THETWO TORT DIT U HUMONUMUNUNUN US 20180010666A1

(19 ) United States

(12 )Marking
Patent Application Publication ( 10) Pub . No.: US 2018 /0010666 A1
(43) Pub . Date : Jan . 11, 2018
(54 ) REMOTELY OPERATED BYPASS FOR A Publication Classification
SUSPENSION DAMPER (51) Int. Ci.
(71) Applicant: Fox Factory, Inc ., Scotts Valley, CA F16F 9 /46 (2006 . 01 )
F16F 9 / 19 (2006 .01)
(US ) B60G 13 /08 ( 2006 . 01)
F16F 9 / 18 ( 2006 .01)
(72) Inventor: John Marking, El Cajon, CA (US) BOOG 17 /08 ( 2006 .01)
F16F 9 /34 ( 2006 .01)
(73 ) Assignee : Fox Factory , Inc ., Scotts Valley, CA B60G 13 / 06 ( 2006 .01)
(US) (52) U . S . CI.
??? ..... ...... ..... F16F 9 /46 (2013 .01) ; F16F 9 / 464
(21) Appl. No.: 15 /686,933 ( 2013 .01); F16F 9 / 34 ( 2013.01 ) ; F16F 9 / 19
(2013 .01) ; B60G 13 /06 ( 2013 . 01) ; F16F 9/ 18
(22) Filed : Aug . 25 , 2017 (2013 .01) ; B60G 17/08 (2013 . 01) ; B60G
13 /08 (2013 .01 ); B60G 2202/24 (2013 .01)
Related U .S . Application Data (57) ABSTRACT
(63 ) Continuation -in -part of application No. 15 /158 ,502 , A damper assembly with a bypass for a vehicle comprises a
filed on May 18 , 2016 , which is a continuation of pressure cylinder with a piston and piston rod for limiting
application No. 14 /038 ,507, filed on Sep . 26 , 2013, the flow rate of damping fluid as it passes from a first to a
now Pat. No . 9 , 353 ,818 , which is a continuation of second side of said piston . A bypass provides a fluid pathway
application No. 13 /010 ,697 , filed on Jan . 20 , 2011 , between the first and second sides of the piston separately
now Pat. No. 8 ,857 ,580. from the flow rare limitation . In one aspect, the bypass is
remotely controllable from a passenger compartment of the
(60 ) Provisional application No. 62 /379,487, filed on Aug . vehicle . In another aspect, the bypass is remotely control
25 , 2016 , provisional application No. 61/296 ,826 , lable based upon one ormore variable parameters associated
filed on Jan . 20 , 2010 . with the vehicle .

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Patent Application Publication Jan. 11 , 2018 Sheet 1 of 9 US 2018 /0010666 A1

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Patent Application Publication Jan. 11 , 2018 Sheet 2 of 9 US 2018 /0010666 A1

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Patent Application Publication Jan. 11 , 2018 Sheet 4 of 9 US 2018 /0010666 A1

POWER STEERING
FLUID

FIG .5 SWITCH

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VALVE

318 TRANSDUCER
(WHEEL ) ER INPUT INPUT
502
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TRANDUCER INPUT LOGIC UNIT

/CONTROL USER
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TRANSDUCER INPUT
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200
BY - PASS
FIG .6 VALVE

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FIG . 7
Patent Application Publication Jan . 11, 2018 Sheet 5 of 9 US 2018 /0010666 A1

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Patent Application Publication Jan. 11 , 2018 Sheet 6 of 9 US 2018 /0010666 A1

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Patent Application Publication Jan . 11, 2018 Sheet 7 of 9 US 2018 /0010666 A1

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Patent Application Publication Jan . 11, 2018 Sheet 8 of 9 US 2018 /0010666 A1

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Patent Application Publication Jan. 11 , 2018 Sheet 9 of 9 US 2018/ 0010666 A1

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US 2018 /0010666 A1 Jan . 11, 2018

REMOTELY OPERATED BYPASS FOR A pathway between the first and second portions of the cylin
SUSPENSION DAMPER der and may be independent of, or in conjunction with , the
aforementioned flow rate limitation . In one aspect, the
CROSS -REFERENCE TO RELATED bypass is remotely controllable from a passenger compart
APPLICATIONS ment of the vehicle . In another aspect, the bypass is remotely
[0001] This application claims benefit of United States controllable based upon one or more variable parameters
Provisional Patent Application Ser . No. 62/ 379 ,487, filed associated with the vehicle .
Aug. 25 , 2016 , which is herein incorporated by reference in BRIEF DESCRIPTION OF THE DRAWINGS
its entirety, and is also a continuation - in -part of U .S . patent
application Ser. No. 15 / 158 ,502 filed on May 18 , 2016 , [0008 ] So that the manner in which the above recited
entitled “ REMOTELY OPERATED BYPASS FOR A SUS features can be understood in detail, a more particular
PENSION DAMPER ” by John Marking , assigned to the description may be had by reference to embodiments , some
assignee of the present application, having Attorney Docket of which are illustrated in the appended drawings. It is to be
No. FOX - 0043US .CON2, which is herein incorporated by noted , however, that the appended drawings illustrate only
reference in its entirety. typical embodiments of this invention and are therefore not
[0002] The application with application Ser. No. 15 / 158 , to be considered limiting of its scope , for the invention may
502 claims to and is a continuation of the then co - pending admit to other equally effective embodiments .
U . S . patent application Ser. No . 14 /038 ,507 filed on Sep . 26 , [0009] FIG . 1 is a section view showing a suspension
2013 , now U . S . Pat. No. 9, 353,818 , entitled “ REMOTELY damping unit with a remotely operable bypass .
OPERATED BYPASS FOR A SUSPENSION DAMPER ” [0010 ] FIG . 2 is an enlarged section view showing the
by John Marking, assigned to the assignee of the present remotely operable valve of the bypass in the open position .
application , having Attorney Docket No. FOX -0043US. [0011 ] FIG . 3 is a section view showing the valve of FIG .
CON , and is hereby incorporated by reference in its entirety . 2 in a closed position .
[ 0003] The application with application Ser. Number
14 /038 , 507 claims to and is a continuation of the then [0012] FIG . 4 is a section view showing the valve of FIG .
co -pending U .S . patent application Ser. No. 13 /010 ,697 filed 2 in a locked -out position .
on Jan . 20 , 2011 , now U .S . Pat. No . 8 ,857 ,580 , entitled [0013] FIG . 5 is a schematic diagram showing a control
" REMOTELY OPERATED BYPASS FOR A SUSPEN arrangement for a remotely operated bypass .
SION DAMPER ” by John Marking , assigned to the assignee [0014 ] FIG . 6 is a schematic diagram showing another
of the present application , having Attorney Docket No. control arrangement for a remotely operated bypass .
FOXF /0043USP1, and is hereby incorporated by reference [0015 ] FIG . 7 is a graph showing some operational char
in its entirety . acteristics of the arrangement of FIG . 4 .
[0004 ] The application with application Ser. No. 13/010 , [0016 ] FIG . 8 is an enlarged section view showing a coil
697 claims priority to the then co -pending U .S . Provisional spring blow off system included in the remotely operable
Patent Application No. 61/296 , 826 , having Attorney Docket valve with of the bypass in the open position .
No. FOXF/0043USL , entitled “ BYPASS LOCK -OUT [0017 ] FIG . 9 is a section view showing the valve of FIG .
VALVE FOR A SUSPENSION DAMPER ” with the filing 8 in a closed position .
date of Jan . 20 , 2010 , by John Marking, and assigned to the [0018 ] FIG . 10 is an enlarged section view showing a coil
assignee of the present application . spring blow off system with a gas pressure supplement
BACKGROUND included in the remotely operable valve of the bypass in the
open position .
Field of the Invention [0019] FIG . 11 is a section view showing the valve of FIG .
10 in a closed position .
[0005 ] Embodiments of the present invention generally [0020 ] FIG . 12 is an enlarged section view showing a gas
relate to a damper assembly for a vehicle .More specifically , pressure supplement included in the remotely operable valve
certain embodiments relate to a remotely operated bypass of the bypass in the open position .
device used in conjunction with a vehicle damper. [0021 ] FIG . 13 is a section view showing the valve of FIG .
[ 0006 ] Vehicle suspension systems typically include a 12 in a closed position .
spring component or components and a dampening compo
nent or components. Typically , mechanical springs , like [0022] FIG . 14 is an enlarged section view showing the
helical springs are used with some type of viscous fluid remotely operable valve of the bypass that includes a
based dampening mechanism and the two are mounted preload adjuster in the open position .
functionally in parallel. In some instances features of the [0023 ] FIG . 15 is a section view showing the valve of FIG .
damper or spring are user -adjustable . What is needed is an 14 in a closed position .
improved method and apparatus for adjusting dampening [0024 ] FIG . 16 is a section view showing the valve ofFIG .
characteristics , including remote adjustment. 14 in a locked -out position .
SUMMARY OF THE INVENTION [0025 ] FIG . 17 is an enlarged section view showing the
remotely operable valve of the bypass that includes a
[0007] The present invention may be used with a damper preload adjuster and hydraulic pressure being applied to
assembly having a bypass . In one aspect, the assembly increase low speed damping .
comprises a cylinder with a piston and piston rod for limiting [0026 ] FIG . 18 is a section view showing the valve of FIG .
the flow rate of damping fluid as it passes from a first to a 17 with the hydraulic pressure being removed to reduce low
second portion of said cylinder. A bypass provides fluid speed damping .
US 2018 /0010666 A1 Jan . 11, 2018

