WO2022106088A1 - HYDRAULISCHER STOßDÄMPFER - Google Patents
HYDRAULISCHER STOßDÄMPFER Download PDFInfo
- Publication number
- WO2022106088A1 WO2022106088A1 PCT/EP2021/074581 EP2021074581W WO2022106088A1 WO 2022106088 A1 WO2022106088 A1 WO 2022106088A1 EP 2021074581 W EP2021074581 W EP 2021074581W WO 2022106088 A1 WO2022106088 A1 WO 2022106088A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- shock absorber
- bypass
- piston
- piston slide
- valve
- Prior art date
Links
- 239000006096 absorbing agent Substances 0.000 title claims abstract description 66
- 230000035939 shock Effects 0.000 title claims abstract description 66
- 238000013016 damping Methods 0.000 claims abstract description 35
- 238000006073 displacement reaction Methods 0.000 claims abstract description 29
- 230000006835 compression Effects 0.000 claims abstract description 23
- 238000007906 compression Methods 0.000 claims abstract description 23
- 230000000694 effects Effects 0.000 claims abstract description 20
- 230000000903 blocking effect Effects 0.000 claims abstract description 19
- 239000012530 fluid Substances 0.000 claims abstract description 11
- 238000000034 method Methods 0.000 abstract description 2
- 230000008569 process Effects 0.000 abstract description 2
- 239000007788 liquid Substances 0.000 description 4
- 230000009467 reduction Effects 0.000 description 4
- 230000008901 benefit Effects 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 239000000725 suspension Substances 0.000 description 2
- 230000007704 transition Effects 0.000 description 2
- 230000009471 action Effects 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 230000036316 preload Effects 0.000 description 1
- 230000000717 retained effect Effects 0.000 description 1
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
- F16F9/50—Special means providing automatic damping adjustment, i.e. self-adjustment of damping by particular sliding movements of a valve element, other than flexions or displacement of valve discs; Special means providing self-adjustment of spring characteristics
- F16F9/512—Means responsive to load action, i.e. static load on the damper or dynamic fluid pressure changes in the damper, e.g. due to changes in velocity
- F16F9/5126—Piston, or piston-like valve elements
-
- 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
- F16F9/461—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 characterised by actuation means
-
- 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
- F16F9/466—Throttling control, i.e. regulation of flow passage geometry
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/50—Special means providing automatic damping adjustment, i.e. self-adjustment of damping by particular sliding movements of a valve element, other than flexions or displacement of valve discs; Special means providing self-adjustment of spring characteristics
- F16F9/516—Special means providing automatic damping adjustment, i.e. self-adjustment of damping by particular sliding movements of a valve element, other than flexions or displacement of valve discs; Special means providing self-adjustment of spring characteristics resulting in the damping effects during contraction being different from the damping effects during extension, i.e. responsive to the direction of movement
-
- 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
- F16F2230/18—Control arrangements
- F16F2230/183—Control arrangements fluid actuated
-
- 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
- F16F2230/24—Detecting or preventing malfunction, e.g. fail safe
-
- 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
Definitions
- the invention relates to a hydraulic shock absorber, the damping effect of which can be changed by the pressure of a control pressure medium, with a shock absorber tube containing a damping fluid, into which a hollow piston rod oscillates corresponding to successive compression stages and rebound stages of the shock absorber and which is connected to a working piston at its free end which divides the interior of the shock absorber tube into two working chambers and contains at least two throttle passages that are permeable alternatively and in opposite directions by respectively assigned check valves, with a bypass additionally connecting the two working chambers of the shock absorber tube running through the working piston, in the course of which one of the shut-off and the Release of this bypass serving, actuated by the pressure of the control pressure medium piston slide valve is arranged, which the control pressure medium via the cavity of the piston rod z is guided, and wherein the piston slide valve contains a piston slide which can be displaced by the control pressure medium against the force of a restoring spring and which blocks or releases the bypass.
- shock absorbers are used, for example, on motor vehicles or motor vehicle trailers, which are used not only in normal traffic, but also in difficult terrain with an uneven road surface and/or with very different loads, for example as ambulances, fire engines or rescue vehicles, as construction vehicles or in the military field.
