US20220099154A1 - Suspension damper having inertia valve and user adjustable pressure-relief - Google Patents
Suspension damper having inertia valve and user adjustable pressure-relief Download PDFInfo
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- US20220099154A1 US20220099154A1 US17/397,770 US202117397770A US2022099154A1 US 20220099154 A1 US20220099154 A1 US 20220099154A1 US 202117397770 A US202117397770 A US 202117397770A US 2022099154 A1 US2022099154 A1 US 2022099154A1
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- pressure
- relief
- fluid
- valve
- inertia
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/50—Special means providing automatic damping adjustment, i.e. self-adjustment of damping by particular sliding movements of a valve element, other than flexions or displacement of valve discs; Special means providing self-adjustment of spring characteristics
- F16F9/504—Inertia, i.e. acceleration,-sensitive means
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
- B62K—CYCLES; CYCLE FRAMES; CYCLE STEERING DEVICES; RIDER-OPERATED TERMINAL CONTROLS SPECIALLY ADAPTED FOR CYCLES; CYCLE AXLE SUSPENSIONS; CYCLE SIDE-CARS, FORECARS, OR THE LIKE
- B62K25/00—Axle suspensions
- B62K25/04—Axle suspensions for mounting axles resiliently on cycle frame or fork
- B62K25/06—Axle suspensions for mounting axles resiliently on cycle frame or fork with telescopic fork, e.g. including auxiliary rocking arms
- B62K25/08—Axle suspensions for mounting axles resiliently on cycle frame or fork with telescopic fork, e.g. including auxiliary rocking arms for front wheel
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/06—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium using both gas and liquid
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/10—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium using liquid only; using a fluid of which the nature is immaterial
- F16F9/14—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect
- F16F9/16—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect involving only straight-line movement of the effective parts
- F16F9/18—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect involving only straight-line movement of the effective parts with a closed cylinder and a piston separating two or more working spaces therein
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/34—Special valve constructions; Shape or construction of throttling passages
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/44—Means on or in the damper for manual or non-automatic adjustment; such means combined with temperature correction
- F16F9/446—Adjustment of valve bias or pre-stress
Definitions
- the present invention is generally related to modern suspension dampers, such as shock absorbers and suspension forks used in vehicle suspensions. More particularly, the present invention is related to the field of suspension dampers having an inertia valve and a user adjustable pressure-relief feature.
- Suspension forks and/or shock absorbers are often utilized on vehicle suspensions, to absorb energy (e.g. bumps) imparted to the wheels by the terrain on which the vehicle is used.
- energy e.g. bumps
- the vehicle is a bicycle, such as a mountain bike or off-road bicycle
- the use of a suspension fork and/or shock absorber allows a rider to traverse rougher terrain, at a greater speed and with less fatigue in comparison to riding a rigid bicycle.
- a suspension fork having an adjustable pressure-relief valve is described.
- the valve can be adjusted “on-the-fly” and without the use of tools, since a control knob is positioned external to the suspension fork for easy manipulation by the user.
- Inertia valve dampers having pressure-relief features may have been suggested in the past, see e.g. U.S. Pat. No. 1,818,141 to Lang; U.S. Pat. No. 1,873,133 to Kindl; and U.S. Pat. No. 1,953,178, also to Kindl.
- dampers such as these, externally adjustable pressure-relief especially for use during the compression stroke does not appear to have been suggested.
- FIG. 1 depicts an overall schematic cross-section view of a leg of a suspension fork according to a first exemplary embodiment of the invention.
- FIG. 2 depicts an enlarged cross-section of a lower portion of the fork leg depicted in FIG. 1 .
- FIGS. 3A and 3B depict a base valve assembly of an exemplary embodiment of the invention in first and second configurations.
- FIGS. 4A and 4B depict the adjustable pressure-relief valve of an exemplary embodiment of the invention in closed and open configurations, respectively.
- FIG. 5 depicts an enlarged cross-section of a lower portion of a suspension fork according to a second exemplary embodiment of the invention.
- FIG. 6 depicts a non-adjustable fluid bleed feature that may be used with a base valve according to the various embodiments of the invention.
- FIG. 7 depicts an adjustable fluid bleed feature that may be used with a base valve according to the various embodiments of the invention.
- FIG. 8 depicts an assembly view of a suspension damper, in the form of a rear shock absorber having a remote reservoir, according to another exemplary embodiment of the invention.
- FIGS. 9A and 9B depict cross-section views of the rear shock absorber and remote reservoir of FIG. 8 , respectively.
- suspension dampers according to any of the various exemplary embodiments described herein, while being improvements relative to our earlier patents ('136, '948, and '751), incorporate much of the theory and most basic technology underlying our earlier patents. Accordingly, to maintain the clarity and conciseness of this patent application, where not critical to an understanding of the invention, reference should be made to our earlier '136, '948, and '751 patents, incorporated by reference herein, for a more detailed description of the various background technologies applicable to the invention. The present application will only point out the most important similarities and differences between the suspension dampers of the current invention and those of our earlier patents.
- the various aspects of the current invention may be implemented in different kinds of suspension dampers.
- the various aspects of the invention are especially suited for implementation in a front suspension fork or a rear shock absorber assembly of a bicycle.
- FIG. 1 depicts an overall schematic cross-section view of a leg 220 of a suspension fork 10 according to a first exemplary embodiment of the invention.
- FIG. 1 depicts a compressible fork leg 220 connected to a fork crown 232 (for connection to a second fork leg—not shown—and that may contain a spring mechanism).
- Fork leg 220 comprises a hollow upper tube 224 that is capable of telescopic motion in the compression and rebound directions relative to a hollow lower tube 226 .
- the lower tube 226 has a closed lower end and an open upper end.
- the upper tube 224 is received into the lower tube 226 through its open upper end.
- a seal 250 is provided at the location where the upper tube 224 enters the open end of the lower tube 226 and is preferably supported by the lower tube 226 and in sealing engagement with the upper tube 224 to substantially prevent damping and/or lubrication fluid from exiting, or a foreign material from entering, the fork leg 220 .
- a hydraulic damping system 240 provides a damping force in both the compression and rebound directions to slow both compression and rebound motions of the suspension fork by controlling the fluid flow of the damping fluid contained within the damping system 240 .
- the damping system 240 is preferably an open-bath, cartridge-type damper assembly having a damping cartridge tube 252 fixed with respect to the closed end of the lower tube 226 , defining a main fluid chamber 263 , and extending vertically upward.
- a damper shaft 254 extends vertically downward from a closed upper end of the upper tube 224 , through cartridge tube cap 260 , and supports a piston 258 at its lower end.
- the piston 258 is fixed for movement with the upper tube 224 while the cartridge tube 252 is fixed for movement with the lower tube 226 .
- the piston 258 divides the main fluid chamber 263 of the cartridge tube 252 into a first variable volume fluid chamber 262 and a second variable volume fluid chamber 264 , which may sometimes be referred to as a compression chamber (best seen in FIG. 2 ).
- the first chamber 262 is positioned above the piston 258 and the second chamber 264 is positioned below the piston 258 .
- a reservoir chamber 266 is defined between the outer surface of the cartridge tube 252 and the inner surfaces of the upper and lower tubes 224 , 226 .
- a base valve assembly 268 is positioned between the second chamber 264 and the reservoir chamber 266 and allows selective fluid communication therebetween. For clarity, the details of base valve assembly 268 are not depicted in FIGS. 1, 2 ; rather the details of base valve assembly 268 are shown in FIGS. 3A, 3B, 4A, 4B .
- Cartridge tube cap 260 includes a one-way refill valve 274 ( FIG. 2 ), which, during inward motion of the damper shaft 254 with respect to the cartridge tube 252 , allows fluid flow from the reservoir chamber 266 into the first chamber 262 .
- a one-way refill valve 274 FIG. 2
- damping fluid flows into and out of the damping cartridge tube 252 .
- Cartridge tube 252 may comprise an upper cartridge portion 290 ( FIG. 2 ) and a lower cartridge portion 292 , which are threadably engaged with a cartridge connector 294 to form the cartridge tube 252 .
- a one-piece cartridge tube may be employed.
- a base valve housing connector 296 is fixed to the end of the lower tube 226 and supports the cartridge tube 252 on top of the base valve assembly 268 (which is located in the cartridge tube 252 ).
- the lower cartridge portion 292 of the cartridge tube 252 is preferably threadably engaged with the base valve housing connector 296 .
- FIGS. 3A and 3B depict the details of a base valve assembly 268 according to an exemplary embodiment of the invention.
- the base valve assembly 268 may include a variety of different types of valves for regulating different aspects of fluid flow through damping mechanism 240 , such as, but not limited to: a compression valve 302 , a pressure-relief valve 400 , and a lockout feature in the form of an inertia valve 306 .
