are evaluated by the formulas below by the condition.
When clutch and brake is used while slipping, an undesirable
condition such as heat generation may occur.
eDuring acceleration/deceleration
Actual engaging time is;
tAllowable energy
The allowable work EeaR and EbaR are the values under and J･nr
tae＝−
−−−
−−−
−−−
−−−
−−−
−−−
−−［s］ …………………………………………@4
ideal condition that the values of Ee and Eb must be sufficiently 9.55（Td−TR）
smaller than them.
Actual braking time is;

Ee≪EeaR ………………………………………………………………!6 J･nr

tab＝−
−−−
−−−
−−−
−−−
−−−
−−−
−−［s］……………………………………………@5
Eb≪EbaR ………………………………………………………………!7 9.55（Td＋TR）

* For the values of EeaR and EbaR, refer to the page of heat dissipation characteristics. rDuring normal rotation
The actual engaging time (acceleration time) when switched the
xEnergy rate normal rotation into reverse rotation is;
A clutch and brake repeats an on-off operation with a high
frequency that examination of capability of heat dissipation is J n1 n2
important.
tae＝−
−−−
−−−
9.55 （−−−T−−−−T
−−
−−−
−＋−
d
−
T ＋T ）
−−
−−−
−−−
−
R
− ［s］ …………………@6
d R

qEngaging energy rate (Pe) n1: Normal rotation velocity [min−1]

n2: Reverse rotation velocity [min−1]
Ee･S
Pe＝−
−−−
−−−
−−≪PeaR［W］…………………………………………!8
60

93
03_特性_E_p076_097.qxd 11.12.7 0:24 PM ページ94

x The coupling/braking time when the coupling/ Total amount of energy before air gap readjustment ET
braking is completed in the process of torque rise Micro electromagnetic clutch and brake
102・112 model
In this case, the coupling/braking time is the sum of the armature
suction time ta and tae' or ta and tab'. Size Total amount of energy E T［J］
qTotal coupling time 02 2×106
03 3×106
tte＝tid＋ta＋tae' [s] ……………………………………………………@7
04 6×106
J･nr tap 05 9×106
tae'＝ −
−−−
−−−
−・−
−−−
−−−
−−［s］……………………………………@8
4.77 0.8･Td
CYT model
wTotal braking time
Size Total amount of energy E T［J］
ttb＝tid＋ta＋tab'［s］ ……………………………………………………@9 025 1×106
J･nr tap 03 1.5×106
tab'＝ −
−−−
−−−
−・−
−−−
−−−
−−［s］……………………………………#0
4.77 0.8･Td 04 2×106

They are applied in the case of TR＝0. Generally, the above Micro electromagnetic clutch and brake (unit)
formulas are used when the load torque (TR) is small in full 101・CS・111 model*
measure. Besides, if the calculated value becomes tae' >tap, tab'> Size Total amount of energy E T［J］
tap, apply the formula @2 ∼ @6. 06 36×106
08 60×106
10 130×106
● Study of maximum operation number
12 250×106
The available amount of energy of clutch and brake before air
Electromagnetic clutches and brakes

gap adjustment is determined. If more volume is required, the 16 470×106

space adjustment is necessary. 20 10×108

The operable number before space adjustment is; 25 20×108
qIn a case of clutch ※ Applicable to each model of the unit (except 180 model)

ET CSZ・ BSZ model

Le＝−
−−−[operation] …………………………………………………#1
Ee Size Total amount of energy E T［J］
ET: Total amount of energy before space readjustment［J］ 05 9×106
wIn a case of brake 06 29×106
ET
Lb＝−
−−−[operation] …………………………………………………#2 08 60×106
Eb
180 model
● Study of stopping accuracy Size Total amount of energy E T［J］
To evaluate the stopping accuracy by a formula is difficult since 06 24×106
the friction energy or control system variation is involved. 08 40×106
Generally, it is evaluated empirically by the formula below to 10 62×106
use as a measure. 12 154×106
16 250×106
zStopping angle (θ)
1
［ﾟ］……………………………………#3
θ＝6nr（tid＋ tp＋ ----------- tab）
2
2
OR θ＝6nr（tid＋ta＋ ----------- tab'）
［ﾟ］………………………………#4
3

xStopping accuracy (△θ)

△θ＝±0.15θ［ﾟ］……………………………………………………#5
If there is a factor to disturb the braking effect such as load
fluctuation, change the constant of the formula #5 to 0.2∼ 0.25.
The system delay or variation caused by a backlash of chain or
gear is not included in the stopping angle and accuracy.

,
tp(ta) tab(tab )

nr

0
θ
θ

94
03_特性_E_p076_097.qxd 11.12.7 0:24 PM ページ95

● Selection Example 1 ● Selection Example 2

Clutch used for a continued operation of load Brake to stop the inertia when turning off a motor
Ｍ １ Ｍ １
1：2 1：2

２ C Ｂ ２
Ｗ Ｗ

The selection of clutches used for a continued operation of load The selection of clutches to stop the inertia when turning off a
as above figure is performed as follows. motor as above figure is performed as follows.
Use conditions Use conditions
Used motor output P 0.4kW (Standard three-phase, 4P) Used motor output P 0.75kW (Standard three-phase, 4P)
Clutch operation frequency S 20［operations/min］ Motor rotating velocity n1 1800［min−1］
Load moment of inertia JA 0.0208［kg・m2］ Motor moment of inertia JM 0.00205［kg・m2］
Load torque Tr Unknown［N・m］ V-belt pulley (motor side) moment of inertia J1 0.00075［kg・m2］
Rotating velocity of the clutch mounting shaft n 750［min−1］ V-belt pulley (brake side) moment of inertia J2 0.00243［kg・m2］
Transmission efficiency η 90％ Load moment of inertia JA 0.05［kg・m2］
Load torque Tr 5.0［N・m］
zStudy of torque Rotating velocity of the brake mounting shaft n 900［min−1］
Stop time t Within 0.5［s］
By the above use conditions, evaluate the torque required for
coupling. Evaluate the load torque first. Assume that the motor
is correctly selected. By the formula q, the load torque Tr is; zStudy of torque
By the above use conditions, evaluate the total moment of inertia of the
9550×0.4

Electromagnetic clutches and brakes

TR＝−
−−−
−−−
−−−
−−−
−−×0.9＝4.58［N・m］ brake shaft conversion.
750
1800 2

From the formula r, the acceleration torque is;

JT（−−−900
−
−−
−
−−
−
−−
−
  
 
 ）×（0.00205＋0.00075）＋0.00243＋
0.0208×750 0.05＝0.06363［kg・m2］
Ta＝−−−−−−−−−−−−−−−−＝3.27［N・m］
9.55×0.5 Evaluate the deceleration torque. Since the operating time of
The acceleration torque is given as a condition, but in the above the brake itself is included in the deceleration time, calculate as
formula, it is estimated from the operation frequency as tae= 0.5 1/2 of the given stop time.
[s]. Therefore, by the formula y, the required torque is; By the formula t

T＝（4.58＋3.27）×2＝15.7［N・m］ 0.06363×900
Ta＝−−−−−−−−−−−−−−−−−＝24.0［N・m］
9.55×0.25
The sign of the load torque Tr is plus (+). The factor K by load
condition is empirically determined as K= 2 for general use of By the formula y, the required torque is;
standard load. According to the above information, select the
T＝（24.0−5.0）×2.4＝45.6［N・m］
clutch size 10 (torque 20N・m) that has more than the required
torque 15.7 [N・m]. The sign of the load torque Tr is minus (-). The factor K by load
condition is determined empirically as K =2.4 for general use of
standard load. By the above information, temporally select the
xStudy of energy
brake size 12 (torque 40N・m) that has brake torque equivalent
Determine the model and evaluate the total load moment of
to the required torque 45.6 [N・m].
inertia by the self-moment of inertia J and load moment of
inertia of the model. In the case of model 101-10-13, the rotating
part moment of inertia J is 0.000678 [kg・m2].
xStudy of energy
Therefore, the total moment of inertia J is;
Determine the model and evaluate the total load moment of
JT’＝0.0208＋0.000678＝0.02148［kg・m2］
inertia by the self-moment of inertia J and load moment of
By the formula !1, evaluate the single engaging energy Ee.
inertia. In the case of model 111-12-11, the moment of inertia of
0.02148×7502 20 the armature is 0.00181 [kg・m2].
Ee＝−
−−−−−−−−−−−−−− ×−−
−−−
−−−
−−−
−−−
−＝86.1［J］
182 （20−4.58） Therefore, the total moment of inertia JT' is;

The sign of the load torque Tr is minus (-). The engaging JT'＝0.06363＋0.00181＝0.06544［kg・m2］
energy E e is smaller than the allowable energy E ear in full
By the formula !2, evaluate the single braking energy Eb.
measure.
Ee≪EeaR 0.06544×9002 40
Eｂ＝−−−−−−−−−−−−−−− ×−−
−
−−
−−
−−
−
−−
−−
−
  
 ＝258.9［J］
Then, evaluate the energy rate by the formula !8. 182 （40＋5）

The sign of the load torque Tr is plus (+). The braking energy
86.1×20
Pe＝−
−−−
−−−
−−−
−−−
−−＝28.7［W］ Eb is smaller than the allowable energy Ebear in full measure.
60

This value is smaller than the allowable energy rate Pear in full Eb≪EbaR
measure, which means that the clutch corresponds to the use
condition, therefore select the model 101-10-13.

95
03_特性_E_p076_097.qxd 11.12.7 0:24 PM ページ96

cStudy of operating time When the factor K by load condition is determined empirically
By the formula @5, evaluate the braking time. as K= 2 for general use of standard load, the clutch is;
0.06544×900
tab＝−
−−−−−−−−−−−−−− ＝0.137［s］ T＝（24.5＋14.7）×2＝78.4［N・m］
9.55×（40＋5）
The sign of the load torque Tr is plus (+). And the armature The brake is;
suction time of the size 12 is 0.027 [s] by the specification table. T＝（24.5−14.7）×2＝19.6［N・m］
And the initial lagging time is 0.05 [s].
By the formula @3, According to the above information select the clutch size 16
(torque 80N・ｍ) and the brake size 10 (torque 20N・m).
ttb＝0.05＋0.027+0.137＝0.214［s］

This value meets the requirement of below 0.5 [s], which means xStudy of energy
that the brake corresponds to the use conditions, therefore
Determine the model and evaluate the total load moment of
select the model 111-12-11.
inertia by the self-moment of inertia J and load moment of
inertia of the model. In the case of clutch model 101-16-15, the
● Selection Example 3
rotating part moment of inertia J is 0.0063 [kg・m2]. And in the case
Clutch and brake to drive a load
of brake model 111-10-11, the armature moment of inertia is
3 0.000663 [kg・m2].
Ｗ Therefore, the total moment of inertia JT' is;
Ｍ Ｇ １
1：1 2：3 JT'＝0.2349＋0.0063＋0.000663＝0.2419［kg・m2］
１ C Ｂ ２ By the formula !1, evaluate the single coupling energy of clutch
Electromagnetic clutches and brakes

［s］
1.5 0.5 Ee.
0.2419×1502 80
The selection of clutches and brakes to drive a load as above Ee＝−
−−−−−−−−−−−−−− ×−−
−−−
−−−
−−−
−−−
−＝36.6［J］
182 （80−14.7）
figure is performed as follows.
Usage conditions By the formula !2, evaluate the single braking energy of brake
Operation frequency S 30 [operations/min]
Eb.
Maximum operating number *1 L 810×104 [operations] or more
V-belt pulley A moment of inertia J1 0.00195 [kg・m 2 ] 0.2419×1502 20
V-belt pulley B moment of inertia J2 0.01668 [kg・m 2 ] Eｂ＝−
−−−−−−−−−−−−−− ×−−
−−−
−−−
−−−
−−−
−＝17.2［J］
182 （20＋14.7）
Load moment of inertia JA 0.5075 [kg・m 2 ]
Load torque Tr 22.0 [N・m]
Rotating velocity of the clutch and brake mounting shaft n 150 [min −1 ] This value meets the requirements for the allowable energy and
Rotating velocity of the load shaft n2 100 [min −1 ] the amount of energy per minute of the selected model.
Coupling time t1 Within 0.3 [s]
Stop time t2 Within 0.3 [s]
*1 When it is used 15 hours a day with no adjustment over a year, L= 30 x 60 min x 15 hours x 300 days=
8,100,000 times
cStudy of maximum operation number
Evaluate the number of operations next. By the specification
zStudy of torque table for each model, the total energy of the size 16 is (470×106)
By the above conditions, convert the load torque into the clutch [J], and for the size 10 is (130×10 6) [J]. Therefore, by the
and brake shaft. From the formula !0, formula #1 and #2, the clutch is;
2
TR＝22.0×−−− ＝14.7［N・m］
3 470×106
L＝−
−−−
−−−
−−−
−−−
−−＝1284×104［operations］
36.6

