US20210222750A1 - Gas spring with travel control - Google Patents
Gas spring with travel control Download PDFInfo
- Publication number
- US20210222750A1 US20210222750A1 US17/195,216 US202117195216A US2021222750A1 US 20210222750 A1 US20210222750 A1 US 20210222750A1 US 202117195216 A US202117195216 A US 202117195216A US 2021222750 A1 US2021222750 A1 US 2021222750A1
- Authority
- US
- United States
- Prior art keywords
- gas
- valve rod
- gas chamber
- gas spring
- valve
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Abandoned
Links
Images
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G11/00—Resilient suspensions characterised by arrangement, location or kind of springs
- B60G11/26—Resilient suspensions characterised by arrangement, location or kind of springs having fluid springs only, e.g. hydropneumatic springs
- B60G11/27—Resilient suspensions characterised by arrangement, location or kind of springs having fluid springs only, e.g. hydropneumatic springs wherein the fluid is a gas
-
- 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
- F16F9/3415—Special valve constructions; Shape or construction of throttling passages characterised by comprising plastics, elastomeric or porous elements
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G17/00—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load
- B60G17/02—Spring characteristics, e.g. mechanical springs and mechanical adjusting means
- B60G17/04—Spring characteristics, e.g. mechanical springs and mechanical adjusting means fluid spring characteristics
- B60G17/052—Pneumatic spring characteristics
-
- 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
-
- 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
- F16F9/02—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium using gas only or vacuum
- F16F9/0209—Telescopic
-
- 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
- F16F9/02—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium using gas only or vacuum
- F16F9/0209—Telescopic
- F16F9/0245—Means for adjusting the length of, or for locking, the spring or dampers
-
- 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
- F16F9/02—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium using gas only or vacuum
- F16F9/0209—Telescopic
- F16F9/0281—Details
-
- 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
- F16F9/32—Details
- F16F9/44—Means on or in the damper for manual or non-automatic adjustment; such means combined with temperature correction
- F16F9/46—Means on or in the damper for manual or non-automatic adjustment; such means combined with temperature correction allowing control from a distance, i.e. location of means for control input being remote from site of valves, e.g. on damper external wall
-
- 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
- F16F9/56—Means for adjusting the length of, or for locking, the spring or damper, e.g. at the end of the stroke
-
- 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
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K15/00—Check valves
- F16K15/02—Check valves with guided rigid valve members
- F16K15/04—Check valves with guided rigid valve members shaped as balls
- F16K15/044—Check valves with guided rigid valve members shaped as balls spring-loaded
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G2202/00—Indexing codes relating to the type of spring, damper or actuator
- B60G2202/10—Type of spring
- B60G2202/15—Fluid spring
- B60G2202/152—Pneumatic spring
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G2206/00—Indexing codes related to the manufacturing of suspensions: constructional features, the materials used, procedures or tools
- B60G2206/01—Constructional features of suspension elements, e.g. arms, dampers, springs
- B60G2206/40—Constructional features of dampers and/or springs
- B60G2206/42—Springs
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G2300/00—Indexing codes relating to the type of vehicle
- B60G2300/12—Cycles; Motorcycles
-
- 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
- B62K2025/048—Axle suspensions for mounting axles resiliently on cycle frame or fork with suspension manual adjustment details
-
- 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
- F16F2238/00—Type of springs or dampers
- F16F2238/02—Springs
Definitions
- the present invention is generally related to the field of gas springs. More particularly, the present invention is related to a method and apparatus for altering the travel settings of gas springs and allowing equalization between the various gas chambers of a gas spring. Further included in the invention is a valve mechanism for controlling the fluid communication between the various gas chambers of the gas spring with turning of an adjustment knob or lever.
- the field of technology of these inventions is related to the technology described in, for example, U.S. Pat. Nos. 6,135,434 and 6,311,962 whose contents are incorporated by reference in their entirety herein.
- Simple shock absorbers which provide damping only, are typically oil-filled cylinders within which a vented piston is mounted.
- the piston is connected to a shaft which extends out of one end of the cylinder.
- the outer end of the shaft is mounted to one point on the vehicle; the other end of the cylinder is mounted to another point on the vehicle so that the shock is parallel to the action of the suspension spring.
- shock absorber which is the type commonly used with motorcycles, off-road vehicles, competition automotive vehicles and off-road bicycles, combines at least part of the suspension function and the shock absorbing function in one unit.
- This second type of shock absorber commonly uses a spring unit to provide all or part of the suspension function coupled with a damping unit to provide the damping function.
- Conventional shock absorber designs commonly incorporate an external coil spring, an internal air spring, or an internal bladder to provide the suspension function.
- a gas spring assembly for a suspension system includes a tube; a piston assembly slidably displaceable relative to the tube, the piston assembly separating the tube into a positive spring gas chamber and a negative spring gas chamber; and a valve mechanism configured to permit gas flow between the positive and negative spring gas chambers when the gas pressure in the negative spring gas chamber exceeds the gas pressure in the positive gas spring chamber.
- a valve mechanism for a gas spring suspension system having positive and negative spring gas chambers includes a gas passageway extending between the positive and negative spring gas chambers; a valve seat; and a valve displaced toward the valve seat to prevent gas flow through the gas passageway when the pressure in the positive spring gas chamber exceeds the pressure in the negative spring gas chamber, the valve displaced away from the valve seat to permit gas flow through the gas passageway when the pressure in the negative spring gas chamber exceeds the pressure in the positive spring gas chamber.
- a valve assembly for a suspension system includes a housing having a plurality of housing fluid flow paths through a housing wall thereof; a fluid conduit disposed adjacent the housing and having at least one conduit fluid flow path through a conduit wall thereof; a seal, located between two of the housing fluid flow paths and isolating a surface of the conduit wall from a surface of the housing wall; a first position wherein the conduit fluid flow path is in fluid communication with a first of the housing fluid flow paths and isolated from a second of the housing fluid flow paths; and a second position wherein the conduit fluid flow path is in fluid communication with the second of the housing fluid flow paths and isolated from the first of the housing fluid flow paths.
- a multi-position valve assembly in another embodiment, includes a first tube having an axial fluid flow path through an interior thereof and a first aperture through a first tube wall and in communication with the flow path; a second tube substantially coaxially disposed relative to the first tube and having a plurality of second apertures through a second tube wall, at least two second apertures being spaced at a first distance apart, the first and the second tubes forming an annulus there between; a plurality of seals disposed in the annulus, at least one each of the seals being located on each side of each of the second apertures thereby forming a discreet annular chamber for each of the second apertures; a first position wherein the first aperture is in fluid communication with a first of the chambers and a second position wherein the first aperture is in fluid communication with a second of the chambers and wherein a distance between the first and second positions is less than half of the first distance.
- a gas spring suspension system in another embodiment, includes a tube; a piston assembly disposed within and movable relative to the tube; a first spring gas chamber and a second spring gas chamber; and a valve mechanism selectively permitting gas flow between the first and second spring gas chambers.
- FIGS. 1A, 1B, and 1C depict simplified cross-section static equilibrium views of a gas spring according to an exemplary embodiment of the present invention.
- FIG. 2A - FIG. 2C depict simplified cross-section dynamic equalization views of the gas spring.
- FIG. 2B is a cross section along line 2 B- 2 B of FIG. 2A .
- FIG. 2C is a cross section along line 2 C- 2 C of FIG. 2A .
- FIGS. 3A, 3B, and 3C are simplified cross-sections depicting the process of converting the gas spring from long travel to short travel.
- FIGS. 4A, 4B, and 4C are simplified cross-sections that depict the process of converting the gas spring from short travel to long travel.
- FIG. 5 are graphs comparing the travel adjustment of the gas spring with the travel adjustment of a gas spring according to another exemplary embodiment of the present invention.
- FIGS. 6A, 6B, and 6C depict simplified schematic static equilibrium views of a gas spring according to another exemplary embodiment of the present invention.
- FIGS. 7A, 7B, 7C depict detailed assembly views of various flow paths available in a gas spring according to the exemplary embodiment of the present invention.
- FIG. 8 depicts another method in which dynamic venting may be achieved.
- FIGS. 9A, 9B, and 9C schematically depict various gas flow paths available in a gas spring according to the exemplary embodiment of the present invention.
- FIG. 10 is another simplified schematic depicting various gas flow paths available in a gas spring according to the exemplary embodiment of the present invention.
- FIG. 11 is a perspective view of a bicycle fork including the gas spring according to the exemplary embodiment of the present invention.
- FIGS. 12A, 12B, and 12C depict the process of converting a gas spring according to the exemplary embodiment of the present invention from long travel to short travel.
- FIGS. 13A, 13B, and 13C depict the process of converting a gas spring according to the exemplary embodiment of the present invention from short travel to long travel.
- FIG. 14A-14C depict various configurations for the through hole for the valve rod.
- FIG. 15A-15B depict an exemplary check valve used with the gas spring of FIG. 1 .
- FIG. 16A-16B depict an exemplary check valve with a faster response than the check valve of FIG. 15 and used in the gas spring of FIG. 6 .
- FIGS. 1A, 1B, and 1C depict simplified cross-section and static equilibrium views of a gas spring 10 ′ according to an exemplary embodiment of the present invention.
- This gas spring 10 ′ is an application for which the valve and valve control unit according to the teachings of the invention would be very suitable.
- gas spring 10 ′ depicts, in a static state (i.e., at rest), a gas spring 10 ′ in a variety of travel mode positions.
- gas spring may refer to, at least, a rear shock or a subcomponent of a front fork of a bicycle.
- the gas spring will typically comprise a gas spring having a gas tube divided into positive and negative gas chambers by a piston.
- gas spring 10 ′ As previously mentioned, the most basic form of the gas spring 10 ′ is shown in FIGS. 1A-C as well as FIGS. 2A-C and includes a gas spring body 15 having a longitudinal axis and defining an internal gas chamber 20 .
- gas spring body 15 When the gas spring 10 ′ is being used in a bicycle fork, gas spring body 15 will be a subcomponent contained within upper leg U of fork F ( FIG. 11 ).
- a hollow valve rod 40 having a hollow interior portion or fluid path 41 therein is provided within the internal gas chamber 20 and parallel to the longitudinal axis of the gas spring body 15 .
- fluid refers to a gas, such as air or nitrogen.
- the hollow valve rod 40 is open at both ends and provided with check valve 50 a and check valve 50 b to selectively seal off the fluid path 41 so that fluid may only leave the fluid path 41 through check valve 50 a or check valve 50 b , i.e., fluid may not enter fluid path 41 through check valve 50 a or check valve 50 b .
- FIG. 15A-15B depict a check valve 50 a and check valve 50 b , in more detail.
- check valve 50 a and check valve 50 b comprise a small vent hole 52 in fluid communication with fluid path 41 and positioned in a closed head portion 42 of hollow valve rod 40 .
- An elastomeric o-ring 51 surrounded the head portion 42 and when in its relaxed position ( FIG. 15A ) blocked small vent hole 52 .
- the pressure of the gas flowing through fluid path 41 and small vent hole 52 is large enough, the pressure causes elastomeric o-ring 51 to deform/expand ( FIG. 15B ) and unblock small vent hole 52 , thereby allowing gas to escape from fluid path 41 .
- the hollow valve rod 40 is also provided with at least one through hole 60 (only one of which is consistently shown herein for clarity purposes and not as an intent to limit the invention in any way), typically located in a depression 61 (see FIG. 2A, 2C ) and therefore in the form of a depressed radial through hole 60 , to provide for completely open (non-checked) fluid communication between the internal gas chamber 20 and the fluid path 41 of the hollow valve rod 40 .
- FIGS. 14A-14C various other potential configurations of through hole 60 are depicted in which through hole 60 is not necessarily radial (the depression 61 is omitted for clarity, as it has been from most of the FIGS herein).
- the height of the through hole 60 may be adjusted by the user without having to open the gas spring body 15 . While it is possible to have the height of the radial through hole 60 be infinitely and continuously adjustable between the long and short travel mode positions, in reality, there may be a plurality of discrete positions, such as 15 discrete positions within 3.5 rotations of knob K allowing for suspension travel between 90-130 mm, or as large as 110-150 mm (however, any travel range is possible).
- the through hole 60 is located deep in the gas spring body 15 and in short travel mode ( FIG. 1C ), the through hole 60 is located towards the top of the gas spring body 15 .
- the through hole 60 may be located anywhere between the short and long travel mode positions.
- a moveable piston assembly 100 is also provided within the internal gas chamber 20 and divides the internal gas chamber 20 into first variable volume gas chamber 22 and second variable volume gas chamber 27 , respectively.
- Moveable piston assembly 100 is rigidly mounted to lower leg L of fork F and mounted for relative movement with respect to hollow valve rod 40 which is rigidly mounted to upper leg U of fork F.
- moveable piston assembly 100 longitudinally moves within internal gas chamber 20 along hollow valve rod 40 , one of gas chambers 22 , 27 will get larger and the other of gas chamber 22 , 27 will get smaller, depending on the direction of movement of moveable piston assembly 100 .
- Moveable piston assembly 100 primarily includes the main piston body 110 and collar portion 115 .
- Moveable piston assembly 100 also includes vent 109 , for reasons to be described later.
- Collar portion 115 of the moveable piston assembly 100 eventually leaves the gas spring body 15 and, in the case of a fork, leaves upper tube U through a seal (not shown) and is affixed to the lower end of lower tube L of fork F ( FIG. 11 ).