- the compression valve 302 includes a compression piston 318 sealingly engaged with the lower portion of the base valve housing connecter 296 .
- the compression valve 302 is positioned in a pocket formed by base valve housing 269 and base valve housing connector 296 .
- compression valve 302 controls the fluid flow of damping fluid that has passed through an open inertia valve 306 .
- the compression piston 318 includes one or more compression passages 326 covered by a compression shim stack 328 .
- the compression shim stack 328 is secured to the lower surface of the compression piston 318 by a shoulder 405 a of the pressure-relief chamber partition 405 .
- the compression shim stack 328 may deflect about the shoulder 405 a to selectively open the compression passages 326 and place them in fluid communication with compression outlet passages 378 during the compression of the suspension fork.
- the inertia valve 306 is preferably somewhat similar to the inertia valve previously described in our earlier '948 and '751 patents. Therefore, we will not provide a complete description of its structure and function at this time, since reference may be made to our other patents for more detail.
- inertia valve 306 includes an inertia mass 362 movable between a closed position, where the inertia mass 362 isolates inertia inflow passage 364 a from inertia outflow passage 364 b ( FIG. 3B ), and an open position, where an annular recess 380 in the inertia mass 362 places inertia inflow passage 364 a and inertia outflow passage 364 b in fluid communication with each other and inertia valve flow path 311 ( FIG. 3A ).
- Inflow and outflow passages 364 a , 364 b may generally comprise a plurality of radially aligned ports formed in the wall of the main fluid flow tube 298 .
- Inertia valve flow path 311 is formed by a space between main fluid flow tube 298 and pressure-relief tube 297 .
- fluid flow is allowed through annular recess 380 , through inertia valve flow path 311 , through the inertia valve fluid chamber 397 , and then through the compression passages 326 , past the shim stack 328 and into the reservoir chamber 266 through compression outlet passages 378 in the base valve housing 269 .
- the inertia valve 306 is closed ( FIG. 3B )
- fluid is, at least partially, and preferably substantially, prevented from flowing into the inertia valve flow path 311 .
- the inertia mass 362 is biased into its closed position ( FIG. 3B ) by inertia valve spring 366 (shown schematically).
- the inertia mass 362 of the current invention is preferably a solid block of high-density material, such as brass, as described in, for example, our earlier '751 and '948 patents. While the inertia mass 362 of the current invention is solid as distinguished from the inertia masses of our earlier patents, which included kidney-shaped axial flow passages to provide an exit for damping fluids displaced from the inertia valve pocket by the inertia mass (see e.g. FIGS. 4A-C of our earlier '948 patent), the current invention may also use the design of our earlier patents.
- fluid displaced from the inertia valve pocket 365 by the inertia mass 362 travels up a first displaced fluid gap 367 , past a displaced fluid check valve 368 , and up a second displaced fluid gap 369 .
- the displaced fluid check valve 368 by allowing fluid to enter and exit the inertia valve pocket 365 only at a controlled rate, facilitates the return of the inertia mass 362 to its rest (closed) position in a predetermined and predictable time period.
- the clearances of the displaced fluid check valves 368 can be important to the responsiveness and quick actuation of the inertia valve 306 .
- the clearances for check valves 368 should be between 0.001′′-0.010′′ wide and the second displaced fluid gap 369 should be between 0.030′′-0.200′′ wide.
- the suspension fork according to the invention is provided with a pressure-relief feature.
- the pressure-relief feature may comprise a pressure-relief valve 400 .
- the pressure-relief valve 400 which may sometimes be referred to as a blowoff valve, is positioned below the pressure-relief chamber partition 405 , and shown in more detail in FIGS. 4A and 4B (although the full details and description of the blow-off valve's operation may be found in our earlier '136 patent).
- the compression valve 302 and the pressure-relief valve 400 are fluidically isolated from one another by the pressure-relief chamber partition 405 .
- a pressure-relief chamber 308 is defined between base valve housing 269 and pressure-relief chamber partition 405 .
- Pressure-relief chamber 308 is in open and unrestricted fluid communication with compression chamber 264 (see FIG. 3A ). Fluid communication is achieved by a fluid passageway 407 in the pressure-relief chamber partition 405 that accesses a fluid passageway 297 a through pressure-relief tube 297 , which itself is positioned within main fluid flow tube 298 . Funnel 299 may be used for directing the fluid from compression chamber 264 into main fluid flow passageway 298 a and fluid passageway 297 a.
- pressure-relief piston 446 does not move relative to the pressure-relief inlet 444 and fluid flow from the pressure-relief chamber 308 to reservoir chamber 266 is substantially prevented ( FIG. 4A ).
- pressure-relief piston 446 will move relative to the pressure-relief inlet 444 and fluid flow from the pressure-relief chamber 308 to reservoir chamber 266 through pressure-relief outlets 454 is allowed ( FIG. 4B ).
- the inertia mass 362 will not move and remains in its closed position, preventing fluid flow through the annular recess 380 and into inertia valve flow path 311 ( FIG. 3B ).
- Increased pressure within the compression chamber 264 due to the force exerted on the suspension fork 10 is communicated through the main fluid flow passageway 298 a , fluid passages 297 a and 407 and into the pressure-relief chamber 308 .
- the pressure-relief valve 400 remains closed, substantially preventing fluid flow. Therefore, the suspension fork 10 remains substantially rigid because most fluid flow has been prevented (i.e., only movement resulting from a fluid bleed, clearance leakage, or fluid compressibility may occur). This is shown in FIG. 4A , where the compression flow does not continue past the pressure relief chamber 308 . Under these conditions, the damping cartridge 252 and suspension fork 10 are referred to as being “locked out”.
- the pressure-relief valve 400 selectively allows fluid flow from the compression chamber 264 to the reservoir 266 at high compressive fluid pressures or shaft speeds. Preferably, the pressure-relief valve 400 remains closed at low and mid-compressive fluid pressures or shaft speeds.
- “lock out” of the suspension fork 10 prevents rider pedal energy from being absorbed by the suspension fork 10 thereby allowing such energy to instead promote forward motion of the bicycle. If a large bump is encountered, such that the pressure within the compression chamber 264 rises above the threshold necessary to open the pressure-relief valve 400 , the valve 400 operates to allow fluid flow from the compression chamber 264 to the reservoir 266 .
- this prevents damage to the various seals of the suspension fork 10 and prevents the entire force of the bump from being transferred to the rider.
- the pressure-relief valve 400 will open to allow fluid to flow into the reservoir chamber 266 through the pressure-relief outlets 454 .
- the suspension fork 10 is able to compress and its compression damping rate is determined primarily by the spring rate of pressure-relief spring 448 of the pressure-relief valve 400 and the diameter of pressure-relief inlet 444 . This is referred to as “blowoff”. This use of the term “blowoff” should not be confused with the less common usage, such as in U.S. Pat. No. 6,120,049 (“blowoff” is used in the context of rebound refill check valves).
- the inertia mass 362 overcomes the biasing force of the inertia valve spring 366 and moves into a position that places the passages 364 a and 364 b into fluid communication with each other via annular recess 380 and fluid flow is allowed into the inertia valve flow path 311 formed by a space between main fluid flow tube 298 and pressure-relief tube 297 .
- This flow proceeds through the inertia valve fluid chamber 397 and then through the compression passages 326 , past the shim stack 328 and into the reservoir chamber 266 through compression outlet passages 378 in the base valve housing 269 , as illustrated in FIG. 3A .
- the inertia mass 362 when the inertia mass 362 is open (down), fluid is permitted to flow from the compression chamber 264 to the reservoir chamber 266 and the suspension fork 10 is able to compress.
- the compression damping rate is determined primarily by the spring rate of the compression shim stack 328 . Under these conditions, the damping cartridge 252 and suspension fork 10 are referred to as being not “locked out”.
- adjustable pressure-relief valve 400 may be very similar to the valve described as a blowoff valve in our earlier '136 patent and therefore we will not provide a complete description of its structure and function at this time, since reference may be made to our earlier '136 patent.
- a rotatable pressure-relief adjustment knob 432 positioned outside of the suspension fork provides the capability of easily adjusting the threshold pressure.
- knob 432 is attached to support shaft 462 . Therefore, rotation of knob 432 causes the rotation of the support shaft 462 . Furthermore, through threads in lower tube and support shaft 462 , rotation of support shaft 462 is converted to axial movement of the support shaft 462 relative to the base valve assembly 268 . This axial movement of the support shaft 462 changes the compressed or pre-loaded length of the portions of the pressure-relief feature positioned within the suspension fork, such as pressure-relief spring 448 , and thereby varies the pre-load on the pressure-relief spring 448 .
