WO2016146660A1 - Hydraulic compression stop member for a hydraulic shock-absorber for a vehicle suspension - Google Patents
Hydraulic compression stop member for a hydraulic shock-absorber for a vehicle suspension Download PDFInfo
- Publication number
- WO2016146660A1 WO2016146660A1 PCT/EP2016/055642 EP2016055642W WO2016146660A1 WO 2016146660 A1 WO2016146660 A1 WO 2016146660A1 EP 2016055642 W EP2016055642 W EP 2016055642W WO 2016146660 A1 WO2016146660 A1 WO 2016146660A1
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- WO
- WIPO (PCT)
- Prior art keywords
- cup
- absorber
- shock
- shaped body
- stop member
- Prior art date
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Classifications
-
- 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
- F16F9/346—Throttling passages in the form of slots arranged in cylinder walls
- F16F9/3465—Slots having a variable section along their length
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G13/00—Resilient suspensions characterised by arrangement, location or type of vibration dampers
- B60G13/02—Resilient suspensions characterised by arrangement, location or type of vibration dampers having dampers dissipating energy, e.g. frictionally
- B60G13/06—Resilient suspensions characterised by arrangement, location or type of vibration dampers having dampers dissipating energy, e.g. frictionally of fluid type
- B60G13/08—Resilient suspensions characterised by arrangement, location or type of vibration dampers having dampers dissipating energy, e.g. frictionally of fluid type hydraulic
-
- 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
- B60G17/06—Characteristics of dampers, e.g. mechanical dampers
- B60G17/08—Characteristics of fluid 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
- F16F9/10—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium using liquid only; using a fluid of which the nature is immaterial
- F16F9/14—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect
- F16F9/16—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect involving only straight-line movement of the effective parts
- F16F9/18—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect involving only straight-line movement of the effective parts with a closed cylinder and a piston separating two or more working spaces therein
- F16F9/185—Bitubular units
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/48—Arrangements for providing different damping effects at different parts of the stroke
- F16F9/49—Stops limiting fluid passage, e.g. hydraulic stops or elastomeric elements inside the cylinder which contribute to changes in fluid damping
-
- 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
- B60G2206/41—Dampers
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G2500/00—Indexing codes relating to the regulated action or device
- B60G2500/10—Damping action or damper
- B60G2500/11—Damping valves
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G2800/00—Indexing codes relating to the type of movement or to the condition of the vehicle and to the end result to be achieved by the control action
- B60G2800/16—Running
- B60G2800/162—Reducing road induced vibrations
-
- 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
- F16F2228/00—Functional characteristics, e.g. variability, frequency-dependence
- F16F2228/06—Stiffness
- F16F2228/066—Variable stiffness
-
- 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
- F16F2230/00—Purpose; Design features
- F16F2230/0023—Purpose; Design features protective
Definitions
- Hydraulic compression stop member for a hydraulic shock-absorber for a vehicle suspension
- the present invention relates in general to a hydraulic stop member intended to be used in a hydraulic shock-absorber for a vehicle suspension, in particular in a twin-tube hydraulic shock-absorber. More specifically, the present invention relates to a hydraulic stop member arranged to operate during the compression stroke of the shock-absorber.
- a twin-tube hydraulic shock-absorber for a vehicle suspension typically comprises an outer cylindrical tube, an inner cylindrical tube coaxial with the outer cylindrical tube and defining with the latter an annular chamber which is filled with gas in an upper portion thereof, a rod arranged coaxially with the two cylindrical tubes and partially projecting from the latter, and a piston which is slidably mounted in the inner cylindrical tube and is attached to the bottom end of the rod.
- the piston separates the inner volume of the inner cylindrical tube into a rebound chamber and a compression chamber, in which a damping fluid (oil) is contained.
- the piston is provided with a first pair of check valves, namely a compensation valve which controls the flow of the damping fluid from the compression chamber to the rebound chamber during the compression stroke of the shock- absorber and a rebound valve which controls the flow of the damping fluid from the re- bound chamber to the compression chamber during the rebound stroke of the shock- absorber.
- a valve assembly is arranged on the bottom of the shock-absorber and comprises a second pair of check valves, namely a compression valve which controls the flow of the damping fluid from the compression chamber to the annular chamber during the compression stroke and an intake valve which controls the flow of the damping fluid from the an- nular chamber to the compression chamber during the rebound stroke.