DETAILED DESCRIPTION “ rebound ” ) fluid meters again through flow paths 110 and
the flow rate and corresponding rebound rate is controlled by
[0027] As used herein , the terms “ down” “ up ” “ down the shims 115 .
ward " " upward ” “ lower" " upper” and other directional 10029 ]. In FIG . 1, the piston 105 is shown at full extension
references are relative and are used for reference only . FIG . and moving downward in a compression stroke, the move
1 is a section view of a suspension damper unit 100 . The ment shown by arrow 157. A bypass assembly 150 includes
damper unit 100 includes a damper cylinder 102 with a rod a tubular body 155 that communicates with the damper
107 and a piston 105 . Typically , the fluid meters from one cylinder 102 through entry pathway 160 and exit pathway
side of the piston 105 to the other side by passing through 165 . The bypass assembly 150 permits damping fluid to
flow paths 110 , 112 formed in the piston 105 . In the travel from a first side of the piston 105 to the other side
embodiment shown , shims 115 , 116 are used to partially without traversing shimmed flow paths 110 , 112 that may
obstruct the flow paths 110 , 112 in each direction . By otherwise be traversed in a compression stroke of the
selecting shims 115 , 116 having certain desired stiffness damper unit 100 . In FIG . 1 , the bypass assembly 150 is
characteristics , the dampening effects caused by the piston shown in an “ open ” position with the flow of fluid through
105 can be increased or decreased and dampening rates can the bypass assembly 150 shown by arrows 156 from a
be different between the compression and rebound strokes of compression portion 104 to a rebound portion 103 of the
the piston 105 . For example , shims 115 are configured to piston 105 . In the embodiment of FIG . 1, the bypass
meter rebound flow from the rebound portion 103 of the assembly 150 includes a remotely controllable , needle - type
check valve /throttle valve 200, located proximate an exit
damper cylinder 102 to the compression portion 104 of the pathway 165 allowing flow in direction arrows 156 and
damper cylinder 102 . Shims 116 , on the other hand , are checking flow in opposite direction .
configured to meter compression flow from the 104 com [0030 ] The entry pathway 160 to the bypass assembly 150
pression portion of the cylinder to the rebound portion 103. in the embodiment shown in FIG . 1 is located towards a
In one embodiment, shims 116 are not included on the lower end of the damper cylinder 102. In one embodiment ,
rebound portion 103 side , nor is there a compression flow as selected by design , the bypass assembly 150 will not
path such as path 112 , leaving the piston 105 essentially operate after the piston 105 passes the entry pathway 160
“ locked out in the compression stroke without somemeans near the end of a compression stroke . This " position sensi
of flow bypass . Note that piston apertures (not shown ) may tive ” feature ensures increased dampening will be in effect
be included in planes other than those shown ( e . g . other than near the end of the compression stoke to help prevent the
apertures used by paths 110 and 112 ) and further that such piston from approaching a “ bottomed out” position (e . g .
apertures may , or may not, be subject to the shims 115 , 116 impact) in the damper cylinder 102 . In some instances,
as shown (because for example , the shims 115 , 116 may be multiple bypasses are used with a single damper and the
clover-shaped or have some other non -circular shape). entry pathways for each may be staggered axially along the
[0028 ] A reservoir 125 is in fluid communication with the length of the damper cylinder in order to provide an ever
damper cylinder 102 for receiving and supplying damping increasing amount of dampening (and less bypass ) as the
fluid as the rod 107 moves in and out of the damper cylinder piston moves through its compression stroke and towards
102. The reservoir 125 includes a reservoir cylinder 128 in the bottom of the damping cylinder. Each bypass may
fluid communication with a rebound portion 103 of the include some or all of the features described herein . Certain
damper cylinder 102 via fluid conduit 129 . The reservoir bypass damper features are described and shown in U . S . Pat.
also includes a floating piston 130 with a volume of gas on Nos . 6 ,296 ,092 and 6 ,415 ,895 , each of which are incorpo
a backside 131 ("blind end” side) of it, the gas being rated herein , in its entirety , by reference . Additionally, the
compressible as the reservoir cylinder 128 , on the " fron bypass assembly 150 and remotely controllable valve 200 of
tside” 132 fills with damping fluid due to movement of the the present embodiments can be used in any combination
rod 107 and piston 105 into the damper cylinder 102. Certain with the bypass valves shown and described in co -pending
features of reservoir type dampers are shown and described U . S. patent application Ser . No. 12 /684,072 .
in U .S . Pat. No. 7, 374 ,028, which is incorporated herein , in [0031] FIGS . 2 , 3 and 4 are enlarged views showing the
its entirety , by reference . The upper portion of the rod 107 remotely controllable valve 200 in various positions. In FIG .
is supplied with a bushing set 109 for connecting to a portion 2 , the remotely controllable valve 200 is in a damping -open
of a vehicle wheel suspension linkage . In another embodi position ( fluid path shown by arrow 201) permitting the
ment, not shown , the upper portion of the rod 107 (opposite bypass assembly 150 to operate in a compression stroke of
the piston ) may be supplied with an eyelet to be mounted to the damper unit 100. The remotely controllable valve 200
one part of the vehicle , while the lower part of the housing includes a valve body 204 housing a movable piston 205
shown with an eyelet 108 is attached to another portion of which is sealed within the body. Three fluid communication
the vehicle , such as the frame, that moves independently of points are provided in the body including an inlet 202 and
the first part. A spring member (not shown ) is usually outlet 203 for fluid passing through the remotely control
mounted to act between the same portions of the vehicle as lable valve 200 as well as an inlet 225 for control fluid as
the damper unit 100 . As the rod 107 and piston 105 move will be described herein . Extending from a first end of the
into damper cylinder 102 (during compression ), the damp piston 205 is a shaft 210 having a cone- shaped member 212
ing fluid slows the movement of the two portions of the (other shapes such as spherical or flat , with corresponding
vehicle relative to each other due to the incompressible fluid seats , will also work suitably well) disposed on an end
moving through the flow paths 112 (past shims 116 ) pro thereof . The cone- shaped member 212 is telescopically
vided in the piston 105 and/or through ametered bypass 150, mounted relative to , and movable on , the shaft 210 and is
as will be described herein . As the rod 107 and piston 105 biased in an extended position ( FIG . 3 ) due to a spring 215
move out of the damper cylinder 102 (during extension or coaxially mounted on the shaft 210 between the cone-shaped
US 2018 /0010666 A1 Jan . 11, 2018