Convert all the inertia moment of rotating part into the clutch The brake is;
and brake shaft.
2

JT＝J1＋（J2＋JA）× （−−23−） 130×106

L＝−
−−−
−−−
−−−
−
17.2
−−
− ＝756×104［operations］
2
2
＝0.00195＋（0.01668＋0.5075）× （−3−−） The required maximum operating numbers are approximately
＝0.2349［kg・m ］ 2 8,100,000 that the size 10 can't meet the requirement. When
changing the model to 111-12-11 for a review, it becomes as
Since the operating time of the clutch and brake is included in below and meets the requirement. (The calculation process is
the acceleration time, calculate as 1/2 of the given coupling time omitted.)
0.3 [s].
By the formula r, 250×106
L＝−
−−
−−−
−−−
−−−
−−−＝1136×104［operations］
22.0
0.2349×150
Ta＝−−−−−−−−−−−−−−−−−＝24.6［N・m］
9.55×0.15
Therefore, the appropriate clutch model is 101-16-15 and brake
By the formula y, the required torque T is; model is 111-12-11 for this example.
T＝（24.5±14.7）×K［N・m］

96
03_特性_E_p076_097.qxd 11.12.7 0:24 PM ページ97

● Selection example 4 rStudy of stopping accuracy

Clutch and brake used for two-stage speed change single-stop Initial lagging time is 0.05 [s].
mechanism By the formula #4, the stopping angle is;
2
D
θ＝6×50× （0.05+0.027＋−−3−−×0.0294）
＝28.98［ﾟ］

Rotating velocity
C C １ 1：4
n1
From the formula #5, the stopping accuracy is;
２ Ｂ
n2 △θ＝±0.15×28.98＝±4.35［ﾟ］

E Time When converting the roll diameter to the circumferential length,

The selection that includes the stopping accuracy of the clutch it becomes ±2.3 [mm].
and brake to drive a load is performed as follows. xStudy of clutch
Usage conditions qStudy of energy
Maximum input rotating velocity n1 1500 [min −1 ]
By the above conditions, evaluate the total moment of inertia
Minimum input rotating velocity n2 200 [min −1 ]
Roll shaft rotating velocity n3 50 [min −1 ] converted to the clutch shaft.
Operation frequency S 12 [operations/min] JT’＝0.000475＋0.000025＋
Maximum operating number *1 L 130×104 [operations] or more
Pulley D moment of inertia J1 0.000025 [kg・m 2 ] 1 2

Pulley E moment of inertia J2 0.005375 [kg・m 2 ] （0.00181＋0.0133×2＋0.005375）× （−−4−）

Roll moment of inertia JA 0.0133 [kg・m 2 ]
Roll load torque Tr 8.0 [N・m] ＝0.0026［kg・m2］
Roll diameter R 60 [mm]
*1 When it is used 6 hours a day with no adjustment over a year, L= 12 x 60 min x 6 hours x 300 days= By using the formula !0, convert the load torque to the clutch

Electromagnetic clutches and brakes

1,300,000 times shaft.
zStudy of brake 1
TR＝8.0×−−− ＝2.0［N・m］
qStudy of energy 4

By the above conditions, evaluate the total moment of inertia for By the formula !1, the single coupling energy Ee of the high-
conversion of the feed roll shaft. Assuming that the inertia of speed side clutch is;
rotating part of the clutch brake unit type 121-08-10 is 0.000475 0.0026×15002 10
[kg・m2], and the armature inertia moment of the brake model Ee＝−
−−−−−−−−−−−−−− ×−−
−
−−
−−
−−
−
−−
−−
−
  
 ＝40.2［J］
182 （10−2）
111-12-12 is 0.00181 [kg・m2],
This value meets the requirement for the allowable energy of
JT＝0.0133×2＋0.00181＋0.005375 the selected model. Evaluate the coupling energy rate Pe next.
2
4
＋（0.000025＋0.000475）× （ ） −−−
1
By the formula !8,
40.2×12
＝0.04179［kg・m ］ 2 Pe＝−
−−−
−−−
−−−
−−−
−−＝8.04［W］
60

By the formula !2, evaluate the single braking energy Eb. This value is smaller than the allowable work rate Pr in full
measure.
0.04179×502 40
Eｂ＝−−−−−−−−−−−−−−−×−−
−−
−−
−−
−−
−−
−−
− 
  
＝0.48［J］
182 （40＋8） wStudy of operation numbers
The sign of the load torque Tr is Plus (+). This value meets the Evaluate the number of operations by the formula #1.
requirements for the allowable energy and the amount of 60×106
energy per minute of the selected model. L＝−
−−
−−−
−−−
−−−
−−−＝149×104［operations］
40.2

wStudy of operation numbers The number of operations in one year is about 1,300,000, which
Evaluate the number of operations next. The total energy of the satisfies the requirement.
size 12 is (250×10 ) [J] that by the formula #2,
6

By the formula !2, the single coupling energy Ee of the low-

250×106 speed side clutch is;
L＝−
−−
−−−
−−−
−−−
−−−＝52083×104［operations］
0.48
2
0.0026×（1500−200） 10
This value meets the requirement in full measure. Ee＝−−−−−−−−−−−−−
−−−
−−−
−−−
−−−  
 ×−−
−−
−
−−
−−
−
−−
−−
 
  ＝20.1［J］
182 （10＋2）

eStudy of operating time This clutch decelerates the load from 1500 [minー1] to 200 [minー1],
Evaluate the braking time. Either the formula @5 or #0 is applied. which is similar actions as brake. Therefore, the sign of the load
In this case, apply the formula #0 to shorten the braking time. torque is Plus (+).
Assume that the torque increment time tap is 0.063 [s]. Also, it is clear that the value meets the requirements of
By the formula #0, the braking time tab' is; operating life number since it is smaller than the high-speed
side clutch.
0.04179 ×50 0.063 By the above information, both clutch and brake meet the
tab’＝ −−−−−−−−−−−−−−− ×−
−−−−−
−−−−
−−＝0.0294［s］
4.77 （0.8×40） requirements.

97
08_安全注意_E_p174-175.qxd 11.10.17 3:57 PM ページ174

Safety Precautions (Please read prior to use)

Please look carefully through the instruction manual and the technical ■ 2.Mounting precautions
information for proper use and safety. In this manual, safety precautions are
classified by "DANGER" and "CAUTION".
●Carry and mount the product by using a
CAUTION
hoist, etc.

DANGER Lifting of a heavy weight could cause back injury.

Use a hoist, etc. when carrying or mounting the
● Death or serious injury may be caused by product.
mishandling

CAUTION
● Disability or physical damage may be caused by ●Bolt tightening torque and slack prevention
DANGER
mishandling must be done completely.

Please contact Miki Pulley for the following applications: atomic energy, Tighten all bolts to their recommended torque
aerospace, medical treatment, transportation, or various safety devices. tightening specification. Failure to tighten the
These applications may result in serious bodily injury or loss of life directly by bolts to the proper tightening specification may
mechanical failure or mishandling, careful examination of the application is result in fatigue and premature failure of the
necessary. Contact Miki Pulley for further information. bolted connection. The use of a thread adhesive
Miki Pulley takes all possible measures to insure quality products. and/or a spring washer is recommended.
Operational consideration such as a continuous rotational state when the
clutch cannot be disengaged or the coasting of the machine when the
brakes disengage may cause injury or death. Please maintain and properly
operate all equipment in order to prevent injury or death.
■ 3.Wiring precautions

●Make sure to connect the motor and the earth

■ 1.Structural precautions DANGER
terminal of the controller to the ground.

●Do not use in explosive or flammable The third ground (below (100), above (1.6)) is
DANGER
atmospheres. suggested as a means of grounding.

Sparks may occur by startup or braking slip. Do

not use the product near flammable liquids or in
gaseous or explosive atmospheres.
If brake or clutch is used in a explosive or flammable
environment then the main unit must be contained in a
sealed unit, not exposed to the atmosphere. ●Use the appropriate wire size in
DANGER
accordance with the current capacity.

An electrical shock or a short circuit can result

DANGER ●Make sure to use a safety cover.
from insulation failure. Which may result in fire.

Due to the rotating system, touching the product

could cause injury. Use a breathable safety cover to
avoid any accident. Also, set up a safety
mechanism for quick stop of the rotating body.

■ 4.Cautions before operation

● Do not use in explosive or flammable

DANGER ●Please check the surrounding environment. DANGER
atmospheres.

Do not use in a place where the product is exposed to Spark may occur by starting or brake slippage. Do not
dust, high temperature, dew condensation, wind or rain. operate the product near flammable liquids or in
Also, do not set the product directly in a place where the gaseous or explosive atmospheres. If brake or clutch is
product is subjected to shock and vibration. These used in a explosive or flammable environment then the
could lead to damage, malfunction or performance main unit must be contained in a sealed unit, not
degradation of the product. exposed to the atmosphere.

174
08_安全注意_E_p174-175.qxd 11.10.17 3:57 PM ページ175

■ 5.Cautions during operation ■ 6.Cautions for maintenance and inspection

●Do not operate the product beyond its

DANGER DANGER ●Do not apply any water or grease.
maximum rpm limit.

If the product's maximum rpm limit is reached, vibrations If water or grease is applied on the friction surface or
may cause damage to the product. It may also result in the body, its torque will be significantly reduced. It can
injury. Keep all operational speeds below the maximum rpm cause the machine to go out of control. It can also lead
limits. to injury.

DANGER ●Do not touch the product during operation. DANGER ●Do not turn on the power to the machine.

Due to the exposed rotor, touching the product When performing any service on clutch or brake all
during operation may cause injury. Make sure not to machine power must be turned off. Serious injury
touch the product during operation. All rotating may occur if machine is started during service.
parts should have a safety guard.

DANGER ●Do not touch the product during operation. DANGER ●Do not dismantle the product.

The surface temperature of the product could increase We will refuse to take responsibility for any damaged
up to 90℃~ 100℃ by heat generation caused by product that is dismantled, remodeled or repaired by a
slippage or built-in coil. Touching the product during third party except our company and the designated
operation may cause a burn injury. Additionally, the company.
surface temperature will not decrease Please use our authorized service network for repair and
immediately.Make sure that the temperature is low dismantlement.
enough when disassembling or checking the product.

●The surface of the body could reach a high

CAUTION ■ 7.Cautions for disposal
temperature just by turning on electricity.

Heat generation of the built-in coil, the surface ●Do not leave the product around where
DANGER
temperature could become high just by turning on young children may play.
electricity. Make sure that the temperature is low
enough to prevent a burn injury.
●Properly dispose of all electrical
CAUTION components in accordance with local
laws and regulations.

●In case of abnormal noises or vibrations,

CAUTION
stop operation immediately.

If abnormal noises or vibrations occur during operation,

improper mounting should be considered. Do not leave the
situation as it is. It may cause damage to the clutch and
brake or the equipment itself.

●Voltage variation must be within ±10%. For

CAUTION the model 546 (Toothed clutch), it must be
within +5% and -10%.

An incorrect voltage may cause performance problems

or fire. Cautions for maintenance and inspection.

Please note that these safety precautions and specifications described in each manual may be changed without prior notice.
If you have any problem or question on these precautions, contact us.