- a hydraulic shock-absorber for a vehicle suspension is provided with a first end stop member, which is arranged inside the shock-absorber and is configured to operate during the rebound stroke of the shock-absorber, and a second end stop member, which is arranged outside the shock-absorber and is configured to operate during the compression stroke of the shock-absorber.
- the end stop members may be of elastic or hydraulic type.
- the elastic end stop members are made of high-stiffness elastic material (for example polyurethane) and have the function of ensuring that when shock-absorber reaches the end- of-travel position, either during the rebound stroke or during the compression stroke, there are elastic shocks between the surfaces that come into contact, instead of shocks between metal surfaces.
- the elastic end stop members behave therefore as springs which at the end- of-travel positions act in parallel with the mechanical springs (main spring) of the suspension and have a much higher stiffness than that of the mechanical spring of the suspension.
- the elastic end stop members do not operate in any intermediate point of the stroke of the shock-absorber.
- the elastic end stop members have, among others, the following disadvantage.
- a heavy shock on the stop members either during the rebound stroke or during the compres- sion stroke, caused for example by obstacles (holes or bumps) on the road
- the kinetic energy of the suspension is converted into elastic deformation energy of the stop member in question.
- the elastic energy stored by the stop member is completely (or almost completely) released in the subsequent phase of change of direction of the motion. Accordingly, after the shock the suspension continues to oscillate without its motion being suffi- ciently dampened, and these oscillations adversely affect the adherence of the tyre with the road, and hence result in a worse road-holding of the vehicle.
- hydraulic stop members are energy dissipating devices which allow, when an end-of-travel position is reached, to hydraulically dissipate the kinetic energy of the suspension by forcing a certain amount of oil contained in the shock-absorber to laminarly flow through suitably calibrated passages.
- the energy produced as a result of a shock is hydraulically dissipated and is not returned to the suspension in the subsequent phase of change of direction of the motion.
- the oscillations of the suspension are thus dampened, which increases the adherence of the tyre with the road and therefore improves the road- holding of the vehicle.
- the hydraulic stop members act in parallel with the respective elastic stop members, part of the energy generated by the shock is hydraulically absorbed and it is therefore possible to reduce the size of the elastic stop members and of the relating supports.
- the action of the elastic stop members depends on the deformation to which these members are subject, the action of the hydraulic stop members is proportional to the speed with which the rod of the shock-absorber reaches the end-of-travel position. The hydraulic stop members allow therefore to manage in a much more progressive manner the impacts occurring when the end-of-travel positions of the shock-absorber are reached.
- the hydraulic stop members are almost exclusively used as rebound stop members.
- Documents EP 2 302 252, WO 2014/165951, US 2014/0360353 and WO 2005/106282 disclose examples of hydraulic stop members which act during the rebound stroke of the hydraulic shock-absorber and are therefore intended to be mounted in the rebound chamber of the shock-absorber.
- EP 1 717 478 discloses a hydraulic stop member for a motor-vehicle comprising a cup-shaped body, which is adapted to be fixedly mounted inside the compression chamber of the shock-absorber, and a plunger, which is adapted to be attached to the bottom end of the rod of the shock- absorber (i.e. the end facing the bottom of the shock-absorber).
- the plunger is able to slide along a cylindrical side wall of the cup-shaped body.
- This wall has a number of holes to allow the oil to flow out of the cup-shaped body when the plunger is urged towards the latter, during the compression stroke of the shock-absorber, and hence compress the oil contained in a working chamber of the cup-shaped body.
- the plunger comprises a shaft and a head, the head being slidably mounted between a shoulder formed by the shaft and a nut mounted at the free end of the shaft.
- Conduits are provided along the perimeter of a central hole of the head (hole through which the shaft extends) to allow the oil to flow there- through when the head is in abutment against the nut during the rebound stroke of the shock-absorber.
- Another object of the present invention is to provide a hydraulic stop member acting during the compression stroke of a hydraulic shock-absorber for a vehicle suspension, in particular a twin-tube hydraulic shock-absorber, which can be manufactured easily and inex- pensively.
- the invention is based on the idea of providing a hydraulic stop member of the type specified in the preamble of independent claim 1, wherein a plurality of axial channels (or grooves) are formed on the inner surface of the side wall of the cup- shaped body for allowing the oil to flow axially out of the working chamber of the cup-shaped body when the piston moves towards the bottom wall of the cup-shaped body, said axial channels having a cross-section whose area decreases continuously along the axial direction towards the bottom wall of the cup- shaped body, and wherein the side wall of the cup- shaped body has a plurality of passages (which may be made as radial openings or axial passages) for putting the portion of the compression chamber comprised between the piston of the shock- absorber and the plunger of the hydraulic stop member into communication with the valve assembly (compression valve and intake valve) arranged on the bottom of the shock- absorber.