member 212 and the piston 205 . Due to the spring 215 position, thereby preventing fluid flow through the bypass
biasing, the cone- shaped member 212 normally seats itself assembly 150 in either direction regardless of compression
against a seat 217 formed in an interior of the valve body or rebound stroke. In the embodiment shown, the control
204 . In the damping open position shown however, fluid inlet 225 provides a fluid path 230 to a piston surface 227
flow through the bypass assembly 150 has provided formed on an end of the piston 205 , opposite the cone
adequate force on the cone - shaped member 212 to urge it shaped member 212 . Specifically , activating pressure is
backwards, at least partially loading the spring 215 and introduced via inlet 225 to move the piston 205 and with it ,
creating fluid path 201 from the bypass assembly 150 into a cone -shaped member 212 toward seat 217 . Sufficient acti
rebound area of the damper cylinder 102 as shown in FIG . vating pressure fully compresses the spring 215 ( substantial
1 . The characteristics of the spring 215 are typically chosen stack out ) and /or closes the gap 220 thereby closing the
to permit the remotely controllable valve 200 ( e .g . cone cone -shaped member 212 against the seat, sealing the
shaped member 212) to open at a predetermined bypass bypass assembly 150 to both compression flow and rebound
pressure , with a predetermined amount of control pressure flow . In the embodiment shown , the remotely controllable
applied to inlet 225 , during a compression stroke of the valve 200 can be shifted to the third , locked - out position
damper unit 100 . For a given spring 215 , higher control from either the first, open position or the second , closed
pressure at inlet 225 will result in higher bypass pressure position . Note that, when in the “ locked out” position , the
required to open the remotely controllable valve 200 and remotely controllable valve 200 as shown will open to
correspondingly higher damping resistance in the bypass compression flow along path shown by arrows 156 when the
assembly 150 (more compression damping due to that compression flow pressure acting over the surface area of
bypass assembly 150 ). In one embodiment, the remotely the cone -shaped member 212 exceeds the inlet 225 pressure
controllable valve 200 is open in both directions when the acting over the surface area of the piston 205 . Such inlet 225
piston 205 is “ topped out” against valve body 204. In pressure may be selected to correspond therefore to a desired
another embodiment however, when the piston 205 is abut compression overpressure relief value or “ blow off " value
ted or " topped out ” against valve body 204 the spring 215 thereby allowing compression bypass under “ extreme” con
and relative dimensions of the remotely controllable valve ditions even when the bypass assembly 150 is “ locked out” .
200 still allow for the cone - shaped member 212 to engage [0034 ] In the embodiment illustrated , the remotely con
the valve seat thereby closing the remotely controllable trollable valve 200 is intended to be shifted to the locked - out
valve 200 . In such embodiment backflow from the rebound position with control fluid acting upon piston 205 . In one
portion 103 of the damper cylinder 102 to the compression embodiment, the activating pressure via inlet 225 is adjusted
portion 104 is always substantially closed and cracking so that the remotely controllable valve 200 is closed to
pressure from flow along path shown by arrows 156 is rebound fluid (with the cone -shaped member 212 in seat
determined by the pre -compression in the spring 215 . In 217 ) but with the spring 215 not fully compressed or stacked
such embodiment, additional fluid pressure may be added to out. In such a position , a high enough compression force
the inlet 225 through port to increase the cracking pressure ( e. g . compression flow ) will still open the remotely control
for flow along path shown by arrows 156 and thereby lable valve 200 and allow fluid to pass through the remotely
increase compression damping through the bypass assembly controllable valve 200 in a compression stroke. In one
150 over that value provided by the spring compression arrangement, the activating pressure , controlled remotely ,
“ topped out.” It is generally noteworthy that while the may be adjusted between levels where the lock -out is not
descriptions herein often relate to compression damping energized and levels where the lock -out is fully energized .
bypass and rebound shut off, some or all of the bypass The activating pressure may also be adjusted at intermediate
channels (or channel) on a given suspension unit may be levels to create more or less damping resistance through the
configured to allow rebound damping bypass and shut off or bypass assembly 150 . The activating pressure may be cre
impede compression damping bypass. ated by hydraulic or pneumatic input or any other suitable
[0032 ] FIG . 3 shows the remotely controllable valve 200 pressure source .
in a closed position (which it assumes during a rebound [0035 ] In one example , the remotely controllable valve
stroke of the damper unit 100 ). As shown, the cone - shaped 200 is moved to a locked - out position and the bypass feature
member 212 is seated against seat 217 due to the force of the is disabled by remote control from a simple operator
spring 215 and absent an opposite force from fluid entering actuated switch located in the passenger compartment of the
the remotely controllable valve 200 along path shown by vehicle . In one embodiment, fluid pressure for controlling
arrows 156 from the bypass assembly 150 . As cone - shaped (e.g . locking -out) the remotely controllable valve 200 is
member 212 telescopes out, a gap 220 is formed between the provided by the vehicle 's on - board source of pressurized
end of the shaft 210 and an interior of cone - shaped member hydraulic fluid created by, for example , the vehicle power
212 . A vent 221 is provided to relieve any pressure formed steering system . In one embodiment, pneumatic pressure is
in the gap 220 . With the fluid path 201 closed , fluid used to control ( e. g. close ) the remotely controllable valve
communication is substantially shut off from the rebound 200 where the pneumatic pressure is generated by an on
portion 103 of the damper cylinder 102 into the valve body board compressor and accumulator system and conducted to
204 (and hence through the bypass assembly 150 back to the the remotely controllable valve 200 via a fluid conduit . In
compression portion 104 is closed) and its “ dead -end” path one embodiment , a linear electric motor ( e . g . solenoid ), or
is shown by arrow 219 . other suitable electric actuator, is used , in lieu of the
[0033] Inlet 225 is formed in the valve body 204 for aforementioned inlet 225 pressure , to move the " piston 205 "
operation of the remotely controllable valve 200. In one axially within valve body 204 . A shaft of the electric actuator
embodiment inlet 225 may be pressurized to shift the (not shown) may be fixed to the piston 205 such that axial
remotely controllable valve 200 to a third or “ locked - out” movement of the shaft causes axial movement of the piston
position . In FIG . 4 , the valve 200 is shown in the locked -out 205 which in turn causes movement of the cone -shaped
US 2018 /0010666 A1 Jan . 11, 2018