175
08_技術資料_E_p176_203.qxd 11.11.10 3:07 PM ページ176

〈Technical Data〉
Inertia moment J calculation formulas
● Inertia moment of a hollow circular cylinder
D
D : Outside diameter of cylinder [m]
d : Inside diameter of cylinder [m]
M : Mass of cylinder [kg]

1
ー （D2＋d2）[ kg・m2 ]
J =  M
8
d

● Inertia moment of a hollow circular cylinder with different rotation center

r : Rotation radius [m]

A M : Mass of cylinder [kg]
JA : Inertia moment of center A rotation [kg÷Em2]
r

J = JA＋M・r 2 [ kg・m2 ]

● Inertia moment of a rotating bar

L : Length of bar [m]
M: Mass of bar [kg]

1
ー M・L2 [ kg・m2 ]
J = 
L 12

● Inertia moment of a bar with different rotation center

L1, L2: Distance from rotation center [m]
M : Mass of bar [kg]

1
ーM（L12＋L1L2＋L 22）[ kg・m2 ]
J = 
12
L2

L1
Technical Data

● Inertia moment of a rectangular solid

b
a, b : Length of side [m]
M : Mass of rectangular solid [kg]

1
ーM（a2＋b2）[ kg・m2 ]
J = 
12
a

● Inertia moment of a linear-motion object

P : Lead of feed screw [m]
M : Load mass [kg]
M
JA : Inertia moment of feed screw [kg÷Em2]

M・P2
J =JA＋   2 [ kg・m2 ]
4π

176
08_技術資料_E_p176_203.qxd 11.11.10 3:07 PM ページ177

● Inertia moment of a winding machine

D
JA : Inertia moment of drum [kg÷Em2]
D : Diameter of drum [m]
M : Load mass [kg]

1
ーM・D2 [ kg・m2 ]
J =JA＋ 
4
M

● Inertia moment of a belt conveyer

M D JA : Inertia moment of roller [kg÷Em2]
D : Diameter of roller [m]
M : Load mass [kg]

1
ーM・D2 [ kg・m2 ]
J =JA＋ 
4

● Inertia moment when running on a rack pinion

Rack M JA : Inertia moment of pinion [kg÷Em2]

D : Diameter of pinion [m]
M : Mass of rack and load [kg]

D 1
ーM・D2 [ kg・m2 ]
J =JA＋ 
4
Pinion

● Inertia moment with a counter balance

D

JA : Inertia moment of drum [kg÷Em2]

D : Diameter of drum [m]
M1, M2 : Mass [kg]

M2 1
ー
J =JA＋  D2 [ kg・m2 ]
（M1＋M2）
4
M1

● Inertia moment of a work between rollers

DA JA : Inertia moment of roller A [kg÷Em2]
Technical Data

Roller A Work JB : Inertia moment of roller B [kg÷Em2]

M DA : Diameter of roller A [m]
DB : Diameter of roller B [m]
M : Equivalent mass of work [kg]
Roller B
DA 2 1 2 
J = JA＋
（   ） ーM・DA [ kg・m2 ]
JB＋ 
DB 4
DB

● Inertia moment of a motor shaft conversion

Z1 : Teeth number of motor-side gear
Z2 : Teeth number of load-side gear
R Gear ratio Z1/Z2
JA : Inertia moment of load [kg÷Em2]
Load
J1 : Inertia moment of motor-side gear [kg÷Em2]
J2 : Inertia moment of load-side gear [kg÷Em2]
Motor
2
J =J1+（JA＋J2）R [ kg・m2 ]

177
08_技術資料_E_p176_203.qxd 11.11.10 3:07 PM ページ178

Inertia moment J quick reference matrix

This table indicates the J [kg/m2] of a circular disc with a steel Cast iron 0.93
(ratio 7.85) thickness of 10mm and diameter of Dmm. The value per Aluminum 0.33
10mm is indicated in the vertical direction and the value per 1mm Copper 1.1
increment is indicated in the horizontal direction. For discs other than
For an aluminum disc with a diameter of 205mm and thickness of
10mm, the value can be evaluated by dividing the thickness
20mm, the value (0.0089826 [kg÷m2]) can be evaluated by
Rmm by 10mm and multiplying the value by the value in the
multiplying 2 by the intersection value 0.01361 in the 200 Dia. row and
table. For materials other than steel, the value can be evaluated by
in the 5J column and multiplying the value by the material factor 0.33.
multiplying respective factors by the value in the table.

Dia. J〔kg・m2〕
〔mm〕 0 1 2 3 4 5 6 7 8 9
10 0.000000077 0.000000113 0.000000160 0.000000220 0.000000296 0.000000390 0.000000505 0.000000644 0.000000809 0.00000104
20 0.00000123 0.00000150 0.00000181 0.00000216 0.00000256 0.00000301 0.00000352 0.00000410 0.00000474 0.00000545
30 0.00000624 0.00000712 0.00000808 0.00000914 0.00001030 0.00001156 0.00001294 0.00001444 0.00001607 0.00001783
40 0.00001973 0.00002178 0.00002398 0.00002635 0.00002889 0.00003160 0.00003451 0.00003761 0.00004091 0.00004443
50 0.00004817 0.00005214 0.00005635 0.00006081 0.00006553 0.00007052 0.00007579 0.00008135 0.00008721 0.00009339
60 0.00009988 0.0001067 0.0001139 0.0001214 0.0001293 0.0001376 0.0001462 0.0001553 0.0001648 0.0001747
70 0.0001850 0.0001958 0.0002071 0.0002189 0.0002311 0.0002439 0.0002571 0.0002709 0.0002853 0.0003002
80 0.0003157 0.0003317 0.0003484 0.0003657 0.0003837 0.0004023 0.0004216 0.0004415 0.0004622 0.0004835
90 0.0005056 0.0005285 0.0005521 0.0005765 0.0006017 0.0006277 0.0006546 0.0006823 0.0007108 0.0007403
100 0.0007707 0.0008020 0.0008342 0.0008674 0.0009016 0.0009368 0.0009730 0.001010 0.001048 0.001088
110 0.001128 0.001170 0.001213 0.001257 0.001302 0.001348 0.001395 0.001444 0.001494 0.001545
120 0.001598 0.001652 0.001707 0.001764 0.001822 0.001882 0.001942 0.002005 0.002069 0.002134
130 0.002201 0.002270 0.002340 0.002411 0.002485 0.002560 0.002636 0.002715 0.002795 0.002877
140 0.002961 0.003046 0.003133 0.003223 0.003314 0.003407 0.003502 0.003599 0.003698 0.003799
150 0.003902 0.004007 0.004114 0.004223 0.004335 0.004448 0.004564 0.004682 0.004803 0.004926
160 0.005051 0.005178 0.005308 0.005440 0.005575 0.005712 0.005852 0.005994 0.006139 0.006287
170 0.006437 0.006590 0.006745 0.006903 0.007064 0.007228 0.007395 0.007564 0.007737 0.007912
180 0.008090 0.008271 0.008456 0.008643 0.008834 0.009027 0.009224 0.009424 0.009627 0.009834
190 0.01004 0.01026 0.01047 0.01069 0.01092 0.01114 0.01137 0.01161 0.01184 0.01209
200 0.01233 0.01258 0.01283 0.01309 0.01335 0.01361 0.1388 0.01415 0.01443 0.01470
210 0.01499 0.01528 0.01557 0.01586 0.01616 0.01647 0.01678 0.01709 0.01741 0.01773
220 0.01805 0.01838 0.01872 0.01906 0.01940 0.01975 0.02010 0.02046 0.02083 0.02119
230 0.02157 0.02194 0.02233 0.02271 0.02311 0.02350 0.02391 0.02431 0.02473 0.02515
240 0.02557 0.02600 0.02643 0.02687 0.02732 0.02777 0.02822 0.02869 0.02915 0.02963
250 0.03010 0.03059 0.03108 0.03158 0.03208 0.03259 0.03310 0.03362 0.03415 0.03468
260 0.03522 0.03576 0.03631 0.03687 0.03744 0.03801 0.03858 0.03917 0.03976 0.04035
270 0.04096 0.04157 0.04218 0.04281 0.04344 0.04408 0.04472 0.04537 0.04603 0.04670
280 0.04737 0.04805 0.04874 0.04943 0.05014 0.05085 0.05156 0.05229 0.05302 0.05376
290 0.05451 0.05526 0.05603 0.05680 0.05758 0.05837 0.05916 0.05996 0.06078 0.06160
300 0.06242 0.06326 0.06411 0.06496 0.06582 0.06669 0.06757 0.06846 0.06935 0.07026
310 0.07117 0.07210 0.07303 0.07397 0.07492 0.07588 0.07685 0.07782 0.07881 0.07981
320 0.08081 0.08183 0.08285 0.08388 0.08493 0.08598 0.08704 0.08812 0.08920 0.09029
330 0.09140 0.09251 0.09363 0.09476 0.09591 0.09706 0.09823 0.09940 0.10059 0.10178
340 0.10299 0.10420 0.10543 0.10667 0.10792 0.10918 0.11045 0.11173 0.11303 0.11433
350 0.11565 0.11698 0.11832 0.11967 0.12103 0.12240 0.12379 0.12518 0.12659 0.12801
360 0.12944 0.13089 0.13234 0.13381 0.13529 0.13679 0.13829 0.13981 0.14134 0.14288
Technical Data

370 0.14444 0.14600 0.14758 0.14918 0.15078 0.15240 0.15404 0.15568 0.15734 0.15901
380 0.16070 0.16239 0.16411 0.16583 0.16757 0.16932 0.17109 0.17287 0.17466 0.17647
390 0.17829 0.18013 0.18198 0.18384 0.18572 0.18761 0.18952 0.19144 0.19338 0.19533
400 0.19729 0.19927 0.20127 0.20328 0.20530 0.20734 0.20940 0.21147 0.21356 0.21566
410 0.21777 0.21991 0.22205 0.22422 0.22640 0.22859 0.23080 0.23303 0.23527 0.23753
420 0.23981 0.24210 0.24441 0.24674 0.24908 0.25143 0.25381 0.25620 0.25861 0.26103
430 0.26348 0.26594 0.26841 0.27091 0.27342 0.27595 0.27849 0.28106 0.28364 0.28624
440 0.28886 0.29149 0.29414 0.29681 0.29950 0.30221 0.30494 0.30768 0.31044 0.31322
450 0.31602 0.31884 0.32168 0.32454 0.32741 0.33030 0.33322 0.33615 0.33910 0.34207
460 0.34506 0.34808 0.35111 0.35416 0.35722 0.36031 0.36342 0.36655 0.36970 0.37287
470 0.37606 0.37927 0.38251 0.38576 0.38903 0.39232 0.39564 0.39897 0.40233 0.40571
480 0.40910 0.41252 0.41597 0.41943 0.42291 0.42642 0.42995 0.43350 0.43707 0.44066
490 0.44428 0.44791 0.45158 0.45526 0.45896 0.46269 0.46644 0.47021 0.47401 0.47783
500 0.48167 0.48553 0.48942 0.49333 0.49727 0.50123 0.50521 0.50922 0.51324 0.51730

178
08_技術資料_E_p176_203.qxd 11.11.10 3:07 PM ページ179

Load torque calculation formulas

● Torque: T when an external force is added to the rotating body

F D D : Diameter of drum [m]

F : External force [N]

1
ーD・F [ N・m]
T = 
2

● Torque: T by frictional and external forces of a feed screw

P : Lead of feed screw [m]
M: Load mass [kg]
g : Acceleration of gravity [m/s2]
M F
μ: Friction factor of feed screw
F : External force [N]

1
T=   P（F＋μMg）[ N・m]
2π
(In ordinary practice, μ: 0.05∼0.2)
● Torque: T by frictional and external forces of a rack pinion
D : Diameter of pinion [m]
F M: Load mass [kg]
Rack M g : Acceleration of gravity [m/s2]
μ: Friction factor of Rack pinion
F : External force [N]
D
1
ーD
T=  （F＋μMg）[ N・m]
Pinion 2
(In ordinary practice, μ: 0.08∼0.1)
● Torque: T by frictional and external forces of a belt conveyer
D : Diameter of roller [m]
M F
M: Load mass [kg]
D
g : Acceleration of gravity [m/s2]
η: Friction factor of conveyer
F : External force [N]

1
ーD
T=  （F＋μMg）[ N・m]
2
(In ordinary practice, μ: 0.05∼0.1)
● Torque: To of a motor shaft conversion
Technical Data

Z1 : Teeth number of motor-side gear

Z2 : Teeth number of load-side gear
R : Gear ratio Z1/Z2
Load
η: Transmission efficiency %/100
T : Load-side torque [N・Em]
Motor
R・T
TO=  η  [ N・m ]

* The value of each friction factor μ varies depending on the processing accuracy or lubricated condition of the machine.
* The transmission efficiency η between motor and load is different depending on the connection method. In general, it is as follows.
Spur gear: 0.85 Chain: 0.9 V-belt: 0.9

179
 Technical Data

Unit ［μm］
Measurement Measurement

180
Classification［mm］ d e f g h js j k m n p r Classification［mm］
Over Incl. d8 d9 e7 e8 e9 f6 f7 f8 g5 g6 h5 h6 h7 h8 h9 js5 js6 js7 j5 j6 k5 k6 m5 m6 n6 p6 r6 Over Incl.
−30 −30 −20 −20 −20 −10 −10 −10 −4 − 4 0 0 0 0 0 ＋3 ＋6 ＋6 ＋9 ＋9 ＋12 ＋16 ＋20 ＋23
3 6 ±2.5 ±4 ±6 3 6
−48 −60 −32 −38 −50 −18 −22 −28 −9 −12 −5 −8 −12 −18 −30 −2 −2 ＋1 ＋1 ＋4 ＋ 4 ＋ 8 ＋12 ＋15
−40 −40 −25 −25 −25 −13 −13 −13 − 5 −5 0 0 0 0 0 ＋4 ＋7 ＋7 ＋10 ＋12 ＋15 ＋19 ＋24 ＋28
6 10 ±3 ±4.5 ±7.5 6 10
−62 −76 −40 −47 −61 −22 −28 −35 −11 −14 −6 −9 −15 −22 −36 −2 −2 ＋1 ＋ 1 ＋ 6 ＋ 6 ＋10 ＋15 ＋19
10 14 −50 −50 −32 −32 −32 −16 −16 −16 −6 −6 0 0 0 0 0 ＋5 ＋8 ＋9 ＋12 ＋15 ＋18 ＋23 ＋29 ＋34 10 14
±4 ±5.5 ±9
14 18 −77 −93 −50 −59 −75 −27 −34 −43 −14 −17 −8 −11 −18 −27 −43 −3 −3 ＋1 ＋ 1 ＋ 7 ＋ 7 ＋12 ＋18 ＋23 14 18
18 24 −65 − 65 −40 −40 −40 −20 −20 −20 −7 −7 0 0 0 0 0 ＋5 ＋9 ＋11 ＋15 ＋17 ＋21 ＋28 ＋35 ＋41 18 24
±4.5 ±6.5 ±10.5
24 30 −98 −117 −61 −73 −92 −33 −41 −53 −16 −20 −9 −13 −21 −33 −52 −4 −4 ＋ 2 ＋ 2 ＋ 8 ＋ 8 ＋15 ＋22 ＋28 24 30
30 40 − 80 − 80 −50 −50 − 50 −25 −25 −25 −9 −9 0 0 0 0 0 ＋6 ＋11 ＋13 ＋18 ＋20 ＋25 ＋33 ＋42 ＋50 30 40
±5.5 ±8 ±12.5
40 50 −119 −142 −75 −89 −112 −41 −50 −64 −20 −25 −11 −16 −25 −39 −62 −5 − 5 ＋ 2 ＋ 2 ＋ 9 ＋ 9 ＋17 ＋26 ＋34 40 50
＋60
50 65 50 65
−100 −100 −60 − 60 − 60 −30 −30 −30 −10 −10 0 0 0 0 0 ＋6 ＋12 ＋15 ＋21 ＋24 ＋30 ＋39 ＋51 ＋41
08_技術資料_E_p176_203.qxd 11.11.10 3:07 PM ページ180