- hollow valve rod 40 and moveable piston assembly 100 are mounted for relative movement with respect to each other and typically that would involve the ability of hollow valve rod 40 to collapse into a bore within the center of the main piston body 110 (See FIGS. 2A-2C ) as the upper U and lower L legs of the fork telescope relative to each other.
- a seal preferably in the form of an o-ring 116 is provided within the bore of the main piston body 110 .
- the thickness of this o-ring 116 may be less than the length of the depression 61 containing through hole 60 .
- Main piston body 110 has an upper surface 110 a and a lower surface 110 b .
- the relative sizes of the surface areas of these two surfaces of the main piston body 110 may be such that the lower surface 110 b of the main piston body 110 may have a smaller surface area than the upper surface 110 a .
- the ratio of upper surface 110 a area [ ⁇ (A1)] 2 to lower surface 110 b area ( ⁇ [(A1) 2 ⁇ S 2 ]) is approximately 1.5:1 (the attached schematic figures are therefore, not to scale).
- the pressure inside the second gas chamber 27 may be higher than the pressure in the first gas chamber 22 .
- first gas chamber 22 is the high pressure chamber and vents to the lower pressure second gas chamber 27 through vent 109 .
- the gas spring will expand towards its rest equilibrium position, which occurs when the forces on both sides of main piston body 110 are equal.
- FIGS. 3A-3C depict how the gas spring 10 ′ can be converted from long travel mode to short travel mode using a gas mechanism.
- FIG. 3A depicts static gas spring 10 ′ in long travel mode. Accordingly, the moveable piston assembly 100 is located low in the internal gas chamber 20 and through hole 60 is positioned close above it. In the static position, the pressure in the second gas chamber 27 is higher than the pressure in the first gas chamber 22 . The user then converts the gas spring 10 to short travel mode by turning an external knob K that results in the moving of the through hole 60 further towards the top of the internal gas chamber 20 .
- the moveable piston assembly 100 does not move to the new travel mode position without additional assistance. Therefore, as shown in FIG. 3B , the user would, for example, preferably pump the moveable piston assembly 100 a few times as symbolized by the double-headed arrow B-B in the FIG. During the downward movement of gas spring body 15 relative to the moveable piston assembly 100 :
- first chamber 22 increases in pressure and is forced from first gas chamber 22 into through hole 60 and fluid path 41 of the hollow valve rod 40 . Since check valve 50 a only allows fluid flow out of fluid path 41 , the gas then exits the hollow valve rod 40 by opening check valve 50 b and enters second gas chamber 27 (whose pressure has temporarily decreased) via vent 109 in the moveable piston assembly 100 (recall this a simplified schematic representation). Accordingly, the pressure in the second gas chamber 27 will increase; and
- FIG. 4A-4C depict how the gas spring 10 ′ can be converted from short travel mode to long travel mode.
- FIG. 4A depicts static gas spring 10 ′ in short travel mode. Accordingly, the moveable piston assembly 100 is located high in the internal gas chamber 20 and through hole 60 is positioned close above it. In this static position, the pressure in the second gas chamber 27 is higher than the pressure in the first gas chamber 22 . The user then converts the gas spring 10 to long travel mode by turning an external knob K that results in the moving of the through hole 60 further towards the bottom of the internal gas chamber 20 . This has the result of moving the through hole 60 from the lower pressure first gas chamber 22 to the higher-pressure second gas chamber 27 .
- the fluid path 41 of the hollow valve rod 40 will have the pressure of the second gas chamber 27 . Because the pressure on the first gas chamber 22 side of the check valve 50 a will be less than on fluid path 41 side, the check valve 50 a will open and gas will flow from the second gas chamber 27 to the first gas chamber 22 . This results in a pressure drop in the second gas chamber 27 and a pressure increase in the first gas chamber 22 . This ultimately results in a downward force on the upper surface 110 a of the main piston body 110 and the moveable piston assembly 100 will accelerate downward to the new equilibrium point in a long travel mode position ( FIG. 4C ) where the pressure in second gas chamber 27 still will exceed the pressure in first gas chamber 22 . Note that unlike the change from long travel mode to short travel mode, the change from short travel mode to long travel mode does not require any pumping on the gas spring 10 since the moving of the through hole 60 into the high pressure second gas chamber 27 creates the necessary pressure differential.
- another embodiment involves incorporating a discrete number of predetermined travel mode positions to the gas spring, preferably: long travel (L), medium travel (M), and short travel (S) modes.
- the typical distance between through hole 60 in the long travel mode position and short travel mode position may be between 40-45 mm, but can vary widely between manufacturers.
- another embodiment of the invention additionally involves the ability to make drastic incremental travel adjustments with only a small angular turn of an adjustment knob; preferably 90°, and typically no more than 240° of rotation (since more than 240° would require a release and re-grip of the knob).
- the travel mode adjust of another embodiment of the invention may be considered a much more non-linear or non-proportional travel adjust than those of the gas spring 10 ′. This is depicted by the graph of FIG. 5 .
- the travel adjust of the gas spring 10 ′ having 15 discrete knob settings corresponding to 15 different and discrete travel levels, the turning of the knob appears to create almost a linear change in the travel of the fork.
- the travel adjust according to another embodiment where there are 3 discrete knob settings corresponding to 3 different and discrete travel modes, but covering the same overall amount of linear travel, the turning of the knob creates a much more stepped and non-linear change in the travel of the fork.
- a valve rod assembly 240 may have three through holes, preferably in the form of three preferably radial through holes, 260 a , 260 b , 260 c corresponding to predetermined damper travels, namely: short travel mode, medium travel mode, and long travel modes, respectively.
- predetermined damper travels namely: short travel mode, medium travel mode, and long travel modes, respectively.
- these through holes (1) need not be in a depression for reasons to be described below and (2) do not provide direct access to the interior of the valve rod assembly 240 and hollow interior portion or fluid path 241 of the gas spring 10 and as pictorially depicted in the FIGs by the solid fill, at least two of the through holes 260 will always be sealed off from fluid communication with the fluid path 241 of the valve rod assembly 240 .
- valve rod assembly 240 may comprise: (a) an outer valve rod 242 having a hollow interior and (b) a valve control assembly including: valve tubes 245 , valve ring 246 , and inner valve rod 255 .
- the valve tubes 245 and valve ring 246 are primarily for structural rigidity of the valve rod assembly 240 and for supporting the seals, as described below.
- Inner valve rod 255 has generally closed walls that surround fluid path 241 except for at least one valve rod bore 257 and openings at its ends that are sealed off by check valves 250 a , 250 b (see FIGS.
- check valves 250 a , 250 b are designed to operate much more rapidly than check valve 50 a and check valve 50 b , and therefore they can be used in place of depression 61 during the equalization process.
- FIG. 16A-16B depict these check valves 250 a , 250 b , in more detail.
- check valves 250 a , 250 b may comprise a small ball bearing 252 blocking fluid path 241 of inner valve rod 255 .
- An elastomeric o-ring 251 surrounds the exit to fluid path 241 to create a good seal when the check valve is in its closed position ( FIG.
- inner valve rod 255 may rotate and move longitudinally to cause longitudinal movement of the at least one valve rod bore 257 relative to valve tube 242 (compare FIGS. 7A-7C ). While the drawings depict only one valve bore 257 , one skilled in the art would recognize that there may be more than one valve bore 257 , so long as all the valve bores 257 are at substantially the same height.
- Each valve tube 245 is trapped in between the outer and inner valve tubes 242 , 255 by an outer seal 271 and an inner seal 270 . These seals will typically be in the form of o-rings. Each valve tube 245 will also have one or more through bores 280 a , 280 c , preferably, corresponding to through holes 260 a , 260 c . Because valve tubes 245 are smaller than the space between the inner valve rod 255 and the outer valve rod 242 , gas gaps 285 a , 285 c that create a venting passageway are formed there between. Finally, as previously mentioned, in between inner seals 270 is valve ring 246 .
- valve ring 246 is smaller than the space between the inner valve rod 255 and the outer valve rod 242 , a gas gap 285 b that creates a venting passageway is formed there between also. However, unless the valve rod bore 257 is aligned to provide fluid communication with a particular gas gap, that gas gap is sealed off from the fluid path 241 .
- gas may enter the valve rod assembly 240 through any of the through holes 260 a , 260 b , or 260 c , flow through their respective through bores 280 a , 280 b , or 280 c , and into their respective gas gaps 285 a , 285 b , or 285 c .
- the gas spring is set to medium travel and therefore, valve rod bore 257 is aligned with gas gap 285 b .
- valve rod assembly 240 gas coming into the valve rod assembly 240 from gas gaps 285 a , 285 c can go no further due to inner seal 270 and outer seal 271 and the fact that valve rod bore 257 does not provide fluid access between gas gaps 285 a , 285 c and fluid path 241 .
- gas may enter the valve rod assembly 240 through hole 260 b for the mid travel setting, flow through the valve ring 246 , into the gas gap, 285 b , and then through valve rod bore 257 into the fluid path 241 of inner valve rod 255 . The gas will then travel to the appropriate valve and chamber.
- gas also enters the valve rod assembly 240 through all of the through holes 260 a , 260 b , and 260 c , flow through their respective through bores 280 a , 280 b , and 280 c , and into their respective gas gaps 285 a , 285 b , and 285 c .
- the gas spring is set to one of either short or long travel modes, respectively, and therefore, valve rod bore 257 is aligned to provide fluid communication between fluid path 241 and gas gap (e.g.) 285 a or 285 c .
- Gas may enter the valve rod assembly 240 through hole 260 a or 260 c for the selected travel setting, flow through the corresponding gas gap, 285 a or 285 c , and then through valve rod bore 257 into the fluid path 241 of inner valve rod 255 . The gas will then travel to the appropriate valve and chamber.
- FIG. 9A-9C This operation is shown schematically in FIG. 9A-9C ( FIG. 8 described below), which also more clearly shows how the method of the invention allows the function and result of moving a radial bore across a very long travel can be achieved without actually having to do so. That is, through less than one complete turn of the adjustment knob K, and preferably approximately 90° rotation of the knob, what can be achieved is the same as three complete turns of an extremely sharply pitched shaft that would be very close to binding due to the sharpness of the pitch.
- the gas spring is configured for short (S) travel mode. Accordingly, a flow path is open between fluid path 241 of inner valve rod 255 and bore 280 a.
- the gas spring is configured for medium (M) travel mode. Accordingly, a flow path is open between fluid path 241 of inner valve rod 255 and bore 280 b.
- the gas spring is configured for long (L) travel mode. Accordingly, a flow path is open between fluid path 241 of inner valve rod 255 and bore 280 c.
- valve rod would have to be rotated a sufficient number of times with a thread pitch sufficient to move the radial hole a longitudinal distance D 1 , approximately equal to 45 mm.
- the valve rod bore 257 only has to be rotated a sufficient number of times with a pitch sufficient to move the radial hole a longitudinal distance D 2 , approximately equal to 2.7 mm, substantially less than the longitudinal distance between now fixed bores 280 .
- These distances are also highlighted in FIGS. 7 A- 7 C. This can be achieved through less than one complete turn of the adjustment knob K, and preferably approximately 90′ rotation of the knob and a less severe thread pitch. This makes the ability to make the travel adjustment much more user-friendly.
- through holes 260 need not be located in depressions in the way that through hole 60 are. Nor, do they have to be larger than o-ring 116 . Rather, it is possible that as shown in simplified FIG. 8 , dynamic venting (cf. FIG. 2C ) is achieved by the overpressure of second chamber 27 directly entering into fluid path 241 through an open through hole 260 and valve rod bore 257 and then up to and out of check valve 250 a and into first chamber 22 (latter part not shown in FIG. 8 ). This process can occur just as rapidly as the venting through the depression of FIG. 2C due to the quick response of check valves 250 a.
- FIGS. 12 and 13 correspond to FIGS. 3 and 4 , respectively in that FIGS. 12 and 13 depict how the gas spring according to another embodiment of the invention may be converted from long travel mode to short travel mode ( FIG. 12 ) or short travel mode to long travel mode ( FIG. 13 ).
- the general operation of the gas springs of FIGS. 12 and 13 only differ from those of FIGS. 3 and 4 in that the valve rod assembly previously described is used instead of a longitudinally moving radial hole 60 .
- a method of changing the travel mode of a gas spring having a gas chamber filled with a gas may be provided.
- the step of using a valve rod may include the step of rotating the valve rod less than one turn.
- the step of rotating the valve rod moves the valve bore a distance substantially less than the distance between the plurality of different travel modes.
- the step of rotating the valve rod and moving the valve bore also includes moving the valve bore longitudinally.
Abstract
Description
- This application is a continuation application of and claims priority to and benefit of co-pending U.S. patent application Ser. No. 16/165,875 filed on Oct. 19, 2018, entitled “GAS SPRING WITH TRAVEL CONTROL” by Joseph Franklin et al., having Attorney Docket No. FOX-0014.P1.CON3, assigned to the assignee of the present application, and incorporated herein, in its entirety, by reference.
- The application Ser. No. 16/165,875 is a continuation application of and claims priority to and benefit of U.S. patent application Ser. No. 15/237,371 filed on Aug. 15, 2016, no U.S. Issued U.S. Pat. No. 10,132,379, entitled “GAS SPRING WITH TRAVEL CONTROL” by Joseph Franklin et al., having Attorney Docket No. FOX-0014.P1.CON2, assigned to the assignee of the present application, and incorporated herein, in its entirety, by reference.
- The application Ser. No. 15/237,371 is a continuation application of and claims priority to and benefit of U.S. patent application Ser. No. 14/336,929 filed on Jul. 21, 2014, now U.S. Issued U.S. Pat. No. 9,415,653, entitled “GAS SPRING WITH TRAVEL CONTROL” by Joseph Franklin et al., having Attorney Docket No. FOX-0014.P1.CON, assigned to the assignee of the present application, and incorporated herein, in its entirety, by reference.