member 212 (and compression of the spring 215 as appro damper mechanism of the damping piston comprises a
priate ). In one embodiment, the electric actuator is config pressure intensifier. In one embodiment one or both of the
ured to “push ” the piston 205 towards a closed position and dampers comprise standard shim type dampers . In one
to “ pull” the piston 205 away from the closed position embodiment one or both of the dampers include an adjust
depending on the direction of the current switched through able needle for low speed bleed . In one embodiment a blow
the actuator. off (e.g . checking poppet type or shim ) is included in one of
10036 ] As in other embodiments , the remotely controllable the flow paths or in a third parallel flow path .
valve 200 may be solenoid operated or hydraulically oper
ated or pneumatically operated or operated by any other [0041] FIG . 5 is a schematic diagram illustrating a control
suitable motive mechanism . The remotely controllable valve arrangement 400 used to provide remote control of a
200 may be operated remotely by a switch 415 or potenti remotely controllable valve 200 using a vehicle ' s power
ometer located in the cockpit of a vehicle or attached to steering fluid (although any suitable fluid pressure source
appropriate operational parts of a vehicle for timely activa may be substituted for reservoir 410 as could be an electrical
tion ( e. g. brake pedal) or may be operated in response to current source in the case of an remotely controllable valve
input from a microprocessor (e.g . calculating desired set 200 ). As illustrated , a fluid pathway 405 having a switch
tings based on vehicle acceleration sensor data ) or any operated valve ( and/ or pressure regulator ) 402 therein runs
suitable combination of activation means. In like manner, a from a fluid (or current) reservoir 410 that is kept pressur
controller for the adjustable pressure source ( or for both the ized by, in one embodiment, a power steering pump (not
source and the valve ) may be cockpit mounted and may be shown ) to a remotely controllable valve 200 that is operable ,
manually adjustable or microprocessor controlled or both or for example,by a user selectable dash board switch 415 . The
selectively either. switch -operated valve 402 permits fluid to travel to the
10037 ] It may be desirable to increase the damping rate remotely controllable valve 200, thereby urging it to a closed
when moving a vehicle from off -road to on highway use . position . When the switch 415 is in the " off " position ,
Off -road use often requires a high degree of compliance to working pressure within the damper unit 100 , and/ or a
absorb shocks imparted by the widely varying terrain . On biasing member such as a spring or annular atmospheric
highway use , particularly with long wheel travel vehicles, chamber (not shown ), returns the bypass assembly 150 to its
often requires more rigid shock absorption to allow a user to normally -open position (with or without residual spring
maintain control of a vehicle at higher speeds. This may be compression as designed ). In another embodiment, a signal
especially true during cornering or braking . line runs from the switch 415 to a solenoid along an
[0038 ] One embodiment comprises a four wheeled vehicle electrically conductive line . Thereafter, the solenoid con
having solenoid valve equipped shock absorbers at each (of verts electrical energy into mechanical movement (identified
four ) wheel. The remotely controllable valve 200 (which in by item 405 ) and shifts a plunger of the remotely control
one embodiment is cable operated instead of solenoid oper lable valve 200 , thereby opening or closing the valve or
ated ) of each of the front shock absorbers may be electrically causing the plunger to assume some predetermined position
connected with a linear switch 415 (such as that which in - between . Hydraulically actuated valving for use with
operates an automotive brake light ) that is activated in additional components is shown and described in U . S . Pat.
conjunction with the vehicle brake pedal. When the brake No . 6 ,073,536 and that patent is incorporated by reference
pedal is depressed beyond a certain distance , corresponding herein in its entirety .
usually to harder braking and hence potential for vehicle [0042 ] While FIG . 5 is simplified and involves control of
nose dive, the electric switch 415 connects a power supply a single bypass valve, it will be understood that the switch
to the normally open solenoid in each of the front shocks operated valve 402 could be plumbed to simultaneously or
thereby closing the paths in those shocks. As such the front selectively ( e . g . multi -position valve ) provide a signal to two
shocks become more rigid during hard braking. Other or more (e . g . four) bypass valves operable with two or more
mechanisms may be used to trigger the shocks such as vehicle dampers and /or with a single damper having mul
accelerometers ( e.g . tri-axial) for sensing pitch and roll of tiple bypass channels and multiple corresponding valves
the vehicle and activating , via a microprocessor, the appro (e .g . remotely controllable valve 200 ) (or multiple dampers
priate remotely controllable valve 200 for optimum vehicle having multiple bypass channels). Additional switches could
control. permit individual operation of separate damper bypass
[0039] In one embodiment, a vehicle steering column valves in individual bypass channels , whether on separate
includes right turn and left turn limit switches such that a dampers or on the samemultiple bypass damper , depending
hard turn in either direction activates the solenoid on the upon an operator ' s needs. While the example of FIG . 5 uses
shocks opposite that direction (for example a hard right turn fluid power for operating the remotely controllable valve
would cause more rigid shocks on the vehicle left side ). 200 , a variety of means are available for remotely control
Again , accelerometers in conjunction with a microprocessor ling a remotely controllable valve 200 . For instance , a
and a switched power supply may perform the solenoid source of electrical power from a 12 volt battery could be
activation function by sensing the actual g - force associated used to operate a solenoid member, thereby shifting a piston
with the turn ( or braking; or throttle acceleration for the rear 205 in remotely controllable valve 200 between open and
shock activation ) and triggering the appropriate solenoid (s ) closed positions . The remotely controllable valve 200 or
at a preset threshold g - force . solenoid operating signal can be either via a physical con
[ 0040 ] In one embodiment, a pressure intensifier damper ductor or an RF signal (or other wireless such as Bluetooth ,
arrangement may be located within the fluid path such that WiFi, ANT) from a transmitter operated by the switch 415
the solenoid - controlled valve controls flow through that to a receiver operable on the remotely controllable valve 200
auxiliary damper which is then additive with the damper (which would derive power from the vehicle power system
mechanism of the damping piston . In one embodiment the such as 12 volt).
US 2018 /0010666 A1 Jan . 11, 2018