- the control pressure medium required for reversing the shock absorbers is either taken from the air suspension system of such vehicles or - if such an air suspension system is not available - provided separately with suitable pressure generators depending on the driving behavior of the vehicle.
- a shock absorber of the type mentioned is known, for example, from EP 1 231 404 B1.
- shock absorber One advantage of such a shock absorber is that the damping effect can be changed by using the control pressure medium to either switch on or shut off the bypass in the working piston located between the two working chambers of the shock absorber tube.
- the shut-off position and the release position are located directly next to one another in this shock absorber, so that intermediate positions are also possible in which the bypass is only partially shut off, so that the two switching states can no longer be clearly separated from one another.
- the throttle passage for the rebound stage which is located in the working piston, generally has a narrower cross section than the throttle passage for the compression stage, which is also located in the working piston. This increased rebound damping is necessary for safety reasons in difficult operating conditions, so that the spring does not return to the expanded state too quickly after it has been compressed.
- the object of the invention to further develop the shock absorber of the type mentioned at the outset in such a way that it can be easily adjusted to a lower damping effect of the rebound stage, i.e. to a release position for comfort mode, by means of targeted pressurization with the control pressure medium and without changing the damping effect of the compression stage. can be switched.
- the shock absorber according to the invention should enable two blocking positions that are clearly separate from the release position, specifically one Blocking position for heavy-duty operation under difficult operating conditions and a blocking position if the control pressure medium fails (faulty operation).
- the invention based on a shock absorber of the type mentioned at the outset, proposes that the piston slide of the piston slide valve at the beginning and at the end of its displacement path has blocking positions that shut off the bypass for error operation on the one hand and heavy-duty operation on the other hand and in the longitudinal region of its displacement path with at least one Bypass releasing release position is provided, wherein the bypass is also assigned a check valve, which prevents the passage of damping fluid through the bypass during the compression stage of the shock absorber and allows during the rebound stage of the shock absorber.
- the shock absorber according to the invention has the advantage that it is possible in a particularly reliable manner to ensure a targeted reduction in the damping effect of the rebound stage during comfort mode by subjecting the piston slide valve to pressurization in a controlled manner using a control pressure medium, without at the same time changing the high damping effect of the compression stage that is fundamentally required and at the same time without jeopardizing operational safety in the event of heavy-duty operation or failure of the control pressure medium.
- the bypass in the working piston is only open during the rebound stage and closed during the compression stage by the check valve located in the bypass.
- the piston slide of the piston slide valve is pushed to the end of its displacement path by an appropriately controlled pressurization with the control pressure medium and then blocks the bypass of the working piston in both flow directions, so that the full damping effect is achieved both in the compression stage and in the rebound stage .
- the check valve located in the bypass of the working piston is closed during the compression stage, so that the bypass is doubly blocked against the flow of damping fluid in the compression stage.
- the pressurization of the piston slide fails completely, so that under the action of its return spring it returns to the start of its displacement path into the blocking position located there and blocks the bypass in the working piston in both flow directions.
- the check valve in the bypass of the working piston is closed during the compression stage, so that the bypass is doubly blocked during the compression stage.
- an expedient development of the invention provides that the piston slide of the piston slide valve has two or more release positions with different passage cross sections at a distance from one another in the length region of its displacement path. Because the two blocking positions for heavy-duty operation and faulty operation are spaced apart at the beginning and end of the displacement path of the piston valve, there is enough space for arranging several release positions along the length of the displacement path.
- the invention also provides that the piston slide valve has one or more additional return springs which are shorter than its return spring and which only then act on the piston slide when it has reached a release position. This ensures that the restoring forces acting on the piston slide of the piston slide valve do not increase continuously over the displacement path, but always increase suddenly when a release position is reached. As a result, the accuracy of the control of the individual release positions can be increased significantly.
- the last-mentioned additional return springs are expediently arranged in spring chambers of the piston slide and act under preload on displaceable support fingers, which protrude in the direction of displacement of the piston slide and are supported on the housing of the piston slide valve as soon as its piston slide reaches the assigned release position.
