WO2022264190A1 - ロータリーダンパ及びその製造方法 - Google Patents
ロータリーダンパ及びその製造方法 Download PDFInfo
- Publication number
- WO2022264190A1 WO2022264190A1 PCT/JP2021/022436 JP2021022436W WO2022264190A1 WO 2022264190 A1 WO2022264190 A1 WO 2022264190A1 JP 2021022436 W JP2021022436 W JP 2021022436W WO 2022264190 A1 WO2022264190 A1 WO 2022264190A1
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- WO
- WIPO (PCT)
- Prior art keywords
- partition
- cylinder
- oil
- rotor
- partition wall
- Prior art date
Links
- 238000004519 manufacturing process Methods 0.000 title claims description 9
- 238000005192 partition Methods 0.000 claims abstract description 79
- 238000005266 casting Methods 0.000 claims abstract description 20
- 238000000034 method Methods 0.000 claims description 6
- 230000002093 peripheral effect Effects 0.000 description 9
- 230000000052 comparative effect Effects 0.000 description 6
- 230000007423 decrease Effects 0.000 description 6
- 239000002184 metal Substances 0.000 description 4
- 238000000465 moulding Methods 0.000 description 3
- 238000007711 solidification Methods 0.000 description 3
- 230000008023 solidification Effects 0.000 description 3
- 230000015572 biosynthetic process Effects 0.000 description 2
- 230000008602 contraction Effects 0.000 description 2
- 238000002788 crimping Methods 0.000 description 1
- 238000013016 damping Methods 0.000 description 1
- 230000000593 degrading effect Effects 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 238000002474 experimental method Methods 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 238000002347 injection Methods 0.000 description 1
- 239000007924 injection Substances 0.000 description 1
Images
Classifications
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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
- F16F9/10—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
-
- 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
- F16F9/145—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect involving only rotary movement of the effective parts
Definitions
- the present invention relates to a rotary damper and its manufacturing method.
- a rotary damper comprising a cylinder having a partition wall and a rotor having a shaft facing the partition wall, wherein the cylinder is a casting.
- the shaft portion is designed to have a straight shape, that is, a shape in which the outer diameter is the same along the length of the shaft portion. It is designed in such a shape that the inside diameter is the same over the length of the tube.
- the cylinder is a casting, there is a problem that a dent is formed on the tip end surface of the partition wall due to external shrinkage. Since this dent enlarges the gap formed between the partition wall and the shaft portion, it has been a factor of degrading the characteristics of the rotary damper.
- a method of manufacturing a rotary damper that includes a step of casting a cylinder having a partition using a mold.
- the portion of the upper mold of the mold for molding the tip of the partition wall has a straight shape, that is, a shape in which the outer diameter is the same over the length direction of the portion.
- shrinkage occurs due to shrinkage at the time of solidification, and a recess is formed on the tip surface of the partition wall.
- a rotary damper that includes a valve that varies the flow of oil through it in a direction dependent on load.
- This rotary damper has the characteristic that the operating time, ie the time required for the rotor or cylinder to rotate through a constant rotation angle, hardly changes with changes in load.
- the cylinder is a casting and the partition wall has a dent on its tip surface due to external shrinkage, a sufficient amount of oil for the valve to function cannot be supplied to the valve. There was a problem that the characteristics deteriorated.
- WO 2012/141242 discloses a cylinder having a partition, a rotor having a shaft facing the partition, vanes projecting from the shaft, oil passages formed in the vanes, and provided in the oil passage. discloses a rotary damper with a non-return valve. This rotary damper has a characteristic that a braking force is generated only when the rotor is rotated in one direction. However, if the cylinder is a casting and the partition has a dent on its tip surface due to external shrinkage, oil will form between the partition and the shaft when the rotor is rotated in one direction. There is a problem that the braking force is reduced because more fluid flows out than expected from the gap.
- An object of the present invention is to prevent the gap formed between the partition and the shaft from expanding.
- a rotary damper comprising a cylinder having a partition, and a rotor having a shaft facing the partition, wherein the cylinder is a casting, and the tip of the partition and the shaft are tapered.