±6.5 ±9.5 ±15

−146 −174 −90 −106 −134 −49 −60 −76 −23 −29 −13 −19 −30 −46 −74 −7 − 7 ＋ 2 ＋ 2 ＋11 ＋11 ＋20 ＋32 ＋62
65 80 ＋43
65 80
(Excerpts from JIS B 0401)

＋73
80 100 80 100
−120 −120 − 72 − 72 − 72 −36 −36 −36 −12 −12 0 0 0 0 0 ＋6 ＋13 ＋18 ＋25 ＋28 ＋35 ＋45 ＋59 ＋51
±7.5 ±11.5 ±17.5
−174 −207 −107 −126 −159 −58 −71 −90 −27 −34 −15 −22 −35 −54 −87 −9 − 9 ＋ 3 ＋ 3 ＋13 ＋13 ＋23 ＋37 ＋76
100 120 ＋54
100 120

＋88
120 140 ＋63
120 140

−145 −145 − 85 − 85 − 85 −43 −43 − 43 −14 −14 0 0 0 0 0 ＋ 7 ＋14 ＋21 ＋28 ＋33 ＋40 ＋52 ＋68 ＋90
140 160 −208 −245 −125 −148 −185 −68 −83 −106 −32 −39 −18 −25 −40 −63 −100 ±9 ±12.5 ±20 −11 −11 ＋ 3 ＋ 3 ＋15 ＋15 ＋27 ＋43 ＋65 140 160

＋93
160 180 ＋68
160 180

＋106
180 200 ＋ 77
180 200

−170 −170 −100 −100 −100 −50 −50 −50 −15 −15 0 0 0 0 0 ＋ 7 ＋16 ＋24 ＋33 ＋37 ＋46 ＋60 ＋79 ＋109
200 225 −242 −285 −146 −172 −215 −79 −96 −122 −35 −44 −20 −29 −46 −72 −115 ±10 ±14.5 ±23 −13 −13 ＋ 4 ＋ 4 ＋17 ＋17 ＋31 ＋50 ＋ 80 200 225

＋113
225 250 ＋ 84
225 250

＋126
250 280 250 280
−190 −190 −110 −110 −110 −56 − 56 − 56 −17 −17 0 0 0 0 0 ＋ 7 ＋16 ＋27 ＋36 ＋43 ＋52 ＋66 ＋88 ＋ 94
±11.5 ±16 ±26
−271 −320 −162 −191 −240 −88 −108 −137 −40 −49 −23 −32 −52 −81 −130 −16 −16 ＋ 4 ＋ 4 ＋20 ＋20 ＋34 ＋56 ＋130
280 315 ＋ 98
280 315

＋144
315 355 315 355
−210 −210 −125 −125 −125 −62 − 62 − 62 −18 −18 0 0 0 0 0 ＋7 ＋18 ＋29 ＋40 ＋46 ＋57 ＋73 ＋98 ＋108
±12.5 ±18 ±28.5
−299 −350 −182 −214 −265 −98 −119 −151 −43 −54 −25 −36 −57 −89 −140 −18 −18 ＋ 4 ＋ 4 ＋21 ＋21 ＋37 ＋62 ＋150
355 400 ＋114
355 400

＋166
Permissible dimensional shaft deviations

400 450 400 450

−230 −230 −135 −135 −135 − 68 − 68 − 68 −20 −20 0 0 0 0 0 ＋ 7 ＋20 ＋32 ＋45 ＋50 ＋63 ＋80 ＋108 ＋126
±13.5 ±20 ±31.5
−327 −385 −198 −232 −290 −108 −131 −165 −47 −60 −27 −40 −63 −97 −155 −20 −20 ＋ 5 ＋ 5 ＋23 ＋23 ＋40 ＋ 68 ＋172
450 500 ＋132
450 500

* The upper value in each column indicates the upper deviation, and the lower value in each column indicates the lower deviation.
 Unit ［μm］
Measurement Measurement
Classification［mm］ E F G H Js J K M N P R Classification［mm］
Over Incl. E7 E8 E9 F6 F7 F8 G6 G7 H5 H6 H7 H8 H9 H10 Js6 Js7 J6 J7 K6 K7 M6 M7 N6 N7 P7 R7 Over Incl.
＋32 ＋38 ＋50 ＋18 ＋22 ＋28 ＋12 ＋16 ＋5 ＋8 ＋12 ＋18 ＋30 ＋48 ＋5 ＋6 ＋2 ＋3 −1 0 − 5 − 4 − 8 −11
3 6 ±4 ±6 3 6
＋20 ＋20 ＋20 ＋10 ＋10 ＋10 ＋ 4 ＋ 4 0 0 0 0 0 0 −3 −6 −6 −9 −9 −12 −13 −16 −20 −23
＋40 ＋47 ＋61 ＋22 ＋28 ＋35 ＋14 ＋20 ＋6 ＋9 ＋15 ＋22 ＋36 ＋58 ＋5 ＋8 ＋2 ＋ 5 − 3 0 − 7 − 4 − 9 −13
6 10 ±4.5 ±7.5 6 10
＋25 ＋25 ＋25 ＋13 ＋13 ＋13 ＋ 5 ＋ 5 0 0 0 0 0 0 −4 −7 −7 −10 −12 −15 −16 −19 −24 −28
10 14 ＋50 ＋59 ＋75 ＋27 ＋34 ＋43 ＋17 ＋24 ＋8 ＋11 ＋18 ＋27 ＋43 ＋70 ＋6 ＋10 ＋2 ＋ 6 − 4 0 − 9 − 5 −11 −16 10 14
±5.5 ±9
14 18 ＋32 ＋32 ＋32 ＋16 ＋16 ＋16 ＋ 6 ＋ 6 0 0 0 0 0 0 −5 − 8 −9 −12 −15 −18 −20 −23 −29 −34 14 18
18 24 ＋61 ＋73 ＋92 ＋33 ＋41 ＋53 ＋20 ＋28 ＋9 ＋13 ＋21 ＋33 ＋52 ＋84 ＋8 ＋12 ＋ 2 ＋ 6 − 4 0 −11 − 7 −14 −20 18 24
±6.5 ±10.5
24 30 ＋40 ＋40 ＋40 ＋20 ＋20 ＋20 ＋ 7 ＋ 7 0 0 0 0 0 0 −5 − 9 −11 −15 −17 −21 −24 −28 −35 −41 24 30
30 40 ＋75 ＋89 ＋112 ＋41 ＋50 ＋64 ＋25 ＋34 ＋11 ＋16 ＋25 ＋39 ＋62 ＋100 ＋10 ＋14 ＋ 3 ＋ 7 − 4 0 −12 − 8 −17 −25 30 40
±8 ±12.5
40 50 ＋50 ＋50 ＋ 50 ＋25 ＋25 ＋25 ＋ 9 ＋ 9 0 0 0 0 0 0 − 6 −11 −13 −18 −20 −25 −28 −33 −42 −50 40 50
−30
50 65 −60
50 65
＋90 ＋106 ＋134 ＋49 ＋60 ＋76 ＋29 ＋40 ＋13 ＋19 ＋30 ＋46 ＋74 ＋120 ＋13 ＋18 ＋ 4 ＋ 9 − 5 0 −14 − 9 −21
08_技術資料_E_p176_203.qxd 11.11.10 3:07 PM ページ181

±9.5 ±15
＋60 ＋ 60 ＋ 60 ＋30 ＋30 ＋30 ＋10 ＋10 0 0 0 0 0 0 − 6 −12 −15 −21 −24 −30 −33 −39 −51 −32
65 80 −62
65 80
(Excerpts from JIS B 0401)

−38
80 100 −73
80 100
＋107 ＋126 ＋159 ＋58 ＋71 ＋90 ＋34 ＋47 ＋15 ＋22 ＋35 ＋54 ＋87 ＋140 ＋16 ＋22 ＋ 4 ＋10 − 6 0 −16 −10 −24
±11 ±17.5
＋ 72 ＋ 72 ＋ 72 ＋36 ＋36 ＋36 ＋12 ＋12 0 0 0 0 0 0 − 6 −13 −18 −25 −28 −35 −38 −45 −59 −41
100 120 −76
100 120

−48
120 140 −88
120 140

＋125 ＋148 ＋185 ＋68 ＋83 ＋106 ＋39 ＋54 ＋18 ＋25 ＋40 ＋63 ＋100 ＋160 ＋18 ＋26 ＋ 4 ＋12 − 8 0 −20 −12 −28 −50
140 ±12.5 ±20 140 160
0 0 0 0 0 0
160 ＋ 85 ＋ 85 ＋ 85 ＋43 ＋43 ＋ 43 ＋14 ＋14 − 7 −14 −21 −28 −33 −40 −45 −52 −68 −90
−53
160 180 −93
160 180

− 60
180 200 −106
180 200

＋146 ＋172 ＋215 ＋79 ＋96 ＋122 ＋44 ＋61 ＋20 ＋29 ＋46 ＋72 ＋115 ＋185 ＋22 ＋30 ＋ 5 ＋13 − 8 0 −22 −14 −33 − 63
200 225 ±14.5 ±23 200 225
＋100 ＋100 ＋100 ＋50 ＋50 ＋ 50 ＋15 ＋15 0 0 0 0 0 0 − 7 −16 −24 −33 −37 −46 −51 −60 −79 −109
−67
225 250 −113
225 250

− 74
250 280 250 280
＋162 ＋191 ＋240 ＋88 ＋108 ＋137 ＋49 ＋69 ＋23 ＋32 ＋52 ＋81 ＋130 ＋210 ＋25 ＋36 ＋ 5 ＋16 − 9 0 −25 −14 −33 −126
±16 ±26
＋110 ＋110 ＋110 ＋56 ＋ 56 ＋ 56 ＋17 ＋17 0 0 0 0 0 0 − 7 −16 −27 −36 −41 −52 −57 −66 −88 − 78
280 315 −130
280 315

− 87
315 355 315 355
＋182 ＋214 ＋265 ＋98 ＋119 ＋151 ＋54 ＋75 ＋25 ＋36 ＋57 ＋89 ＋140 ＋230 ＋29 ＋39 ＋ 7 ＋17 −10 0 −26 −16 −41 −144
±18 ±28.5
＋125 ＋125 ＋125 ＋62 ＋ 62 ＋ 62 ＋18 ＋18 0 0 0 0 0 0 − 7 −18 −29 −40 −46 −57 −62 −73 −98 − 93
355 400 −150
355 400
Permissible dimensional bore deviations

−103
400 450 400 450
＋198 ＋232 ＋290 ＋108 ＋131 ＋165 ＋60 ＋83 ＋27 ＋40 ＋63 ＋97 ＋155 ＋250 ＋33 ＋43 ＋ 8 ＋18 −10 0 −27 −17 − 45 −166
±20 ±31.5
＋135 ＋135 ＋135 ＋ 68 ＋ 68 ＋ 68 ＋20 ＋20 0 0 0 0 0 0 − 7 −20 −32 −45 −50 −63 −67 −80 −108 −109
450 500 −172
450 500

181
* The upper value in each column indicates the upper deviation, and the lower value in each column indicates the lower deviation.