- This arrangement and design of the additional return springs makes it possible to easily replace them and adapt them to needs to be able to, which is important for the series production of such shock absorbers that have to be easily adapted to different operating conditions.
- the invention also provides that the return spring of the piston slide and/or the additional return springs of the support fingers are prestressed in the extension direction.
- the passage cross-section of the bypass not only be graded as a function of the displacement path of the piston slide in the piston slide valve, but also be able to be changed continuously.
- the invention provides, as an alternative to the proposals discussed last, that the release position extends over a portion of the displacement path of the piston slide and that the piston slide simultaneously actuates a needle valve located in the bypass, the passage cross section of which continuously extends over this portion of the displacement path until the blocked position is reached gets smaller. This makes it possible for the first time to steplessly reduce the cross section of the bypass until the transition to the blocked position.
- Figure 1 schematically shows a longitudinal section through the shock absorber tube
- FIG. 2 the shock absorber tube according to FIG. 1 during the compression stage in comfort mode
- FIG. 3 the shock absorber tube according to Figure 1 during the rebound at
- Figure 4 the shock absorber tube according to Figure 1 during rebound at
- FIG. 5 an external view of the working piston and the piston slide valve connected thereto;
- FIG. 6 an exploded representation of FIG. 5;
- FIG. 7a/7b in the same representation as FIG. 1, a modified embodiment of a shock absorber according to the invention, in which the piston slide of the piston slide valve has two release positions with different passage cross sections;
- FIG 8 the shock absorber according to Figures 7a and 7b in the
- FIG. 9 the shock absorber according to Figures 7a and 7b in the
- FIG 10 the shock absorber according to Figures 7a and 7b in the
- FIG. 11 an external view of the working piston shown in FIGS. 7a and 7b and the piston slide valve connected thereto;
- FIG. 12 an exploded representation of FIG. 11;
- FIG. 13 schematic longitudinal section—in a representation similar to FIG.
- Fig. 1 - a modified embodiment of the devices controlling passage through the bypass
- FIG. 14 an external view of that resulting from FIG
- a partial section of a shock absorber tube filled with a damping fluid is denoted by the reference numeral 1.
- a hollow piston rod 2 oscillates into this shock absorber tube 1 and is connected, for example, to the unsprung mass of a vehicle (not shown in the drawing), which in turn is connected to the shock absorber tube 1 .
- the cavity 2a of the hollow piston rod 2 is used to supply a gaseous or liquid control pressure medium (S), which is used for pressure-controlled switching of the shock absorber into its various operating states, as will be explained in detail below.
- the control pressure medium (S) used for switching comes either from the hydraulically or pneumatically supported spring system of the vehicle itself, but can also be generated from other control pressure sources.
- the free end of the piston rod 2 which oscillates into the shock absorber tube 1 , is screwed to a multi-part fastening device 3 which carries a working piston 4 .
- This working piston 4 is guided in a sealed manner at its periphery in the shock absorber tube 1 and divides the interior of the shock absorber tube 1 into two working chambers, namely a working chamber 1a below the working piston 4 and a working chamber 1b above the working piston 4.
- the working piston 4 is provided with throttle passages 5a and 5b which connect the working chambers 1a and 1b to one another.
- These throttle passages 5a and 5b are assigned non-return valves 6a and 6b which are permeable in the opposite direction and which have the effect that the throttle passage 5a is permeable only in the direction of the working chamber 1a located below the working piston 4 and the throttle passage 5b is only permeable in the direction of the working chamber 1a located above the working piston 4 located working space 1b is permeable.
- the cross sections of the two throttle passages 5a and 5b are different, so that the damping fluid passing through different flow resistances in the rebound stage Z (movement of the working piston 4 upwards) and the compression stage D (movement of the working piston 4 downwards).