[0043] A remotely controllable valve 200 like the one velocity in its travel towards the bottom end of a damper at
described above is particularly useful with an on /off road a predetermined speed of the vehicle . In one embodimentthe
vehicle . These vehicles can have as much as 20 " of shock system 500 adds dampening (and control) in the event of
absorber travel to permit them to negotiate rough , uneven rapid operation ( e . g . high rod velocity ) of the damper unit
terrain at speed with usable shock absorbing function . In 100 to avoid a bottoming out of the damper rod as well as
off-road applications, compliant dampening is necessary as a loss of control that can accompany rapid compression of
the vehicle relies on its long travel suspension when encoun a shock absorber with a relative long amount of travel. In
tering often large off-road obstacles . Operating a vehicle one embodiment the system 500 adds dampening (e.g .
with very compliant, long travel suspension on a smooth closes or throttles down the bypass ) in the event that the rod
road at higher speeds can be problematic due to the springi velocity in compression is relatively low , but the rod pro
ness/ sponginess of the suspension and corresponding gresses past a certain point in the travel. Such configuration
vehicle handling problems associated with that ( e. g . turning aids in stabilizing the vehicle against excessive low rate
roll, braking pitch ). Such compliance can cause reduced suspension movement events such as cornering roll, braking
handling characteristics and even loss of control. Such and acceleration yaw and pitch and “ g -out.”
control issues can be pronounced when cornering at high
speed as a compliant, long travel vehicle may tend to roll [0046 ] FIG . 6 illustrates , for example , a system including
excessively . Similarly, such a vehicle may pitch and yaw three variables: rod speed , rod position and vehicle speed .
excessively during braking and acceleration . With the Any or all of the variables shown may be considered by
remotely operated bypass dampening and “ lock out" processor 502 in controlling the solenoid in the remotely
described herein , dampening characteristics of a shock controllable valve 200 . Any other suitable vehicle operation
absorber can be completely changed from a compliantly variable may be used in addition to or in lieu of the variables
dampened “ springy ” arrangement to a highly dampened and 515 , 505 , 510 such as for example piton rod compression
“ stiffer” (or fully locked out) system ideal for higher speeds strain , eyelet strain , vehicle mounted accelerometer (or
on a smooth road . In one embodiment where compression tilt /inclinometer ) data or any other suitable vehicle or com
flow through the piston is completely blocked , closure of the ponent performance data . In one embodiment the position of
bypass assembly 150 results in substantial “ lock out” of the
suspension (the suspension is rendered essentially rigid piston 105 within damper cylinder 102 is determined using
except for the movement of fluid through shimmed valve) . an accelerometer to sense modal resonance of damper
In one embodiment where some compression flow is cylinder 102 . Such resonance will change depending on the
allowed through the piston 105 ( e . g . port 112 and shims position of the piston 105 and an on - board processor ( com
116 ), closure of the bypass assembly 150 ( closure of puter ) is calibrated to correlate resonance with axial posi
remotely controllable valve 200) results in a stiffer but still tion . In one embodiment, a suitable proximity sensor or
functional compression damper. linear coil transducer or other electro -magnetic transducer is
[0044 ] In one embodiment, the shims 116 are sized , to incorporated in the damper cylinder 102 to provide a sensor
optimize damping when the bypass assembly 150 is open to monitor the position and /or speed of the piston 105 (and
and when bypass assembly 150 is closed based on total suitable magnetic tag ) with respect to the damper cylinder
anticipated driving conditions. In one embodiment the 102 . In one embodiment, the magnetic transducer includes a
remotely controllable valve 200 is closed butmay be opened waveguide and a magnet, such as a doughnut ( toroidal)
at a predetermined compression flow pressure resulting in magnet that is joined to the cylinder and oriented such that
fairly stiff handling butmaintaining an ability for the vehicle the magnetic field generated by the magnet passes through
to absorb relatively large bumps. In one embodiment a the piston rod 107 and the waveguide. Electric pulses are
bypass assembly 150 having an entry pathway 160 located applied to the waveguide from a pulse generator that pro
axially toward an upward ( or “ rebound” end ) end of damper vides a stream of electric pulses , each of which is also
cylinder 102 remains wide open while other bypass channels provided to a signal processing circuit for timing purposes .
having corresponding openings 160 located axially more When the electric pulse is applied to the waveguide a
toward the compression end of damper cylinder 102 are magnetic field is formed surrounding the waveguide . Inter
closed or highly restricted . Such would result in a suspen action of this field with the magnetic field from the magnet
sion that would readily absorb small amplitude compres causes a torsional strain wave pulse to be launched in the
sions ( smooth highway ride ) but would resist large com waveguide in both directions away from the magnet. A coil
pression deflections of low force magnitude ( as during assembly and sensing tape is joined to the waveguide . The
heavy cornering or braking) and would absorb large deflec strain wave causes a dynamic effect in the permeability of
tions of high force magnitude. A vehicle so configured the sensing tape which is biased with a permanent magnetic
would ride well on pavement (smooth surface ), would field by the magnet. The dynamic effect in the magnetic field
absorb large unexpected bumps and would generally not of the coil assembly due to the strain wave pulse, results in
wallow when cornering or braking . an output signal from the coil assembly that is provided to
[0045 ] In addition to , or in lieu of, the simple , switch the signal processing circuit along signal lines. By compar
operated remote arrangement of FIG . 5 ; the remotely con ing the time of application of a particular electric pulse and
trollable valve 200 can be operated automatically based a time of return of a sonic torsional strain wave pulse back
upon one or more driving conditions. FIG . 6 shows a along the waveguide, the signal processing circuit can
schematic diagram of a remote control system 500 based calculate a distance of themagnet from the coil assembly or
upon any or all of vehicle speed , damper rod speed , and the relative velocity between the waveguide and the magnet.
damper rod position . One embodiment of the arrangement of The signal processing circuit provides an output signal,
FIG . 6 is designed to automatically increase dampening in a either digital, or analog , proportional to the calculated
shock absorber in the event a damper rod reaches a certain distance and /or velocity . A transducer -operated arrangement
US 2018 /0010666 A1 Jan . 11, 2018