Technical Data
08_技術資料_E_p176_203.qxd 11.11.10 3:07 PM ページ182

Dimensions and Tolerances of Parallel Keys

and Keyways

b2
b1

t2
t1

r1
b

r2

c or r
d

h
d

Cross section of shaft Cross section of bore Cross section of key

■ JIS (Excerpts from JIS B 1301-1996) Unit [mm]

key dimensions keyway dimensions
Nominal b h Basic Fastening type Normal type t1 t2
Applicable
dimensions c dimensi r1
shaft Basic Basic Tolerances b1 b2 Basic Basic
of keys or ons of and
diameters d dimen Tolerances dimen Tolerance of b1.b2 Tolerances Tolerances dimen Tolerances dimen Tolerances
b×h (h9) r b1 and r2
sions sions (P9) (N9) (Js9) sions sions
b2
2× 2 6 to 8 2 0 2 0 0.16 2 −0.006 −0.004 0.08 1.2 1.0
±0.0125
3× 3 8 to 10 3 −0.025 3 −0.025 ∼ 3 −0.031 −0.029 ∼ 1.8 1.4
0.25 0.16 ＋0.1 ＋0.1
4× 4 10 to 12 4 4 h9 4 2.5 1.8
0 0 −0.012 0 0 0
5× 5 12 to 17 5 5 0.25 5 ±0.0150 0.16 3.0 2.3
−0.030 −0.030 −0.042 −0.030
6× 6 17 to 22 6 6 ∼ 6 ∼ 3.5 2.8
8× 7 22 to 30 8 7 0.40 8 0.25 4.0 3.3
0 −0.015 0
±0.0180
10× 8 30 to 38 10 −0.036 8 10 −0.051 −0.036 5.0 3.3
0
12× 8 38 to 44 12 8 0.40 12 0.25 5.0 3.3
−0.090
14× 9 44 to 50 14 0 9 ∼ 14 −0.018 0 ∼ 5.5 3.8
0.60 ±0.0215 0.40
16×10 50 to 58 16 −0.043 10 16 −0.061 −0.043 6.0 4.3
18×11 58 to 65 18 11 18 7.0 ＋0.2 4.4 ＋0.2
h11
20×12 65 to 75 20 12 20 7.5 0 4.9 0
22×14 75 to 85 22 0 14 22 −0.022 0 9.0 5.4
0 0.60 ±0.0260 0.40
25×14 85 to 95 25 −0.052 14 25 −0.074 −0.052 9.0 5.4
−0.110 ∼ ∼
28×16 95 to 110 28 16 0.80 28 0.60 10.0 6.4
0 −0.026 0
32×18 110 to 130 32 18 32 ±0.0310 11.0 7.4
−0.062 −0.088 −0.062
Technical Data

182
08_技術資料_E_p176_203.qxd 11.11.10 3:07 PM ページ183

■ Previous edition of JIS First class (Excerpts form JIS B 1301-1959) Unit [mm]
key dimensions keyway dimensions
Nominal b h Basic t1 t2
dimensions Applicable shaft c dimensi b1 b2 r1
of keys diameters d Basic Basic Basic Basic
Tolerances Tolerances or ons of Tolerances Tolerances and
b×h dimen dimen dimen Tolerances dimen Tolerances
(h7) (h9) r b1 and (H8) (F7) r2
sions sions sions sions
b2
4× 4 10 or more 13 or less 4 ＋0.024 4 0 4 ＋0.018 ＋0.022 2.5 1.5
5× 5 More than 13 20 or less 5 ＋0.012 5 −0.030 0.5 5 0 ＋0.010 0.4 3 2
7× 7 More than 20 30 or less 7 ＋0.030 7 7 ＋0.022 ＋0.028 4 3
10× 8 More than 30 40 or less 10 ＋0.015 8 0 10 0 ＋0.013 4.5 3.5
12× 8 More than 40 50 or less 12 8 −0.036 0.8 12 0.6 4.5 3.5
＋0.036 ＋0.027 ＋0.034
15×10 More than 50 60 or less 15 10 15 5 ＋0.05 5 ＋0.05
＋0.018 0 ＋0.016
18×12 More than 60 70 or less 18 12 18 6 0 6 0
20×13 More than 70 80 or less 20 13 0 20 7 6
＋0.043 1.2 ＋0.033 ＋0.041 1.0
24×16 More than 80 95 or less 24 16 −0.043 24 8 8
＋0.022 0 ＋0.020
28×18 More than 95 110 or less 28 18 28 9 9
＋0.051 0 ＋0.039 ＋0.050
32×20 More than 110 125 or less 32 20 2 32 1.6 10 10
＋0.026 −0.052 0 ＋0.025

■ Previous edition of JIS Second class (Excerpts from JIS B 1301-1959) Unit [mm]
key dimensions keyway dimensions
Nominal b h Basic t1 t2
dimensions Applicable shaft c dimensi b1 b2 r1
of keys diameters d Basic Basic Basic Basic
Tolerances Tolerances or ons of Tolerances Tolerances and
b×h dimen dimen dimen Tolerances dimen Tolerances
(h8) (h10) r b1 and (H9) (E9) r2
sions sions sions sions
b2
4× 4 10 or more 13 or less 4 0 4 0 4 ＋0.030 ＋0.050 2.5 1.5
5× 5 More than 13 20 or less 5 −0.018 5 −0.048 0.5 5 0 ＋0.020 0.4 3 2
7× 7 More than 20 30 or less 7 0 7 7 ＋0.036 ＋0.061 4 3
10× 8 More than 30 40 or less 10 −0.022 8 0 10 0 ＋0.025 4.5 3.5
12× 8 More than 40 50 or less 12 8 −0.058 0.8 12 0.6 4.5 3.5
0 ＋0.043 ＋0.075
15×10 More than 50 60 or less 15 10 15 5 ＋0.1 5 ＋0.1
−0.027 0 ＋0.032
18×12 More than 60 70 or less 18 12 18 6 0 6 0
20×13 More than 70 80 or less 20 13 0 20 7 6
0 1.2 ＋0.052 ＋0.092 1.0
24×16 More than 80 95 or less 24 16 −0.070 24 8 8
−0.033 0 ＋0.040
28×18 More than 95 110 or less 28 18 28 9 9
0 0 ＋0.062 ＋0.112
32×20 More than 110 125 or less 32 20 2 32 1.6 10 10
−0.039 −0.084 0 ＋0.050
Technical Data

183
08_技術資料_E_p176_203.qxd 11.11.10 3:07 PM ページ184

Miki Pulley clutches and brakes standard

bore machining specifications
z Bore machining tolerances for mating shaft
tolerance cSetscrew nominal diameter for keyway
Unless there is a request, it is machining by H7. For below 10mm of Keyway basic dimensions b2 Setscrew nominal diameters
spring-applied brakes, it is H8. Except the tolerance class H7, 4 M4
prearrangement is necessary. When an additional machining of a 5 M4
pilot bore is performed, the surface treatment of the machining 6 M5
portion is shaved. If an additional surface treatment after bore 7 M6
machining is necessary, contact us. 8 M6
The shaft tolerance by load condition is as follows. 10 M8
Load conditions Shaft tolerances Notes 12 M8
Shaft below (φ10) h6 h7 If accuracy is required, it should be h5. 14 M10
15 M10
Light/Normal load h6 H6 for motor shaft
js6 js7 16 M10,M12
and variable load J6 for clutch and brake unit shaft
j6   j7 18 M12,M16
Heavy load and 20 M16
K6 K7
impact load m6 22 M16
* A keyway is not processed for a bore processing under 10mm.

x Keyway dimensions for bore diameters

(following table)
b2 b
t2

0゜
12
2-M
Previous edition of JIS (Second class) correspondence
Unit [mm] v Setscrew nominal diameter for bore
b2 t2 Keyway diameter (in the case of no keyway)
Bore dia. dimensions
Basic dimensions Tolerances (E9) Basic dimensions Tolerances b×h
Bore diameter Setscrew nominal diameter
10 or more 13 or less 4 ＋0.05 1.5 4×4
5 ＋0.02 2.0 5×5 More than 6 less than 10 M3
More than 13 20 or less
More than 20 30 or less 7 ＋0.061 3.0 7×7
More than 30 40 or less 10 ＋0.025 10×8
3.5 ＋0.5
More than 40 50 or less 12 0 12×8
＋0.075
More than 50 60 or less 15 5.0 15×10
＋0.032
More than 60 70 or less 18 18×12
＋0.092 6.0
More than 70 80 or less 20 20×13
＋0.040
0゜

* Recommended key specification is former JIS 1class (width tolerance P7).

Technical Data

12

New JIS correspondence Unit [mm]

b2 t2 Keyway
Bore dia. dimensions 2-M
Basic dimensions Tolerances (P9) Basic dimensions Tolerances b×h
6 or more 8 or less 2 −0.006 0.8 ＋0.3 2×2
−0.031 0 Note
More than 8 10 or less 3 1.2 3×3
This specification is applicable to bore machining of 6mm~
More than 10 12 or less 4 1.5 4×4
−0.012 85mm for the following products. For the clutches and brakes with
More than 12 17 or less 5 −0.042 2.0 5×5
bore machining as a standard product, it may not suitable.
More than 17 22 or less 6 2.5 6×6 ■Applicable products
More than 22 30 or less 8 −0.015 8×7 ● Micro electromagnetic clutches and brakes (except CYT

More than 30 38 or less 10 −0.051 3.0 10×8 model)

＋0.5
More than 38 44 or less 12 0 12×8 ● Electromagnetic clutches and brakes (except CSZ and BSZ

More than 44 50 or less 14 3.5 14×9 model)

−0.018
● Tooth clutches
More than 50 58 or less 16 −0.061 16×10
4.0 ● Spring-applied brakes (except BXW model)
More than 58 65 or less 18 18×11
More than 65 75 or less 20 −0.022 4.5 20×12
More than 75 85 or less 22 −0.074 5.0 22×14
* Recommended key specification is new JIS (width tolerance h9).

184
08_技術資料_E_p176_203.qxd 11.11.10 3:07 PM ページ185

Shim dimensions

φD

φd
t

Unit [mm]

Inside diameters Outside diameters Thickness t

φd φD Applicable shafts Applicable bores
0.05 0.1 0.15 0.5
6.3 8.7 ⃝ ⃝ ― ⃝ 6
8.3 11.7 ⃝ ⃝ ― ⃝ 8
10.3 13.7 ⃝ ⃝ ― ⃝ 10
12.3 15.7 ― ⃝ ⃝ ⃝ 12
15.3 20.7 ― ⃝ ⃝ ⃝ 15
17.3 25.7 ― ⃝ ⃝ ⃝ 17 26
20.3 27.7 ― ⃝ ⃝ ⃝ 20 28
25.3 31.7 ― ⃝ ⃝ ⃝ 25 32
25.3 34.7 ― ⃝ ― ⃝ 25 35
30.3 39.7 ― ⃝ ⃝ ⃝ 30 40
35.3 41.7 ― ⃝ ⃝ ⃝ 35 42
35.3 46.7 ― ⃝ ― ⃝ 35 47
40.3 51.7 ― ⃝ ⃝ ⃝ 40 52
45.3 51.7 ― ⃝ ⃝ ⃝ 45 52
45.3 54.7 ― ⃝ ― ⃝ 45 55
50.3 61.7 ― ⃝ ― ⃝ 50 62
50.3 67.7 ― ⃝ ― ⃝ 50 68
55.3 67.7 ― ⃝ ― ⃝ 55 68
60.3 71.7 ― ⃝ ― ⃝ 60 72
60.3 84.7 ― ⃝ ― ⃝ 60 85
65.3 79.7 ― ⃝ ― ⃝ 65 80
70.3 79.7 ― ⃝ ― ⃝ 70 80
75.3 89.7 ― ⃝ ― ⃝ 75 90
Technical Data

85.3 99.7 ― ⃝ ― ⃝ 85 100

90.3 109.7 ― ⃝ ― ⃝ 90 110
105.3 124.7 ― ⃝ ― ⃝ 125
115.3 129.7 ― ⃝ ― ⃝ 130

185
08_技術資料_E_p176_203.qxd 11.11.10 3:07 PM ページ186

Configurations and Dimensions of Hexagon

Bolts (Grade A parts) (Excerpts from JIS B 1180-1985)
X portion closeup
15 °
∼30
°
Chamfer the edge. It's not k The shaded area
necessary for the M4 and below. indicates the
d k´ f
maximum and
X minimum range of the
fillet under the head.
φds
e

r
r
Incomplete thread
c Rs 2P and below
s
Rg (b)