- a bypass that additionally connects the two working chambers 1a and 1b of the shock absorber tube 1 runs through the fastening device 3 of the working piston 4, in the course of which a piston slide valve 7, which serves to shut off or release and is actuated by the pressure of the control pressure medium (S), is arranged, to which the Actuation serving gaseous or liquid control pressure medium (S) via the cavity 2a of the piston rod 2 is supplied.
- This piston slide valve 7 has a cylindrical valve housing 7a, in which a piston slide 7b can be displaced in a sealed manner, which is acted upon in one direction by the pressure of the control pressure medium (S) and in the opposite direction by the force of a restoring spring 8 supported on the underside of the valve housing 7a , which presses the piston valve 7b against the upper side of the valve housing 7a in the absence of pressurization.
- S control pressure medium
- a restoring spring 8 supported on the underside of the valve housing 7a , which presses the piston valve 7b against the upper side of the valve housing 7a in the absence of pressurization.
- the above-mentioned bypass which bridges the working piston 4, runs via a passage 9 in the holding device 3 of the working piston 4, the interior of the valve housing 7a of the piston slide valve 7 and a passage opening 10 in the cylindrical wall of the piston slide 7b of this piston slide valve 7.
- this passage opening 10 there is a passage opening 11, which opens into the working chamber 1b of the shock absorber tube 1, in the cylindrical wall of the valve housing 7a of the piston slide valve 7.
- a check valve 12 is arranged in the bypass, which is aligned in such a way that the bypass only opens in the direction of the lower working chamber 1b of the shock absorber tube 1 can be passed.
- this check valve 12 is located at the lower end of the passage opening 9, but it can also be arranged elsewhere in the bypass. This check valve 12 ensures that the bypass can basically only be activated during the rebound stage Z of the shock absorber.
- the piston slide valve 7 only releases the bypass if the piston slide 7b is moved relative to the valve housing 7a into a position in which the two corresponding passage openings 10 and 11 are opposite one another (release position).
- release position the bypass is open and ensures a reduction in the damping effect during the rebound stage Z shown in FIG.
- the working piston 4 moves upward relative to the shock absorber tube 1, which is indicated by the arrow Z.
- the damping fluid in the rebound stage Z shown passes both through the throttle passage 5a and, parallel thereto, through the bypass in the direction of the working chamber 1a.
- the corresponding passage openings 10 and 11 in the cylindrical wall of the piston slide 7b and the cylindrical wall of the valve housing 7a are arranged in the longitudinal area of the displacement path of the piston slide 7b such that when the piston slide 7b is displaced in the direction of the underside of the valve housing 7a result in blocking positions both before the release position is reached and after the release position has been exceeded, i.e. positions in which the passage openings in FIGS. 10 and 11 do not overlap.
- there are two blocking positions in which the bypass is interrupted namely a first blocking position (cf. Figure 3) when the control pressure medium (S) has a high pressure (heavy-duty operation), or a second blocking position (cf. Figure 4) when there is no control pressure at all due to a fault in the control system (faulty operation).
- spring chambers 13 are arranged in the side of the piston slide 7b facing the underside of the valve housing 7a, in which additional return springs 14 are arranged, which are shorter than the return spring 8 and run parallel to the return spring 8 and biased to act on slidable support fingers 15 projecting towards the underside of the valve body 7a.
- These support fingers 15 are based on this underside of the valve housing 7a as soon as the piston slide 7b moved by the control pressure medium (S) reaches the release position.
- FIGS. 7-12 largely correspond to the exemplary embodiment in FIGS. 1-6, so that the same reference numbers could be used for the parts that correspond to one another.
- additional return springs 14 and support fingers 15 are also provided in the embodiment of Figures 7-12, the length of which is adapted to the positions of the additional release positions 8 of the piston slide 7b - biased in the extension direction in order to achieve the lowest possible hysteresis for all switching processes.
- only one release position is provided between the two blocking positions at the beginning and at the end of the displacement path of the piston slide 7b, which here, however, extends over a partial area of the displacement path of the piston slide 7b.
- a passage opening 11c which is elongated in the direction of displacement and extends over the above-mentioned partial area of the displacement path.
- a needle valve 16 actuated by the piston slide 7b is arranged in the bypass, the passage cross section of which becomes continuously smaller until the heavy-duty blocking position is reached.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Fluid-Damping Devices (AREA)
- Glass Compositions (AREA)
- Lubricants (AREA)
Abstract
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
AU2021382222A AU2021382222A1 (en) | 2020-11-23 | 2021-09-07 | Hydraulic shock absorber |
US18/038,110 US20240003401A1 (en) | 2020-11-23 | 2021-09-07 | Hydraulic shock absorber |
EP21777645.9A EP4248105A1 (de) | 2020-11-23 | 2021-09-07 | HYDRAULISCHER STOßDÄMPFER |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102020130940.6 | 2020-11-23 | ||
DE102020130940.6A DE102020130940A1 (de) | 2020-11-23 | 2020-11-23 | Hydraulischer Stoßdämpfer |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2022106088A1 true WO2022106088A1 (de) | 2022-05-27 |
Family
ID=77914285
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/EP2021/074581 WO2022106088A1 (de) | 2020-11-23 | 2021-09-07 | HYDRAULISCHER STOßDÄMPFER |
Country Status (5)
Country | Link |
---|---|
US (1) | US20240003401A1 (de) |
EP (1) | EP4248105A1 (de) |
AU (1) | AU2021382222A1 (de) |
DE (1) | DE102020130940A1 (de) |
WO (1) | WO2022106088A1 (de) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN115848547A (zh) * | 2023-02-22 | 2023-03-28 | 无锡天禧机械设备制造有限公司 | 基于电动车缓冲用前叉减震机构 |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR3141978A1 (fr) * | 2022-11-10 | 2024-05-17 | Psa Automobiles Sa | Amortisseur hydraulique de suspension de véhicule automobile. |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1231404A2 (de) * | 2001-02-12 | 2002-08-14 | Delphi Technologies, Inc. | Kolben- und Kolbenstangeneinheit für pneumatisch betätigte, einstellbare Dämpfung |
US20130140117A1 (en) * | 2011-05-31 | 2013-06-06 | Chun Sung YU | Valve structure of shock absorber |
US20150354660A1 (en) * | 2013-01-25 | 2015-12-10 | (Kayaba Industry Co., Ltd.) | Shock absorber |
-
2020
- 2020-11-23 DE DE102020130940.6A patent/DE102020130940A1/de active Pending
-
2021
- 2021-09-07 WO PCT/EP2021/074581 patent/WO2022106088A1/de active Application Filing
- 2021-09-07 EP EP21777645.9A patent/EP4248105A1/de active Pending
- 2021-09-07 US US18/038,110 patent/US20240003401A1/en active Pending
- 2021-09-07 AU AU2021382222A patent/AU2021382222A1/en active Pending
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1231404A2 (de) * | 2001-02-12 | 2002-08-14 | Delphi Technologies, Inc. | Kolben- und Kolbenstangeneinheit für pneumatisch betätigte, einstellbare Dämpfung |
EP1231404B1 (de) | 2001-02-12 | 2006-05-10 | Delphi Technologies, Inc. | Kolben- und Kolbenstangeneinheit für pneumatisch betätigte, einstellbare Dämpfung |
US20130140117A1 (en) * | 2011-05-31 | 2013-06-06 | Chun Sung YU | Valve structure of shock absorber |
US20150354660A1 (en) * | 2013-01-25 | 2015-12-10 | (Kayaba Industry Co., Ltd.) | Shock absorber |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN115848547A (zh) * | 2023-02-22 | 2023-03-28 | 无锡天禧机械设备制造有限公司 | 基于电动车缓冲用前叉减震机构 |
CN115848547B (zh) * | 2023-02-22 | 2023-04-25 | 无锡天禧机械设备制造有限公司 | 基于电动车缓冲用前叉减震机构 |
Also Published As
Publication number | Publication date |
---|---|
US20240003401A1 (en) | 2024-01-04 |
DE102020130940A1 (de) | 2022-05-25 |
AU2021382222A1 (en) | 2023-07-06 |
EP4248105A1 (de) | 2023-09-27 |
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