for measuring rod speed and velocity is described in U . S . [0051] FIG . 7 is a graph that illustrates a possible opera
Pat. No . 5 , 952 ,823 and that patent is incorporated by refer- tion of one embodiment of the bypass assembly 500 of FIG .
ence herein in its entirety . 6 . The graph assumes a constant vehicle speed . For a given
[0047 ] While a transducer assembly located at the damper vehicle speed , rod position is shown on a y axis and rod
unit 100 measures rod speed and location , a separate wheel velocity is shown on an x axis. The graph illustrates the
speed transducer for sensing the rotational speed of a wheel possible on /off conditions of the bypass at combinations of
about an axle includes housing fixed to the axle and con relative rod position and relative rod velocity . For example,
taining therein , for example, two permanent magnets . In one it may be desired that the bypass is operable (bypass “ on ” )
embodiment the magnets are arranged such that an elon unless the rod is near its compressed position and /or the rod
gated pole piece commonly abuts first surfaces of each of the velocity is relatively high (such as is exemplified in FIG . 7).
magnets, such surfaces being of like polarity . Two inductive The on /off configurations of FIG . 7 are by way of example
coils having flux -conductive cores axially passing there only and any other suitable on / off logic based on the variable
through abut each of themagnets on second surfaces thereof, shown or other suitable variables may be used . In one
the second surfaces of the magnets again being of like
polarity with respect to each other and of opposite polarity embodiment it is desirable that the damper unit 100 become
with respect to the first surfaces . Wheel speed transducers relatively stiff at relatively low rod velocities and low rod
are described in U .S . Pat. No. 3 ,986 ,118 which is incorpo compressive strain (corresponding for example to vehicle
rated herein by reference in its entirety . roll, pitch or yaw ) but remains compliant in other positions .
[0048 ] In one embodiment, as illustrated in FIG . 6 , a logic In one embodiment the rod 107 includes a " blow off”
(overpressure relief valve typically allowing overpressure
unit 502 with user -definable settings receives inputs from flow from the compression portion 104 to the rebound
the rod speed 510 and location 505 transducers as well as the portion 103 ) valve positioned in a channel coaxially dis
wheel speed transducer 515 . The logic unit 502 is user
programmable and depending on the needs of the operator, posed though the rod 107 and communicating one side of the
the unit records the variables and then if certain criteria are piston 105 (and cylinder) with the other side of the piston
met, the logic circuit sends its own signal to the bypass to 105 (and cylinder ) independently of the apertures 110 ,112
either close or open ( or optionally throttle ) the remotely and the bypass assembly 150 .
controllable valve 200 . Thereafter, the condition of the [0052 ] In one embodiment, the logic shown in FIG . 6
bypass valve is relayed back to the logic unit 502 . assumes a single damper unit 100 but the logic circuit is
[0049] In one embodiment, the logic shown in FIG . 6 usable with any number of dampers or groups of dampers .
assumes a single damper but the logic circuit is usable with For instance , the dampers on one side of the vehicle can be
any number of dampers or groups of dampers . For instance , acted upon while the vehicles other dampers remain unaf
the dampers on one side of the vehicle can be acted upon fected .
while the vehicles other dampers remain unaffected .
[0050 ] While the examples illustrated relate to manual [0053] While the examples illustrated relate to manual
operation and automated operation based upon specific operation and automated operation based upon specific
parameters , the remotely controllable valve 200 or the parameters , the remotely operated bypass can be used in a
remote operation of pressure source 201 can be used in a variety of ways with many different driving and road vari
variety of ways with many different driving and road vari ables . In one example , the bypass is controlled based upon
ables. In one example , the remotely controllable valve 200 vehicle speed in conjunction with the angular location of the
is controlled based upon vehicle speed in conjunction with vehicle 's steering wheel. In this manner, by sensing the
the angular location of the vehicle 's steering wheel. In this steering wheel turn severity (angle of rotation ), additional
manner , by sensing the steering wheel turn severity (angle of dampening can be applied to one damper unit 100 or one set
rotation ), additional dampening can be applied to one of dampers on one side of the vehicle (suitable for example
damper or one set of dampers on one side of the vehicle to mitigate cornering roll ) in the event of a sharp turn at a
( suitable for example to mitigate cornering roll) in the event relatively high speed . In another example , a transducer , such
of a sharp turn at a relatively high speed . In another example, as an accelerometer measures other aspects of the vehicle ' s
a transducer, such as an accelerometer, measures other
aspects of the vehicle ' s suspension system , like axle force suspension system , like axle force and /or moments applied
and / ormoments applied to various parts of the vehicle , like to various parts of the vehicle , like steering tie rods, and
steering tie rods, and directs change to the bypass valve directs change to the bypass valve positioning in response
positioning in response thereto . In another example , the thereto . In another example, the bypass can be controlled at
bypass can be controlled at least in part by a pressure least in part by a pressure transducer measuring pressure in
transducer measuring pressure in a vehicle tire and adding a vehicle tire and adding dampening characteristics to some
dampening characteristics to some or all of the wheels in the or all of the wheels in the event of, for example, an increased
event of, for example , an increased or decreased pressure or decreased pressure reading. In one embodiment the
reading. In one embodiment, the damper bypass or bypasses damper bypass or bypasses are controlled in response to
are controlled in response to braking pressure (as measured , braking pressure (as measured for example by a brake pedal
for example, by a brake pedal sensor or brake fluid pressure sensor or brake fluid pressure sensor or accelerometer) In
sensor or accelerometer ). In still another example , a param still another example , a parameter might include a gyro
eter might include a gyroscopic mechanism that monitors scopic mechanism that monitors vehicle trajectory and iden
vehicle trajectory and identifies a " spin -out” or other loss of tifies a " spin -out” or other loss of control condition and adds
control condition and adds and /or reduces dampening to and /or reduces dampening to some or all of the vehicle 's
some or all of the vehicle ' s dampers in the event of a loss of dampers in the event of a loss of control to help the operator
control to help the operator of the vehicle to regain control. of the vehicle to regain control.
US 2018 /0010666 A1 Jan . 11 , 2018