- The application Ser. No. 14/336,929 is a continuation application of and claims priority to and benefit of U.S. patent application Ser. No. 12/176,160, now abandoned, filed on Jul. 18, 2008 entitled “GAS SPRING WITH TRAVEL CONTROL” by Joseph Franklin et al., having Attorney Docket No. FOXF/0014.P1, assigned to the assignee of the present application, and incorporated herein, in its entirety, by reference.
- The application Ser. No. 12/176,160 is a continuation-in-part and claims priority of U.S. patent application Ser. No. 10/237,333 (Atty. Dock. No. FOXF/0010), now U.S. Issued U.S. Pat. No. 7,703,585, filed Sep. 5, 2002, which claims benefit of U.S. provisional patent application Ser. No. 60/392,802, filed Jun. 28, 2002, and U.S. provisional patent application Ser. No. 60/391,991, filed Jun. 25, 2002. Each of the aforementioned related patent applications is herein incorporated by reference in its entirety.
- The application Ser. No. 12/176,160 is also a continuation-in-part and claims priority of U.S. patent application Ser. No. 11/560,403 (Atty. Dock. No. FOXF/0011), now U.S. Issued U.S. Pat. No. 8,464,850, filed Nov. 16, 2006, which is herein incorporated by reference in its entirety
- The application Ser. No. 12/176,160 is also a continuation-in-part and claims priority of U.S. patent application Ser. No. 11/372,707 (Atty. Dock. No. FOXF/0014), now abandoned, filed Mar. 10, 2006, which claims benefit of U.S. provisional patent application Ser. No. 60/667,495, filed Apr. 1, 2005. Each of the aforementioned related patent applications is herein incorporated by reference in its entirety.
- The application Ser. No. 12/176,160 also claims benefit of U.S. provisional patent application Ser. No. 61/038,015 (Atty. Dock. No. FOXF/0022L), filed Mar. 19, 2008, which is herein incorporated by reference in its entirety.
- The present invention is generally related to the field of gas springs. More particularly, the present invention is related to a method and apparatus for altering the travel settings of gas springs and allowing equalization between the various gas chambers of a gas spring. Further included in the invention is a valve mechanism for controlling the fluid communication between the various gas chambers of the gas spring with turning of an adjustment knob or lever. The field of technology of these inventions is related to the technology described in, for example, U.S. Pat. Nos. 6,135,434 and 6,311,962 whose contents are incorporated by reference in their entirety herein.
- Conventional automotive vehicles typically have separate suspension springs and separate simple shock absorbers. Simple shock absorbers, which provide damping only, are typically oil-filled cylinders within which a vented piston is mounted. The piston is connected to a shaft which extends out of one end of the cylinder. The outer end of the shaft is mounted to one point on the vehicle; the other end of the cylinder is mounted to another point on the vehicle so that the shock is parallel to the action of the suspension spring.
- Another type of shock absorber, which is the type commonly used with motorcycles, off-road vehicles, competition automotive vehicles and off-road bicycles, combines at least part of the suspension function and the shock absorbing function in one unit. This second type of shock absorber commonly uses a spring unit to provide all or part of the suspension function coupled with a damping unit to provide the damping function. Conventional shock absorber designs commonly incorporate an external coil spring, an internal air spring, or an internal bladder to provide the suspension function.
- The present invention is generally related to the field of gas springs. In one embodiment, a gas spring assembly for a suspension system includes a tube; a piston assembly slidably displaceable relative to the tube, the piston assembly separating the tube into a positive spring gas chamber and a negative spring gas chamber; and a valve mechanism configured to permit gas flow between the positive and negative spring gas chambers when the gas pressure in the negative spring gas chamber exceeds the gas pressure in the positive gas spring chamber.
- In another embodiment, a valve mechanism for a gas spring suspension system having positive and negative spring gas chambers includes a gas passageway extending between the positive and negative spring gas chambers; a valve seat; and a valve displaced toward the valve seat to prevent gas flow through the gas passageway when the pressure in the positive spring gas chamber exceeds the pressure in the negative spring gas chamber, the valve displaced away from the valve seat to permit gas flow through the gas passageway when the pressure in the negative spring gas chamber exceeds the pressure in the positive spring gas chamber.
- In another embodiment, a valve assembly for a suspension system includes a housing having a plurality of housing fluid flow paths through a housing wall thereof; a fluid conduit disposed adjacent the housing and having at least one conduit fluid flow path through a conduit wall thereof; a seal, located between two of the housing fluid flow paths and isolating a surface of the conduit wall from a surface of the housing wall; a first position wherein the conduit fluid flow path is in fluid communication with a first of the housing fluid flow paths and isolated from a second of the housing fluid flow paths; and a second position wherein the conduit fluid flow path is in fluid communication with the second of the housing fluid flow paths and isolated from the first of the housing fluid flow paths.
- In another embodiment, a multi-position valve assembly includes a first tube having an axial fluid flow path through an interior thereof and a first aperture through a first tube wall and in communication with the flow path; a second tube substantially coaxially disposed relative to the first tube and having a plurality of second apertures through a second tube wall, at least two second apertures being spaced at a first distance apart, the first and the second tubes forming an annulus there between; a plurality of seals disposed in the annulus, at least one each of the seals being located on each side of each of the second apertures thereby forming a discreet annular chamber for each of the second apertures; a first position wherein the first aperture is in fluid communication with a first of the chambers and a second position wherein the first aperture is in fluid communication with a second of the chambers and wherein a distance between the first and second positions is less than half of the first distance.
- In another embodiment, a gas spring suspension system includes a tube; a piston assembly disposed within and movable relative to the tube; a first spring gas chamber and a second spring gas chamber; and a valve mechanism selectively permitting gas flow between the first and second spring gas chambers.
- So that the manner in which the above recited features of the present invention can be understood in detail, a more particular description of the invention, briefly summarized above, may be had by reference to embodiments, some of which are illustrated in the appended drawings. It is to be noted, however, that the appended drawings illustrate only typical embodiments of this invention and are therefore not to be considered limiting of its scope, for the invention may admit to other equally effective embodiments.
-
FIGS. 1A, 1B, and 1C depict simplified cross-section static equilibrium views of a gas spring according to an exemplary embodiment of the present invention. -
FIG. 2A -FIG. 2C depict simplified cross-section dynamic equalization views of the gas spring.FIG. 2B is a cross section alongline 2B-2B ofFIG. 2A .FIG. 2C is a cross section along line 2C-2C ofFIG. 2A . -
FIGS. 3A, 3B, and 3C are simplified cross-sections depicting the process of converting the gas spring from long travel to short travel. -
FIGS. 4A, 4B, and 4C are simplified cross-sections that depict the process of converting the gas spring from short travel to long travel. -
FIG. 5 are graphs comparing the travel adjustment of the gas spring with the travel adjustment of a gas spring according to another exemplary embodiment of the present invention. -
FIGS. 6A, 6B, and 6C depict simplified schematic static equilibrium views of a gas spring according to another exemplary embodiment of the present invention. -
FIGS. 7A, 7B, 7C depict detailed assembly views of various flow paths available in a gas spring according to the exemplary embodiment of the present invention. -
FIG. 8 depicts another method in which dynamic venting may be achieved. -
FIGS. 9A, 9B, and 9C schematically depict various gas flow paths available in a gas spring according to the exemplary embodiment of the present invention. -
FIG. 10 is another simplified schematic depicting various gas flow paths available in a gas spring according to the exemplary embodiment of the present invention. -
FIG. 11 is a perspective view of a bicycle fork including the gas spring according to the exemplary embodiment of the present invention. -
FIGS. 12A, 12B, and 12C depict the process of converting a gas spring according to the exemplary embodiment of the present invention from long travel to short travel. -
FIGS. 13A, 13B, and 13C depict the process of converting a gas spring according to the exemplary embodiment of the present invention from short travel to long travel. -
FIG. 14A-14C depict various configurations for the through hole for the valve rod. -
FIG. 15A-15B depict an exemplary check valve used with the gas spring ofFIG. 1 . -
FIG. 16A-16B depict an exemplary check valve with a faster response than the check valve ofFIG. 15 and used in the gas spring ofFIG. 6 . - Finally, the following symbolic conventions have been used throughout the drawings where applicable:
- a) dense cross-hatching indicates higher pressures than less-dense cross-hatching;
- b) filled circles represent closed valves or openings.
- With reference to the drawings, an exemplary embodiment of a gas spring with travel control will now be described.
-
FIGS. 1A, 1B, and 1C depict simplified cross-section and static equilibrium views of agas spring 10′ according to an exemplary embodiment of the present invention. Thisgas spring 10′ is an application for which the valve and valve control unit according to the teachings of the invention would be very suitable. - In particular, these figures depict, in a static state (i.e., at rest), a
gas spring 10′ in a variety of travel mode positions. As used herein, “gas spring” may refer to, at least, a rear shock or a subcomponent of a front fork of a bicycle. However, the invention is not so limited. As will be further described, the gas spring will typically comprise a gas spring having a gas tube divided into positive and negative gas chambers by a piston. - As previously mentioned, the most basic form of the
gas spring 10′ is shown inFIGS. 1A-C as well asFIGS. 2A-C and includes agas spring body 15 having a longitudinal axis and defining aninternal gas chamber 20. When thegas spring 10′ is being used in a bicycle fork,gas spring body 15 will be a subcomponent contained within upper leg U of fork F (FIG. 11 ). - A
hollow valve rod 40 having a hollow interior portion orfluid path 41 therein is provided within theinternal gas chamber 20 and parallel to the longitudinal axis of thegas spring body 15. As used herein, “fluid” refers to a gas, such as air or nitrogen. Thehollow valve rod 40 is open at both ends and provided withcheck valve 50 a andcheck valve 50 b to selectively seal off thefluid path 41 so that fluid may only leave thefluid path 41 throughcheck valve 50 a orcheck valve 50 b, i.e., fluid may not enterfluid path 41 throughcheck valve 50 a orcheck valve 50 b.FIG. 15A-15B depict acheck valve 50 a andcheck valve 50 b, in more detail. In particular,check valve 50 a andcheck valve 50 b comprise asmall vent hole 52 in fluid communication withfluid path 41 and positioned in aclosed head portion 42 ofhollow valve rod 40. An elastomeric o-ring 51 surrounded thehead portion 42 and when in its relaxed position (FIG. 15A ) blockedsmall vent hole 52. When the pressure of the gas flowing throughfluid path 41 andsmall vent hole 52 is large enough, the pressure causes elastomeric o-ring 51 to deform/expand (FIG. 15B ) and unblocksmall vent hole 52, thereby allowing gas to escape fromfluid path 41. - Accordingly, to accelerate gas flow during equalization stages, the
hollow valve rod 40 is also provided with at least one through hole 60 (only one of which is consistently shown herein for clarity purposes and not as an intent to limit the invention in any way), typically located in a depression 61 (seeFIG. 2A, 2C ) and therefore in the form of a depressed radial throughhole 60, to provide for completely open (non-checked) fluid communication between theinternal gas chamber 20 and thefluid path 41 of thehollow valve rod 40. InFIGS. 14A-14C , various other potential configurations of throughhole 60 are depicted in which throughhole 60 is not necessarily radial (thedepression 61 is omitted for clarity, as it has been from most of the FIGS herein). - Through any conventional mechanism (not shown), such as a screw mechanism, connected to a conventional adjuster in the form of a knob K (
FIG. 11 ) or lever (not shown) and collectively sometimes referred to herein as a “knob” positioned outside the gas spring body 15 (or fork F), the height of the throughhole 60 may be adjusted by the user without having to open thegas spring body 15. While it is possible to have the height of the radial throughhole 60 be infinitely and continuously adjustable between the long and short travel mode positions, in reality, there may be a plurality of discrete positions, such as 15 discrete positions within 3.5 rotations of knob K allowing for suspension travel between 90-130 mm, or as large as 110-150 mm (however, any travel range is possible). Thus, in long travel mode (FIG. 1A ), the throughhole 60 is located deep in thegas spring body 15 and in short travel mode (FIG. 1C ), the throughhole 60 is located towards the top of thegas spring body 15. For medium-travel mode (FIG. 1B ), the throughhole 60 may be located anywhere between the short and long travel mode positions. - A
moveable piston assembly 100 is also provided within theinternal gas chamber 20 and divides theinternal gas chamber 20 into first variablevolume gas chamber 22 and second variablevolume gas chamber 27, respectively.Moveable piston assembly 100 is rigidly mounted to lower leg L of fork F and mounted for relative movement with respect tohollow valve rod 40 which is rigidly mounted to upper leg U of fork F. Asmoveable piston assembly 100 longitudinally moves withininternal gas chamber 20 alonghollow valve rod 40, one ofgas chambers gas chamber moveable piston assembly 100.Moveable piston assembly 100 primarily includes themain piston body 110 andcollar portion 115.Moveable piston assembly 100 also includesvent 109, for reasons to be described later.Collar portion 115 of themoveable piston assembly 100 eventually leaves thegas spring body 15 and, in the case of a fork, leaves upper tube U through a seal (not shown) and is affixed to the lower end of lower tube L of fork F (FIG. 11 ). - As previously mentioned,
hollow valve rod 40 andmoveable piston assembly 100 are mounted for relative movement with respect to each other and typically that would involve the ability ofhollow valve rod 40 to collapse into a bore within the center of the main piston body 110 (SeeFIGS. 2A-2C ) as the upper U and lower L legs of the fork telescope relative to each other. To create a seal between themoveable piston assembly 100 and thehollow valve rod 40 so there is no fluid communication between thefirst gas chamber 22 andsecond gas chamber 27 in the area where themoveable piston assembly 110 is mounted on thehollow valve rod 40, a seal, preferably in the form of an o-ring 116 is provided within the bore of themain piston body 110. For reasons to be described later, the thickness of this o-ring 116 may be less than the length of thedepression 61 containing throughhole 60. -
Main piston body 110 has anupper surface 110 a and alower surface 110 b. The relative sizes of the surface areas of these two surfaces of themain piston body 110 may be such that thelower surface 110 b of themain piston body 110 may have a smaller surface area than theupper surface 110 a. Typically, the ratio ofupper surface 110 a area [π(A1)]2 tolower surface 110 b area (π[(A1)2−S2]) is approximately 1.5:1 (the attached schematic figures are therefore, not to scale). Accordingly, when thegas spring 10 is in static equilibrium and the forces on both sides of themoveable piston assembly 100 are equal, according to the formula P=F/A, due to the fact that the surface areas on each side ofmoveable piston assembly 100 are different, the pressure inside thesecond gas chamber 27 may be higher than the pressure in thefirst gas chamber 22. - The basic pressure equalization operation of the