- a cylinder having a partition comprising a rotor having a shaft facing the partition; vanes projecting from the shaft; a first oil passage formed in the partition or the vane;
- a rotary damper comprising a valve for changing the flow rate of passing oil in accordance with a load, wherein the cylinder is a casting, and the tip of the partition and the shaft are tapered.
- the cylinder is a casting, and the tip of the partition and the shaft are tapered.
- the cylinder is a casting.
- the tip of the partition wall is tapered, it is possible to prevent the formation of a recess due to external shrinkage on the tip surface of the partition wall.
- the shaft portion facing the partition wall is also tapered, it is possible to prevent the gap formed between the partition wall and the shaft portion from expanding. be.
- the second aspect of the present invention as described above, it is possible to prevent the gap formed between the partition wall and the shaft from expanding. It is possible to supply a large amount of oil. Therefore, according to the present invention described in 2 above, it is possible to reduce the width of change in operating time caused by changes in load.
- the third aspect of the present invention it is possible to prevent the gap formed between the partition wall and the shaft from expanding. It is possible to prevent a decrease in power.
- the rotor when the rotor is rotated in the reverse direction, it becomes difficult for oil to pass through the gap formed between the partition wall and the shaft portion.
- the oil when the rotor rotates in the opposite direction, the oil can pass through two oil passages, that is, the first oil passage and the second oil passage. It is possible to reduce the resistance of the oil to be applied.
- the upper mold used in the step of casting a cylinder having a partition has a tapered portion for forming the tip of the partition into a tapered shape, and a tapered portion on the surface of the tapered portion.
- FIG. 1 is a plan view of a rotary damper according to an embodiment.
- FIG. 2 is a sectional view taken along the line AA of FIG.
- FIG. 3 is a cross-sectional view taken along line BB of FIG.
- FIG. 4 is a cross-sectional view taken along line CC of FIG.
- FIG. 5 is a plan view of the cylinder employed in the example.
- FIG. 6 is a perspective view of the rotor employed in the example.
- FIG. 7 is a front view of the rotor employed in the example.
- FIG. 8 is a perspective view of the valve body of the valve employed in the embodiment.
- FIG. 9 is a sectional view showing the initial state of the valve employed in the example.
- FIG. 10 is a cross-sectional view for explaining the operation of the valve employed in the example.
- FIG. 11 is a cross-sectional view for explaining the operation of the valve employed in the example.
- FIG. 12 is a cross-sectional view for explaining the operation of the valve employed in the example.
- FIG. 13 is a cross-sectional view of a check valve employed in the example.
- FIG. 14 is a perspective view of the valve body of the check valve employed in the embodiment.
- FIG. 15 is a cross-sectional view for explaining the operation of the check valve employed in the embodiment.
- FIG. 16 is a schematic partial cross-sectional view of an upper mold used in the manufacturing method according to the present invention.
- FIG. 17 is a schematic partial cross-sectional view of an upper mold used in the prior art.
- FIG. 18 is a graph showing the relationship between operating time and load.
- the rotary damper includes a cylinder 10 and a rotor 20.
- the cylinder 10 is a tubular component that contains oil therein.
- the rotor 20 is a rotating component. However, the rotor 20 may not rotate.
- the damping action for rotation in the direction, ie counterclockwise in FIGS. 1 and 4 is the same.
- the cylinder 10 adopted in the embodiment is a casting.
- the cylinder 10 has a peripheral wall 11, an end wall 12 closing one end of the peripheral wall 11, and a partition wall 13 protruding from the peripheral wall 11 toward the center. ing.
- the cylinder 10 has a flange 14 projecting from the peripheral wall 11.
- Flange 14 is connected to something that secures cylinder 10 against rotation or that allows cylinder 10 to rotate.
- the other end of the peripheral wall 11 is closed with a lid 30 as shown in FIGS. Lid 30 is attached to cylinder 10 by crimping the end of peripheral wall 11 .
- FIGS. 1 the cylinder 10 has a peripheral wall 11, an end wall 12 closing one end of the peripheral wall 11, and a partition wall 13 protruding from the peripheral wall 11 toward the center. ing.
- the cylinder 10 has a flange 14 projecting from the peripheral wall 11.
- Flange 14 is connected to something that secures cylinder 10 against rotation or that allows cylinder 10 to rotate.
- cylinder 10 has a projection 15 projecting from end wall 12 .
- the tip of the partition 13 is tapered. In other words, the distance between the two partition walls 13, 13 decreases toward one end such that the inner diameter D1 at one end is smaller than the inner diameter D2 at the other end.
- the rotor 20 adopted in the embodiment is a casting. However, the rotor 20 does not have to be a casting. As shown in FIGS. 2 , 3 , 4 , 6 and 7 , the rotor 20 has a shaft portion 21 facing the partition wall 13 . As shown in FIG. 7, the shaft portion 21 has a tapered shape. That is, the outer diameter of the shaft portion 21 decreases toward one end such that the outer diameter D3 at one end is smaller than the outer diameter D4 at the other end. The taper angle of the shaft portion 21 is the same as the taper angle of the tip of the partition wall 13 .
- the rotor 20 is installed so that the shaft portion 21 can rotate within the cylinder 10.
- one end of the rotor 20 is formed with a concave portion 22 that fits into the convex portion 15 formed on the cylinder 10 .
- the other end of the rotor 20 is provided with a hole into which an object for rotating the rotor 20 or an object for fixing the rotor 20 so as not to rotate is inserted. 23 are formed.
- the rotor 20 has vanes 24 protruding from the shaft portion 21 .
- the vane 24 includes a valve body 71 and a holding portion 25 that holds the valve body 71 .
- a groove 26 is formed at the tip of the holding portion 25 integrally formed with the shaft portion 21 .
- the cylinder 10 has four oil chambers partitioned by the partition wall 13 and the vane 24, that is, a first oil chamber 41, a second oil chamber 42, a third oil chamber 43 and a third oil chamber. 4 oil chambers 44 are formed. Oil is injected into each of the oil chambers 41-44.
- the partition wall 13 has a first oil passage 51 formed therein.
- the first oil passage may be formed in the vane.
- a valve 60 is provided in the first oil passage 51 .
- the valve 60 has a valve body 61 and a valve seat 62 .
- the valve body 61 is a leaf spring.
- the valve seat 62 consists of two slopes 62a and 62b formed on the partition wall 13. As shown in FIG. This valve 60 increases the distortion of the valve body 61 by making the inclination angle of one slope 62a different from the inclination angle of the other slope 62b.
- This valve 60 has the function of changing the flow rate of oil passing through the first oil passage 51 in one direction according to the load.
- Oil that passes through the first oil passage 51 in one direction means oil that moves from the first oil chamber 41 to the fourth oil chamber 44 via the first oil passage 51, and oil that flows through the first oil passage 51. It means the oil that moves from the third oil chamber 43 to the second oil chamber 42 as a result.
- Oil flow rate means the amount of oil that passes through the first oil passage 51 within a unit time.
- Load is the force that causes the rotor 20 to rotate in one direction, i.e., clockwise in Figures 1 and 4, or the cylinder 10 to rotate in the opposite direction, i.e., counterclockwise in Figures 1 and 4. means power.
- varying is meant that the oil flow rate decreases with increasing load.
- valve 60 The oil pressure acting on the valve body 61 increases as the load increases. However, the restoring force of the valve body 61 acts as resistance to the oil pressure. Therefore, according to this valve 60, when the load is large, the valve body 61 does not close the first oil passage 51 as shown in FIG. reduce the degree. On the other hand, when the load is small, as shown in FIG. 11, the amount of deformation of the valve body 61 decreases, so the opening of the valve 60 increases. As a result, this valve 60 has a shorter operating time, i.e., the rotor 20 rotates a constant angle of rotation in one direction or the cylinder 10 rotates a constant angle of rotation in the opposite direction, even if the load changes. It is possible to make the time required for the process substantially constant.