Secondary Pressure Sensitive Bypass Check Valve bypass assembly 150 back to the compression portion 104 is
[0054 ] FIGS. 8 - 18 are enlarged views showing the closed ) and its “ dead -end ” path is shown by arrow 219 .
remotely controllable valve 200 in various positions and [0059] Preload adjuster 815 is formed in the valve body
204 for operation of the remotely controllable valve 200 .
with slightly different configurations. However, the remotely When comparing FIG . 8 and FIG . 9 it is apparent that the
controllable valve 200 shown in FIGS . 8 - 18 are similar to preload adjuster 815 has been moved inward significantly in
those shown in FIGS. 2 -4 . As such , and for purposes of FIG . 9 to provide additional force onto piston 205 from coil
clarity , unless otherwise indicated , it should be appreciated spring 810 .
that the components of FIGS . 8 - 18 are similar to those of
FIGS. 2 -4 and rely upon the previous descriptions found in [0060] FIG . 10 is an enlarged section view showing a coil
spring blow off system with a gas pressure supplement
the discussion of FIGS. 2 - 4 . included in the remotely operable valve with of the bypass
[0055 ] FIG . 8 is an enlarged section view showing a coil in the open position . For example , a gas such as nitrogen , air,
spring blow off system included in the remotely operable or the like , can be added via inlet 915 into air chamber 920 .
valve with of the bypass in the open position . In general, the The pressure of the gas can be adjusted remotely or at the
coil spring blow off system includes a coil spring 810 that is unit to vary the force required to open the remotely con
between a coil spring piston 820 and a preload adjuster 815 . trollable valve 200 . By increasing or decreasing the gas
The remotely controllable valve 200 is in a damping -open pressure in air chamber 920 low speed compression and
position (fluid path shown by arrow 201) permitting the rebound can be adjusted . Again , the blow off valve also
bypass assembly 150 to operate in a compression stroke of allows greater flow at high speed since the initial setting
the damper unit 100 . does not prevent full flow .
[ 0056 ] The remotely controllable valve 200 includes a [0061] FIG . 11 is a section view showing the remotely
valve body 204 housing a movable piston 205 which is controllable valve 200 of FIG . 10 in a closed position .
sealed within the body. Two fluid communication points are (which it assumes during a rebound stroke of the damper
provided in the body including an inlet 202 and outlet 203 unit 100 ). As shown , the cone - shaped member 212 is seated
for fluid passing through the remotely controllable valve due to the force of the spring 215 , coil spring 810 , and air
200 . On one end of piston 205 is shaft 210 having a pressure in gas chamber 920 , and absent an opposite force
cone -shaped member 212 (other shapes such as spherical or from fluid entering the remotely controllable valve 200
flat, with corresponding seats, will also work suitably well ) along path shown by arrows 156 from the bypass assembly
disposed on an end thereof. On the opposite end of piston 150 . With the fluid path 201 closed , fluid communication is
205 is shaft 830 which rests against coil spring piston 820 . substantially shut off from the rebound portion 103 of the
Coil spring piston 820 is being pressed on its other side by damper cylinder 102 into the valve body 204 ( and hence
coil spring 810 which is sandwiched between coil spring through the bypass assembly 150 back to the compression
piston 820 and preload adjuster 815 . Preload adjuster 815 portion 104 is closed ) and its “ dead - end” path is shown by
can be adjusted remotely or at the remotely controllable arrow 219 .
valve 200 by actions such as twisting, to increase or decrease [0062] Gas inlet 915 is formed in the valve body 204 for
the force applied to coil spring 810 . By varying the force on operation of the remotely controllable valve 200 . When
coil spring 810, the force required to open the valve can be comparing FIGS. 10 and 11 it is apparent that the air
varied . By adjusting preload adjuster 815 low speed com pressure in gas chamber 920 has been increased which has
pression and rebound in the area governed by the bypass moved coil spring piston 820 inward significantly in FIG . 11
tubes can be changed . Further, the coil spring blow off setup to provide additional force onto coil spring piston 820.
will allow greater flow at high speed since the initial setting 10063 ] FIG . 12 is an enlarged section view showing an air
does not prevent full flow . spring blow off system included in the remotely operable
[0057] The characteristics of coil spring 810 are typically valve with of the bypass in the open position . For example ,
chosen to permit the remotely controllable valve 200 (e .g . a gas such as nitrogen , air, or the like, can be added via inlet
cone- shaped member 212 ) to open at a predetermined 915 into air chamber 920 . The pressure of the gas can be
bypass pressure, with a predetermined amount of control adjusted remotely or at the unit to vary the force required to
pressure applied to inlet 225 , during a compression stroke of open the remotely controllable valve 200 . By increasing or
the damper unit 100 . For a given spring 215 , increased decreasing the gas pressure in air chamber 920 low speed
compression of coil spring 810 based on adjustments made compression and rebound can be adjusted . Again , the blow
to preload adjuster 815 will result in higher bypass pressure off valve also allows greater flow at high speed since the
required to open the remotely controllable valve 200 and initial setting does not prevent full flow .
correspondingly higher damping resistance in the bypass 10064 ] FIG . 13 is a section view showing the remotely
assembly 150 (more compression damping due to that controllable valve 200 of FIG . 12 in a closed position (which
bypass assembly 150). it assumes during a rebound stroke of the damper unit 100 ).
[0058 ] FIG . 9 shows the remotely controllable valve 200 As shown , the cone-shaped member 212 is seated due to the
in a closed position (which it assumes during a rebound force of the spring 215 and air pressure in gas chamber 920 ,
stroke of the damper unit 100 ). As shown , the cone - shaped and absent an opposite force from fluid entering the
member 212 is seated due to the force of the spring 215 and remotely controllable valve 200 along path shown by arrows
coil spring 810 , and absent an opposite force from fluid 156 from the bypass assembly 150 . With the fluid path 201
entering the remotely controllable valve 200 along path closed , fluid communication is substantially shut off from
shown by arrows 156 from the bypass assembly 150 . With the rebound portion 103 of the damper cylinder 102 into the
the fluid path 201 closed , fluid communication is substan valve body 204 ( and hence through the bypass assembly 150
tially shut off from the rebound portion 103 of the damper back to the compression portion 104 is closed ) and its
cylinder 102 into the valve body 204 ( and hence through the “ dead - end ” path is shown by arrow 219 .
US 2018 /0010666 A1 Jan . 11 , 2018

[0065 ] As described above, gas inlet 915 is formed in the secondary system to the shock will increase reliability . In the
valve body 204 for operation of the remotely controllable event of a failure of the secondary system , by retaining the
valve 200 . When comparing FIGS. 12 and 13 it is apparent primary check valve , the vehicle can continue on with the
that the air pressure in gas chamber 920 has been increased same characteristics as the current system provide .
to provide additional force onto coil spring piston 820 . [0071 ] While the foregoing is directed to embodiments of
[0066 ] FIG . 14 is an enlarged section view showing the the present invention , other and further embodiments of the
remotely operable valve of the bypass that includes a invention may be devised without departing from the basic
preload adjuster in the open position . FIG . 15 is a section scope thereof, and the scope thereof is determined by the
view showing the valve of FIG . 14 in a closed position . FIG . claims that follow .
16 is a section view showing the valve of FIG . 14 in a What we claim is:
locked -out position . In general, the operation ofFIGS. 14 - 16 1. A vehicle suspension damper comprising :
is the same as that of FIGS. 2 - 4 . For example , FIG . 14 shows a damper cylinder;
remotely controllable valve 200 in the open position similar a damping fluid disposed within said damper cylinder ;
to FIG . 2 ; FIG . 15 shows remotely controllable valve 200 in a piston assembly disposed within said damper cylinder,
the closed no rebound flow position similar to FIG . 3 ; and said piston assembly comprising:
FIG . 16 shows remotely controllable valve 200 in the a piston having a flow path formed through said piston ;
lockout energized position similar to FIG . 4 . a shim disposed to meter a flow of said damping fluid
[0067] However, in addition to the actions described in through said flow path ; and
FIGS. 2 -4 , FIGS. 14 - 16 utilize preload adjuster 815 to a piston rod coupled to said piston ; and
provide an additional layer of adjustment such that increased a bypass assembly providing a fluid pathway between a
pressure adjustments made to preload adjuster 815 will first side of said piston and a second side of said piston ,
result in higher bypass pressure required to open the said bypass assembly comprising:
remotely controllable valve 200 and correspondingly higher a remotely controllable valve for controlling the flow of
damping resistance in the bypass assembly 150 (more com said damping fluid through said bypass assembly,
pression damping due to that bypass assembly 150 ). said remotely controllable valve controlled by an
[0068] FIG . 17 is an enlarged section view showing the operator -actuated switch located in a passenger com
remotely operable valve of the bypass that includes a partment of a vehicle to which said vehicle suspen
preload adjuster and hydraulic pressure being applied from sion damper is coupled , and
to increase low speed damping . Similar to the discussion of a pneumatic input providing activating pressure to
FIG . 4 , in the embodiment shown , the control inlet 225 adjust the remotely controllable valve between an
provides a fluid path 230 to a piston surface 227 formed on open position , a lock -out position , and an interme
an end of the piston 205 , opposite the cone -shaped member diate position between the open position and the
212 . Specifically , activating pressure is introduced via inlet lock - out position .
225 to move the piston 205 and with it, cone- shaped member 2 . The vehicle suspension damper of claim 1 wherein the
212 toward seat 217 putting the maximum spring load on remotely controllable valve further comprising :
spring 215 . However, FIG . 17 also includes preload adjuster a closing member,
815 which can also be used in conjunction with control inlet the closing member comprising a moveable piston ;
225 such that less pressure is needed through inlet 225 to a seating member,
obtain the desired pre - load . In FIG . 17 , the increase in the the seating member selectively positionable with
spring pre - load results in an increase in low - speed damping . respect to the moveable piston ; and
[0069] FIG . 18 is a section view showing the valve of FIG . a biasing element interposed between the moveable piston
17 with the hydraulic pressure being removed to reduce low and the seating member to bias the seating member in
speed damping. That is , when the pressure is removed from a direction away from the moveable piston .
inlet 225 , the pre - load piston releases the spring 215 pre 3 . The vehicle suspension damper of claim 1 further
load thereby reducing low -speed damping. comprising:
[0070 ] Thus, using one or a combination of the additional a reservoir in fluid communication with said damper
features including coil spring 810 , preload adjuster 815 , coil cylinder , said reservoir comprising:
spring piston 820 , and inlet 915 , internal pressure sensitivity a reservoir cylinder portion ;
can be added to the position sensitivity of the bypass shock . a rebound portion in fluid communication with said
The secondary spring constantly adjusts flow to the pressure damper cylinder , and
created with each suspension event. In one embodiment, a floating piston disposed within said reservoir cylinder
using the gas plus spring 810 version adds infinite adjust portion .
ability of check valve crack pressure to aid with tuning . 4 . The vehicle suspension damper of claim 1 , wherein said
Moreover, the coil spring 810 can be adjusted similarly with remotely controllable valve is configured to selectively
spring rate and preload . It also adds reliability due to the permit said flow of said damping fluid through said bypass
simple mechanical nature . By providing the pressure sensi assembly .
tive characteristics, the remotely controllable valve 200 only 5 . The vehicle suspension damper of claim 1 , wherein said
allows the amount of flow thru the check valve that the remotely controllable valve is configured to selectively
suspension event demands. This simply and automatically prevent said flow of said damping fluid through said bypass
keeps the vehicle more stable in the low shaft speed events assembly .
such as braking turning and acceleration yet allows the 6 . The vehicle suspension damper of claim 1 wherein said
suspension to soak up the big hits and allows free movement damper cylinder further comprises:
in the square edge hits which makes the ride more comfort an entry pathway, said entry pathway located in said
able and controlled . Moreover , the added redundancy of the damper cylinder and fluidically coupling said bypass
US 2018 /0010666 A1 Jan . 11, 2018