gas spring 10′ will now be described with reference toFIGS. 2A-2C . During compression of thegas spring 10′, themoveable piston assembly 100 will move relative to thehollow valve rod 40 and therefore also with respect to the throughhole 60. - Whenever the portion of the
hollow valve rod 40 including the throughhole 60 travels into the bore of themain piston body 110 to the point where the o-ring 116 overlapsdepression 61 and through hole 60 (FIG. 2A, 2C ), dynamic venting and equalization occurs. Becausedepression 61 of throughhole 60 may have a larger diameter than the thickness of the o-ring 116, a vent is created that allows for very rapid fluid communication between thefirst gas chamber 22 andsecond gas chamber 27. This very rapid fluid communication is represented by arrow Q and may be much faster than that which could be achieved by the possible flow of fluid throughfluid path 41 and outcheck valve 50 a andcheck valve 50 b. During this dynamic operation, the high-pressure gas chamber will vent to the lower pressure gas chamber. In the dynamic examples ofFIGS. 2A, 2C ,first gas chamber 22 is the high pressure chamber and vents to the lower pressuresecond gas chamber 27 throughvent 109. There will be a pressure drop in thefirst gas chamber 22 and a pressure rise in thesecond gas chamber 27. According to the formula P=F/A, with force directly proportional to pressure, the decreased pressure onupper surface 110 a will result in a decreased force onupper surface 110 a and increased pressure onlower surface 110 b will result in an increased force onlower surface 110 b and therefore there will be an unbalanced force upward, i.e., compression. Thus, the gas spring will expand towards its rest equilibrium position, which occurs when the forces on both sides ofmain piston body 110 are equal. -
FIGS. 3A-3C depict how thegas spring 10′ can be converted from long travel mode to short travel mode using a gas mechanism.FIG. 3A depictsstatic gas spring 10′ in long travel mode. Accordingly, themoveable piston assembly 100 is located low in theinternal gas chamber 20 and throughhole 60 is positioned close above it. In the static position, the pressure in thesecond gas chamber 27 is higher than the pressure in thefirst gas chamber 22. The user then converts thegas spring 10 to short travel mode by turning an external knob K that results in the moving of the throughhole 60 further towards the top of theinternal gas chamber 20. However, as the mere moving of the throughhole 60 does not directly affect the pressures or forces in either of thefirst gas chamber 22 orsecond gas chamber 27, themoveable piston assembly 100 does not move to the new travel mode position without additional assistance. Therefore, as shown inFIG. 3B , the user would, for example, preferably pump the moveable piston assembly 100 a few times as symbolized by the double-headed arrow B-B in the FIG. During the downward movement ofgas spring body 15 relative to the moveable piston assembly 100: - A. The gas in
first chamber 22 increases in pressure and is forced fromfirst gas chamber 22 into throughhole 60 andfluid path 41 of thehollow valve rod 40. Sincecheck valve 50 a only allows fluid flow out offluid path 41, the gas then exits thehollow valve rod 40 by openingcheck valve 50 b and enters second gas chamber 27 (whose pressure has temporarily decreased) viavent 109 in the moveable piston assembly 100 (recall this a simplified schematic representation). Accordingly, the pressure in thesecond gas chamber 27 will increase; and - B. With an increase in pressure in the
second gas chamber 27 due to the pumping, an upward force will result on thelower surface 110 b of themain piston body 110 and themoveable piston assembly 100 will move upward into the new equilibrium point in a short travel mode position (FIG. 3C ) where the pressure insecond gas chamber 27 exceeds the pressure infirst gas chamber 22. -
FIG. 4A-4C depict how thegas spring 10′ can be converted from short travel mode to long travel mode.FIG. 4A depictsstatic gas spring 10′ in short travel mode. Accordingly, themoveable piston assembly 100 is located high in theinternal gas chamber 20 and throughhole 60 is positioned close above it. In this static position, the pressure in thesecond gas chamber 27 is higher than the pressure in thefirst gas chamber 22. The user then converts thegas spring 10 to long travel mode by turning an external knob K that results in the moving of the throughhole 60 further towards the bottom of theinternal gas chamber 20. This has the result of moving the throughhole 60 from the lower pressurefirst gas chamber 22 to the higher-pressuresecond gas chamber 27. Via thevent 109 in themoveable piston assembly 100, thefluid path 41 of thehollow valve rod 40 will have the pressure of thesecond gas chamber 27. Because the pressure on thefirst gas chamber 22 side of thecheck valve 50 a will be less than onfluid path 41 side, thecheck valve 50 a will open and gas will flow from thesecond gas chamber 27 to thefirst gas chamber 22. This results in a pressure drop in thesecond gas chamber 27 and a pressure increase in thefirst gas chamber 22. This ultimately results in a downward force on theupper surface 110 a of themain piston body 110 and themoveable piston assembly 100 will accelerate downward to the new equilibrium point in a long travel mode position (FIG. 4C ) where the pressure insecond gas chamber 27 still will exceed the pressure infirst gas chamber 22. Note that unlike the change from long travel mode to short travel mode, the change from short travel mode to long travel mode does not require any pumping on thegas spring 10 since the moving of the throughhole 60 into the high pressuresecond gas chamber 27 creates the necessary pressure differential. - In particular, while it may seem that having a large or infinite number of travel positions between long and short may be optimal, a rider may not need such a wide range of positions. Accordingly, another embodiment involves incorporating a discrete number of predetermined travel mode positions to the gas spring, preferably: long travel (L), medium travel (M), and short travel (S) modes.
- Additionally, when the
gas spring 10′ has been incorporated in a front fork of a bicycle, the typical distance between throughhole 60 in the long travel mode position and short travel mode position may be between 40-45 mm, but can vary widely between manufacturers. Using the maximum available thread pitch that would not mechanically bind, it may still take a plurality of complete turns, such as three, of the adjustment knob K to bring the radial hole from the long travel mode position to the short travel mode position for a 45 mm travel change. Having to make a plurality of complete turns during a ride may be impractical for a rider. Accordingly, another embodiment of the invention additionally involves the ability to make drastic incremental travel adjustments with only a small angular turn of an adjustment knob; preferably 90°, and typically no more than 240° of rotation (since more than 240° would require a release and re-grip of the knob). - The travel mode adjust of another embodiment of the invention may be considered a much more non-linear or non-proportional travel adjust than those of the
gas spring 10′. This is depicted by the graph ofFIG. 5 . InFIG. 5 , in the travel adjust of thegas spring 10′ having 15 discrete knob settings corresponding to 15 different and discrete travel levels, the turning of the knob appears to create almost a linear change in the travel of the fork. InFIG. 5 , in the travel adjust according to another embodiment, where there are 3 discrete knob settings corresponding to 3 different and discrete travel modes, but covering the same overall amount of linear travel, the turning of the knob creates a much more stepped and non-linear change in the travel of the fork. - As schematically shown in the static equilibrium views of
FIG. 6A-6C , avalve rod assembly 240 may have three through holes, preferably in the form of three preferably radial through holes, 260 a, 260 b, 260 c corresponding to predetermined damper travels, namely: short travel mode, medium travel mode, and long travel modes, respectively. The same variability concerning the structure and number of throughholes 60 discussed above applies to throughholes 260. However, these through holes: (1) need not be in a depression for reasons to be described below and (2) do not provide direct access to the interior of thevalve rod assembly 240 and hollow interior portion orfluid path 241 of thegas spring 10 and as pictorially depicted in the FIGs by the solid fill, at least two of the throughholes 260 will always be sealed off from fluid communication with thefluid path 241 of thevalve rod assembly 240. - The structure of the
valve rod assembly 240 is more clearly shown inFIGS. 7A-7C . In particular,valve rod assembly 240 may comprise: (a) anouter valve rod 242 having a hollow interior and (b) a valve control assembly including:valve tubes 245,valve ring 246, andinner valve rod 255. Thevalve tubes 245 andvalve ring 246 are primarily for structural rigidity of thevalve rod assembly 240 and for supporting the seals, as described below.Inner valve rod 255 has generally closed walls that surroundfluid path 241 except for at least one valve rod bore 257 and openings at its ends that are sealed off bycheck valves FIGS. 12A-B , 13A-B, 16A-B), similarly as previously described with respect to thegas spring 10′. However,check valves check valve 50 a andcheck valve 50 b, and therefore they can be used in place ofdepression 61 during the equalization process.FIG. 16A-16B depict thesecheck valves check valves small ball bearing 252 blockingfluid path 241 ofinner valve rod 255. An elastomeric o-ring 251 surrounds the exit tofluid path 241 to create a good seal when the check valve is in its closed position (FIG. 15A ) and aspring 253biases ball bearing 252 into the seat of o-ring 251. When the pressure of the gas flow Q throughfluid path 241 is large enough, thespring 253 forces can be overcome and theball bearing 252 unseated (FIG. 16B ), thereby allowing the gas flow Q to escape fromfluid path 241.Spring 253, which is highly responsive, coupled with the fairly large flow path that is created when the valve opens results in a check valve that operates more rapidly than that of thecheck valves 50 a,b as well as with less pressure differential across the valve. - Furthermore, as with the
gas spring 10′,inner valve rod 255 may rotate and move longitudinally to cause longitudinal movement of the at least one valve rod bore 257 relative to valve tube 242 (compareFIGS. 7A-7C ). While the drawings depict only one valve bore 257, one skilled in the art would recognize that there may be more than one valve bore 257, so long as all the valve bores 257 are at substantially the same height. - Each
valve tube 245 is trapped in between the outer andinner valve tubes outer seal 271 and aninner seal 270. These seals will typically be in the form of o-rings. Eachvalve tube 245 will also have one or more throughbores holes valve tubes 245 are smaller than the space between theinner valve rod 255 and theouter valve rod 242,gas gaps inner seals 270 isvalve ring 246. Becausevalve ring 246 is smaller than the space between theinner valve rod 255 and theouter valve rod 242, agas gap 285 b that creates a venting passageway is formed there between also. However, unless the valve rod bore 257 is aligned to provide fluid communication with a particular gas gap, that gas gap is sealed off from thefluid path 241. - Thus, for example, in
FIG. 7 A, gas may enter thevalve rod assembly 240 through any of the throughholes bores respective gas gaps FIG. 7 A, the gas spring is set to medium travel and therefore, valve rod bore 257 is aligned withgas gap 285 b. Thus, gas coming into thevalve rod assembly 240 fromgas gaps inner seal 270 andouter seal 271 and the fact that valve rod bore 257 does not provide fluid access betweengas gaps fluid path 241. However, gas may enter thevalve rod assembly 240 throughhole 260 b for the mid travel setting, flow through thevalve ring 246, into the gas gap, 285 b, and then through valve rod bore 257 into thefluid path 241 ofinner valve rod 255. The gas will then travel to the appropriate valve and chamber. - For the examples in
FIGS. 7B and 7C , gas also enters thevalve rod assembly 240 through all of the throughholes bores respective gas gaps FIGS. 7B and 7C , however, the gas spring is set to one of either short or long travel modes, respectively, and therefore, valve rod bore 257 is aligned to provide fluid communication betweenfluid path 241 and gas gap (e.g.) 285 a or 285 c. Gas may enter thevalve rod assembly 240 throughhole fluid path 241 ofinner valve rod 255. The gas will then travel to the appropriate valve and chamber. - This operation is shown schematically in
FIG. 9A-9C (FIG. 8 described below), which also more clearly shows how the method of the invention allows the function and result of moving a radial bore across a very long travel can be achieved without actually having to do so. That is, through less than one complete turn of the adjustment knob K, and preferably approximately 90° rotation of the knob, what can be achieved is the same as three complete turns of an extremely sharply pitched shaft that would be very close to binding due to the sharpness of the pitch. - In
FIG. 9A , the gas spring is configured for short (S) travel mode. Accordingly, a flow path is open betweenfluid path 241 ofinner valve rod 255 and bore 280 a. - In
FIG. 9B , the gas spring is configured for medium (M) travel mode. Accordingly, a flow path is open betweenfluid path 241 ofinner valve rod 255 and bore 280 b. - In
FIG. 90 , the gas spring is configured for long (L) travel mode. Accordingly, a flow path is open betweenfluid path 241 ofinner valve rod 255 and bore 280 c. - This all is summarily showed in
FIG. 10 . For thegas spring 10′, the valve rod would have to be rotated a sufficient number of times with a thread pitch sufficient to move the radial hole a longitudinal distance D1, approximately equal to 45 mm. However, with the design according to another embodiment, the valve rod bore 257 only has to be rotated a sufficient number of times with a pitch sufficient to move the radial hole a longitudinal distance D2, approximately equal to 2.7 mm, substantially less than the longitudinal distance between now fixed bores 280. These distances are also highlighted inFIGS. 7 A-7C. This can be achieved through less than one complete turn of the adjustment knob K, and preferably approximately 90′ rotation of the knob and a less severe thread pitch. This makes the ability to make the travel adjustment much more user-friendly. - As previously mentioned, through
holes 260 need not be located in depressions in the way that throughhole 60 are. Nor, do they have to be larger than o-ring 116. Rather, it is possible that as shown in simplifiedFIG. 8 , dynamic venting (cf.FIG. 2C ) is achieved by the overpressure ofsecond chamber 27 directly entering intofluid path 241 through an open throughhole 260 and valve rod bore 257 and then up to and out ofcheck valve 250 a and into first chamber 22 (latter part not shown inFIG. 8 ). This process can occur just as rapidly as the venting through the depression ofFIG. 2C due to the quick response ofcheck valves 250 a. - Finally,
FIGS. 12 and 13 , correspond toFIGS. 3 and 4 , respectively in thatFIGS. 12 and 13 depict how the gas spring according to another embodiment of the invention may be converted from long travel mode to short travel mode (FIG. 12 ) or short travel mode to long travel mode (FIG. 13 ). The general operation of the gas springs ofFIGS. 12 and 13 only differ from those ofFIGS. 3 and 4 in that the valve rod assembly previously described is used instead of a longitudinally movingradial hole 60. - Thus, in conclusion, by:
- a) providing a valve rod assembly having an internal fluid path;
- b) placing the gas chamber in fluid communication with the fluid path at a plurality of longitudinal positions corresponding to a plurality of different travel modes; and
- c) using a valve rod having at least one valve bore to place only one of the longitudinal positions in fluid communication with the fluid path, a method of changing the travel mode of a gas spring having a gas chamber filled with a gas may be provided.