- the pre-load of the pressure-relief spring 448 influences the threshold pressure within the pressure-relief chamber 308 that is necessary to open the pressure-relief valve 400 . More pre-load raises the threshold pressure, while less pre-load decreases the threshold pressure.
- pressure-relief threshold adjustment knob 432 positioned external to the cartridge tube 252 , the suspension fork leg 220 , and tubes 224 , 226 , allows for the operator/rider to have the ability to select and/or adjust the threshold pressure on a regular basis and especially “on-the-fly”, in the sense of “on the trail” and without the use of tools was proposed.
- FIG. 5 depicts an enlarged cross-section of a lower portion of a suspension damper according to a second exemplary embodiment of the invention.
- This exemplary embodiment is similar to the first exemplary embodiment in that it comprises a suspension fork with a damping mechanism 240 ′ that includes a base valve assembly 268 ′ having an: inertia valve 306 ; a compression valve 302 and an adjustable pressure-relief valve 400 .
- What differentiates the second exemplary embodiment from the first exemplary embodiment are: the complete sealing of cartridge tube 252 , the inclusion of a fluid biasing element (for example, in the form of a bladder), and the elimination of reservoir chamber 266 . These differences convert the open-bath damper of the first exemplary embodiment into the closed damper of the second exemplary embodiment.
- Benefits of closed dampers over open-bath dampers are: decreased amount of damping fluid needed to operate the damping mechanism and less chance for the damping fluid to become aerated. Aeration tends to degrade the performance of damping fluid (i.e., degrades its incompressibility) and results in an effect sometimes referred to as “lockout lag”.
- base valve housing connector 296 ′ has been made unitary with the compression piston. Therefore, base valve housing connector 296 ′ has compression passages 326 ′ (in fluidic communication with the inertia valve flow path 311 ) selectively blocked by compression shim stack 328 . Similarly, base valve housing connector 296 ′ has first and second rebound passages 409 , 410 and rebound check plate 411 , loaded by rebound spring 412 , for controlling rebound flow through second rebound passage 410 .
- Base valve housing 269 of the first exemplary embodiment is now replaced with cartridge bottom 510 that is connected to base valve housing connector 296 ′ via extension cylinder 511 .
- a portion of the inner volume bound by the extension cylinder 511 defines an internal fluid reservoir 512 .
- a fluid biasing element preferably in the form of a bladder 520 , a well-known component in damping technology, and that may be made of any known flexible, fluid resistant, and resilient material.
- the bladder 520 preferably has an annular shape defining an open center portion 521 .
- Support shaft 462 ′ can extend through the open center portion 521 from the general area of the pressure-relief piston 446 ′ and pressure-relief spring 448 ′ to, and external of, cartridge bottom 510 .
- This annular bladder 520 is described in more detail in our co-pending application entitled “Damping Cylinder with Annular Bladder”, U.S. patent application Ser. No. 11/291,058, filed on Nov. 29, 2005, and incorporated by reference herein.
- bladder 520 acts in a manner similar to other fluid biasing elements, such as gas or coil spring-backed internal floating pistons (“IFPs”) to keep the damping fluid in the internal fluid reservoir 512 under pressure as the damping fluid exits and enters internal fluid reservoir 512 and keep the gas within bladder 512 and the damping fluid separate.
- IFPs gas or coil spring-backed internal floating pistons
- the second exemplary suspension fork embodiment there is no circulation of fluid outside of cartridge tube 252 during the operation of the damping mechanism 240 ′. This reduces the opportunity for the fluid to become aerated and have its performance degraded.
- the first exemplary embodiment has a cartridge tube 252 that was substantially sealed (i.e., fluid normally contained within the cartridge but can enter and leave the cartridge during rebound and compression, respectively)
- the second exemplary embodiment has a cartridge tube 252 that is completely sealed (i.e., fluid cannot enter and leave the cartridge absent deconstruction or rupturing of cartridge tube 252 ).
- a fluid bleed feature can be incorporated into any of the suspension dampers according to the various exemplary embodiments of the invention.
- An example of a fluid bleed is shown in FIG. 6 , which is a modification of the exemplary embodiment of FIG. 5 .
- pressure-relief piston 446 ′′ is not solid as depicted in other figures herein, but includes a bleed inlet passage 517 and a bleed outlet passage 519 , having an exemplary diameter of 0′′-0.012′′ that provides at least one alternative fluid path between fluid passage 297 a and internal fluid reservoir 512 to allow for a bleed flow Q.
- bleed passages 517 , 519 provide for only low speed fluid flows because at higher speeds, the resulting fluid pressures open the pressure-relief feature.
- An exemplary purpose for having this low-speed fluid bleed path is to provide a means by which when a rider mounts their bicycle (not shown) and places the initial load (i.e., their body weight) on the suspension fork, the suspension fork can slowly compress to its loaded position (“sag”).
- the suspension fork can slowly compress to its loaded position (“sag”).
- locked out either manually or by use of an inertia valve
- the suspension fork retains at least some degree of compressibility (regardless of whether the fluid pressure-relief valve has opened). Therefore, under such conditions the fork is not, nor would it be considered, “completely rigid”.
- the fluid bleed feature may also be manually adjustable.
- FIG. 7 An exemplary embodiment of a manually adjustable fluid bleed feature is shown in FIG. 7 .
- Pressure-relief spring 448 ′′ is maintained between pressure-relief piston 446 ′′ and the upper surface 462 a of shaft 462 .
- Support shaft 462 is now provided with a tapered bleed needle 525 at its upper end.
- bleed needle 525 will move towards or away from bleed inlet 517 in pressure-relief piston 446 ′′ (which is biased against pressure-relief inlet 444 ) to vary the size of the bleed path while also varying the pre-load on pressure-relief spring 448 ′′.
- Adjustable bleed allows a rider to control the rate at which the fluid may pass through the fixed-radius bleed inlet 517 and hence the ability of the suspension fork to sag or compensate for very low speed compression flows.
- FIG. 8 depicts an assembly view of a suspension damper 30 according to another exemplary embodiment of the invention, in the form of a compressible rear shock absorber 38 having a remote reservoir 44 .
- FIG. 9A depicts a cross-section view of the rear shock absorber 38 .
- FIG. 9B depicts a cross-section view of remote reservoir 44 , which contains an inertia valve 138 .
- rear shock absorber 38 is shown herein as fluidically connected to remote reservoir 44 by hose 46 , it is also possible for reservoir 44 to be a piggyback reservoir, as known in the art. The operation of suspension dampers such as these is described in great detail in our earlier '751 and '948 patents.
- the current exemplary embodiment of the invention provides these types of suspension dampers with an externally adjustable pressure-relief feature.
- reservoir 44 comprises a reservoir tube 122 containing an inertia valve 138 .
- reservoir tube 122 a portion of the adjustable pressure-relief feature is provided in the exemplary form of a pressure-relief port 540 and a pressure-relief valve 541 .
- Pressure-relief port 540 may be located in fastener 168 . When open, pressure-relief port 540 provides an additional fluid flow circuit between blowoff chamber 170 and reservoir chamber 128 (i.e., in addition to blowoff valve 140 ).
- Pressure-relief valve 541 comprises a pressure-relief valve element 545 , having a shaft portion 546 and a head portion 547 , is mounted for longitudinal movement in a pressure-relief bore 548 in control shaft 549 , and biased by spring 550 towards a position that blocks pressure-relief port 540 .
- Control shaft 549 is attached to an adjuster, positioned outside of the suspension damper, for example, a rotatable adjustment knob 551 , in any conventional manner that, depending upon the direction in which knob 551 is turned, control shaft 549 moves either towards or away from the blowoff valve 140 . Accordingly, depending upon the direction in which knob 551 is turned, the pre-load on spring 550 increases or decreases.
- the pre-load of spring 550 influences the threshold fluid pressure within the blowoff chamber 170 that is necessary to open the pressure-relief valve 541 . More pre-load raises the threshold pressure, while less pre-load decreases the threshold pressure. The pre-load created by spring 550 will never exceed the spring force/pressure needed to open blowoff valve 140 . Therefore, by the user rotating knob 551 , the user can manually adjust the threshold pressure.
- the blowoff valve 140 is primarily comprised of a cylindrical base and a blowoff cap.
- the upper end of the base is open and includes a threaded counterbore.
- the blowoff cap is includes a threaded outer surface engaging the threaded counterbore.
- a threaded fastener 168 fixes a valve seat of the pressure relief valve 541 to the blowoff cap.
- a lower end of the base is threaded and engages a threaded upper end of the reservoir shaft 134 .