φdw
φda

φds
k R

Unit [mm]
Nominal designations (d) M3 M4 M5 M6 M8 M10 M12 (M14) M16 M20 M24
Screw pitches (P) 0.5 0.7 0.8 1 1.25 1.5 1.75 2 2 2.5 3
b R≦125 12 14 16 18 22 26 30 34 38 46 54
(Reference) 125＜R≦150 ― ― ― ― ― ― ― 40 44 52 60
Minimum 0.15 0.15 0.15 0.15 0.15 0.15 0.15 0.15 0.2 0.2 0.2
c
Maximum 0.4 0.4 0.5 0.5 0.6 0.6 0.6 0.6 0.8 0.8 0.8
da Maximum 3.6 4.7 5.7 6.8 9.2 11.2 13.7 15.7 17.7 22.4 26.4
Max (Basic dimensions) 3 4 5 6 8 10 12 14 16 20 24
ds
Minimum 2.86 3.82 4.82 5.82 7.78 9.78 11.73 13.73 15.73 19.67 23.67
dw Minimum 4.57 5.88 6.88 8.88 11.63 14.63 16.63 19.64 22.49 28.19 33.61
e Minimum 6.01 7.66 8.79 11.05 14.38 17.77 20.03 23.36 26.75 33.53 39.98
f Maximum 1 1.2 1.2 1.4 2 2 3 3 3 4 4
Designations (Basic dimensions) 2 2.8 3.5 4 5.3 6.4 7.5 8.8 10 12.5 15
k Minimum 1.875 2.675 3.35 3.85 5.15 6.22 7.32 8.62 9.82 12.285 14.785
Maximum 2.125 2.925 3.65 4.15 5.45 6.58 7.68 8.98 10.18 12.715 15.215
k' Minimum 1.31 1.87 2.35 2.7 3.61 4.35 5.12 6.03 6.87 8.6 10.35
r Minimum 0.1 0.2 0.2 0.25 0.4 0.4 0.6 0.6 0.6 0.8 0.8
Max (Basic dimensions) 5.5 7 8 10 13 16 18 21 24 30 36
s
Minimum 5.32 6.78 7.78 9.78 12.73 15.73 17.73 20.67 23.67 29.67 35.38
* The nominal diameter in parentheses is preferably not to be used.
Technical Data

186
08_技術資料_E_p176_203.qxd 11.11.10 3:07 PM ページ187

Unit [mm]
Nominal designations M3 M4 M5 M6 M8 M10 M12 (M14) M16 M20 M24
R Rs andRg
Nominal lengths
Rs Rg Rs Rg Rs Rg Rs Rg Rs Rg Rs Rg Rs Rg Rs Rg Rs Rg Rs Rg Rs Rg
(Basic Min. Max.
dimensions)
Min. Max. Min. Max. Min. Max. Min. Max. Min. Max. Min. Max. Min. Max. Min. Max. Min. Max. Min. Max. Min. Max.
20 19.58 20.42 5.5 8
25 24.58 25.42 10.5 13 7.5 11 5 9
30 29.58 30.42 15.5 18 12.5 16 10 14 7 12
35 34.5 35.5 17.5 21 15 19 12 17
40 39.5 40.5 22.5 26 20 24 17 22 11.75 18
45 44.5 45.5 25 29 22 27 16.75 23 11.5 19
50 49.5 50.5 30 34 27 32 21.75 28 16.5 24 11.25 20
55 54.4 55.6 32 37 26.75 33 21.5 29 16.25 25
60 59.4 60.6 37 42 31.75 38 26.5 34 21.25 30 16 26
65 64.4 65.6 36.75 43 31.5 39 26.25 35 21 31 17 27
70 69.4 70.6 41.75 48 36.5 44 31.25 40 26 36 22 32
80 79.4 80.6 51.75 58 46.5 54 41.25 50 36 46 32 42 21.5 34
90 89.3 90.7 56.5 64 51.25 60 46 56 42 52 31.5 44 21 36
100 99.3 100.7 66.5 74 61.25 70 56 66 52 62 41.5 54 31 46
110 109.3 110.7 71.25 80 66 76 62 72 51.5 64 41 56
120 119.3 120.7 81.25 90 76 86 72 82 61.5 74 51 66
130 129.2 130.8 80 90 76 86 65.5 78 55 70
140 139.2 140.8 90 100 86 96 75.5 88 65 80
150 149.2 150.8 96 106 85.5 98 75 90
* The gray portion ( ) indicates the nominal length (r) recommended for the nominal designations.

Technical Data

187
08_技術資料_E_p176_203.qxd 11.11.10 3:07 PM ページ188

Configurations and Dimensions of Hexagon

Socket Bolts (Excerpts from JIS B 1176-1988)

The maximum state of the

Rounded or radii under the head
t
w Chamfer the edge. It's not chamfered head
Cone
base necessary for the M4 and below.
Roundness f f (Max.) ＝1.7r (Max.)
d

V
r da (Max.) −ds (Max.)
r (Max.) ＝
120°

r 2

r
(Min.)

φdw
φdk
φda
φds
φdk

r (Min.) ＝ Depending on the value of

e

the appendix table

r
Incomplete thread
Rs

da
V

ds
s (2P and below) Chamfering
Rg b (Reference)
45°.)
Internal chamfering can be x Rounding or chamfering can be performed on the top or
performed on the hexagon socket. K R (Ma bearing surface of the head. Any burr should be removed.
Unit [mm]
Nominal designations (d) M1.6 M2 M2.5 M3 M4 M5 M6 M8 M10 M12 (M14) M16 (M18) M20
Screw pitches (P) 0.35 0.4 0.45 0.5 0.7 0.8 1 1.25 1.5 1.75 2 2 2.5 2.5
b References 15 16 17 18 20 22 24 28 32 36 40 44 48 52
Max (Basic dimensions)＊1 3 3.8 4.5 5.5 7 8.5 10 13 16 18 21 24 27 30
dk Maximum ＊2 3.14 3.98 4.68 5.68 7.22 8.72 10.22 13.27 16.27 18.27 21.33 24.33 27.33 30.33
Minimum 2.86 3.62 4.32 5.32 6.78 8.28 9.78 12.73 15.73 17.73 20.67 23.67 26.67 29.67
da Maximum 2 2.6 3.1 3.6 4.7 5.7 6.8 9.2 11.2 13.7 15.7 17.7 20.2 22.4
Max (Basic dimensions) 1.6 2 2.5 3 4 5 6 8 10 12 14 16 18 20
ds
Minimum 1.46 1.86 2.36 2.86 3.82 4.82 5.82 7.78 9.78 11.73 13.73 15.73 17.73 19.67
e Minimum 1.73 1.73 2.30 2.87 3.44 4.58 5.72 6.86 9.15 11.43 13.72 16.00 16.00 19.44
f Maximum 0.34 0.51 0.51 0.51 0.60 0.60 0.68 1.02 1.02 1.45 1.45 1.45 1.87 2.04
Max (Basic dimensions) 1.6 2 2.5 3 4 5 6 8 10 12 14 16 18 20
k
Minimum 1.46 1.86 2.36 2.86 3.82 4.82 5.70 7.64 9.64 11.57 13.57 15.57 17.57 19.48
r Minimum 0.1 0.1 0.1 0.1 0.2 0.2 0.25 0.4 0.4 0.6 0.6 0.6 0.6 0.8
Designations (Basic dimensions) 1.5 1.5 2 2.5 3 4 5 6 8 10 12 14 14 17
Minimum 1.52 1.52 2.02 2.52 3.02 4.02 5.02 6.02 8.025 10.025 12.032 14.032 14.032 17.050
s
Column 1 1.560 1.560 2.060 2.580 3.080 4.095 5.140 6.140 8.175 10.175 12.212 14.212 14.212 17.230
Max.
Column 2 1.545 1.545 2.045 2.560 3.080 4.095 5.095 6.095 8.155 10.115 12.142 14.142 14.142 17.230
t Minimum 0.7 1 1.1 1.3 2 2.5 3 4 5 6 7 8 9 10
v Maximum 0.16 0.2 0.25 0.3 0.4 0.5 0.6 0.8 1 1.2 1.4 1.6 1.8 2
dw Minimum 2.72 3.40 4.18 5.07 6.53 8.03 9.38 12.33 15.33 17.23 20.17 23.17 25.87 28.87
w Minimum 0.55 0.55 0.85 1.15 1.4 1.9 2.3 3.3 4 4.8 5.8 6.8 7.7 8.6
* Perform a knurling on the side surface of the head. In this case, the maximum dk is shown in the Maximum*2. For no knurling, refer to the Maximum *1.
* The column 1 of the S (Maximum) is used for the strength class 8.8 and 10.9, and for the property class A2-50 and A2-70. The column 2 is applied to the strength class 12.9. The column 1
can be applied to the strength class 12.9 by agreement of the parties concerned.
* The nominal diameters in parentheses are preferably not to be used.
Technical Data

188
08_技術資料_E_p176_203.qxd 11.11.10 3:07 PM ページ189

Unit [mm]
Nominal designations M1.6 M2 M2.5 M3 M4 M5 M6 M8 M10 M12 (M14) M16 (M18) M20
R Rs andRg
Nominal Rs Rg Rs Rg Rs Rg Rs Rg Rs Rg Rs Rg Rs Rg Rs Rg Rs Rg Rs Rg Rs Rg Rs Rg Rs Rg Rs Rg
Min. Max.
lengths Min. Max. Min. Max. Min. Max. Min. Max. Min. Max. Min. Max. Min. Max. Min. Max. Min. Max. Min. Max. Min. Max. Min. Max. Min. Max. Min. Max.
2.5 2.30 2.70
3 2.80 3.20
4 3.76 4.24
5 4.76 5.24
6 5.76 6.24
8 7.71 8.29
10 9.71 10.29
12 11.65 12.35
16 15.65 16.35
20 19.58 20.42 2 4
25 24.58 25.42 5.75 8 4.5 7
30 29.58 30.42 9.5 12 6.5 10 4 8
35 34.5 35.5 11.5 15 9 13 6 11
40 39.5 40.5 16.5 20 14 18 11 16 5.75 12
45 44.5 45.5 19 23 16 21 10.75 17 5.5 13
50 49.5 50.5 24 28 21 26 15.75 22 10.5 18 5.25 14
55 54.4 55.6 26 31 20.75 27 15.5 23 10.25 19
60 59.4 60.6 31 36 25.75 32 20.5 28 15.25 24 10 20 6 16
65 64.4 65.6 30.75 37 25.5 33 20.25 29 15 25 11 21 4.5 17
70 69.4 70.6 35.75 42 30.5 38 25.25 34 20 30 16 26 9.5 22 5.5 18
80 79.4 80.6 45.75 52 40.5 48 35.25 44 30 40 26 36 19.5 32 15.5 28
90 89.3 90.7 50.5 58 45.25 54 40 50 36 46 29.5 42 25.5 38
100 99.3 100.7 60.5 68 55.25 64 50 60 46 56 39.5 52 35.5 48
110 109.3 110.7 65.25 74 60 70 56 66 49.5 62 45.5 58
120 119.3 120.7 75.25 84 70 80 66 76 59.5 72 55.5 68
130 129.2 130.8 80 90 76 86 69.5 82 65.5 78
140 139.2 140.8 90 100 86 96 79.5 92 75.5 88
150 149.2 150.8 96 106 89.5 102 85.5 98
160 159.2 160.8 106 116 99.5 112 95.5 108
180 179.2 180.8 119.5 132 115.5 128
200 199.05 200.95 135.5 148
* The gray portion ( ) indicates the nominal lengths (r) recommended for the nominal designations. Besides, the nominal length (r) that is above the dashed line position is a complete
thread. The incomplete thread length under the head is about 3P.

Technical Data

189
08_技術資料_E_p176_203.qxd 11.11.10 3:07 PM ページ190

Configurations and Dimensions of Hexagon

socket set screws (Excerpts from JIS B 1176-1988)

■ The inlet of a hexagon socket can be rounded or chamfered.

＊1 ＊2
＊1
90゜or 120゜ ＊2
About 45゜ 90゜or 120゜ About 45゜
Borer base Borer base
t d t d t
t

About 120゜
φdp
φdf
e
φdp
φdf
e

s Incomplete thread
s Cone base
Cone base The inlet of hexagon (2P and below)
Incomplete thread l
The inlet of hexagon (2P and below) socket can be rounded
l
socket can be rounded or chamfered.
or chamfered.