- Additionally, it is possible that in the method, the step of using a valve rod may include the step of rotating the valve rod less than one turn.
- Additionally, it is further possible in the method that the step of rotating the valve rod moves the valve bore a distance substantially less than the distance between the plurality of different travel modes.
- Additionally, it is further possible in the method that the step of rotating the valve rod and moving the valve bore also includes moving the valve bore longitudinally.
- The above description is given in reference to exemplary embodiments of an improved gas spring control for a suspension. However, it is understood that many variations are apparent to one of ordinary skill in the art from a reading of the above specification and such variations are within the spirit and scope of the instant invention as defined by the following appended claims.
-
List of Reference Numerals Used U Upper fork leg F Fork K Knob L Lower fork leg Q Gas flow 10 Gas spring 15 Gas spring body 20 Gas chamber 22 First gas chamber 27 Second gas chamber 40 Valve rod 41 Fluid path 42 Closed head portion 51 o- ring 52 Vent hole 60 Through hole 61 Depression 50A, 50B Check valve 100 Piston assembly 109 Vent 110 Main piston body 110a, b Piston surfaces 115 Collar portion 116 o- ring 240 Valve rod assembly 241 Fluid path 242 Valve tubes 245 Valve tubes 246 Valve ring 250a, 250b Check valves 251 o- ring 252 Ball bearing 253 Spring 255 Inner valve rod 257 Valve rod bore 260a, 260b, 260c Through holes 270 Outer seals 271 Inner seals 280a, 280b, 280c Bores 285a, 285b, 285c Gas gaps
Claims (1)
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US17/195,216 US20210222750A1 (en) | 2002-06-25 | 2021-03-08 | Gas spring with travel control |
Applications Claiming Priority (12)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US39199102P | 2002-06-25 | 2002-06-25 | |
US39280202P | 2002-06-28 | 2002-06-28 | |
US10/237,333 US7703585B2 (en) | 2002-06-25 | 2002-09-05 | Integrated and self-contained suspension assembly having an on-the-fly adjustable air spring |
US66749505P | 2005-04-01 | 2005-04-01 | |
US37270706A | 2006-03-10 | 2006-03-10 | |
US11/560,403 US8464850B2 (en) | 2006-11-16 | 2006-11-16 | Gas spring curve control in an adjustable-volume gas-pressurized device |
US3801508P | 2008-03-19 | 2008-03-19 | |
US12/176,160 US20080296814A1 (en) | 2002-06-25 | 2008-07-18 | Gas spring with travel control |
US14/336,929 US9415653B2 (en) | 2002-06-25 | 2014-07-21 | Gas spring with travel control |
US15/237,371 US10132379B2 (en) | 2002-06-25 | 2016-08-15 | Gas spring with travel control |
US16/165,875 US10941828B2 (en) | 2002-06-25 | 2018-10-19 | Gas spring with travel control |
US17/195,216 US20210222750A1 (en) | 2002-06-25 | 2021-03-08 | Gas spring with travel control |
Related Parent Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US16/165,875 Continuation US10941828B2 (en) | 2002-06-25 | 2018-10-19 | Gas spring with travel control |
Publications (1)
Publication Number | Publication Date |
---|---|
US20210222750A1 true US20210222750A1 (en) | 2021-07-22 |
Family
ID=70281037
Family Applications (2)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US16/165,875 Expired - Lifetime US10941828B2 (en) | 2002-06-25 | 2018-10-19 | Gas spring with travel control |
US17/195,216 Abandoned US20210222750A1 (en) | 2002-06-25 | 2021-03-08 | Gas spring with travel control |
Family Applications Before (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US16/165,875 Expired - Lifetime US10941828B2 (en) | 2002-06-25 | 2018-10-19 | Gas spring with travel control |
Country Status (1)
Country | Link |
---|---|
US (2) | US10941828B2 (en) |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102017010876B4 (en) * | 2017-11-24 | 2023-06-01 | Günther Zimmer | Cylinder-piston unit with load-dependent throttle |
US11255399B2 (en) * | 2018-03-14 | 2022-02-22 | Zf Friedrichshafen Ag | Damping valve for a vibration damper |
US11279194B2 (en) * | 2020-04-02 | 2022-03-22 | Thyssenkrupp Bilstein Of America Inc. | Damper with reservoir |
Family Cites Families (310)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US865151A (en) | 1907-05-13 | 1907-09-03 | Int Harvester Co | Force-pump. |
US1094567A (en) | 1912-06-20 | 1914-04-28 | Josef Hofmann | Pneumatic spring for vehicles. |
US1281079A (en) | 1915-03-11 | 1918-10-08 | Willard T Sears | Shock-absorber. |
US1492328A (en) | 1921-09-24 | 1924-04-29 | James S Lang | Shock absorber |
US1946882A (en) | 1928-09-06 | 1934-02-13 | Detroit Lubricator Co | Valve |
US1992490A (en) | 1932-08-11 | 1935-02-26 | Firestone Tire & Rubber Co | Nozzle |
FR757515A (en) | 1932-09-26 | 1933-12-27 | Advanced air suspension system | |
US2101265A (en) | 1934-01-09 | 1937-12-07 | Mercier Jean | Shock absorber |
US2115072A (en) | 1937-01-25 | 1938-04-26 | Gen Motors Corp | Pneumatic suspension device |
US2265435A (en) | 1938-02-11 | 1941-12-09 | Universal Hydraulic Corp | Tube valve |
DE725659C (en) | 1941-05-17 | 1942-09-26 | Gelsenberg Benzin Ag | Device for transferring pressurized gases or liquid gases |
US2329803A (en) | 1941-10-06 | 1943-09-21 | Monroe Auto Equipment Co | Inertia controlled shock absorber |
US2569503A (en) | 1943-02-17 | 1951-10-02 | Dana Corp | Clutch plate |
US2528822A (en) | 1947-06-20 | 1950-11-07 | Ernest A Dunn | Automatic shutoff valve |
DE837508C (en) | 1950-11-08 | 1952-04-28 | Stabilus Ind Und Handelsgesell | Shock absorber arrangement for power and bicycles |
US2774448A (en) | 1953-04-28 | 1956-12-18 | Clifford T Hultin | Inertia responsive shock absorber |
BE557514A (en) | 1956-05-15 | |||
US3001538A (en) | 1956-06-22 | 1961-09-26 | Manning Maxwell & Moore Inc | Error detector for pneumatic transmission system |
US2944639A (en) | 1956-07-30 | 1960-07-12 | William T Blake | Shock absorber with vacuum compensator |
FR1157081A (en) | 1956-07-31 | 1958-05-27 | Rech S Etudes | Monochronous air suspension for vehicles |
US2894742A (en) | 1957-02-04 | 1959-07-14 | Adolphe C Peterson | Automotive air spring means |
GB865151A (en) | 1958-04-22 | 1961-04-12 | Dust Control Processes Ltd | Improvements in or relating to dust separators |
NL236456A (en) | 1959-02-24 | |||
DE1092781B (en) | 1959-04-08 | 1960-11-10 | Boge Gmbh | Suspension working with a fluid with stabilizing device and height regulation of the body, in particular of motor vehicles |
US3085771A (en) | 1960-03-14 | 1963-04-16 | Adolphe C Peterson | Yieldable support means for land and air vehicles |
US3146862A (en) | 1960-09-21 | 1964-09-01 | Daimler Benz Ag | Remote controlled fluid-shockabsorber for vehicles |
FR1327917A (en) | 1962-04-13 | 1963-05-24 | Pneumatic device allowing in particular the modification of the characteristics of vehicle suspensions | |
US3114705A (en) | 1962-08-20 | 1963-12-17 | Gen Motors Corp | Means for controlling the dampening of an elastically suspended rotating drum duringcentrifuging |
US3237726A (en) | 1962-09-07 | 1966-03-01 | Bendix Corp | Shock absorber lock |
US3201110A (en) | 1963-11-07 | 1965-08-17 | Taccone Corp | Cushioning device |
DE1216800B (en) | 1964-03-17 | 1966-05-12 | Fichtel & Sachs Ag | Hydraulic vibration damper for a washing machine with spin cycle |
US3215283A (en) * | 1964-03-18 | 1965-11-02 | Pullman Inc | Long travel hydraulic cushion device |
GB1095657A (en) | 1964-09-08 | 1967-12-20 | Girling Ltd | Improvements in hydraulic dampers for vehicle suspension |
DE1455159A1 (en) | 1964-11-05 | 1969-03-27 | Maschf Augsburg Nuernberg Ag | Adjustable gas suspension for laterally movable brackets |
US3379430A (en) | 1966-01-17 | 1968-04-23 | W E Hennells Company Inc | Twin piston pneumatic spring |
US3414092A (en) | 1967-01-03 | 1968-12-03 | Frank H. Speckhart | Shock absorbing device |
CH514317A (en) | 1969-06-19 | 1971-10-31 | Bauer Fritz | Lifting device for stepless adjustment of a wing, in particular the seat of chairs or stools |
DE2024749C3 (en) * | 1970-05-21 | 1980-08-14 | Stabilus Gmbh, 5400 Koblenz | Device for continuously adjusting the inclination of the backrest of seats, in particular motor vehicle seats |
USRE29055E (en) | 1970-12-21 | 1976-11-30 | Pump and method of driving same | |
GB1380900A (en) | 1970-12-29 | 1975-01-15 | Girling Ltd | Suspension systems |
US3722875A (en) | 1971-04-29 | 1973-03-27 | Us Air Force | Adjustable suspension unit |
US3836132A (en) | 1971-07-19 | 1974-09-17 | Maremont Corp | Self-leveling combined shock absorber and fluid spring assist unit |
DE2231050A1 (en) | 1972-06-24 | 1974-01-17 | Stabilus Gmbh | PISTON ROD SEAL FOR GAS SPRINGS WITH SEALING LIP SUPPORTED ON THE GUIDE |
DE2236402C3 (en) | 1972-07-25 | 1974-12-19 | Hoesch Werke Ag, 4600 Dortmund | Hydropneumatic suspension system with level control for vehicles, in particular motor vehicles |
US3889934A (en) | 1973-12-19 | 1975-06-17 | Houdaille Industries Inc | Hydraulic buffer |
FR2264223B1 (en) | 1974-03-14 | 1977-06-17 | Peugeot & Renault | |
JPS5176745A (en) | 1974-12-26 | 1976-07-02 | Showa Mfg | Banbaayokanshoki oyobi sonokumitateho |
IT1039678B (en) | 1975-07-02 | 1979-12-10 | Arces Srl | IMPROVEMENT IN SUSPENSION FOR MOTORCYCLES |
SU623759A1 (en) | 1976-12-07 | 1978-09-15 | Московское Ордена Ленина И Ордена Трудового Красного Знамени Высшее Техническое Училище Им.Н.Э.Баумана | Vehicle suspension |
HU174666B (en) | 1977-06-30 | 1980-03-28 | Autoipari Kutato Intezet | Amortiseur having air spring and telescopic damper of damping limited in direct ratio to loading particularly for motor vehicles |
US4122923A (en) | 1977-07-11 | 1978-10-31 | Ace Controls, Inc. | Adjustable hydraulic shock absorber |
US4132395A (en) | 1977-11-17 | 1979-01-02 | Fox Jr Robert C | Shock absorber with improved extension damping |
US4153266A (en) | 1977-12-05 | 1979-05-08 | Uhls Jimmie J | Air shock apparatus for motorcycles |
FR2411341A1 (en) | 1977-12-12 | 1979-07-06 | Messier Hispano Sa | OLEOPNEUMATIC SUSPENSION WITH VARIABLE LAMINATION PORTS, ESPECIALLY FOR LANDING GEAR OF AERODYNES |
DE2758083A1 (en) | 1977-12-24 | 1979-07-05 | Stabilus Gmbh | FREQUENCY-DEPENDENT VIBRATION DAMPER |
US4159756A (en) | 1978-01-17 | 1979-07-03 | Kayaba K.K. | Adjusting device for damping force of rear shock-absorbers of motorcycles |
US4159105A (en) | 1978-02-21 | 1979-06-26 | Bouvier Robert A | Shock absorber with adjustable spring load |
JPS54138249A (en) | 1978-04-17 | 1979-10-26 | Kayaba Industry Co Ltd | Shock absorber for twoowheel barrow |