- a floating piston is disposed in the reservoir chamber 128 and isolates gas from the damping fluid.
- the control shaft 549 extends through the floating piston.
- suspension damper 30 When suspension damper 30 is subjected to a bump-induced compression that is not of a magnitude or direction that causes inertia valve 138 to open, fluid pressure in central passage 136 of reservoir shaft 134 is communicated to blowoff chamber 170 .
- pressure-relief valve 541 When the fluid pressure in blowoff chamber 170 is greater than or equal to the threshold pressure required to overcome the pre-load of spring 550 , pressure-relief valve 541 will open and fluid will flow from blowoff chamber 170 to reservoir chamber 128 through pressure-relief port 540 . This fluid flow allows the shock absorber to compress.
- knob 551 positioned outside of the shock absorber 38 and the reservoir 44 , the operator/rider will have the ability to select and/or adjust the threshold pressure on a regular basis and especially “on-the-fly” (e.g. during the course of a ride) and without the use of tools.
- suspension fork 10 suspension fork (suspension damper) 30 suspension damper (shock absorber/reservoir) 38 rear shock absorber 44 remote reservoir 46 hose 122 reservoir tube 128 reservoir chamber 134 reservoir shaft 136 central passage 138 inertia valve assembly (remote reservoir) 140 blowoff valve 168 fastener 170 blowoff chamber 220 fork leg 224 upper tube 226 lower tube 232 crown 240 damping system 250 seal 252 damping cartridge tube 254 damper shaft 258 piston 260 tube cap 262 first variable volume fluid chamber 263 main fluid chamber 264 second variable volume fluid chamber/compression chamber 266 reservoir chamber 268 base valve assembly 269 base valve housing 274 refill valve 290 upper cartridge portion 292 lower cartridge portion 294 cartridge connector 296 base valve housing connector 297 pressure-relief flow tube 297a fluid passageway 298 main fluid flow tube 298a main fluid flow passage 299 funnel 302 compression valve 306 inertia valve 308 pressure-relief chamber 311 inertia valve flow path 318 compression piston 326
Abstract
Description
- This application claims priority to and is a continuation of the co-pending patent application Ser. No. 16/516,127, Attorney Docket Number FOX-0012USC6, entitled “SUSPENSION DAMPER HAVING INERTIA VALVE AND USER ADJUSTABLE PRESSURE-RELIEF,” with filing date Jul. 18, 2019, by William M. Becker et al., which is incorporated herein, in its entirety, by reference.
- The application with Ser. No. 16/516,127 claims priority to and is a continuation of the patent application Ser. No. 15/685,811, now U.S. Pat. No. 10,359,092, Attorney Docket Number FOX-0012USC5, entitled “SUSPENSION DAMPER HAVING INERTIA VALVE AND USER ADJUSTABLE PRESSURE-RELIEF,” with filing date Aug. 24, 2017, by William M. Becker et al., which is incorporated herein, in its entirety, by reference.
- The application with Ser. No. 15/685,811 claims priority to and is a continuation of the patent application Ser. No. 15/001,035, now U.S. Pat. No. 9,746,049, Attorney Docket Number FOX-0012USC4, entitled “SUSPENSION DAMPER HAVING INERTIA VALVE AND USER ADJUSTABLE PRESSURE-RELIEF,” with filing date Jan. 19, 2016, by William M. Becker et al., which is incorporated herein, in its entirety, by reference.
- The application with Ser. No. 15/001,035 claims priority to and is a continuation of the patent application Ser. No. 14/107,963, now U.S. Pat. No. 9,261,163, Attorney Docket Number FOXF/0012USC3, entitled “SUSPENSION DAMPER HAVING INERTIA VALVE AND USER ADJUSTABLE PRESSURE-RELIEF,” with filing date Dec. 16, 2013, by William M. Becker et al., which is incorporated herein, in its entirety, by reference.
- The application with Ser. No. 14/107,963 claims priority to and is a continuation of the patent application Ser. No. 13/555,364, now U.S. Pat. No. 8,607,942, Attorney Docket Number FOXF/0012USC2, entitled “SUSPENSION DAMPER HAVING INERTIA VALVE AND USER ADJUSTABLE PRESSURE-RELIEF,” with filing date Jul. 23, 2012, by William M. Becker et al., which is incorporated herein, in its entirety, by reference.
- The application with Ser. No. 13/555,364 claims priority to and is a continuation of the patent application Ser. No. 12/752,886, now U.S. Pat. No. 8,261,893, Attorney Docket Number FOXF/0012USC1, entitled “SUSPENSION DAMPER HAVING INERTIA VALVE AND USER ADJUSTABLE PRESSURE-RELIEF,” with filing date Apr. 1, 2010, by William M. Becker et al., which is incorporated herein, in its entirety, by reference.
- The application with Ser. No. 12/752,886 claims priority to and is a continuation of the patent application Ser. No. 11/535,552, now U.S. Pat. No. 7,699,146, Attorney Docket Number FOXF/0012, entitled “SUSPENSION DAMPER HAVING INERTIA VALVE AND USER ADJUSTABLE PRESSURE-RELIEF,” with filing date Sep. 27, 2006, by William M. Becker et al., which is incorporated herein, in its entirety, by reference.
- The application with Ser. No. 11/535,552 claims priority to the patent application, Ser. No. 60/744,128, Attorney Docket Number FOX-IV-002F-P, entitled “SUSPENSION DAMPER HAVING INERTIA VALVE AND USER-ADJUSTABLE PRESSURE-RELIEF,” with filing date Apr. 2, 2006, by William M. Becker, which is incorporated herein, in its entirety, by reference.
- This application is related to Assignee's patent application, entitled: Bicycle Fork Having Lock-out, Blow-off, and Adjustable Blow-off Threshold, U.S. patent application Ser. No. 10/620,323 filed Jul. 15, 2003, now U.S. Pat. No. 7,163,222, which is a continuation of Assignee's U.S. Pat. No. 6,592,136 (hereinafter the '136 patent).
- This application is also related to Assignee's patent applications, entitled: Inertia Valve Shock Absorber, U.S. patent application Ser. No. 10/778,882, filed Feb. 13, 2004, now U.S. Pat. No. 7,128,192, and Inertia Valve Shock Absorber, U.S. patent application Ser. No. 11/259,629, filed Oct. 26, 2005, now U.S. Pat. No. 7,273,137, both of which are children of Assignee's U.S. Pat. No. 6,581,948 (hereinafter the '948 patent) and U.S. Pat. No. 6,604,751 (hereinafter the '751 patent).
- All patents and patent applications referred to herein and especially our earlier '136, '948, and '751 patents are incorporated by reference in their entirety in this patent application.
- The present invention is generally related to modern suspension dampers, such as shock absorbers and suspension forks used in vehicle suspensions. More particularly, the present invention is related to the field of suspension dampers having an inertia valve and a user adjustable pressure-relief feature.
- Suspension forks and/or shock absorbers are often utilized on vehicle suspensions, to absorb energy (e.g. bumps) imparted to the wheels by the terrain on which the vehicle is used. When the vehicle is a bicycle, such as a mountain bike or off-road bicycle, the use of a suspension fork and/or shock absorber allows a rider to traverse rougher terrain, at a greater speed and with less fatigue in comparison to riding a rigid bicycle.
- In our earlier '136 patent, a suspension fork having an adjustable pressure-relief valve is described. The valve can be adjusted “on-the-fly” and without the use of tools, since a control knob is positioned external to the suspension fork for easy manipulation by the user.
- In our earlier '948 and '751 patents, rear shock absorbers and suspension forks having an inertia valve and a pressure-relief valve are described. However, in these two earlier patents, the threshold pressure at which the pressure-relief valve opens is not adjustable without a damper rebuild that involves using tools to replace the pressure-relief shim stack in the damper with another shim stack having a different thickness/spring rate.
- Inertia valve dampers having pressure-relief features may have been suggested in the past, see e.g. U.S. Pat. No. 1,818,141 to Lang; U.S. Pat. No. 1,873,133 to Kindl; and U.S. Pat. No. 1,953,178, also to Kindl. However, in dampers such as these, externally adjustable pressure-relief especially for use during the compression stroke does not appear to have been suggested.
- Thus, there is room for improvement within the art of suspension dampers, shock absorbers, suspension forks, and bicycle suspensions.