- a plurality of axial channels are formed on the inner surface of the side wall of the cup- shaped body for allowing the oil
- the area of the flow section through which the oil contained in the working chamber may flow out of the cup-shaped body decreases continuously towards the bottom wall of the cup- shaped body, and therefore the damping effect produced by the stop member on the rod of the shock-absorber increases continuously and progressively as the latter moves towards the compression end-of-travel position.
- the damping effect produced by the stop member on the rod of the shock-absorber increases continuously and progressively as the latter moves towards the compression end-of-travel position.
- the side wall and the bottom wall of the cup-shaped body are made as separate pieces and are securely connected to each other, for example by force- fitting. This makes the manufacturing process of the stop member easier and less expensive.
- the side wall of the cup- shaped body comprises a first wall portion of cylindrical shape, or inlet wall portion, which faces towards the opposite side of the bottom wall of the cup-shaped body, a second wall portion of cylindrical shape, or lower wall portion, which faces towards the bottom wall of the cup-shaped body, and a third, tapered wall portion, or intermediate wall portion, which connects the inlet wall portion with the lower wall portion, wherein the inlet wall portion has an outer diameter substantially equal to the inner diameter of the inner cylindrical tube of the shock-absorber and is arranged to be securely connected to that tube inside the compression chamber of the shock-absorber, wherein the lower wall portion has an outer diameter smaller than the inner diameter of the inner cylindrical tube, and hence smaller than the outer diameter of the inlet wall portion as well, so as to form an annular passage with that tube.
- the axial channels are formed on the inner surface of the lower wall portion.
- Such an embodiment allows to easily mount the cup- shaped body, at the inlet portion thereof, onto the inner cylindrical tube of the shock-absorber and at the same time, by virtue of the openings provided in the intermediate wall portion, it does not jeopardize the operation of the shock- absorber, as the openings ensure that the oil volume comprised between the piston of the shock-absorber and the plunger of the stop member always communicates with the oil volume comprised in the annular passage, which is turn in communication with the valve assembly on the bottom of the shock-absorber.
- the plunger of the hydraulic stop member comprises a cylindrical body which is adapted to be attached to the rod of the shock- absorber and has an outer diameter smaller than the inner diameter of the lower wall portion of the cup- shaped body, a seal ring which is mounted so as to be axially slidable around the cylindrical body and is adapted to seal against the inner surface of the lower wall portion of the cup- shaped body, and a first and second annular abutment member, which are axially restrained onto the cylindrical body and are configured to axially limit, in either direction, the axial sliding movement of the seal ring along the cylindrical body, wherein the seal ring, the first abutment member and the second abutment member are configured such that when the seal ring slides along the inner surface of the lower wall portion of the cup-shaped body during the compression stroke of the shock-absorber the seal ring is in abutment against the first abutment member and there is no oil flow from one side of the seal ring to the other,
- a plurality of passages are provided in the bottom wall of the cup-shaped body for allowing the oil to flow out of the working chamber of the cup-shaped body to limit the maximum pressure of the oil in that chamber.
- the pressure in the working chamber of the cup-shaped body is thus prevented from reaching excessive values which might jeopardize the structural integrity of the stop member.
- a gauged ring gap of the seal ring may perform the function of limiting the maximum pressure in the working chamber of the cup- shaped body.
- the assembly formed by the first and second abutment members is axially restrained onto the cylindrical body of the piston by means of a pair of snap rings which are received in respective circumferential grooves formed in that body. This allows to easily and quickly assemble the plunger, without requiring for example welding operations.
- Figure 1 is an axial section view of a twin-tube hydraulic shock-absorber for a vehicle suspension provided with a hydraulic compression stop member according to an embodiment of the present invention
- Figure 2 is an axial section view, on an enlarged scale, of the bottom portion of the inner cylindrical tube of the shock-absorber of Figure 1;
- FIG 3 is an exploded view of the hydraulic stop member of the shock-absorber of Figure 1;
- Figures 4 and 5 are axial section views of the hydraulic stop member of the shock- absorber of Figure 1, during the compression stroke and during the rebound stroke of the shock-absorber, respectively, with the seal ring of the plunger of the hydraulic stop member sliding along the inner surface of the lower wall portion of the cup-shaped body of the hydraulic stop member;
- Figure 6 is an exploded view of another embodiment of a hydraulic compression stop member for a twin-tube hydraulic shock-absorber for a vehicle suspension.