US4206934A (en) | 1978-08-11 | 1980-06-10 | Grumman Flexible Corporation | Control valve mechanism for an air spring vehicle suspension |
US4273310A (en) | 1978-09-05 | 1981-06-16 | Peter Ginzler | Device for blocking or releasing fluid flow |
JPS5565741A (en) | 1978-11-10 | 1980-05-17 | Tokico Ltd | Shock absorber |
JPS5718509Y2 (en) | 1979-04-01 | 1982-04-19 | ||
US4256293A (en) | 1979-05-29 | 1981-03-17 | Tom Mcguane Industries, Inc. | Throttle control dash pot |
IT1196653B (en) | 1979-07-26 | 1988-11-25 | Fiat Auto Spa | OLEOPNEUMATIC SHOCK ABSORBER |
US4298101A (en) | 1979-10-05 | 1981-11-03 | Enertrols, Inc. | Shock absorber |
IT1119229B (en) | 1979-10-17 | 1986-03-03 | Roberto Perlini | PNEUMATIC OR HYDROPNEUMATIC SUSPENSION PARTICULARLY FOR HEAVY VEHICLES |
DE2942455A1 (en) | 1979-10-20 | 1981-04-30 | Fritz Bauer + Söhne oHG, 8503 Altdorf | LENGTH ADJUSTABLE GAS SPRINGS |
US4457340A (en) | 1979-12-13 | 1984-07-03 | Krueger Wallace F | Power-assisted valve, particularly for systems handling viscous materials |
JPS578509A (en) | 1980-06-19 | 1982-01-16 | Canon Inc | Lens barrel |
US4337849A (en) | 1980-07-24 | 1982-07-06 | The United States Of America As Represented By The Secretary Of The Army | Energy management damper |
JPS6025308B2 (en) | 1980-09-16 | 1985-06-17 | 株式会社昭和製作所 | Front forks of motorcycles, etc. |
US4390159A (en) | 1981-04-27 | 1983-06-28 | Duncan Ronnie J | Snap-on shut off valve |
US4527676A (en) | 1982-02-13 | 1985-07-09 | Atsugi Motor Parts Co., Ltd. | Variable-damping-force shock absorber |
US4452117A (en) | 1982-04-12 | 1984-06-05 | Rockwell International Corporation | Self-adjusting fence for motorized saw unit |
US4620619A (en) | 1982-05-20 | 1986-11-04 | Atsugi Motor Parts Co., Ltd. | Variable-damping-force shock absorber |
FR2528140B1 (en) | 1982-06-03 | 1985-10-11 | Messier Hispano Sa | FLUIDIC TYPE SHOCK ABSORBER |
JPS5926639A (en) | 1982-07-30 | 1984-02-10 | Hino Motors Ltd | Air suspension device |
US4452177A (en) | 1982-08-25 | 1984-06-05 | Dec International, Inc. | Valve for use in a suction line |
DE3233160A1 (en) | 1982-09-07 | 1984-03-15 | Daimler-Benz Ag, 7000 Stuttgart | Device for providing suspension for and stabilising vehicles, in particular motor vehicles |
US4509730A (en) | 1982-10-25 | 1985-04-09 | Imperial Clevite Inc. | Flexible wall spring damper |
JPS5981290A (en) | 1982-11-01 | 1984-05-10 | 本田技研工業株式会社 | Attitude controller on braking of motorcycle |
US4492290A (en) | 1983-01-12 | 1985-01-08 | Maremont Corporation | Acceleration sensitive compression head |
JPS59137207A (en) | 1983-01-24 | 1984-08-07 | Nissan Motor Co Ltd | Suspension device |
JPS59120612U (en) | 1983-02-02 | 1984-08-14 | 三菱自動車工業株式会社 | Vehicle suspension device |
GB2135020B (en) | 1983-02-03 | 1986-08-06 | Mitsubishi Motors Corp | Vehicle suspension unit with damping and spring rate adjustable in response to suspension extension |
JPS6064011A (en) | 1983-09-17 | 1985-04-12 | Nissan Motor Co Ltd | Suspension control system in car |
JPS6069711U (en) | 1983-10-20 | 1985-05-17 | トキコ株式会社 | Damping force adjustable hydraulic shock absorber |
JPS6099107U (en) | 1983-12-14 | 1985-07-06 | トヨタ自動車株式会社 | air spring suspension |
JPS60105213U (en) | 1983-12-23 | 1985-07-18 | トヨタ自動車株式会社 | Suspension buffer force adjustment mechanism |
JPS60105215U (en) | 1983-12-24 | 1985-07-18 | トヨタ自動車株式会社 | Suspension buffer force adjustment mechanism |
ZA842579B (en) | 1984-04-05 | 1984-11-28 | Gert Nel Janse Van Rensburg | Flow valve |
JPS611522A (en) | 1984-06-14 | 1986-01-07 | Nissan Motor Co Ltd | Suspension controller in vehicles |
IT1178992B (en) | 1984-06-27 | 1987-09-16 | Fiat Auto Spa | VARIABLE STRENGTH PNEUMATIC SPRING PARTICULARLY FOR VEHICLE SUSPENSIONS |
US4629170A (en) | 1984-06-29 | 1986-12-16 | The Goodyear Tire & Rubber Company | Dual chamber air spring |
JPS6120410U (en) | 1984-07-12 | 1986-02-06 | トヨタ自動車株式会社 | air spring suspension |
US4558587A (en) | 1984-08-29 | 1985-12-17 | Varian Associates, Inc. | Ball-type vacuum valve for leak detection apparatus |
JPS6194806A (en) | 1984-10-15 | 1986-05-13 | Toyota Motor Corp | Switching valve for pneumatic spring type suspension |
JPS6194822A (en) | 1984-10-16 | 1986-05-13 | Toyota Motor Corp | Power transferring device for 4-wheel driven car |
JPS6198604A (en) | 1984-10-18 | 1986-05-16 | Toyota Motor Corp | Shock absorber installation structure |
US4697796A (en) | 1984-10-20 | 1987-10-06 | Tokico Ltd. | Suspension device |
JPS61155010A (en) | 1984-10-24 | 1986-07-14 | Nissan Motor Co Ltd | Suspension control device in vehicle |
JPS61113510A (en) | 1984-11-08 | 1986-05-31 | Toyota Motor Corp | Suspension system |
JPS61122015A (en) | 1984-11-19 | 1986-06-10 | Toyota Motor Corp | Suspension for car |
JPS61129309A (en) | 1984-11-27 | 1986-06-17 | Toyota Motor Corp | Suspension system for vehicle |
US4613116A (en) | 1984-11-28 | 1986-09-23 | Toyota Jidosha Kabushiki Kaisha | Air suspension |
JPS61135808A (en) | 1984-12-06 | 1986-06-23 | Toyota Motor Corp | Air suspension |
JPS61139505A (en) | 1984-12-12 | 1986-06-26 | Toyota Motor Corp | Air suspension |
US4606440A (en) | 1984-12-13 | 1986-08-19 | General Motors Corporation | Vehicle damping apparatus with simultaneous bleed orifice and blowoff control |
US4576258A (en) | 1984-12-24 | 1986-03-18 | General Motors Corporation | Adaptive ride hydraulic damper |
US4660688A (en) | 1984-12-24 | 1987-04-28 | General Motors Corporation | Adaptive ride hydraulic damper with piston rod dress cap |
JPS61163009A (en) | 1985-01-14 | 1986-07-23 | Toyota Motor Corp | Vehicle |
US4686135A (en) | 1985-01-29 | 1987-08-11 | Hiraoka & Co., Ltd. | Composite sheet material |
JPH0444904Y2 (en) | 1985-02-26 | 1992-10-22 | ||
US4650212A (en) | 1985-03-20 | 1987-03-17 | Mazda Motor Corporation | Vehicle suspension system |
US4667696A (en) | 1985-04-04 | 1987-05-26 | Rensburg Gert N J Van | Flow valve |
DE3524863A1 (en) | 1985-04-12 | 1986-10-30 | Robert Bosch Gmbh, 7000 Stuttgart | METHOD AND DEVICE FOR CONTROLLING THE SUSPENSION, IN PARTICULAR FOR VEHICLES |
JPS61235215A (en) | 1985-04-12 | 1986-10-20 | Nippon Denso Co Ltd | Immediately effectual heating apparatus for vehicles |
DE3524862A1 (en) | 1985-04-12 | 1986-10-30 | Robert Bosch Gmbh, 7000 Stuttgart | DEVICE FOR DAMPING MOTION PROCESSES |
EP0205256B1 (en) | 1985-05-10 | 1991-01-09 | Toyota Jidosha Kabushiki Kaisha | Gas switching valve device for a gas suspension system |
US4631116A (en) | 1985-06-05 | 1986-12-23 | Hughes Aircraft Company | Method of monitoring trace constituents in plating baths |
JP2532059B2 (en) | 1985-09-13 | 1996-09-11 | 日産自動車株式会社 | Vehicle suspension control device |
US5296089A (en) | 1985-12-04 | 1994-03-22 | Massachusetts Institute Of Technology | Enhanced radiative zone-melting recrystallization method and apparatus |
JPS61235212A (en) | 1986-04-08 | 1986-10-20 | Mitsubishi Motors Corp | Suspension system for vehicle |
JPH0737203B2 (en) | 1986-05-08 | 1995-04-26 | 日産自動車株式会社 | Vehicle height control device |
US4974820A (en) | 1986-05-09 | 1990-12-04 | Suzuki Sogyo Kabushiki Kaisha | Bellows type shock absorber |
IT1191559B (en) | 1986-05-09 | 1988-03-23 | Enrico Ceriani | FORK FOR MOTORCYCLE |
US4746106A (en) | 1986-08-15 | 1988-05-24 | Nhk Spring Co., Ltd. | Car suspension system |
US4930336A (en) | 1987-01-22 | 1990-06-05 | Kenneth L. Smedberg | Single action cylinder |
DE3706338A1 (en) | 1987-02-27 | 1988-09-08 | Wagner Gmbh J | DIAPHRAGM PUMP DEVICE |
US4844428A (en) | 1987-03-31 | 1989-07-04 | Aisin Seiki Kabushiki Kaisha | Air spring assembly |
US4789051A (en) | 1987-06-08 | 1988-12-06 | General Motors Corporation | Damper with internally powered selective ride valving |
US4838306A (en) | 1987-08-10 | 1989-06-13 | Aladdin Engineering & Mfg., Inc. | Pneumatic locking valve with manual override |
US4944705A (en) | 1987-10-26 | 1990-07-31 | Kayaba Kogyo Kabushiki Kaisha | Tilt damper |
DE3772389D1 (en) | 1987-10-26 | 1991-09-26 | Bendix Espana | SHOCK ABSORBER. |
EP0318817A3 (en) | 1987-11-28 | 1990-05-30 | Hermann Hemscheidt Maschinenfabrik GmbH & Co. | Hydropneumatic shock and vibration damper with an inner tube |
DE3742213C2 (en) | 1987-12-12 | 1995-03-30 | Dorma Gmbh & Co Kg | Door closer with a closer shaft loaded by a spring arrangement in the closing direction |
US4901986A (en) | 1988-03-07 | 1990-02-20 | General Motors Corporation | Air bladder controlled hydraulic engine mount |
DE8806642U1 (en) | 1988-05-20 | 1988-09-08 | Stabilus Gmbh, 5400 Koblenz, De | |
US5201388A (en) | 1988-07-28 | 1993-04-13 | Ohlins Racing Ab | Shock absorber |
US5139119A (en) | 1988-08-13 | 1992-08-18 | Robert Bosch Gmbh | Apparatus for damping resilient vehicle wheel suspension systems |
DE3835788A1 (en) | 1988-10-20 | 1990-04-26 | Deutsche Forsch Luft Raumfahrt | QUICK-SWITCHING BALL VALVE |
US4958706A (en) | 1988-11-14 | 1990-09-25 | Richardson Donald G | Adjustable shock absorbers |
US4993523A (en) | 1989-02-10 | 1991-02-19 | Lord Corporation | Fluid circuit for semiactive damper means |
JPH02217635A (en) | 1989-02-16 | 1990-08-30 | Toyota Motor Corp | Liquid pressure damper |
US4936424A (en) | 1989-05-09 | 1990-06-26 | Costa Vince F | Hydraulic shock absorber with pressure sensitive external valving |
DE3943585C2 (en) | 1989-08-31 | 1995-04-27 | Wagner Gmbh J | Diaphragm pump |
GB8921962D0 (en) | 1989-09-28 | 1989-11-15 | Browning Michael R S | Variable suspension system |
US5332068A (en) | 1990-04-03 | 1994-07-26 | Richardson Technologies, Ltd. | Self contained automatic terrain condition adjusting shock absorber |
JP2587627Y2 (en) | 1990-05-28 | 1998-12-24 | 株式会社ユニシアジェックス | Damping force control device |
DE4018712A1 (en) | 1990-06-12 | 1991-12-19 | Bosch Gmbh Robert | Air spring with variable stiffness for motor vehicle - has rigid-walled auxiliary air chamber surrounding main air chamber adjusted by level of liq. filling |
US5201389A (en) | 1990-07-26 | 1993-04-13 | General Motors Corporation | Method of varying a suspension damping force as a vehicle is steered |
US5080205A (en) | 1990-07-26 | 1992-01-14 | General Motors Corporation | Steer-sensitive variable damping strut |
DE4124516A1 (en) | 1990-09-07 | 1992-03-26 | Iveco Magirus | MULTI-STAGE AIR SPRING, IN PARTICULAR FOR AN AIR SPRING VEHICLE AXLE OF A COMMERCIAL VEHICLE |
US5067517A (en) | 1990-10-29 | 1991-11-26 | Ting Chih Liu | Quantitative liquid level controlling device |
US5111735A (en) | 1990-10-30 | 1992-05-12 | Beloit Corporation | Air spring with quick release valve |