-
FIG. 1 depicts an overall schematic cross-section view of a leg of a suspension fork according to a first exemplary embodiment of the invention. -
FIG. 2 depicts an enlarged cross-section of a lower portion of the fork leg depicted inFIG. 1 . -
FIGS. 3A and 3B depict a base valve assembly of an exemplary embodiment of the invention in first and second configurations. -
FIGS. 4A and 4B depict the adjustable pressure-relief valve of an exemplary embodiment of the invention in closed and open configurations, respectively. -
FIG. 5 depicts an enlarged cross-section of a lower portion of a suspension fork according to a second exemplary embodiment of the invention. -
FIG. 6 depicts a non-adjustable fluid bleed feature that may be used with a base valve according to the various embodiments of the invention. -
FIG. 7 depicts an adjustable fluid bleed feature that may be used with a base valve according to the various embodiments of the invention. -
FIG. 8 depicts an assembly view of a suspension damper, in the form of a rear shock absorber having a remote reservoir, according to another exemplary embodiment of the invention. -
FIGS. 9A and 9B depict cross-section views of the rear shock absorber and remote reservoir ofFIG. 8 , respectively. - Prior to describing the various exemplary embodiments of the invention, it should be noted that suspension dampers according to any of the various exemplary embodiments described herein, while being improvements relative to our earlier patents ('136, '948, and '751), incorporate much of the theory and most basic technology underlying our earlier patents. Accordingly, to maintain the clarity and conciseness of this patent application, where not critical to an understanding of the invention, reference should be made to our earlier '136, '948, and '751 patents, incorporated by reference herein, for a more detailed description of the various background technologies applicable to the invention. The present application will only point out the most important similarities and differences between the suspension dampers of the current invention and those of our earlier patents. Additionally, where possible, reference numerals from the '136, '948 and '751 patents have been carried over to the present application. Furthermore, where a technical feature appears more than once in a FIG, in many instances only one reference numeral is included to prevent clutter. Finally, a table outlining the reference numerals used has been provided to aid cross-reference.
- The various aspects of the current invention may be implemented in different kinds of suspension dampers. In particular, however, the various aspects of the invention are especially suited for implementation in a front suspension fork or a rear shock absorber assembly of a bicycle.
- First, the invention will be described with respect to suspension dampers in the exemplary form of front suspension forks.
-
FIG. 1 depicts an overall schematic cross-section view of aleg 220 of asuspension fork 10 according to a first exemplary embodiment of the invention. - In particular,
FIG. 1 depicts acompressible fork leg 220 connected to a fork crown 232 (for connection to a second fork leg—not shown—and that may contain a spring mechanism).Fork leg 220 comprises a hollowupper tube 224 that is capable of telescopic motion in the compression and rebound directions relative to a hollowlower tube 226. - The
lower tube 226 has a closed lower end and an open upper end. Theupper tube 224 is received into thelower tube 226 through its open upper end. Aseal 250 is provided at the location where theupper tube 224 enters the open end of thelower tube 226 and is preferably supported by thelower tube 226 and in sealing engagement with theupper tube 224 to substantially prevent damping and/or lubrication fluid from exiting, or a foreign material from entering, thefork leg 220. - A hydraulic damping
system 240 provides a damping force in both the compression and rebound directions to slow both compression and rebound motions of the suspension fork by controlling the fluid flow of the damping fluid contained within the dampingsystem 240. In the first exemplary embodiment, the dampingsystem 240 is preferably an open-bath, cartridge-type damper assembly having a dampingcartridge tube 252 fixed with respect to the closed end of thelower tube 226, defining a mainfluid chamber 263, and extending vertically upward. Adamper shaft 254 extends vertically downward from a closed upper end of theupper tube 224, throughcartridge tube cap 260, and supports apiston 258 at its lower end. Thus, thepiston 258 is fixed for movement with theupper tube 224 while thecartridge tube 252 is fixed for movement with thelower tube 226. - The
piston 258 divides the mainfluid chamber 263 of thecartridge tube 252 into a first variablevolume fluid chamber 262 and a second variablevolume fluid chamber 264, which may sometimes be referred to as a compression chamber (best seen inFIG. 2 ). Thefirst chamber 262 is positioned above thepiston 258 and thesecond chamber 264 is positioned below thepiston 258. Areservoir chamber 266 is defined between the outer surface of thecartridge tube 252 and the inner surfaces of the upper andlower tubes base valve assembly 268 is positioned between thesecond chamber 264 and thereservoir chamber 266 and allows selective fluid communication therebetween. For clarity, the details ofbase valve assembly 268 are not depicted inFIGS. 1, 2 ; rather the details ofbase valve assembly 268 are shown inFIGS. 3A, 3B, 4A, 4B . -
Cartridge tube cap 260 includes a one-way refill valve 274 (FIG. 2 ), which, during inward motion of thedamper shaft 254 with respect to thecartridge tube 252, allows fluid flow from thereservoir chamber 266 into thefirst chamber 262. Thus, in an open-bath damper such as this, damping fluid flows into and out of the dampingcartridge tube 252. -
Cartridge tube 252 may comprise an upper cartridge portion 290 (FIG. 2 ) and alower cartridge portion 292, which are threadably engaged with acartridge connector 294 to form thecartridge tube 252. Optionally, a one-piece cartridge tube may be employed. A basevalve housing connector 296 is fixed to the end of thelower tube 226 and supports thecartridge tube 252 on top of the base valve assembly 268 (which is located in the cartridge tube 252). Thelower cartridge portion 292 of thecartridge tube 252 is preferably threadably engaged with the basevalve housing connector 296. -
FIGS. 3A and 3B depict the details of abase valve assembly 268 according to an exemplary embodiment of the invention. - The
base valve assembly 268 according to an exemplary embodiment of the invention may include a variety of different types of valves for regulating different aspects of fluid flow through dampingmechanism 240, such as, but not limited to: acompression valve 302, a pressure-relief valve 400, and a lockout feature in the form of aninertia valve 306. - The
compression valve 302 includes acompression piston 318 sealingly engaged with the lower portion of the basevalve housing connecter 296. Thecompression valve 302 is positioned in a pocket formed bybase valve housing 269 and basevalve housing connector 296. As will be described below,compression valve 302 controls the fluid flow of damping fluid that has passed through anopen inertia valve 306. - The
compression piston 318 includes one ormore compression passages 326 covered by acompression shim stack 328. Thecompression shim stack 328 is secured to the lower surface of thecompression piston 318 by ashoulder 405 a of the pressure-relief chamber partition 405. Thecompression shim stack 328 may deflect about theshoulder 405 a to selectively open thecompression passages 326 and place them in fluid communication withcompression outlet passages 378 during the compression of the suspension fork. - The
inertia valve 306 is preferably somewhat similar to the inertia valve previously described in our earlier '948 and '751 patents. Therefore, we will not provide a complete description of its structure and function at this time, since reference may be made to our other patents for more detail. - Generally,
inertia valve 306 includes aninertia mass 362 movable between a closed position, where theinertia mass 362 isolatesinertia inflow passage 364 a frominertia outflow passage 364 b (FIG. 3B ), and an open position, where anannular recess 380 in theinertia mass 362 placesinertia inflow passage 364 a andinertia outflow passage 364 b in fluid communication with each other and inertia valve flow path 311 (FIG. 3A ). Inflow andoutflow passages fluid flow tube 298. Inertiavalve flow path 311 is formed by a space between mainfluid flow tube 298 and pressure-relief tube 297. When theinertia valve 306 is open (FIG. 3A ), fluid flow is allowed throughannular recess 380, through inertiavalve flow path 311, through the inertiavalve fluid chamber 397, and then through thecompression passages 326, past theshim stack 328 and into thereservoir chamber 266 throughcompression outlet passages 378 in thebase valve housing 269. When theinertia valve 306 is closed (FIG. 3B ), fluid is, at least partially, and preferably substantially, prevented from flowing into the inertiavalve flow path 311. - The