Nominal designations (d) M1.6 M2 M2.5 M3 M4 M5 M6 M8 M10 M12 M16 M20 M24
Pitches (P) 0.35 0.4 0.45 0.5 0.7 0.8 1 1.25 1.5 1.75 2 2.5 3
Maximum 0.80 1.00 1.5 2.00 2.50 3.5 4 5.5 7.00 8.50 12.00 15.00 18.00
dp
Minimum 0.55 0.75 1.25 1.75 2.25 3.2 3.7 5.2 6.64 8.14 11.57 14.57 17.57
Maximum 0.80 1.00 1.20 1.40 2.00 2.50 3.00 5.0 6.0 8.00 10.00 14.00 16.00
dz
Minimum 0.55 0.75 0.95 1.15 1.75 2.25 2.75 4.7 5.7 7.64 9.64 13.57 15.57
df Almost the diameter of screw groove
e＊3 Minimum 0.803 1.003 1.427 1.73 2.3 2.87 3.44 4.58 5.72 6.86 9.15 11.43 13.72
Designation 0.7 0.9 1.3 1.5 2 2.5 3 4 5 6 8 10 12
s＊4 Maximum 0.724 0.902 1.295 1.545 2.045 2.560 3.071 4.084 5.084 6.095 8.115 10.115 12.142
Minimum 0.711 0.889 1.270 1.520 2.020 2.520 3.020 4.020 5.020 6.020 8.025 10.025 12.032
Minimum＊5 0.7 0.8 1.2 1.2 1.5 2 2 3 4 4.8 6.4 8 10
t
Minimum＊6 1.5 1.7 2 2 2.5 3 3.5 5 6 8 10 12 15
R
Nominal lengths Minimum Maximum (Reference) Outline mass per 1000 units / kg (Density:7.85kg/dm3)
2 1.8 2.2 0.021 0.029 0.05 0.059
2.5 2.3 2.7 0.025 0.037 0.063 0.08 0.099
3 2.8 3.2 0.029 0.044 0.075 0.1 0.14 0.2
4 3.76 4.24 0.037 0.059 0.1 0.14 0.22 0.32 0.41
5 4.76 5.24 0.046 0.074 0.125 0.18 0.3 0.44 0.585 0.945
6 5.76 6.24 0.054 0.089 0.15 0.22 0.38 0.56 0.76 1.26 1.77
8 7.71 8.29 0.07 0.119 0.199 0.3 0.54 0.8 1.11 1.89 2.78 4
Flat point

10 9.71 10.29 0.148 0.249 0.38 0.7 1.04 1.46 2.52 3.78 5.4 8.5
12 11.65 12.35 0.299 0.46 0.86 1.28 1.81 3.15 4.78 6.8 11.1 15.8
16 15.65 16.35 0.62 1.18 1.76 2.51 4.41 6.78 9.6 16.3 24.1 30
20 19.58 20.42 1.49 2.24 3.21 5.67 8.76 12.4 21.5 32.3 42
25 24.58 25.42 2.84 4.09 7.25 11.2 15.9 28 42.6 57
30 29.58 30.42 4.94 8.82 13.7 19.4 34.6 52.9 72
35 34.5 35.5 10.4 16.2 22.9 41.1 63.2 87
40 39.5 40.5 12 18.7 26.4 47.7 73.5 102
45 44.5 45.5 21.2 29.9 54.2 83.8 117
50 49.5 50.5 23.7 33.4 60.7 94.1 132
55 54.4 55.6 36.8 67.3 104 147
60 59.4 60.6 40.3 73.7 115 162
2 1.8 2.2 0.019 0.029 0.05
2.5 2.3 2.7 0.025 0.037 0.063 0.079
3 2.8 3.2 0.029 0.044 0.075 0.1 0.155
4 3.76 4.24 0.037 0.059 0.1 0.14 0.23 0.3
5 4.76 5.24 0.046 0.074 0.125 0.18 0.305 0.42 0.565
6 5.76 6.24 0.054 0.089 0.15 0.22 0.38 0.54 0.74 1.25
8 7.71 8.29 0.07 0.119 0.199 0.3 0.53 0.78 1.09 1.88 2.71
Concave point

10 9.71 10.29 0.148 0.249 0.38 0.68 1.02 1.44 2.51 3.72 5.3
12 11.65 12.35 0.299 0.46 0.83 1.26 1.79 3.14 4.73 6.7 10.5
Technical Data

16 15.65 16.35 0.62 1.13 1.74 2.49 4.4 6.73 9.5 15.7 22.9
20 19.58 20.42 1.42 2.22 3.19 5.66 8.72 12.3 20.9 31.1 40.2
25 24.58 25.42 2.82 4.07 7.24 11.2 15.8 27.4 41.4 55.2
30 29.58 30.42 4.94 8.81 13.7 19.3 33.9 51.7 70.3
35 34.5 35.5 10.4 16.2 22.7 40.4 62 85.3
40 39.5 40.5 12 18.7 26.2 46.9 72.3 100
45 44.5 45.5 21.2 29.7 53.3 82.6 115
50 49.5 50.5 23.6 33.2 59.8 92.6 130
55 54.4 55.6 36.6 66.3 103 145
60 59.4 60.6 40.1 72.8 114 160
* *1 For the nominal lengths (r) that is shorter than the stepped double line, perform a 120o of chamfering.
* *2 The angle of approx. 45o corresponds to the slope portion below the core diameter.
* *3 e minimum= 1.14 x s minimum. Nominal diameters M1.6, M2 and M2.5 are excluded.
* For the *4 s, use the specified hexagon socket gauge to examine.
* The upper value of *5 t minimum is applicable to the nominal lengths (r) shorter than the stepped double line.
* The lower value of *6 t minimum is applicable to the nominal lengths (r) longer than the stepped double line.

Remarks
1. The recommended nominal lengths (R) for the nominal designations are
indicated within the heavy-line frame.
2. Dimensional symbols correspond to the JIS B 0143.
3. The configuration of a hexagon socket base can be either cone or borer base.
For a borer base, the bore depth must not be more than 1.2 times the hexagon
socket depth t.

190
08_技術資料_E_p176_203.qxd 11.11.10 3:07 PM ページ191

Configurations and Dimensions of Hexagon

bar wrenches (Excerpts from JIS B 4648-1994)

s
R
0゜

e
t9
ou
l

Ab

Configurations/Dimensions [mm] Mechanical properties

Nominal s e L l R Hardness (Min.)
＊1
Proof torque
＊2

designations Max. Min. Max. Min. About About About Rockwell hardness Vickers hardness [N・m]
0.7 0.711 0.698 0.79 0.76 32 6 1.5 0.08
0.9 0.889 0.876 0.99 0.96 32 10 1.5 0.18
1.3 1.270 1.244 1.42 1.37 40 12 1.5 0.53
1.5 1.500 1.475 1.68 1.63 45 14 1.5 0.82
2 2.00 1.960 2.25 2.18 50 16 2 1.9
52HRC 545HV
2.5 2.50 2.460 2.82 2.75 56 18 2.5 3.8
3 3.00 2.960 3.39 3.31 63 20 3 6.6
4 4.00 3.952 4.53 4.44 70 25 4 16
5 5.00 4.952 5.67 5.58 80 28 5 30
6 6.00 5.952 6.81 6.71 90 32 6 52
8 8.00 7.942 9.09 8.97 100 36 8 50HRC 513HV 120
10 10.00 9.942 11.37 11.23 112 40 10 220
12 12.00 11.89 13.65 13.44 125 45 12 48HRC 485HV 370
14 14.00 13.89 15.93 15.70 140 56 14 590
17 17.00 16.89 19.35 19.09 160 63 17 980
19 19.00 18.87 21.63 21.32 180 70 19 1360
22 22.00 21.87 25.05 24.71 200 80 22 2110
24 24.00 23.87 27.33 26.97 224 90 24 45HRC 446HV 2750
27 27.00 26.87 30.75 30.36 250 100 27 3910
32 32.00 31.84 36.45 35.98 315 125 32 6510
36 36.00 35.84 41.01 40.50 355 140 36 9260
* The hardness *1 corresponds to either Rockwell hardness or Vickers hardness.
* A wrench will not be damaged by the torque *2 or below. Avoid any abnormalities such as unendurable torsion, hexagon shape deformation or bending.

Remarks
Chamfering of the wrench edge is not necessary if it can be inserted easily into the Chamfering of spanner edge
hexagon socket. If chamfering is required, leave the width across bolt (s) as shown Chamfering
90゜
±4゜
in the right figure. Besides, the side surfaces of long and short shafts are at a right
angle to respective shafts.
Therefore, it must not bend more than ±4o. (Refer to the right figure.) About 45゜ S Technical Data

■ Proof torque of strength class 45H (Reference)

Nominal Proof torques Recommended tightening torques
Wrench sizes
designations d [N・m] [N・m]
M1.6 0.07 0.04 0.7
2 0.15 0.09 0.9
2.5 0.44 0.26 1.3
（2.6） 0.44 0.26 1.3
3 1.17 0.69 1.5
4 2.74 1.67 2
5 5.88 3.53 2.5
6 9.8 5.9 3
8 23.5 14.2 4
10 45.1 27.5 5
12 77.5 47.1 6
（14） 88.3 53.0 6
16 186 118 8
（18） 211 128 8
20 363 216 10

191
08_技術資料_E_p176_203.qxd 11.11.10 3:07 PM ページ192

How to use Hexagon socket set screws

Hexagon socket set screws are widely used as a fixation method of cShaft diameter and shaft holding power
shafts and hubs or flanges. It is a highly reliable and a low cost The fixation limit (shaft holding power) of shaft and hub or flange is
method if it is used properly. How to use hexagon socket set
related to the friction factor between the tip of set screw and
screws based on test results is described below. Use as a
shaft. The fixation limit based on the data of examination results is
reference for size selection.
described below.
10,000

Shaft holding power [N・cm]

■ How to select a set screw M5 T=441N・cm

zShaft diameter and set screw size

5,000

The impression of screw tip should clearly appear on the shaft

1,000
cylinder surface. A correlation between the shaft diameters and set
M4 T=216N・cm
screws are shown below. 500

M3 T=98N・cm
200

Good example Bad example

5 10 15 20 25 30 35
Shaft diameter [mm]

Correlation between the shaft diameters and shaft holding

Screw tip impression power (concave point)
* Shaft holding power of set screws are related to the size of the shaft diameter.
60

50
vHardness and shaft holding power
shaft diameter [mm]

er
et

Shaft holding power decreases as the hardness of the shaft

am

40
di
ft

increases. The relationship between the hardness and the shaft

ha
.s

30
ax

holding power is described below.

M

(Example)
20
r
ete
d iam
aft
10 sh
Decreasing rate of shaft holding power

n.
Mi

3 4 5 6 8 10 12
1.0
set screw diameter [mm] Se
ts
cre
Se w
ts HR
Correlation between the set screws and shaft diameters cre C5
w 0
HR
xIf the size of set screw can not be enlarged C4
0

Two set screws are sometimes used when a large shaft holding 0.5

power is required. However, using two set screws does not

necessarily mean that the shaft holding power is doubled. This is
because shaft holding power is different depending on the open
angle (alignment) between two set screws. The following diagram
Technical Data

indicates the relationship between set screw open angles and 20 25 30 35 40 45 50 55 60

shaft holding power. Hardness of shaft [HRC]

Correlation between the set screws and shaft hardness and

θ shaft holding power

2.0
Magnification of shaft holding

1.8
power per set screw

1.6

1.4

1.2

1.0

0 30 60 90 120 150 180 In case

of one.
Set screw open angle θ
［゜］

Correlation between the set screw open angles and shaft

holding power

192
08_技術資料_E_p176_203.qxd 11.11.10 3:07 PM ページ193

■ Internal thread ■ Accuracy of fit between shaft and

zSet screw and length of fit hub or flange bore
Because of the widespread use of zinc die casting or iron
As indicated below, shaft holding power doesn't decrease till
sintered alloy an internal thread material, the maximum load of
shaft accuracy of h9. However, the effect of fit accuracy is
internal thread decreases, and which can be a source of trouble.
expected in the actual use environment.
However, it can be solved by increasing the thickness of the
internal thread part. The relationship between the length of fit and the
material strength is described below. Shaft diameter 15φ
1.0

External thread outside diameter= JIS 2 Class max

Decreasing rate of shaft holding power

Pitch diameter of internal thread= MIN
M5 C
γ=Allowable shear stress of internal thread [N/mm2] onca
ve po
int

15
M5 Fla
t point

0.5

9 8
γ=
Lower limit of length of fit [mm]

10

h10

h11
h7

h8

h9
47
γ=1

20 40 60 80 100 120
6
γ=19
5 Fit gap between bore and shaft [μm]
γ=294
γ=392 Correlation between the fit accuracy with bush bores and
shaft holding power

M3-98 M4-216 M5-441 M6-735

Nominal designation- Tightening torque [N・cm] Reference: Socket screw group technology
How to select and use hexagon socket set screw
Correlation between the strength of internal threads and set
screw lengths of fit

xOff-center distance of internal thread bore

If the internal thread bore is not centered with the shaft center, the shaft
holding power may decrease. The following is the test results using a
M4 set screw.

a
Set screw=M4
Shaft diameter=10φ
Technical Data

1.0
Decreasing rate of shaft holding power

0.5

0 1 2 3 4 5

Off-center amount a [mm]

Correlation between the off-center distance of setscrew

bores and shaft holding power

193
08_技術資料_E_p176_203.qxd 11.11.10 3:07 PM ページ194

Bearing mounting methods

B
R

rs

φDH

φDH
φdS

φdS

φD
φd
rs

Unit [mm] Unit [mm]