- Figure 7 is a plan view of the cup- shaped body of the hydraulic stop member of Figure 6.
- axial and axially identify the direction of the longitudinal axis of the shock-absorber, coinciding with the direction of the longitudinal axis of the hydraulic stop member.
- terms such as “upper” and “lower” are to be intended as referring to the arrangement of the shock-absorber shown in Figure 1, where the piston of the shock-absorber is mounted at the bottom end of the rod and therefore the rod and the piston move downwards during the compression stroke of the shock- absorber and upwards during the rebound stroke of the shock-absorber.
- a twin-tube hydraulic shock-absorber for a vehicle suspension is generally indicated 10 and comprises, in per- se -known manner, an outer cylindrical tube 12, an inner cylindrical tube 14 which is arranged coaxially with the outer cylindrical tube 12 and defines with the latter an annular chamber 16 filled with gas in an upper portion thereof, a rod 18 which is arranged coaxially with the two cylindrical tubes 12 and 14 and partially projects from the latter, and a piston 20 which is slidably mounted in the inner cylindrical tube 14 and is attached to the bottom end of the rod 18.
- the piston 20 separates the inner volume of the inner cylindrical tube 14 into an upper chamber 22, or rebound chamber, and a lower chamber 24, or compression chamber, which chambers contain a damping fluid. Oil is typically used as damping fluid, and therefore the damping fluid will be referred to hereinafter, for the sake of simplicity, with the term "oil". It is however clear that the present invention is not limited to the use of oil as damping fluid.
- the piston 20 is provided, in per-se-known manner, with a first valve assembly 26 comprising a pair of check valves, namely a compensation valve, which during the compres- sion stroke of the shock-absorber controls the flow of the oil from the compression chamber 24 to the rebound chamber 22, and a rebound valve, which during the rebound stroke of the shock-absorber controls the flow of the oil from the rebound chamber 22 to the compression chamber 24.
- a compensation valve which during the compres- sion stroke of the shock-absorber controls the flow of the oil from the compression chamber 24 to the rebound chamber 22
- a rebound valve which during the rebound stroke of the shock-absorber controls the flow of the oil from the rebound chamber 22 to the compression chamber 24.
- a second valve assembly 28 is arranged, in per-se-known manner, on the bottom of the shock-absorber 10, namely on the bottom of the inner cylindrical tube 14, and comprises a pair of check valves, namely a compression valve, which during the compression stroke controls the flow of the oil from the compression chamber 24 to the annular chamber 16, and an intake valve, which during the rebound stroke controls the flow of the oil from the annular chamber 16 to the compression chamber 24.
- the longitudinal axis of the shock-absorber 10 is indicated z.
- the shock-absorber 10 is provided with a hydraulic stop member, generally indicated 30, operating during the compression stoke of the shock-absorber to hydraulically dissipate the kinetic energy of the suspension when the shock-absorber is close to the compression end-of-travel position.
- the hydraulic stop member 30 is arranged in the compression chamber 24 of the shock-absorber, in particular on the bottom of the inner cylindrical tube 14.
- the hydraulic stop member 30 basically comprises a cup- shaped body 32, which is attached to the inner cylindrical tube 14 of the shock-absorber and extends coaxially therewith, and a plunger 34, which is connected to the rod 18 of the shock-absorber, preferably releasably (for example by means of a threaded connection), and is arranged to axially slide in the cup- shaped body 32 to compress the oil contained inside it.
- the cup-shaped body 32 is open at its top end, i.e. at its end facing towards the piston 20 of the shock-absorber, and comprises a side wall 36 and a bottom wall 38.
- the side wall 36 and the bottom wall 38 are made as separate pieces and are securely connected to each other, for example by force-fitting and/or suitable retaining means.
- the side wall 36 comprises a first wall portion 36a, or inlet wall portion, which faces towards the opposite side of the bottom wall 38, i.e.
- the inlet wall portion 36a has an outer diameter substantially equal to the inner di- ameter of the inner cylindrical tube 14.
- the inlet wall portion 36a is securely connected to the inner cylindrical tube 14, for example by force-fitting and/or by suitable retaining means.
- the lower wall portion 36b has an outer diameter smaller than the inner diameter of the inner cylindrical tube 14, and hence also smaller than the outer diameter of the inlet wall portion 36a.