DE4123643A1 (en) | 1990-11-30 | 1992-06-04 | Peter Kleinbreuer | Bicycle with sprung wheels - has each damper connected to its pressure accumulator via manually-operated valve |
US5285875A (en) | 1990-12-05 | 1994-02-15 | Nissan Research & Development, Inc. | Impact sensitive shock absorber |
US5186481A (en) | 1991-04-03 | 1993-02-16 | Rockshox, Inc. | Bicycle with improved front fork wheel suspension |
US5067518A (en) | 1991-05-01 | 1991-11-26 | Ransburg Corporation | Pressure feed paint cup valve |
FR2678032B1 (en) | 1991-06-18 | 1993-10-01 | Aerospatiale Ste Nationale Indle | DEVICE FOR ELASTIC CONNECTION BETWEEN TWO PARTS, AND AIRCRAFT WITH TURNING WING COMPRISING SAID DEVICE. |
US5163538A (en) | 1991-09-03 | 1992-11-17 | General Motors Company | Low level damping valve and method for a semi-active hydraulic damper |
US5169129A (en) | 1991-09-26 | 1992-12-08 | Bridgestone/Firestone, Inc. | Variable rate air spring suspension system |
DE4132262A1 (en) | 1991-09-27 | 1993-04-01 | Teves Gmbh Alfred | HYDRAULIC VIBRATION DAMPER FOR MOTOR VEHICLES |
US5180186A (en) | 1991-11-12 | 1993-01-19 | General Motors Corporation | Strut and method for steer-sensitive damping |
IT1253888B (en) | 1991-11-15 | 1995-08-31 | Calzolari Isabella | ADJUSTABLE RESPONSE SHOCK ABSORBER WITH MANUAL CONTROL FOR BICYCLES AND Mopeds |
US5396973A (en) | 1991-11-15 | 1995-03-14 | Lord Corporation | Variable shock absorber with integrated controller, actuator and sensors |
US5150775A (en) | 1991-12-19 | 1992-09-29 | General Motors Corporation | Steer-sensitive variable damper and method utilizing a ring valve |
US5158270A (en) | 1991-12-31 | 1992-10-27 | Lin Norman R M | Enclosed hydraulic cylinder acting as a tension-buffer |
JP3342719B2 (en) | 1992-02-03 | 2002-11-11 | トキコ株式会社 | Suspension control device |
FR2687632B1 (en) | 1992-02-21 | 1994-04-15 | Messier Bugatti | AIRCRAFT LANDING TRAIN DESCENT. |
JPH05238233A (en) | 1992-03-02 | 1993-09-17 | Toyota Motor Corp | Control device for suspension |
US5251927A (en) | 1992-03-20 | 1993-10-12 | General Motors Corporation | Steer-sensitive hydraulic shock absorber and method |
GB2265435B (en) | 1992-03-25 | 1995-04-05 | Lee Wang Industry Ltd | A cushion device |
US5598903A (en) | 1992-05-05 | 1997-02-04 | Ricor Racing & Development, L.P. | Acceleration sensitive flow sensitive mcpherson strut |
US5462140A (en) | 1992-05-05 | 1995-10-31 | Richardson Technologies, Ltd. | Acceleration sensitive shock absorber |
DE4223165A1 (en) | 1992-05-13 | 1993-11-18 | Peter Wolschke | Two or three wheelers |
JP3080266B2 (en) | 1992-05-21 | 2000-08-21 | 株式会社ユニシアジェックス | Vehicle suspension system |
JPH0613993U (en) | 1992-07-29 | 1994-02-22 | 株式会社ショーワ | Bicycle wheel suspension |
US5275264A (en) | 1992-09-25 | 1994-01-04 | Calzolari Isella | Setting shock absorber for cycles |
US5823305A (en) | 1992-10-08 | 1998-10-20 | Ricor Racing & Development, L.P. | Flow sensitive, acceleration sensitive shock absorber |
GB9223414D0 (en) | 1992-11-07 | 1992-12-23 | Air Log Ltd | Variable ride height vehicle suspension system |
NL9300316A (en) * | 1993-02-19 | 1994-09-16 | Koni Bv | One-pipe shock absorber. |
JP3370130B2 (en) | 1993-03-18 | 2003-01-27 | 株式会社ショーワ | Front wheel suspension for bicycle |
DE4311626A1 (en) * | 1993-04-08 | 1994-10-13 | Stabilus Gmbh | Oscillation damper with a variable damping force |
CA2120862C (en) | 1993-04-30 | 1997-03-18 | Mark A. Popjoy | Self-blocking gas spring with temperature-responsive bypass valve |
US5470090A (en) | 1993-09-07 | 1995-11-28 | Manitou Mountain Bikes, Inc. | Precision suspension fork for bicylces |
US5413316A (en) | 1993-12-13 | 1995-05-09 | Bridgestone/Firestone, Inc. | Adjustable rate air spring |
JPH07167189A (en) | 1993-12-15 | 1995-07-04 | Toyota Motor Corp | Air suspension device |
JPH07205865A (en) | 1994-01-26 | 1995-08-08 | Daikin Mfg Co Ltd | Shock absorber for automobile |
EP0750724B1 (en) | 1994-03-17 | 1999-06-02 | André Ricard | Adjustable variable oleopneumatic shock absorbing device |
GB2287769B (en) | 1994-03-21 | 1998-04-29 | Monroe Auto Equipment Co | Automatic damper system |
US5456480A (en) | 1994-06-06 | 1995-10-10 | Rockshox, Inc. | Fork suspension with variable hydraulic damping |
US5580075A (en) * | 1994-06-06 | 1996-12-03 | Rockshox, Inc. | Bicycle fork suspension with exchangeable spring unit |
US5529152A (en) | 1994-07-08 | 1996-06-25 | Aimrite Systems International, Inc. | Variable constant force hydraulic components and systems |
US5632471A (en) | 1994-08-02 | 1997-05-27 | Fichtel & Sachs Ag | Air suspension system of a motor vehicle with air shocks or air spring with a compressed air container in the air suspension system |
DE4429562C2 (en) | 1994-08-19 | 1998-03-19 | Stefan Maier | Hydraulic vibration damper for the sprung front wheel of a bicycle |
ES1029231Y (en) | 1994-10-18 | 1995-11-01 | Pariente Antonio Cabrerizo | CUSHIONED BIKE FORK. |
FR2725948B1 (en) | 1994-10-20 | 1997-01-17 | Gluck Jean | ARTICULATED SEAT FOR INDIVIDUAL GOODS TRANSPORT TROLLEY (OF THE TYPE OF HYPERMARKET OR STATION AND AIRPORT TROLLEYS) |
FR2728948B1 (en) | 1994-12-28 | 1997-03-14 | Renault | TWO-CHAMBER PNEUMATIC SPRING WITH INDEPENDENT POWER SUPPLY, MOTOR VEHICLE WITH SUSPENSION COMPRISING SUCH A SPRING AND SPRING-SHOCK ABSORBER ASSEMBLY |
US5775677A (en) | 1995-02-07 | 1998-07-07 | Englund; Arlo C. | Air or gas sprung and dampened shock absorber |
US5954167A (en) | 1995-03-01 | 1999-09-21 | Ricor Racing & Development, L.P. | Flow sensitive acceleration sensitive shock absorber with added flow control |
JPH08262559A (en) | 1995-03-22 | 1996-10-11 | Fuji Photo Optical Co Ltd | Camera |
FR2733564B1 (en) | 1995-04-27 | 1997-06-20 | Peugeot | DAMPING ARRANGEMENT BY ROLLING A FLUID AND SUSPENSION SYSTEM, ESPECIALLY A MOTOR VEHICLE, EQUIPPED WITH SUCH A DAMPING ARRANGEMENT |
US5538276A (en) | 1995-05-23 | 1996-07-23 | Tullis; Jay K. | Tunable air spring |
US5620194A (en) * | 1995-06-07 | 1997-04-15 | The Boler Company | Self-steering suspension lockout mechanism |
KR970015078A (en) | 1995-09-30 | 1997-04-28 | 전성원 | Strut assembly of car suspension |
DE19604962A1 (en) | 1996-02-10 | 1997-08-14 | Suspa Compart Ag | Adjustable gas spring |
SE9602507L (en) | 1996-06-25 | 1997-12-26 | Oehlins Racing Ab | Shock |
US5957252A (en) | 1996-08-02 | 1999-09-28 | Berthold; Brian D. | Hydraulic suspension unit |
US5799758A (en) | 1996-08-20 | 1998-09-01 | Huang; Chen-Tan | Double-acting hydraulic cylinder for use in an exercising apparatus |
US5996978A (en) | 1996-08-27 | 1999-12-07 | Honda Giken Kogyo Kabushiki Kaisha | Hydraulic damper for vehicle |
SE510129C2 (en) | 1996-09-09 | 1999-04-19 | Lennart Nilsson | Active controlled ball valve |
FR2753510B1 (en) | 1996-09-17 | 1999-01-22 | S I P M | PROGRESSIVE MECHANICAL CONTROL OR CMP |
US5848675A (en) | 1996-10-03 | 1998-12-15 | Answer Products, Inc. | Damping apparatus for bicycle forks |
US6241060B1 (en) | 1996-10-03 | 2001-06-05 | Answer Products, Inc. | Oil damped fork |
US6050583A (en) | 1997-01-13 | 2000-04-18 | Bohn; David D. | Electronically controlled bicycle suspension apparatus |
US5971116A (en) | 1997-03-13 | 1999-10-26 | Cannondale Corporation | Electronic suspension system for a wheeled vehicle |
US6244398B1 (en) | 1997-05-15 | 2001-06-12 | K2 Bike Inc. | Shock absorber with variable bypass damping |
DE19729287B4 (en) | 1997-07-09 | 2006-06-22 | Zf Boge Elastmetall Gmbh | impact absorbers |
US6095541A (en) | 1997-07-16 | 2000-08-01 | Rockshox, Inc. | Adjustable gas spring suspension system |
US6105988A (en) | 1997-07-16 | 2000-08-22 | Rockshox, Inc. | Adjustable suspension system having positive and negative springs |
US5921572A (en) | 1997-07-31 | 1999-07-13 | Outback Bicycles, Inc. | Continuously compensating bicycle suspension system |
DE19737293A1 (en) | 1997-08-27 | 1999-03-11 | Hunger Walter Dr Ing E H | bicycle |
US6036212A (en) | 1997-09-16 | 2000-03-14 | Rockshox, Inc. | Damping system having separately adjustable damping circuits |
US6010119A (en) | 1997-11-04 | 2000-01-04 | Che Hsing Co., Ltd. | Adjustable pneumatically operated cylinder |
US6105987A (en) | 1997-12-17 | 2000-08-22 | Rockshox, Inc. | Valve mechanism for damping system |
US6311962B1 (en) | 1998-02-03 | 2001-11-06 | Fox Factory, Inc. | Shock absorber with external air cylinder spring |
US6135434A (en) | 1998-02-03 | 2000-10-24 | Fox Factory, Inc. | Shock absorber with positive and negative gas spring chambers |
AU3894999A (en) | 1998-05-11 | 1999-11-29 | Rockshox, Inc. | Damping and spring system for suspension system |
DE19827657A1 (en) | 1998-06-22 | 1999-12-23 | Suspa Compart Ag | Adjustable gas spring |
US6296092B1 (en) | 1998-10-28 | 2001-10-02 | Fox Factory, Inc. | Position-sensitive shock absorber |
US6360857B1 (en) | 1999-03-19 | 2002-03-26 | Fox Factory, Inc. | Damping adjuster for shock absorber |
US6267400B1 (en) | 1999-04-06 | 2001-07-31 | Specialized Bicycle Components, Inc. | Bicycle damping enhancement system |
US6318525B1 (en) | 1999-05-07 | 2001-11-20 | Marzocchi, S.P.A. | Shock absorber with improved damping |
JP2000343989A (en) | 1999-06-07 | 2000-12-12 | Delta Tooling Co Ltd | Stepless slide adjuster with safe lock |
US6464053B1 (en) | 1999-07-26 | 2002-10-15 | Tenneco Automotive Operating Company, Inc. | Single piece piston |
US6254067B1 (en) | 1999-08-02 | 2001-07-03 | Giant Manufacturing Co., Ltd. | Fluid regulating device for use with a hydraulic cylinder to obtain a variable shock absorbing effect |
US6659240B2 (en) | 1999-08-10 | 2003-12-09 | Lars Dernebo | Arrangement for a piston and cylinder device |
SE514386C2 (en) | 1999-08-10 | 2001-02-19 | Ld Design Electronics Ab | Device at a piston-cylinder means |
DE19940198C1 (en) | 1999-08-25 | 2001-02-01 | Continental Ag | Regulation method for suspension system for road vehicle involves adjustment of throttle between pneumatic spring and parallel shock absorber before independent adjustment of shock absorber |
DE19944183A1 (en) | 1999-09-15 | 2001-03-22 | Bayerische Motoren Werke Ag | Hydraulic shock absorbers for motor vehicles |
FR2800702A1 (en) | 1999-11-10 | 2001-05-11 | Romain Alain Venchiarutti | Cycle or motorcycle shock absorber has pressurised air chamber and second chamber with piston separating air and oil for anti-dive braking |
US6543799B2 (en) | 2000-01-13 | 2003-04-08 | Shimano Inc. | Bicycle suspension |
DE20022708U1 (en) | 2000-03-20 | 2002-02-28 | Albrecht Stephan | bicycle |