Nominal No. d D B rs min DH max ds min R max Nominal No. d D B rs min DH max ds min R max
6000 10 26 8 0.3 23.5 12.5 0.3 6201 12 32 10 0.6 27 17 0.6
6001 12 28 8 0.3 25.5 14.5 0.3 6202 15 35 11 0.6 30 20 0.6
6002 15 32 9 0.3 29.5 17.5 0.3 6203 17 40 12 0.6 35 22 0.6
6003 17 35 10 0.3 32.5 19.5 0.3 6204 20 47 14 1 41 26 1
6004 20 42 12 0.6 37 25 0.6 6205 25 52 15 1 46 31 1
6005 25 47 12 0.6 42 30 0.6 6206 30 62 16 1 56 36 1
6006 30 55 13 1 49 36 1 6208 40 80 18 1.1 73 47 1
6007 35 62 14 1 56 41 1 6210 50 90 20 1.1 83 57 1
6008 40 68 15 1 62 46 1 6211 55 100 21 1.5 91.5 63.5 1.5
6010 50 80 16 1 74 56 1 6212 60 110 22 1.5 101.5 68.5 1.5
6011 55 90 18 1.1 83 62 1 6214 70 125 24 1.5 116.5 78.5 1.5
6012 60 95 18 1.1 88 67 1 6302 15 42 13 1 36 21 1
6013 65 100 18 1.1 93 72 1 6303 17 47 14 1 41 23 1
6014 70 110 20 1.1 103 77 1 6304 20 52 15 1.1 45 27 1
6015 75 115 20 1.1 108 82 1 6305 25 62 17 1.1 55 32 1
* Seal symbol of each maker 6306 30 72 19 1.1 65 37 1
* NTN: LLB NSK: VV KOYO: 2RU
* rs min is the minimum permissible value of chamfering. 6307 35 80 21 1.5 71.5 43.5 1.5
Technical Data

194
08_技術資料_E_p176_203.qxd 11.11.10 3:07 PM ページ195

Groove dimensions for C-shaped

retaining rings (Excerpts from JIS B 2804-1978)

n m
m

φd 2
φd 4

φd 1
φd2

φd1
φd5

Unit [mm] Unit [mm]

d2 m n min d5 d2 m n min d4
d1 Basic dimensions Tolerances Basic dimensions Tolerances (References) (Reference values)
d1 Basic dimensions Tolerances Basic dimensions Tolerances (References) (Reference values)
 0
10 9.6 −0.09 17 26 27.2 ＋0.21 16
12 11.5 19 28 29.4  0 1.35 1.5 18
 0 1.15
15 14.3
−0.11
23 32 33.7 21
17 16.2 1.5 25 35 37 1.75 24
＋0.25
20 19 28 40 42.5 28
 0 1.35  0
25 23.9
−0.21
34 42 44.5 1.95 2 30
30 28.6 40 47 49.5 ＋0.14 34
1.75  0
35 33 46 52 55 39
＋0.14
40 38  0 53 55 58 2.2 41
1.95  0 ＋0.3
45 42.5 −0.25 58 62 65 48
 0
50 47 2 64 68 71 2.5 53
55 52 2.2 70 72 75 2.7 57
60 57 75 80 83.5 64
65 62  0 81 90 93.5 ＋0.35 73
70 67 −0.3 86 95 98.5  0 3.2 3 77
2.7 2.5
75 72 92 100 103.5 ＋0.18 82
80 76.5 97 110 114 ＋0.54  0 89
85 81.5 103 115 119  0 4.2 94
＋0.63
90 86.5  0 108 125 129  0 4 103
3.2 3
95 91.5 −0.35 114 ＊160 165 ＋0.7 ＋0.2 134
＋0.18 4.2
 100  96.5 119 ＊200 205  0  0 171
 0
110 106  0 131 * with * mark is not included in the JIS standard.
120 116 −0.54 4.2 4 143
 0
125 121 −0.63 148

Technical Data

195
08_技術資料_E_p176_203.qxd 11.11.10 3:07 PM ページ196

Physical and Mechanical Properties of Metals

■ Physical properties
Longitudinal elastic Rigidity Thermal Thermal expansions
Metal materials Ratios modulus ×103 modulus ×103 conductivities ×10−6
［N/mm2］ ［N/mm2］ ［W/(M・k)］ ［1/k］
Low-carbon steel (0.08C∼0.12C) 7.86 206 79 57∼60 11.3∼11.6
Medium carbon steel (0.40C∼0.50C) 7.84 205 82 44 10.7
High-carbon steel (0.8C∼1.6C) 7.81∼7.83 196∼202 80∼81 37∼43 9.6∼10.9
Chrome steel (SCr430) 7.84 ― ― 44.8 12.6 (300~470k)
Chrome-molybdenum steel (SCM440) 7.83 ― ― 42.7 12.3
Martensitic stainless steel (SUS410) 7.80 200 ― 24.9 9.9
Austenitic stainless steel (SUS304) 8.03 197 73.7 15 17.3
Tool steel (SKD6) 7.75 206 82 42.2(373k) 10.8
Gray iron (FC) 7.05∼7.3 73.6∼127.5 28.4∼39.2 44∼58.6 9.2∼11.8
Nodular graphite cast iron (FCD) 7.10 161 78 33.5∼37.7 10
Duralumin (A2017-T4) 2.79 69 ― 201 23.4
Super duralumin (A2024-T4) 2.77 74 29 121 23.2
Extra super duralumin (A7075-T6) 2.80 72 28 130 23.6
Lautan (AC2A-T6) 2.79 72 ― 121 24.0
Silumin (AC3A-F) 2.66 71 ― 121 20.4
Aluminum casting alloy (AC4CH-T6) 2.68 72 ― 151 21.5
Aluminum die casting alloy (ADC12) 2.70 72 ― 100 21.0
Zinc die casting alloy (ZDC-2) 6.60 89 ― 113 27.4

■ Mechanical properties
Yield points Tensile strengths Hardnesses
Metal materials
［N/mm2］ ［N/mm2］ ［HB］
S20C-N 245 402 116∼174
S30C-N 284 471 137∼197
S30C-H 333 539 152∼212
S45C-N 343 569 167∼229
S45-H 490 686 201∼269
SS400 216 402∼510 ―
SCM420 ― 932 262∼352
SCM435 785 932 269∼331
SUS303 206 520 187 or less
SUS304 206 520 200 or less
FC200 ― 200 223 or less
FC250 ― 250 241 or less
FC300 ― 300 262 or less
FC350 ― 350 277 or less
Technical Data

FCD400 250 400 201 or less

FCD450 280 450 143∼217
FCD500 320 500 170∼241
A2014-T4 245 412 ―
A2017-T4 196 353 ―
A7075-T6 471 539 ―

196
08_技術資料_E_p176_203.qxd 11.11.10 3:07 PM ページ197

World's power source conditions

Country names Frequencies Voltages

Japan 50Hz/60Hz Single-phase 100V, Three-phase200V

U.S.A. 60Hz Single-phase 120V, Three-phase240V
Canada 60Hz Single-phase 120V, Three-phase240V
Korea 60Hz Single-phase 220V, Three-phase220V/380V
Taiwan 60Hz Single-phase 110V/220V, Three-phase220V/380V
Hong Kong 50Hz Single-phase 200V, Three-phase346V
China 50Hz Single-phase 220V, Three-phase380V
Philipines 60Hz Single-phase 110V, Three-phase220V
Thailand 50Hz Single-phase 220V, Three-phase380V
Singapore 50Hz Single-phase 230V, Three-phase400V
Malaysia 50Hz Single-phase 240V, Three-phase415V
Indonesia 50Hz Single-phase 220V, Three-phase380V
Australia 50Hz Single-phase 240V, Three-phase415V
New Zealand 50Hz Single-phase 230V, Three-phase400V
Austria 50Hz Single-phase 220V, Three-phase380V
Belgium 50Hz Single-phase 220V, Three-phase380V
Bulgaria 50Hz Single-phase 220V, Three-phase380V
Denmark 50Hz Single-phase 220V, Three-phase380V
Finland 50Hz Single-phase 220V, Three-phase380V
France 50Hz Single-phase 220V, Three-phase380V
Germany 50Hz Single-phase 220V, Three-phase380V
Greece 50Hz Single-phase 220V, Three-phase380V
Hungary 50Hz Single-phase 220V, Three-phase380V
Italy 50Hz Single-phase 220V, Three-phase380V
Luxembourg 50Hz Single-phase 220V, Three-phase380V
Netherlands 50Hz Single-phase 220V, Three-phase380V
Norway 50Hz Single-phase 230V, Three-phase380V
Poland 50Hz Single-phase 220V, Three-phase380V
Portugal 50Hz Single-phase 220V, Three-phase380V
Romania 50Hz Single-phase 220V, Three-phase380V
Spain 50Hz Single-phase 220V, Three-phase380V
Sweden 50Hz Single-phase 220V, Three-phase380V
Technical Data

Switzerland 50Hz Single-phase 220V, Three-phase380V

England 50Hz Single-phase 240V, Three-phase415V
* The above voltages may differ depending on the area and the city in the country.
* The standard voltage of USA and Canada is a single-phase 115V, but it is normally indicated as 120V.

197
08_技術資料_E_p176_203.qxd 11.11.10 3:07 PM ページ198

General-purpose motor specifications list

■ Two-poles

Outputs [kW] 0.2 0.4 0.75 1.5 2.2 3.7 5.5 7.5 11 15 18.5 22 30 37 45

Frame numbers 63 71M 80M 90L 90L 112M 132S 132S 160M 160M 160L 180M 180L 200LB 200LB
Shaft diameters [mm] 11 14 19 24 24 28 38 38 42 42 42 48 55 55 55
200V 50Hz 1.1 2.0 3.5 6.0 9.0 14.2 21.5 28 41 55 67 82 109 133 161
Rated
currents 200V 60Hz 1.0 1.8 3.1 5.8 8.4 13.4 20 27 38 52 63 76 104 127 152
[A] 220V 60Hz 1.0 1.8 3.0 5.4 8.0 12.4 18.5 25 35 47 57 70 94 117 141
Rated 200V 50Hz 2800 2910 2890 2900 2870 2880 2900 2900 2910 2920 2920 2920 2930 2930 2930
rotation
speeds 200V 60Hz 3340 3480 3470 3470 3440 3440 3490 3480 3500 3510 3510 3510 3510 3510 3510
[minー1] 220V 60Hz 3400 3500 3490 3490 3460 3460 3510 3510 3520 3530 3530 3530 3530 3530 3530
* The above values are reference values. They may differ depending on the motor maker.

■ Four-poles

Outputs [kW] 0.2 0.4 0.75 1.5 2.2 3.7 5.5 7.5 11 15 18.5 22 30 37 45

Frame numbers 63 71M 80M 90L 100L 112M 132S 132M 160M 160L 180M 180M 180L 200LB 200L
Shaft diameters [mm] 11 14 19 24 28 28 38 38 42 42 48 48 55 60 60
200V 50Hz 1.26 2.5 3.9 7.0 9.9 15.8 23 30 44 58 72 84 114 139 168
Rated
currents 200V 60Hz 1.1 2.1 3.5 6.3 8.9 14.5 21 28 40 53 66 78 106 132 159
[A]
220V 60Hz 1.1 2.2 3.4 6.0 8.6 13.6 20 26 38 50 62 73 99 123 148
Rated 200V 50Hz 1430 1420 1420 1430 1430 1430 1440 1440 1450 1450 1455 1455 1460 1460 1460
rotation
speeds 200V 60Hz 1730 1700 1700 1720 1720 1710 1730 1730 1740 1740 1750 1750 1750 1750 1750
[minー1] 220V 60Hz 1740 1710 1710 1730 1730 1730 1740 1740 1750 1750 1760 1760 1760 1760 1760
* The above values are reference values. They may differ depending on the motor maker.

■ Six-poles

Outputs [kW] 0.2 0.4 0.75 1.5 2.2 3.7 5.5 7.5 11 15 18.5 22 30 37 45

Frame numbers 71 80M 90L 100L 112M 132S 132M 160M 160L 180M 180L 180L 200L 200L 225S
Shaft diameters [mm] 14 19 24 28 28 38 38 42 42 48 55 55 60 60 65
200V 50Hz 1.4 2.8 4.4 7.5 10.8 16.8 25 32 43 61 75 89 120 145 174
Rated
Technical Data

currents 200V 60Hz 1.3 2.5 3.9 6.8 9.8 16 23 28 40 56 69 82 110 134 163
[A]
220V 60Hz 1.3 2.5 3.9 6.6 9.4 15 22 27 38 53 65 77 105 128 156
Rated 200V 50Hz 930 940 940 940 950 940 950 960 960 965 965 965 970 970 970
rotation
speeds 200V 60Hz 1110 1130 1130 1120 1130 1120 1140 1150 1150 1160 1160 1160 1165 1165 1165
[minー1] 220V 60Hz 1120 1140 1140 1130 1140 1130 1150 1160 1160 1170 1165 1165 1170 1170 1170
* The above values are reference values. They may differ depending on the motor maker.

198