- annular passage 40 ( Figure 2), which is in fluid communication with the portion of the compression chamber 24 underneath the bottom wall 38 of the hydraulic stop member.
- the intermediate wall portion 36c has a plurality of radial openings 42 configured to put the portion of the com- pression chamber 24 comprised between the piston 20 of the shock-absorber and the plunger 34 of the hydraulic stop member into communication with the annular passage 40, and hence with the second valve assembly 28 placed on the bottom of the inner cylindrical tube 14 of the shock-absorber, thereby allowing hydraulic supply of the second valve assembly 28 and hence correct operation of the shock-absorber.
- a plurality of axial channels 44 are formed on the inner surface of the side wall 36 of the cup-shaped body 32, in particular on the inner surface of the lower wall portion 36b, and possibly also of the intermediate wall portion 36c, and are configured to allow axial flow of the oil out of the chamber (hereinafter referred to as working chamber 46) enclosed by the lower wall portion 36b and comprised between the plunger 34 and the bottom wall 38, when the plunger 34 moves towards the bottom wall 38.
- the axial channels 44 extend parallel to the axis z (longitudinal axis of the cup- shaped body 32), hence along the direction of the movement of the plunger 34.
- the axial channels 44 have a cross-section whose area decreases continuously towards the bottom wall 38.
- the axial channels 44 have a width (i.e. a size in the circumferential direction) which decreases continuously, for example linearly, towards the bottom wall 38.
- the depth (i.e. the size in the radial direction) of the axial channels 44 also decreases continuously, for example linearly, towards the bottom wall 38.
- the area of the flow section through which the oil is allowed to pass flowing out of the working chamber 46 decreases therefore continuously as the plunger 34 moves in the cup-shaped body 32 towards the bottom wall 38.
- the decrease in the area of the flow section results in a progressive increase in the damping force generated on the plunger 34 of the hydraulic stop member, and hence on the rod 18 of the shock- absorber to which the plunger 34 is attached.
- a plurality of passages 48 are advantageously formed in the bottom wall 38 of the cup- shaped body 32 and are configured to allow the oil to flow out of the cup- shaped body 32 to limit the maximum pressure of the oil in the working chamber 46.
- the pressure in the working chamber 46 of the cup-shaped body 32 is thus pre- vented from reaching excessive values which might jeopardize the structural integrity of the hydraulic stop member 30.
- the plunger 34 of the hydraulic stop member 30 comprises a cylindrical body 50 which extends coaxially with the cup-shaped body 32 and is connected to the rod 18 of the shock- absorber, for example by means of a threaded connection 52, so as to move along the axis z as a single piece with the rod 18.
- the cylindrical body 50 has an outer diameter smaller than the inner diameter of the lower wall portion 36b of the cup-shaped body 32.
- the plunger 34 further comprises a seal ring 54, which is mounted so as to be axially slidable around the cylindrical body 50 and is adapted to seal against the inner surface of the lower wall portion 36b of the cup-shaped body 32.
- the seal ring 54 has, in per-se-known manner, a gap 54a.
- the plunger 34 further comprises a pair of annular abutment elements 56 and 58, namely an upper abutment member 56 which is arranged above the seal ring 54, i.e. on the side of the seal ring facing towards the piston 20 of the shock-absorber, and a lower abutment member 58 which is arranged beneath the seal ring 54, i.e. on the side of the seal ring facing towards the working chamber 46 of the hydraulic stop member.
- the assembly formed by the two abutment elements 56 and 58 is axially restrained onto the cylindrical body 50 by means of a pair of snap rings 60 and 62 received in respective circumferential grooves 64 and 66 formed in the cylindrical body 50.
- the upper abutment member 56 forms an axial abutment surface 56a, axially facing downwards, i.e. towards the lower abutment member 58, against which the seal ring 54 comes into abutment during the compression stroke (Figure 4).
- the lower abutment member 58 comprises an upper portion 68, around which the seal ring 54 is arranged, and a lower portion 70 having an outer diameter larger than that of the upper portion 68.
- the lower portion 70 of the lower abutment member 58 forms a shoulder 58a, axially facing upwards, i.e. towards the upper abutment member 56, on which a plurality of projections 72 are formed, against which the seal ring 54 comes into abutment during the rebound stroke (Figure 5).
- the seal ring 54 can thus move axially between the axial abutment surface 56a of the upper abutment member 56 and the upper face of the projections 72 of the lower abutment member 58.