US6279703B1 (en) | 2000-05-15 | 2001-08-28 | A-Pro Cycles, Inc. | Shock absorbing adjusting structure |
TW576900B (en) | 2000-05-22 | 2004-02-21 | Kayaba Industry Co Ltd | Air spring |
DE10025749C1 (en) | 2000-05-24 | 2001-10-31 | Continental Ag | Valve used in vehicle pneumatic springs, comprises a star-shaped nozzle having a valve seat and concentric arms having a specified length and width |
DE10025753C2 (en) | 2000-05-24 | 2003-10-23 | Continental Ag | Motor vehicle air spring with an additional volume |
US6609722B1 (en) | 2000-09-14 | 2003-08-26 | Shimano Inc. | Bicycle crown or crown cover with electrical connector support |
US6386525B1 (en) | 2000-10-24 | 2002-05-14 | The Boler Company. | Dual volume air spring for suspensions |
US6340153B1 (en) | 2000-11-02 | 2002-01-22 | General Dynamics Advanced Technology Systems, Inc. | Shock and acoustic mount |
AU2002212516A1 (en) | 2000-11-09 | 2002-05-21 | Peter Kendall-Torry | Suspension system |
US6343807B1 (en) | 2001-01-19 | 2002-02-05 | Answer Products, Inc. | Multi-travel suspension fork for cycles |
US6457730B1 (en) | 2001-02-16 | 2002-10-01 | Trw Inc. | Anti-roll bar with link actuator for controlling torsional rigidity |
US20020117830A1 (en) | 2001-02-27 | 2002-08-29 | Holt Laurence James | Automatic suspension lockout for bicycles |
DE10122729B4 (en) | 2001-05-10 | 2006-04-20 | Dt Swiss Ag | Spring damper system for bicycles |
DE10122730B4 (en) | 2001-05-10 | 2006-07-13 | Dt Swiss Ag | Spring system for bicycles |
US6592136B2 (en) | 2001-07-02 | 2003-07-15 | Fox Factory, Inc. | Bicycle fork cartridge assembly |
US7182358B2 (en) | 2001-07-06 | 2007-02-27 | Andreas Felsl | Bicycle |
US6491146B1 (en) | 2001-08-21 | 2002-12-10 | Chen-Shing Yi | Damping adjustable shock absorber for a bicycle |
US6659241B2 (en) | 2001-08-22 | 2003-12-09 | Meritor Heavy Vehicle Technology, Llc | Shock absorber compression damping adjustment |
US6581948B2 (en) | 2001-08-30 | 2003-06-24 | Fox Factory, Inc. | Inertia valve shock absorber |
US7128192B2 (en) | 2001-08-30 | 2006-10-31 | Fox Factory, Inc. | Inertia valve shock absorber |
US6604751B2 (en) | 2001-08-30 | 2003-08-12 | Fox Factory, Inc. | Inertia valve shock absorber |
US6648109B2 (en) | 2001-09-13 | 2003-11-18 | Meritor Heavy Vehicle Technology, Llc | Adjustable shock absorber |
US6698730B2 (en) | 2001-10-04 | 2004-03-02 | Bfs Diversified Products, Llc | Dual rate air spring |
KR100422551B1 (en) | 2001-10-08 | 2004-03-11 | 현대자동차주식회사 | air suspension of vehicle |
DE10163996A1 (en) * | 2001-12-24 | 2003-07-03 | Suspa Holding Gmbh | Adjustable gas spring |
DE50200029D1 (en) | 2002-01-21 | 2003-10-02 | Storz Karl Gmbh & Co Kg | Medical instrument for rinsing and / or suction |
US6669219B2 (en) | 2002-04-10 | 2003-12-30 | Maverick American Llc | Telescoping suspension fork having a quick release wheel axle clamp |
US6712373B2 (en) | 2002-04-15 | 2004-03-30 | Specialized Bicycle Components, Inc. | Bicycle rear suspension |
DE10219753B4 (en) | 2002-05-02 | 2006-12-21 | Voith Turbo Gmbh & Co. Kg | Hydrodynamic brake |
DE60325964D1 (en) | 2002-05-29 | 2009-03-12 | Progressive Suspension Inc | HYDRAULIC SHOCK ABSORBER WITH PRESSURE CONTROL VALVE AND SECONDARY PISTON |
US6708803B2 (en) | 2002-06-10 | 2004-03-23 | Mark Andrew Jensen | Self-leveling dual spring rate strut |
US7703585B2 (en) | 2002-06-25 | 2010-04-27 | Fox Factory, Inc. | Integrated and self-contained suspension assembly having an on-the-fly adjustable air spring |
US20080296814A1 (en) | 2002-06-25 | 2008-12-04 | Joseph Franklin | Gas spring with travel control |
US8464850B2 (en) | 2006-11-16 | 2013-06-18 | Fox Factory, Inc. | Gas spring curve control in an adjustable-volume gas-pressurized device |
DE10236621B4 (en) | 2002-08-09 | 2005-02-03 | Daimlerchrysler Ag | Air suspension system of a McPherson strut |
US6691989B1 (en) | 2002-08-16 | 2004-02-17 | Bfs Diversified Products, Llc | Variable rate air spring assembly |
US7219881B2 (en) | 2002-08-28 | 2007-05-22 | Denk Engineering Gmbh | Shock absorber |
US7963509B2 (en) | 2007-01-31 | 2011-06-21 | Fox Factory, Inc. | Travel control for a gas spring and gas spring having very short travel modes |
US6883810B2 (en) | 2002-11-04 | 2005-04-26 | Volvo Trucks North America, Inc. | Air spring stiffness controller |
US6883650B2 (en) | 2002-11-15 | 2005-04-26 | Arvinmeritor Technology, Llc. | Adjustable shock absorber |
US6708999B1 (en) | 2002-12-02 | 2004-03-23 | Sram Corporation | Indicator for a bicycle suspension system for indicating travel of the suspension system |
US6966412B2 (en) | 2003-02-24 | 2005-11-22 | Arctic Cat Inc. | Position-sensitive shock absorber |
DE102004011466A1 (en) | 2003-04-03 | 2004-10-21 | Phoenix Ag | Vehicle pneumatic spring arrangement has dynamic valve system that opens/closes connection or chokes air feed depending on air column frequency and/or amplitude and/or pressure and/or air speed |
US6786498B1 (en) | 2003-04-28 | 2004-09-07 | Giant Manufacturing Co., Ltd. | Shock absorbing device for a bicycle |
US7011325B2 (en) | 2003-05-15 | 2006-03-14 | Kinzler Frederick W | Adjustable length suspension fork for a bicycle |
DE10329746B4 (en) | 2003-07-02 | 2006-06-01 | Zf Sachs Ag | Self-pumping hydropneumatic strut |
WO2006054994A1 (en) | 2004-11-18 | 2006-05-26 | Fox Robert C | Damper with pressure-sensitive compression damping |
US7374028B2 (en) | 2003-07-08 | 2008-05-20 | Fox Factory, Inc. | Damper with pressure-sensitive compression damping |
US7320388B2 (en) | 2003-09-15 | 2008-01-22 | Tenneco Automotive Operating Company Inc. | Stroke dependent damping |
DE10353903A1 (en) * | 2003-11-18 | 2005-06-16 | Suspa Holding Gmbh | Length adjustable compression spring |
US6974001B2 (en) | 2003-11-19 | 2005-12-13 | Arvinmeritor Technology, Llc. | Temperature compensating gas spring |
US7163223B2 (en) | 2003-11-19 | 2007-01-16 | Sram Corporation | Lockout mechanism for a suspension system |
US7195234B2 (en) | 2003-11-28 | 2007-03-27 | Sram Corporation | Adjustable gas spring suspension system |
DE10356438B3 (en) | 2003-12-03 | 2005-05-19 | Continental Aktiengesellschaft | Pneumatic spring-damper unit for automobile has damping spaces defined within cylinder housing by piston unit with 2 separation pistons and spring space defined by rolled bellows around projecting piston rod |
DE10358331A1 (en) | 2003-12-12 | 2005-07-07 | Dt Swiss Ag | Shock absorber in particular for bicycle, comprising valve for opening and closing connection between chambers |
US7011193B2 (en) | 2004-02-13 | 2006-03-14 | Tenneco Automotive Operating Company Inc. | Rod guide and seal system for gas filled shock absorbers |
FR2866628A1 (en) | 2004-02-24 | 2005-08-26 | Rexam Cosmetic Closures | Liquid product dispenser filling procedure uses removable spacer between upper and lower sections of container to create temporary dead volume |
DE102004021586B4 (en) | 2004-05-03 | 2010-09-23 | Continental Aktiengesellschaft | air spring |
US7441638B2 (en) | 2004-12-09 | 2008-10-28 | Kayaba Industry Co., Ltd. | Front fork |
US7017893B1 (en) * | 2004-12-16 | 2006-03-28 | Vincenzo F Costa | Pull-type suspension |
US7401800B2 (en) | 2005-09-14 | 2008-07-22 | Slam Corporation | Gas spring suspension system |
US7516969B2 (en) | 2005-10-25 | 2009-04-14 | Hui-Hsiung Chen | Travel adjustable front suspension fork |
US7870936B2 (en) | 2006-08-18 | 2011-01-18 | Sram, Llc | Bicycle suspension system |
US8869959B2 (en) * | 2008-07-24 | 2014-10-28 | Fox Factory, Incorporated | Vehicle suspension damper |
US20100244340A1 (en) * | 2008-03-19 | 2010-09-30 | Wootten Dennis K | Methods and apparatus for combined variable damping and variable spring rate suspension |
US9168972B2 (en) * | 2014-01-02 | 2015-10-27 | Taiwan Hodaka Industrial Co., Ltd. | Control device for the rear shock absorber of a bicycle |
JP6295120B2 (en) * | 2014-03-25 | 2018-03-14 | 株式会社ショーワ | Hydraulic shock absorber |
-
2018
- 2018-10-19 US US16/165,875 patent/US10941828B2/en not_active Expired - Lifetime
-
2021
- 2021-03-08 US US17/195,216 patent/US20210222750A1/en not_active Abandoned
Also Published As
Publication number | Publication date |
---|---|
US20200124130A1 (en) | 2020-04-23 |
US10941828B2 (en) | 2021-03-09 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
US10132379B2 (en) | Gas spring with travel control | |
US20210222750A1 (en) | Gas spring with travel control | |
US10731724B2 (en) | Suspension system | |
US11370261B2 (en) | Methods and apparatus for suspending vehicles | |
US8894050B2 (en) | Methods and apparatus for suspending vehicles | |
JP4712703B2 (en) | Shock absorber assembly | |
US6427986B1 (en) | Air suspension apparatus | |
US20160263958A1 (en) | Vehicle suspension system | |
CN112682453B (en) | Position dependent front fork damping for bicycles and motorcycles | |
US20060175166A1 (en) | Controllable piston valve and /or flat valve for a vibration damper | |
JP2009156348A (en) | Hydraulic shock absorber | |
US20160288869A1 (en) | Shock absorber | |
EP3409972A1 (en) | Pressurized telescopic front fork leg, front fork and vehicle | |
JP2003042215A (en) | Air suspension device for vehicle | |
JPH11344069A (en) | Damping force generating structure of hydraulic shock absorber | |
JPH0727166A (en) | Damping force regulating device for shock absorber | |
JPH0996336A (en) | Damping force adjustment type hydraulic shock absorber | |
JP2010038171A (en) | Hydraulic shock absorber | |
JP2017096311A (en) | Front fork |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
AS | Assignment |
Owner name: FOX FACTORY, INC., GEORGIA Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:FRANKLIN, JOSEPH;FOX, ROBERT C.;SIGNING DATES FROM 20080722 TO 20080725;REEL/FRAME:055523/0809 |
|
STPP | Information on status: patent application and granting procedure in general |
Free format text: APPLICATION DISPATCHED FROM PREEXAM, NOT YET DOCKETED |
|
STPP | Information on status: patent application and granting procedure in general |
Free format text: DOCKETED NEW CASE - READY FOR EXAMINATION |
|
AS | Assignment |
Owner name: WELLS FARGO BANK, NATIONAL ASSOCIATION, NORTH CAROLINA Free format text: SECURITY INTEREST;ASSIGNOR:FOX FACTORY, INC.;REEL/FRAME:059616/0435 Effective date: 20220405 |
|
STPP | Information on status: patent application and granting procedure in general |
Free format text: NON FINAL ACTION MAILED |
|
STCB | Information on status: application discontinuation |
Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION |