WO2017013766A1 - ピストン - Google Patents
ピストン Download PDFInfo
- Publication number
- WO2017013766A1 WO2017013766A1 PCT/JP2015/070827 JP2015070827W WO2017013766A1 WO 2017013766 A1 WO2017013766 A1 WO 2017013766A1 JP 2015070827 W JP2015070827 W JP 2015070827W WO 2017013766 A1 WO2017013766 A1 WO 2017013766A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- piston
- port
- peripheral surface
- damper
- outer peripheral
- Prior art date
Links
- 230000002093 peripheral effect Effects 0.000 claims abstract description 45
- 230000000149 penetrating effect Effects 0.000 claims 1
- 230000006835 compression Effects 0.000 description 28
- 238000007906 compression Methods 0.000 description 28
- 239000010720 hydraulic oil Substances 0.000 description 12
- 238000013016 damping Methods 0.000 description 6
- 239000012530 fluid Substances 0.000 description 6
- 239000003921 oil Substances 0.000 description 5
- 230000008602 contraction Effects 0.000 description 4
- 238000005452 bending Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 230000002238 attenuated effect Effects 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 238000005192 partition Methods 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
- 238000003466 welding Methods 0.000 description 1
Images
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
- F16F9/3207—Constructional features
- F16F9/3214—Constructional features of pistons
-
- 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
- F16F9/348—Throttling passages in the form of annular discs or other plate-like elements which may or may not have a spring action, operating in opposite directions or singly, e.g. annular discs positioned on top of the valve or piston body
- F16F9/3481—Throttling passages in the form of annular discs or other plate-like elements which may or may not have a spring action, operating in opposite directions or singly, e.g. annular discs positioned on top of the valve or piston body characterised by shape or construction of throttling passages in piston
-
- 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
- F16F9/348—Throttling passages in the form of annular discs or other plate-like elements which may or may not have a spring action, operating in opposite directions or singly, e.g. annular discs positioned on top of the valve or piston body
- F16F9/3482—Throttling passages in the form of annular discs or other plate-like elements which may or may not have a spring action, operating in opposite directions or singly, e.g. annular discs positioned on top of the valve or piston body the annular discs being incorporated within the valve or piston body
-
- 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
- F16F9/50—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
- F16F9/5165—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 by use of spherical valve elements or like free-moving bodies
-
- 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
- F16F9/3207—Constructional features
- F16F9/3228—Constructional features of connections between pistons and piston rods
-
- 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
- F16K15/14—Check valves with flexible valve members
- F16K15/148—Check valves with flexible valve members the closure elements being fixed in their centre
Definitions
- the present invention relates to a piston used for a damper.
- US Pat. No. 6,401,755 B2 discloses a damper piston having a trapezoidal (fan-shaped) cross section of a port.
- the cross-sectional area of the port that is, the flow passage area through which the working fluid passes can be increased, so that the damping force characteristic of the damper can be improved.
- An object of the present invention is to reduce the stress generated in the disk valve while increasing the cross-sectional area of the port.
- FIG. 1 is a cross-sectional view of a damper according to an embodiment of the present invention.
- FIG. 2 is a view of the piston as viewed from the side of the expansion side chamber.
- 3 is a cross-sectional view taken along the line III-III in FIG.
- a reservoir 130 for storing hydraulic oil is formed between the inner tube 1 and the outer tube 2.
- the reservoir 130 is filled with compressed gas to prevent cavitation of the hydraulic oil.
- the end on the pressure side chamber 120 side which is the bottom side of the outer tube 2 is closed by the bottom member 5.
- the bottom member 5 is fixed to the outer tube 2 by welding. Further, the bottom member 5 is provided with a connecting member 6 for attaching the damper 100 to the vehicle.
- a rod guide (not shown) that slidably supports the piston rod 4 at the end of the inner tube 1 on the extension side chamber 110 side, and for preventing hydraulic oil and compressed gas from leaking outside the damper 100. And an oil seal (not shown). Further, a base member 8 that partitions the pressure side chamber 120 and the reservoir 130 is provided at an end portion on the pressure side chamber 120 side that is the bottom side of the inner tube 1.
- the disc valve 9 is a check valve, and opens when the damper 100 is extended by the differential pressure between the pressure side chamber 120 and the reservoir 130 to open the expansion side port 8b. Further, when the damper 100 is contracted, the expansion side port 8b is closed.
- the disk valve 12 is opened by the differential pressure between the expansion side chamber 110 and the pressure side chamber 120 when the damper 100 is contracted to open the pressure side port 3b, and moves from the pressure side chamber 120 to the expansion side chamber 110 through the pressure side port 3b. Resists the flow of hydraulic fluid. Further, when the damper 100 is extended, the compression side port 3b is closed.
- the disk valve 13 is opened by the differential pressure between the expansion side chamber 110 and the compression side chamber 120 when the damper 100 is extended to open the expansion side port 3a, and from the expansion side chamber 110 to the compression side chamber 120 through the expansion side port 3a. Provides resistance to the flow of hydraulic fluid moving to Further, when the damper 100 is contracted, the expansion side port 3a is closed.
- the damper 100 imparts resistance to the flow of the hydraulic oil passing through the expansion side port 3a by the disk valve 13 and generates a differential pressure between the expansion side chamber 110 and the compression side chamber 120, thereby reducing the damping force. appear.
- the operation is performed by passing the compression side port 3 b from the compression side chamber 120 whose volume is reduced by the movement of the piston 3 to the expansion side chamber 110 where the volume is increased. Oil moves. Further, the hydraulic oil corresponding to the volume of the piston rod 4 that has entered the inner tube 1 passes through the pressure side port 8 c and is discharged from the pressure side chamber 120 to the reservoir 130.
- the damper 100 gives resistance to the flow of the hydraulic oil passing through the pressure side port 3b and the pressure side port 8c by the disc valve 12 and the disc valve 10, respectively. A pressure is generated to generate a damping force.
- the damper 100 is supplied with hydraulic oil from the reservoir 130 to the pressure side chamber 120 during the extension operation, and is discharged from the pressure side chamber 120 to the reservoir 130 during the contraction operation. Thereby, the volume change in the inner tube 1 is compensated.
- FIG. 2 is a view of the piston 3 as seen from the extension side chamber side. 3 is a cross-sectional view taken along the line III-III in FIG.
- the piston 3 includes a through-hole 3c through which the piston rod 4 is inserted, an extension-side inner sheet surface 3d formed around the through-hole 3c on the end surface on the extension-side chamber 110 side, and a through-hole 3c on the end surface on the pressure-side chamber 120 side. And a pressure side inner sheet surface 3e (see FIG. 3) formed around the periphery.
- the expansion side port 3a has a circular cross section, and is divided into six circumferentially equal portions of the piston 3 on the outer peripheral side of the piston 3 with respect to the expansion side inner sheet surface 3d and the pressure side inner sheet surface 3e. Provided.
- the compression side port 3b includes an arc-shaped inner peripheral surface 3f, an arc-shaped outer peripheral surface 3g having a longer circumferential length than the inner peripheral surface 3f, and two side surfaces 3h connecting the inner peripheral surface 3f and the outer peripheral surface 3g. Are defined along the circumferential direction of the piston 3.
- the compression-side port 3b is provided at six locations equally divided in the circumferential direction of the piston 3 so as to be alternately arranged with the expansion-side port 3a on the outer peripheral side of the piston 3 with respect to the pitch circle passing through the center of the six expansion-side ports 3a. .
- annular pressure side outer seat surface 3i on which the disc valve 13 is seated is formed between the expansion side port 3a and the pressure side port 3b on the end surface of the piston 3 on the pressure side chamber 120 side.
- cylindrical part 3j which continues from an outer peripheral surface is formed in the outer peripheral side in the end surface by the side of the pressure side 120 of piston 3.
- extension side seat surfaces 3m are formed surrounding the openings of the six compression side ports 3b.
- the portion facing the space inside each stretch side seat surface 3m while sitting on the stretch side seat surface 3m is the pressure receiving surface of the disc valve 12 until the damper 100 is opened during the contraction operation.
- the stretch side sheet surface 3m is provided apart from the stretch side inner sheet surface 3d. Thereby, the annular path 3n which connects each opening part by the side of the expansion side chamber 110 of the six expansion side ports 3a is formed between the expansion side sheet surface 3m and the expansion side inner sheet surface 3d.
- the two convex parts 3p are provided in the outer peripheral surface 3g of the compression side port 3b.
- the convex portion 3p protrudes to the inside of the compression side port 3b and extends in the axial direction to the extension side sheet surface 3m. That is, as shown in FIG. 2, the end portion of the convex portion 3p on the stretch side sheet surface 3m side forms a part of the stretch side sheet surface 3m.
- the two convex portions 3p are provided symmetrically with respect to the center in the circumferential direction on the outer peripheral surface 3g. Further, a notch 3q that forms an orifice channel between the disk valve 12 and the two convex portions 3p on the stretch side seat surface 3m is provided.
- the notch 3q is formed by coining, for example. The notch 3q may not be provided if not required.
- the damper 100 applies a resistance to the flow of the hydraulic oil passing through the extension side port 3a by the disc valve 13 and generates a differential pressure between the extension side chamber 110 and the compression side chamber 120, thereby reducing the damping force. Is generated. Further, at the time of contraction operation, a resistance is given to the flow of the hydraulic oil passing through the pressure side port 3b and the pressure side port 8c by the disc valve 13 and the disc valve 10 respectively, and a differential pressure is generated between the extension side chamber 110 and the pressure side chamber 120 to be attenuated. Generate power.
- the damping force characteristic can be improved by increasing the cross-sectional area of the port, that is, the flow passage area through which the working fluid passes.
- the compression-side port 3b of the piston 3 includes the arc-shaped inner peripheral surface 3f, the arc-shaped outer peripheral surface 3g having a longer circumferential length than the inner peripheral surface 3f, and the inner peripheral surface.
- the cross-sectional area is enlarged by defining along the circumferential direction of the piston 3 with the two side surfaces 3h which connect the surface 3f and the outer peripheral surface 3g.
- the stretch side sheet surface 3m provided surrounding the periphery is also enlarged. Since the pressure of the expansion side chamber 110 acts on the back surface of the disc valve 12 during the extension operation of the damper 100 in which the disc valve 12 closes the compression side port 3b, when the extension side seat surface 3m on which the disc valve 12 is seated expands, the disc valve 12 Increases the stress generated in the disk valve 12.
- the bending of the disc valve 12 can be suppressed as compared with the case where the convex portion 3p is not provided, and the stress generated in the disc valve 12 can be reduced. Moreover, since only the convex part 3p needs to be provided, the cross-sectional area of the compression side port 3b is not greatly reduced. Therefore, the stress generated in the disk valve 12 can be reduced while increasing the cross-sectional area of the compression side port 3b.
- the stress concentration portions in the disk valve 12 can be distributed to the contact portions with the two convex portions 3p, and the maximum stress generated at the contact portions with the respective convex portions can be reduced. .
- the two convex portions 3p are provided symmetrically with respect to the circumferential center of the outer peripheral surface 3g. According to this, the stress which generate
- the notch 3q forming the orifice channel is formed at the center in the circumferential direction of the compression side port 3b in consideration of the stability of the orifice characteristic.
- the convex portion 3p is at the center of the outer peripheral surface 3g or at a position corresponding to the center, the notch 3q and the convex portion 3p overlap each other. In this case, variations in the flow path length and flow path shape of the orifice flow path are likely to occur, and it is difficult to stabilize the orifice characteristics.
- the two convex portions 3p are provided symmetrically with respect to the center in the circumferential direction on the outer peripheral surface 3g, and a notch 3q is provided between the two convex portions 3p on the stretch-side sheet surface 3m. Therefore, the notch 3q and the convex part 3p do not overlap. Therefore, it is possible to prevent variations in the channel length and the channel shape of the orifice channel, and it is possible to stabilize the orifice characteristics.
- the pressure side port 3b is provided with two convex portions 3p, but may be three or more.
- the number of convex portions 3p be an even number and be provided symmetrically with respect to the center of the outer peripheral surface 3g. According to this, as described above, it is possible to prevent the notch 3q and the protrusion 3p from overlapping.
- the annular piston 3 used in the damper 100 penetrates in the axial direction, and includes a plurality of compression side ports 3b formed along the circumferential direction of the piston 3, and each of the compression side ports 3b on the end surface of the piston 3 on the extension side chamber 110 side.
- An expansion side seat surface 3m that is formed surrounding the opening and on which the disk valve 12 that opens and closes the compression side port 3b is seated.
- the compression side port 3b includes an arcuate inner peripheral surface 3f and an inner peripheral surface 3f. Is defined by an arcuate outer circumferential surface 3g having a long circumferential length, and two side surfaces 3h connecting the inner circumferential surface 3f and the outer circumferential surface 3g.
- the outer circumferential surface 3g of the compression side port 3b has a compression side port 3b. And at least two convex portions 3p extending in the axial direction to the extended side sheet surface 3m.
- the number of the convex portions 3p is two, and they are provided symmetrically with respect to the circumferential center of the outer peripheral surface 3g.
- the stress generated in each contact portion of the disc valve 12 with the two convex portions 3p can be made substantially uniform. Therefore, the maximum stress generated at the contact portion of each disc valve 12 with each convex portion 3p can be reduced to the maximum.
- a notch 3q that forms an orifice channel between the two convex portions 3p on the stretch side seat surface 3m and the disk valve 12 is provided.
- the notch 3q and the protrusion 3p do not overlap. Therefore, it is possible to prevent variations in the channel length and the channel shape of the orifice channel, and it is possible to stabilize the orifice characteristics.
- the working oil is used as the working fluid, but other liquids such as water may be used.
- the piston 3 is provided with six expansion-side ports 3a and six compression-side ports 3b, but the number of ports can be arbitrarily set to two or more.
- the damper 100 is a twin tube damper, but may be a monotube damper.
- the convex part 3p is provided in the pressure side port 3b of the piston 3, the structure similar to the pressure side port 3b and the convex part 3p is applied to the expansion side port of a piston, or the port of a base member. Also good.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Fluid-Damping Devices (AREA)
Abstract
Description
Claims (3)
- ダンパに用いられる環状のピストンであって、
軸方向に貫通し、前記ピストンの周方向に沿って形成される複数のポートと、
前記ピストンの一方側の端面に前記ポートそれぞれの開口部を囲んで形成され、前記ポートを開閉するディスクバルブが着座するシート面と、
を有し、
前記ポートは、
円弧状の内周面と、
前記内周面よりも周方向長さが長い円弧状の外周面と、
前記内周面と前記外周面とを繋ぐ2つの側面と、
によって画成され、
前記ポートの前記外周面には、前記ポートの内側に突出するとともに軸方向に前記シート面まで延在する少なくとも2つの凸部が設けられる、
ピストン。 - 請求項1に記載のピストンであって、
前記凸部は2つであって、前記外周面における周方向の中心に対して対称に設けられる、
ピストン。 - 請求項2に記載のピストンであって、
前記シート面における2つの前記凸部の間には、前記ディスクバルブとの間にオリフィス流路を形成する切欠きが設けられる、
ピストン。
Priority Applications (5)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CN201580081048.2A CN107683377A (zh) | 2015-07-22 | 2015-07-22 | 活塞 |
JP2017529232A JP6401862B2 (ja) | 2015-07-22 | 2015-07-22 | ピストン |
PCT/JP2015/070827 WO2017013766A1 (ja) | 2015-07-22 | 2015-07-22 | ピストン |
US15/738,251 US20180163810A1 (en) | 2015-07-22 | 2015-07-22 | Piston |
DE112015006724.8T DE112015006724T5 (de) | 2015-07-22 | 2015-07-22 | Kolben |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PCT/JP2015/070827 WO2017013766A1 (ja) | 2015-07-22 | 2015-07-22 | ピストン |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2017013766A1 true WO2017013766A1 (ja) | 2017-01-26 |
Family
ID=57834190
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2015/070827 WO2017013766A1 (ja) | 2015-07-22 | 2015-07-22 | ピストン |
Country Status (5)
Country | Link |
---|---|
US (1) | US20180163810A1 (ja) |
JP (1) | JP6401862B2 (ja) |
CN (1) | CN107683377A (ja) |
DE (1) | DE112015006724T5 (ja) |
WO (1) | WO2017013766A1 (ja) |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20010035212A1 (en) * | 2000-03-08 | 2001-11-01 | Mannesmann Sachs Ag | Damping valve |
JP2009281488A (ja) * | 2008-05-22 | 2009-12-03 | Kayaba Ind Co Ltd | バルブシート部構造 |
JP2013190045A (ja) * | 2012-03-14 | 2013-09-26 | Kyb Co Ltd | 緩衝器のバルブ構造 |
Family Cites Families (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH0292154U (ja) * | 1989-01-10 | 1990-07-23 | ||
DE10005180C1 (de) * | 2000-02-05 | 2001-08-23 | Mannesmann Sachs Ag | Dämpfventil, insbesondere für einen Schwingungsdämpfer |
JP4868166B2 (ja) * | 2007-11-30 | 2012-02-01 | 日立オートモティブシステムズ株式会社 | 流体圧緩衝器 |
JP2009209960A (ja) * | 2008-02-29 | 2009-09-17 | Hitachi Ltd | 緩衝器 |
KR20110001283A (ko) * | 2009-06-30 | 2011-01-06 | 주식회사 만도 | 쇽업소버의 피스톤 밸브 조립체 |
-
2015
- 2015-07-22 JP JP2017529232A patent/JP6401862B2/ja active Active
- 2015-07-22 CN CN201580081048.2A patent/CN107683377A/zh active Pending
- 2015-07-22 DE DE112015006724.8T patent/DE112015006724T5/de not_active Withdrawn
- 2015-07-22 WO PCT/JP2015/070827 patent/WO2017013766A1/ja active Application Filing
- 2015-07-22 US US15/738,251 patent/US20180163810A1/en not_active Abandoned
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20010035212A1 (en) * | 2000-03-08 | 2001-11-01 | Mannesmann Sachs Ag | Damping valve |
JP2009281488A (ja) * | 2008-05-22 | 2009-12-03 | Kayaba Ind Co Ltd | バルブシート部構造 |
JP2013190045A (ja) * | 2012-03-14 | 2013-09-26 | Kyb Co Ltd | 緩衝器のバルブ構造 |
Also Published As
Publication number | Publication date |
---|---|
CN107683377A (zh) | 2018-02-09 |
JPWO2017013766A1 (ja) | 2018-04-12 |
DE112015006724T5 (de) | 2018-04-12 |
JP6401862B2 (ja) | 2018-10-10 |
US20180163810A1 (en) | 2018-06-14 |
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