- the seal ring 54 is in abutment against the axial abutment surface 56a of the upper abutment member 56.
- the area of the flow section formed by the axial channels 44 decreases continuously as the plunger 34 moves towards the bottom wall 38 of the cup-shaped body 32.
- FIG. 6 A variant of embodiment of the invention is illustrated in Figures 6 and 7, where parts and elements identical or corresponding to those of Figures 1 to 5 have been given the same reference signs.
- axial passages 42' are used in place of radial openings in the intermediate wall portion 36c of the cup-shaped body 32, which axial passages are formed on the outer surface of the inlet wall portion 36a and of the intermediate wall portion 36c and extend axially along the whole inlet wall portion 36a and the whole intermediate wall portion 36c (or at least along the largest part of the latter).
- axial passages 42' are used in place of radial openings in the intermediate wall portion 36c of the cup-shaped body 32, which axial passages are formed on the outer surface of the inlet wall portion 36a and of the intermediate wall portion 36c and extend axially along the whole inlet wall portion 36a and the whole intermediate wall portion 36c (or at least along the largest part of the latter).
- a hydraulic stop member according to the present invention allows to produce a damping force on the plunger of the stop member, and hence on the rod of the shock-absorber, which continuously and progressively varies with the compression stroke of the shock-absorber.
- the law of variation of the damping force as a function of the travel may be defined in advance by suitably designing the cross-section of the axial channels on the inner surface of the cup-shaped body.
- the hydraulic stop member can be manufactured in a simple and inexpensive manner, thanks to the structure of the plunger and of the cup- shaped body.
- the bottom wall 38 of the cup-shaped body 32 may have no passages 48 for the oil to flow out of the working chamber 46, in which case the function of limiting the maximum pressure of the oil in the working chamber may be performed by suitably calibrating the thickness of the gap 54a of the seal ring 54 of the plunger 34.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Fluid-Damping Devices (AREA)
- Axle Suspensions And Sidecars For Cycles (AREA)
Abstract
Description
Claims
Priority Applications (5)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
MA42588A MA42588B1 (en) | 2015-03-16 | 2016-03-16 | Hydraulic compression stopper for a hydraulic shock absorber for vehicle suspension |
BR112017019643-3A BR112017019643B1 (en) | 2015-03-16 | 2016-03-16 | HYDRAULIC SHOCK ABSORBER FOR VEHICLE SUSPENSION |
EP16710723.4A EP3295051B1 (en) | 2015-03-16 | 2016-03-16 | Hydraulic compression stop member for a hydraulic shock-absorber for a vehicle suspension |
CN201680016614.6A CN107636344B (en) | 2015-03-16 | 2016-03-16 | Hydraulic damper for vehicle suspension |
US15/557,598 US10371226B2 (en) | 2015-03-16 | 2016-03-16 | Hydraulic shock-absorber for a vehicle suspension |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
IT102015000008777 | 2015-03-16 | ||
ITUB20150072 | 2015-03-16 |
Publications (1)
Publication Number | Publication Date |
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WO2016146660A1 true WO2016146660A1 (en) | 2016-09-22 |
Family
ID=53539838
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/EP2016/055642 WO2016146660A1 (en) | 2015-03-16 | 2016-03-16 | Hydraulic compression stop member for a hydraulic shock-absorber for a vehicle suspension |
Country Status (6)
Country | Link |
---|---|
US (1) | US10371226B2 (en) |
EP (1) | EP3295051B1 (en) |
CN (1) | CN107636344B (en) |
BR (1) | BR112017019643B1 (en) |
MA (1) | MA42588B1 (en) |
WO (1) | WO2016146660A1 (en) |
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DE102020209847A1 (en) | 2020-08-05 | 2022-02-10 | Zf Friedrichshafen Ag | Vibration damper with a hydraulic pressure stop |
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US11892056B2 (en) | 2021-10-08 | 2024-02-06 | DRiV Automotive Inc. | Hydraulic damper having a pressure tube and a ring |
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Also Published As
Publication number | Publication date |
---|---|
EP3295051A1 (en) | 2018-03-21 |
US20180058533A1 (en) | 2018-03-01 |
BR112017019643B1 (en) | 2022-11-22 |
MA42588B1 (en) | 2020-05-29 |
CN107636344B (en) | 2019-11-01 |
BR112017019643A2 (en) | 2018-05-15 |
US10371226B2 (en) | 2019-08-06 |
EP3295051B1 (en) | 2020-01-15 |
CN107636344A (en) | 2018-01-26 |
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