inertia mass 362 is biased into its closed position (FIG. 3B ) by inertia valve spring 366 (shown schematically). Theinertia mass 362 of the current invention is preferably a solid block of high-density material, such as brass, as described in, for example, our earlier '751 and '948 patents. While theinertia mass 362 of the current invention is solid as distinguished from the inertia masses of our earlier patents, which included kidney-shaped axial flow passages to provide an exit for damping fluids displaced from the inertia valve pocket by the inertia mass (see e.g.FIGS. 4A-C of our earlier '948 patent), the current invention may also use the design of our earlier patents. - In the current invention, fluid displaced from the
inertia valve pocket 365 by theinertia mass 362 travels up a first displacedfluid gap 367, past a displacedfluid check valve 368, and up a second displacedfluid gap 369. The displacedfluid check valve 368, by allowing fluid to enter and exit theinertia valve pocket 365 only at a controlled rate, facilitates the return of theinertia mass 362 to its rest (closed) position in a predetermined and predictable time period. - Finally, the clearances of the displaced
fluid check valves 368 can be important to the responsiveness and quick actuation of theinertia valve 306. We have determined that the clearances forcheck valves 368 should be between 0.001″-0.010″ wide and the second displacedfluid gap 369 should be between 0.030″-0.200″ wide. - The suspension fork according to the invention is provided with a pressure-relief feature. The pressure-relief feature may comprise a pressure-
relief valve 400. The pressure-relief valve 400, which may sometimes be referred to as a blowoff valve, is positioned below the pressure-relief chamber partition 405, and shown in more detail inFIGS. 4A and 4B (although the full details and description of the blow-off valve's operation may be found in our earlier '136 patent). Thecompression valve 302 and the pressure-relief valve 400 are fluidically isolated from one another by the pressure-relief chamber partition 405. A pressure-relief chamber 308 is defined betweenbase valve housing 269 and pressure-relief chamber partition 405. - Pressure-
relief chamber 308 is in open and unrestricted fluid communication with compression chamber 264 (seeFIG. 3A ). Fluid communication is achieved by afluid passageway 407 in the pressure-relief chamber partition 405 that accesses afluid passageway 297 a through pressure-relief tube 297, which itself is positioned within mainfluid flow tube 298. Funnel 299 may be used for directing the fluid fromcompression chamber 264 into mainfluid flow passageway 298 a andfluid passageway 297 a. - When the fluid pressure of the damping fluid within the pressure-
relief chamber 308 has not achieved a threshold value sufficient to overcome the pre-load of pressure-relief spring 448, pressure-relief piston 446 does not move relative to the pressure-relief inlet 444 and fluid flow from the pressure-relief chamber 308 toreservoir chamber 266 is substantially prevented (FIG. 4A ). - When the fluid pressure of the damping fluid within the pressure-
relief chamber 308 achieves a threshold value sufficient to overcome the pre-load of pressure-relief spring 448, pressure-relief piston 446 will move relative to the pressure-relief inlet 444 and fluid flow from the pressure-relief chamber 308 toreservoir chamber 266 through pressure-relief outlets 454 is allowed (FIG. 4B ). - Having described the basic structure of a
suspension fork 10 and abase valve assembly 268 according to an exemplary embodiment of the invention, their basic operation will now be described. - When the front wheel (not shown) of a bicycle (not shown) encounters a bump, as is generally known to those skilled in the art, a force is exerted on the
suspension fork 10 that tends to compress thefork tubes lower fork tube 226. If the upward acceleration of thelower fork tube 226 along its longitudinal axis (which is the same as the axis of travel of the inertia mass 362) is below a predetermined threshold defined by the pre-load oninertia valve spring 366, theinertia mass 362 will not move and remains in its closed position, preventing fluid flow through theannular recess 380 and into inertia valve flow path 311 (FIG. 3B ). Increased pressure within thecompression chamber 264 due to the force exerted on thesuspension fork 10 is communicated through the mainfluid flow passageway 298 a,fluid passages relief chamber 308. - If the fluid pressure within the pressure-
relief chamber 308 has not achieved the threshold value needed to overcome the pre-load of pressure-relief spring 448, the pressure-relief valve 400 remains closed, substantially preventing fluid flow. Therefore, thesuspension fork 10 remains substantially rigid because most fluid flow has been prevented (i.e., only movement resulting from a fluid bleed, clearance leakage, or fluid compressibility may occur). This is shown inFIG. 4A , where the compression flow does not continue past thepressure relief chamber 308. Under these conditions, the dampingcartridge 252 andsuspension fork 10 are referred to as being “locked out”. - The pressure-
relief valve 400 selectively allows fluid flow from thecompression chamber 264 to thereservoir 266 at high compressive fluid pressures or shaft speeds. Preferably, the pressure-relief valve 400 remains closed at low and mid-compressive fluid pressures or shaft speeds. Advantageously, “lock out” of thesuspension fork 10 prevents rider pedal energy from being absorbed by thesuspension fork 10 thereby allowing such energy to instead promote forward motion of the bicycle. If a large bump is encountered, such that the pressure within thecompression chamber 264 rises above the threshold necessary to open the pressure-relief valve 400, thevalve 400 operates to allow fluid flow from thecompression chamber 264 to thereservoir 266. Advantageously, this prevents damage to the various seals of thesuspension fork 10 and prevents the entire force of the bump from being transferred to the rider. - If the fluid pressure within the pressure-
relief chamber 308 due to the fluid flow of damping fluid into pressure-relief chamber 308 achieves the threshold pressure needed to overcome the pre-load of pressure-relief spring 448, the pressure-relief valve 400 will open to allow fluid to flow into thereservoir chamber 266 through the pressure-relief outlets 454. Thus, thesuspension fork 10 is able to compress and its compression damping rate is determined primarily by the spring rate of pressure-relief spring 448 of the pressure-relief valve 400 and the diameter of pressure-relief inlet 444. This is referred to as “blowoff”. This use of the term “blowoff” should not be confused with the less common usage, such as in U.S. Pat. No. 6,120,049 (“blowoff” is used in the context of rebound refill check valves). - When the upward acceleration of the
lower fork leg 226 exceeds a predetermined threshold, theinertia mass 362 overcomes the biasing force of theinertia valve spring 366 and moves into a position that places thepassages annular recess 380 and fluid flow is allowed into the inertiavalve flow path 311 formed by a space between mainfluid flow tube 298 and pressure-relief tube 297. This flow proceeds through the inertiavalve fluid chamber 397 and then through thecompression passages 326, past theshim stack 328 and into thereservoir chamber 266 throughcompression outlet passages 378 in thebase valve housing 269, as illustrated inFIG. 3A . Accordingly, at pressures lower than the predetermined pressure-relief pressure, when theinertia mass 362 is open (down), fluid is permitted to flow from thecompression chamber 264 to thereservoir chamber 266 and thesuspension fork 10 is able to compress. The compression damping rate is determined primarily by the spring rate of thecompression shim stack 328. Under these conditions, the dampingcartridge 252 andsuspension fork 10 are referred to as being not “locked out”. - In some prior inertia valve suspension forks, such as those described in our earlier '751 and '948 patents, pressure-relief was achieved using a pressure-relief shim stack for controlling the fluid flow between what is called a blowoff chamber, the separator chamber, and the reservoir (see
FIG. 17 and associated text in our earlier '751 and '948 patents). In these prior designs, there is no capability to externally (and especially “on-the-fly”) adjust the threshold pressure because the pressure-relief feature was contained entirely inside the suspension damper. Therefore, the threshold pressure could only be changed by taking the suspension fork and cartridge apart and replacing the pressure-relief shim stack with another shim stack having a different thickness/spring rate. This process was not conducive to the operator/rider selecting and/or adjusting the threshold pressure on any regular basis and especially “on-the-fly” (e.g. during the course of a ride) and without the use of tools. - However, as described in our earlier '136 patent, it is often preferable for the operator/rider to have the ability to select and/or adjust the threshold pressure on a regular basis. Therefore, an ability to adjust the threshold pressure “on-the-fly”, in the sense of “on the trail” and without the use of tools was proposed.