assembly and said damper cylinder, said entry pathway a reservoir in fluid communication with said cylinder, said
disposed at a location in said damper cylinder such that reservoir comprising :
said damping fluid will not flow from said damper a reservoir cylinder portion ;
cylinder into said bypass assembly after said piston a rebound portion in fluid communication with said
passes said entry pathway during a compression stroke. cylinder ; and
7 . The vehicle suspension damper of claim 1 wherein said a floating piston disposed within said reservoir cylinder
remotely controllable valve is coupled to an on -board source portion .
of pressurized hydraulic fluid for a vehicle to which said 13 . The vehicle suspension damper of claim 11 , wherein
vehicle suspension damper is coupled . said remotely controllable valve is configured to :
selectively permit said flow of said damping fluid through
8 . The vehicle suspension damper of claim 1 wherein said said bypass assembly ; and
remotely controllable valve is coupled to a power steering selectively prevent said flow of said damping fluid
system for a vehicle to which said vehicle suspension through said bypass assembly .
damper is coupled . 14 . The vehicle suspension damper of claim 11 wherein
9. The vehicle suspension damper of claim 1 wherein said said cylinder further comprises:
remotely controllable valve is coupled to a pneumatic pres an entry pathway, said entry pathway located in said
sure , said pneumatic pressure is generated by an on -board cylinder and fluidically coupling said bypass assembly
compressor and accumulator system and conducted to said and said cylinder, said entry pathway disposed at a
remotely controllable valve via a fluid conduit, said on location in said cylinder such that said damping fluid
board compressor and said accumulator system coupled to will not flow from said cylinder into said bypass
said vehicle to which said vehicle suspension damper is assembly after said piston passes said entry pathway
coupled . during a compression stroke.
15 . The vehicle suspension damper of claim 11 wherein
10 . The vehicle suspension damper of claim 1 wherein said remotely controllable valve is coupled to an on -board
said remotely controllable valve is coupled to a linear source of pressurized hydraulic fluid for a vehicle to which
electric motor, said linear electric motor coupled to said said vehicle suspension damper is coupled .
vehicle to which said vehicle suspension damper is coupled . 16 . The vehicle suspension damper of claim 11 wherein
11 . A vehicle suspension damper comprising : said remotely controllable valve is coupled to a power
a cylinder; steering system for a vehicle to which said vehicle suspen
a damping fluid disposed within said cylinder ; sion damper is coupled .
17 . The vehicle suspension damper of claim 11 wherein
a piston assembly disposed within said cylinder, said said remotely controllable valve is coupled to a pneumatic
piston assembly comprising : pressure , said pneumatic pressure is generated by an on
a piston having a flow path formed through said piston ; board compressor and accumulator system and conducted to
a shim disposed to meter a flow of said damping fluid said remotely controllable valve via a fluid conduit, said
through said flow path ; and on - board compressor and said accumulator system coupled
a piston rod coupled to said piston ; and to said vehicle to which said vehicle suspension damper is
coupled .
a bypass assembly providing a fluid pathway between a 18 . The vehicle suspension damper of claim 11 wherein
first side of said piston and a second side of said piston , said remotely controllable valve is coupled to a linear
said bypass assembly comprising : electric motor, said linear electric motor coupled to said
a remotely controllable valve for permitting or prevent vehicle to which said vehicle suspension damper is coupled .
ing the flow of said damping fluid through said 19 . The vehicle suspension damper of claim 11 wherein
bypass assembly , said remotely controllable valve said variable parameter associated with said vehicle is
controlled based upon a variable parameter associ selected from the group consisting of : vehicle speed , piston
ated with a vehicle to which said vehicle suspension rod speed , and piston rod position .
damper is coupled , and 20 . The vehicle suspension damper of claim 11 wherein
a coil spring preload blow off assembly, said coil spring said variable parameter associated with said vehicle is
selected from the group consisting of: piston rod compres
preload blow off assembly comprising : sion strain , eyelet strain , vehicle mounted accelerometer
a coil spring piston having a first side abut to a data , and tilt / inclinometer data .
second piston rod coupled to an opposite side of 21 . The vehicle suspension damper of claim 11 wherein
said piston from said piston rod , said variable parameter associated with said vehicle is
a coil spring fixedly coupled between said coil spring selected from the group consisting of: speed of said vehicle
piston and a preload adjuster, in conjunction with an angular location of a steering wheel
the preload adjuster providing a variable level of of said vehicle , aspects of a suspension system of said
compression to said coil spring to vary a force vehicle , pressure in a tire of said vehicle , braking pressure
required to open the remotely controllable valve . applied to a brake of said vehicle , and trajectory of said
12 . The vehicle suspension damper of claim 11 further vehicle .
comprising: * * * *