- Accordingly, the
suspension fork 10 according to the current invention has been provided with a pressure-relief feature in the form of an adjustable pressure-relief valve 400 having portions positioned inside and outside the suspension fork. As previously mentioned, adjustable pressure-relief valve 400 may be very similar to the valve described as a blowoff valve in our earlier '136 patent and therefore we will not provide a complete description of its structure and function at this time, since reference may be made to our earlier '136 patent. - However, generally, a rotatable pressure-
relief adjustment knob 432, positioned outside of the suspension fork provides the capability of easily adjusting the threshold pressure. - In particular,
knob 432 is attached to supportshaft 462. Therefore, rotation ofknob 432 causes the rotation of thesupport shaft 462. Furthermore, through threads in lower tube andsupport shaft 462, rotation ofsupport shaft 462 is converted to axial movement of thesupport shaft 462 relative to thebase valve assembly 268. This axial movement of thesupport shaft 462 changes the compressed or pre-loaded length of the portions of the pressure-relief feature positioned within the suspension fork, such as pressure-relief spring 448, and thereby varies the pre-load on the pressure-relief spring 448. The pre-load of the pressure-relief spring 448 influences the threshold pressure within the pressure-relief chamber 308 that is necessary to open the pressure-relief valve 400. More pre-load raises the threshold pressure, while less pre-load decreases the threshold pressure. - Thus, pressure-relief
threshold adjustment knob 432, positioned external to thecartridge tube 252, thesuspension fork leg 220, andtubes -
FIG. 5 depicts an enlarged cross-section of a lower portion of a suspension damper according to a second exemplary embodiment of the invention. This exemplary embodiment is similar to the first exemplary embodiment in that it comprises a suspension fork with a dampingmechanism 240′ that includes abase valve assembly 268′ having an:inertia valve 306; acompression valve 302 and an adjustable pressure-relief valve 400. What differentiates the second exemplary embodiment from the first exemplary embodiment are: the complete sealing ofcartridge tube 252, the inclusion of a fluid biasing element (for example, in the form of a bladder), and the elimination ofreservoir chamber 266. These differences convert the open-bath damper of the first exemplary embodiment into the closed damper of the second exemplary embodiment. Benefits of closed dampers over open-bath dampers are: decreased amount of damping fluid needed to operate the damping mechanism and less chance for the damping fluid to become aerated. Aeration tends to degrade the performance of damping fluid (i.e., degrades its incompressibility) and results in an effect sometimes referred to as “lockout lag”. - As shown in
FIG. 5 , the differences between the first exemplary embodiment and the second exemplary embodiment generally begin in the area of basevalve housing connector 296′. In this second exemplary embodiment, basevalve housing connector 296′ has been made unitary with the compression piston. Therefore, basevalve housing connector 296′ hascompression passages 326′ (in fluidic communication with the inertia valve flow path 311) selectively blocked bycompression shim stack 328. Similarly, basevalve housing connector 296′ has first andsecond rebound passages check plate 411, loaded byrebound spring 412, for controlling rebound flow throughsecond rebound passage 410. -
Base valve housing 269 of the first exemplary embodiment is now replaced withcartridge bottom 510 that is connected to basevalve housing connector 296′ viaextension cylinder 511. A portion of the inner volume bound by theextension cylinder 511 defines aninternal fluid reservoir 512. Additionally, withinextension cylinder 511 is a fluid biasing element, preferably in the form of abladder 520, a well-known component in damping technology, and that may be made of any known flexible, fluid resistant, and resilient material. Thebladder 520 preferably has an annular shape defining anopen center portion 521.Support shaft 462′ can extend through theopen center portion 521 from the general area of the pressure-relief piston 446′ and pressure-relief spring 448′ to, and external of,cartridge bottom 510. Thisannular bladder 520 is described in more detail in our co-pending application entitled “Damping Cylinder with Annular Bladder”, U.S. patent application Ser. No. 11/291,058, filed on Nov. 29, 2005, and incorporated by reference herein. - As is known in the art,
bladder 520 acts in a manner similar to other fluid biasing elements, such as gas or coil spring-backed internal floating pistons (“IFPs”) to keep the damping fluid in theinternal fluid reservoir 512 under pressure as the damping fluid exits and enters internalfluid reservoir 512 and keep the gas withinbladder 512 and the damping fluid separate. - Having described the basic structure of a
suspension fork 10 according to this second exemplary embodiment of the invention and in the form of a closed damper that does not allow fluid to flow into and out of the dampingcartridge 252, its basic operation will now be described. - a) Inertia Valve Closed—Fluid flows down
fluid passage 297 a, through pressure-relief inlet 444 and into contact with pressure-relief piston 446′. If the fluid threshold pressure is reached, the fluid pressure on pressure-relief piston 446′ will overcome the pre-load of pressure-relief spring 448′ and cause pressure-relief piston 446′ to descend and open, and fluid flow intoreservoir 512 throughpassage 409 is allowed. If the threshold pressure is not reached, the fluid pressure on pressure-relief piston 446 will not overcome the pre-load of pressure-relief spring 448′, pressure-relief piston 446′ will remain closed, and fluid flow intointernal fluid reservoir 512 throughpassage 409 will be substantially prevented. Therefore,tubes suspension fork 10 will remain substantially rigid. - b) Inertia Valve Open—Fluid flows down inertia
valve flow path 311, through inertiavalve fluid chamber 397, and intocompression passages 326′. The fluid pressure on the fluid will overcome the spring force ofcompression shim stack 328 and fluid will flow intointernal fluid reservoir 512 providing the fork the ability to compress. - c) Rebound—As
tubes compression chamber 264, fluid will flow from theinternal fluid reservoir 512 back to thecompression chamber 264. This rebound flow will travel uppassages rebound spring 412, deflectrebound plate 411 and allow the fluid flow to continue uppassage 297′ and back into thecompression chamber 264. - Thus, with the second exemplary suspension fork embodiment, there is no circulation of fluid outside of
cartridge tube 252 during the operation of the dampingmechanism 240′. This reduces the opportunity for the fluid to become aerated and have its performance degraded. In other words, while the first exemplary embodiment has acartridge tube 252 that was substantially sealed (i.e., fluid normally contained within the cartridge but can enter and leave the cartridge during rebound and compression, respectively), the second exemplary embodiment has acartridge tube 252 that is completely sealed (i.e., fluid cannot enter and leave the cartridge absent deconstruction or rupturing of cartridge tube 252). - A fluid bleed feature can be incorporated into any of the suspension dampers according to the various exemplary embodiments of the invention. An example of a fluid bleed is shown in
FIG. 6 , which is a modification of the exemplary embodiment ofFIG. 5 . - In
FIG. 6 , pressure-relief piston 446″ is not solid as depicted in other figures herein, but includes ableed inlet passage 517 and ableed outlet passage 519, having an exemplary diameter of 0″-0.012″ that provides at least one alternative fluid path betweenfluid passage 297 a andinternal fluid reservoir 512 to allow for a bleed flow Q. These bleedpassages - The fluid bleed feature may also be manually adjustable.
- An exemplary embodiment of a manually adjustable fluid bleed feature is shown in
FIG. 7 . Pressure-relief spring 448″ is maintained between pressure-relief piston 446″ and theupper surface 462 a ofshaft 462.Support shaft 462 is now provided with atapered bleed needle 525 at its upper end. Thus, asshaft 462 axially moves as it is rotated by turningknob 432, bleedneedle 525 will move towards or away frombleed inlet 517 in pressure-relief piston 446″ (which is biased against pressure-relief inlet 444) to vary the size of the bleed path while also varying the pre-load on pressure-relief spring 448″. - Adjustable bleed allows a rider to control the rate at which the fluid may pass through the fixed-
radius bleed inlet 517 and hence the ability of the suspension fork to sag or compensate for very low speed compression flows. -
FIG. 8 depicts an assembly view of a suspension damper 30 according to another exemplary embodiment of the invention, in the form of a compressiblerear shock absorber 38 having aremote reservoir 44.FIG. 9A depicts a cross-section view of therear shock absorber 38.FIG. 9B depicts a cross-section view ofremote reservoir 44, which contains aninertia valve 138. Whilerear shock absorber 38 is shown herein as fluidically connected toremote reservoir 44 byhose 46, it is also possible forreservoir 44 to be a piggyback reservoir, as known in the art. The operation of suspension dampers such as these is described in great detail in our earlier '751 and '948 patents. - The current exemplary embodiment of the invention provides these types of suspension dampers with an externally adjustable pressure-relief feature.
- According to this exemplary embodiment of the current invention, as shown in
FIG. 9B ,reservoir 44 comprises areservoir tube 122 containing aninertia valve 138. Withinreservoir tube 122, a portion of the adjustable pressure-relief feature is provided in the exemplary form of a pressure-relief port 540 and a pressure-relief valve 541. Pressure-relief port 540 may be located in fastener 168. When open, pressure-relief port 540 provides an additional fluid flow circuit betweenblowoff chamber 170 and reservoir chamber 128 (i.e., in addition to blowoff valve 140). Pressure-relief valve 541 comprises a pressure-relief valve element 545, having ashaft portion 546 and ahead portion 547, is mounted for longitudinal movement in a pressure-relief bore 548 incontrol shaft 549, and biased byspring 550 towards a position that blocks pressure-relief port 540.Control shaft 549 is attached to an adjuster, positioned outside of the suspension damper, for example, arotatable adjustment knob 551, in any conventional manner that, depending upon the direction in whichknob 551 is turned,control shaft 549 moves either towards or away from theblowoff valve 140. Accordingly, depending upon the direction in whichknob 551 is turned, the pre-load onspring 550 increases or decreases. As with other embodiments of the invention described herein, the pre-load ofspring 550 influences the threshold fluid pressure within theblowoff chamber 170 that is necessary to open the pressure-relief valve 541. More pre-load raises the threshold pressure, while less pre-load decreases the threshold pressure. The pre-load created byspring 550 will never exceed the spring force/pressure needed to openblowoff valve 140. Therefore, by theuser rotating knob 551, the user can manually adjust the threshold pressure. - The
blowoff valve 140 is primarily comprised of a cylindrical base and a blowoff cap. The upper end of the base is open and includes a threaded counterbore. The blowoff cap is includes a threaded outer surface engaging the threaded counterbore. A threaded fastener 168 fixes a valve seat of the pressure relief valve 541 to the blowoff cap. A lower end of the base is threaded and engages a threaded upper end of thereservoir shaft 134. A floating piston is disposed in the reservoir chamber 128 and isolates gas from the damping fluid. Thecontrol shaft 549 extends through the floating piston. - Having described the basic structure of a suspension damper 30 according to this exemplary embodiment of the invention and in the form of a
rear shock absorber 38 having aremote reservoir 44, its basic operation will now be described. - When suspension damper 30 is subjected to a bump-induced compression that is not of a magnitude or direction that causes
inertia valve 138 to open, fluid pressure incentral passage 136 ofreservoir shaft 134 is communicated toblowoff chamber 170. When the fluid pressure inblowoff chamber 170 is greater than or equal to the threshold pressure required to overcome the pre-load ofspring 550, pressure-relief valve 541 will open and fluid will flow fromblowoff chamber 170 to reservoir chamber 128 through pressure-relief port 540. This fluid flow allows the shock absorber to compress. - When
shock absorber 38 is subjected to a large bump-induced compression that is still not of a magnitude or direction that causesinertia valve 138 to open, the fluid flow throughcentral passage 136 ofreservoir shaft 134 greatly increases the fluid pressure withinblowoff chamber 170. Despite the fact that pressure-relief valve 541 will open and allow some fluid flow through pressure-relief port 540, if the fluid pressure withinblowoff chamber 170 achieves a high enough value, the threshold pressure ofblowoff valve 140 will be overcome and fluid will flow from theblowoff chamber 170 to the reservoir chamber 128 via theblowoff valve 140. - Thus, using
knob 551, positioned outside of theshock absorber 38 and thereservoir 44, the operator/rider will have the ability to select and/or adjust the threshold pressure on a regular basis and especially “on-the-fly” (e.g. during the course of a ride) and without the use of tools. - Though the invention has been described with respect to certain exemplary embodiments, the scope of the invention is solely limited by the scope of the appended claims.
-
-
10 suspension fork (suspension damper) 30 suspension damper (shock absorber/reservoir) 38 rear shock absorber 44 remote reservoir 46 hose 122 reservoir tube 128 reservoir chamber 134 reservoir shaft 136 central passage 138 inertia valve assembly (remote reservoir) 140 blowoff valve 168 fastener 170 blowoff chamber 220 fork leg 224 upper tube 226 lower tube 232 crown 240 damping system 250 seal 252 damping cartridge tube 254 damper shaft 258 piston 260 tube cap 262 first variable volume fluid chamber 263 main fluid chamber 264 second variable volume fluid chamber/compression chamber 266 reservoir chamber 268 base valve assembly 269 base valve housing 274 refill valve 290 upper cartridge portion 292 lower cartridge portion 294 cartridge connector 296 base valve housing connector 297 pressure-relief flow tube 297a fluid passageway 298 main fluid flow tube 298a main fluid flow passage 299 funnel 302 compression valve 306 inertia valve 308 pressure-relief chamber 311 inertia valve flow path 318 compression piston 326 compression passages 328 compression shim stack 362 inertia mass 364a inertia inflow passage 364b inertia outflow passage 365 inertia valve pocket 366 spring 367 first displaced fluid gap 368 displaced fluid check valve 369 second displaced fluid gap 378 compression outlet passages 380 annular recess 397 inertia valve fluid chamber 400 pressure-relief valve 405 pressure-relief chamber partition 405a pressure-relief chamber partition shoulder 407 fluid passageway 409 first rebound passage 410 second rebound passage 411 rebound check plate 412 rebound spring 432 knob 444 pressure-relief inlet 446 pressure-relief piston 448 pressure-relief spring 454 pressure-relief outlet 462 support shaft 462 shaft portion 462a stationary surface 510 cartridge bottom 511 extension cylinder 512 internal fluid reservoir 517 bleed inlet 519 bleed outlet 520 bladder 521 open center portion (of bladder) 525 bleed needle 540 pressure relief port 541 pressure-relief valve 545 pressure-relief valve element 546 pressure-relief valve shaft portion 547 pressure-relief valve head portion 548 pressure-relief bore 549 control shaft 550 spring 551 knob
Claims (1)
Priority Applications (1)
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US17/397,770 US20220099154A1 (en) | 2006-04-02 | 2021-08-09 | Suspension damper having inertia valve and user adjustable pressure-relief |
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US11/535,552 US7699146B1 (en) | 2006-04-02 | 2006-09-27 | Suspension damper having inertia valve and user adjustable pressure-relief |
US12/752,886 US8261893B2 (en) | 2006-04-02 | 2010-04-01 | Suspension damper having inertia valve and user adjustable pressure-relief |
US13/555,364 US8607942B2 (en) | 2006-04-02 | 2012-07-23 | Suspension damper having inertia valve and user adjustable pressure-relief |
US14/107,963 US9261163B2 (en) | 2006-04-02 | 2013-12-16 | Suspension damper having inertia valve and user adjustable pressure-relief |
US15/001,035 US9746049B2 (en) | 2006-04-02 | 2016-01-19 | Suspension damper having inertia valve and user adjustable pressure-relief |
US15/685,811 US10359092B2 (en) | 2006-04-02 | 2017-08-24 | Suspension damper having inertia valve and user adjustable pressure-relief |
US16/516,127 US11085503B2 (en) | 2006-04-02 | 2019-07-18 | Suspension damper having inertia valve and user adjustable pressure-relief |
US17/397,770 US20220099154A1 (en) | 2006-04-02 | 2021-08-09 | Suspension damper having inertia valve and user adjustable pressure-relief |
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US16/516,127 Continuation US11085503B2 (en) | 2006-04-02 | 2019-07-18 | Suspension damper having inertia valve and user adjustable pressure-relief |
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US12/752,886 Active US8261893B2 (en) | 2006-04-02 | 2010-04-01 | Suspension damper having inertia valve and user adjustable pressure-relief |
US13/555,364 Active US8607942B2 (en) | 2006-04-02 | 2012-07-23 | Suspension damper having inertia valve and user adjustable pressure-relief |
US14/107,963 Active 2026-11-07 US9261163B2 (en) | 2006-04-02 | 2013-12-16 | Suspension damper having inertia valve and user adjustable pressure-relief |
US15/001,035 Active US9746049B2 (en) | 2006-04-02 | 2016-01-19 | Suspension damper having inertia valve and user adjustable pressure-relief |
US15/685,811 Active US10359092B2 (en) | 2006-04-02 | 2017-08-24 | Suspension damper having inertia valve and user adjustable pressure-relief |
US16/516,127 Active 2026-09-28 US11085503B2 (en) | 2006-04-02 | 2019-07-18 | Suspension damper having inertia valve and user adjustable pressure-relief |
US17/397,770 Abandoned US20220099154A1 (en) | 2006-04-02 | 2021-08-09 | Suspension damper having inertia valve and user adjustable pressure-relief |
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US11/535,552 Active 2028-05-08 US7699146B1 (en) | 2006-04-02 | 2006-09-27 | Suspension damper having inertia valve and user adjustable pressure-relief |
US12/752,886 Active US8261893B2 (en) | 2006-04-02 | 2010-04-01 | Suspension damper having inertia valve and user adjustable pressure-relief |
US13/555,364 Active US8607942B2 (en) | 2006-04-02 | 2012-07-23 | Suspension damper having inertia valve and user adjustable pressure-relief |
US14/107,963 Active 2026-11-07 US9261163B2 (en) | 2006-04-02 | 2013-12-16 | Suspension damper having inertia valve and user adjustable pressure-relief |
US15/001,035 Active US9746049B2 (en) | 2006-04-02 | 2016-01-19 | Suspension damper having inertia valve and user adjustable pressure-relief |
US15/685,811 Active US10359092B2 (en) | 2006-04-02 | 2017-08-24 | Suspension damper having inertia valve and user adjustable pressure-relief |
US16/516,127 Active 2026-09-28 US11085503B2 (en) | 2006-04-02 | 2019-07-18 | Suspension damper having inertia valve and user adjustable pressure-relief |
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US20160131218A1 (en) | 2016-05-12 |
US11085503B2 (en) | 2021-08-10 |
US20170356521A1 (en) | 2017-12-14 |
US8261893B2 (en) | 2012-09-11 |
US20100187055A1 (en) | 2010-07-29 |
US20120285778A1 (en) | 2012-11-15 |
US9261163B2 (en) | 2016-02-16 |
US7699146B1 (en) | 2010-04-20 |
US9746049B2 (en) | 2017-08-29 |
US8607942B2 (en) | 2013-12-17 |
US20140102839A1 (en) | 2014-04-17 |
US10359092B2 (en) | 2019-07-23 |
US20190338824A1 (en) | 2019-11-07 |
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