- Oil moves from the fourth oil chamber 44 to the first oil chamber 41 via the first oil passage 51, and oil moves from the second oil chamber 42 to the third oil chamber 43 via the first oil passage 51. 12, the valve element 61 is greatly deformed by the pressure of the oil, and the opening of the valve 60 becomes larger than the initial state shown in FIG. Therefore, this valve 60 can reduce the oil resistance acting on the rotor 20 rotating in the opposite direction or the cylinder 10 rotating in one direction.
- the vane 24 has a second oil passage 52 formed therein.
- the second oil passage is formed in the partition or vane where the first oil passage is not formed.
- the second oil passage 52 is a combination of grooves 71 c to 71 f formed in the valve body 71 and the groove 26 formed in the holding portion 25 .
- the second oil passage 52 is provided with a check valve 70 .
- the check valve 70 is configured with a valve body 71 .
- the valve body 71 has an arcuate body portion 71a and a projecting portion 71b projecting from the body portion 71a.
- the body portion 71a has two grooves 71c and 71d formed on the inner surface, and the protruding portion 71b has a groove 71e formed at the tip and a groove 71f formed on one side surface.
- the body portion 71a is arranged between the peripheral wall 11 and the holding portion 25.
- the projecting portion 71 b is arranged in the groove 26 formed in the holding portion 25 . Since there is play between the groove 26 and the projecting portion 71b, the valve body 71 can move in the circumferential direction.
- the body portion 71a of the valve body 71 preferably has elasticity. This is because the gap formed between the peripheral wall 11 and the valve body 71 can be sealed by the elasticity of the body portion 71a.
- This check valve 70 rotates when the rotor 20 rotates in one direction, i.e. clockwise in FIGS. 1 and 4, or when the cylinder 10 rotates in the opposite direction, i.e. counterclockwise in FIGS. 13, the protruding portion 71b of the valve body 71 contacts one side surface of the groove 26 of the holding portion 25 to close the second oil passage 52, and the rotor 20 rotates in the opposite direction, that is, 1 and 4, or when the cylinder 10 rotates in one direction, i.e., clockwise in FIGS.
- the projecting portion 71b contacts the other side surface of the groove 26 of the holding portion 25 to open the second oil passage 52 .
- the rotary damper according to the embodiment can prevent the gap formed between the partition wall 13 and the shaft portion 21 from expanding, it becomes difficult for oil to pass through the gap.
- the oil can pass through two oil passages, namely the first oil passage 51 and the second oil passage 52, the rotor 20 is rotated in the opposite direction or when the cylinder 10 is rotated in one direction. It is possible to reduce the resistance of the oil acting on 20 or cylinder 10 .
- a manufacturing method of a rotary damper includes a step of casting a cylinder having partition walls using a mold.
- the mold used in this process is a combination of an upper mold and a lower mold.
- the upper die 80 has a tapered portion 81 for forming the tip of the partition into a tapered shape, and a recess 82 formed on the surface of the tapered portion 81 .
- the tapered portion 81 has a tapered shape. That is, the outer diameter of the tapered portion 81 decreases toward one end such that the outer diameter D5 at one end is smaller than the outer diameter D6 at the other end. Since the upper die 80 has a recess 82 on the surface of the tapered portion 81, the injection of the molten metal into the recess 82 causes external shrinkage on the front end surface of the partition wall, and a recess due to the external shrinkage on the front end surface of the partition wall. can be prevented from forming.
- the portion of the upper mold that forms the tip of the partition wall (hereinafter referred to as the "molding portion") is straight, that is, has the same outer diameter along the length of the molding portion.
- external shrinkage occurred due to contraction of the molten metal during solidification, and a dent was formed on the tip surface of the partition wall due to the external shrinkage.
- the prior art as shown in FIG. 17, since the diameter D9 of the recess 82' is smaller than the outer diameter D8 of one end of the molded portion 81', part of the tip of the partition protrudes into the recess 82'. In this case, demolding becomes impossible. Therefore, the prior art cannot form the depression 82' in the surface of the molded portion 81'.
- the tip of the partition wall 13 is tapered, so it is possible to prevent the tip surface of the partition wall 13 from forming a dent due to external shrinkage. Further, since the shaft portion 21 facing the partition wall 13 is also tapered, it is possible to prevent the gap formed between the partition wall 13 and the shaft portion 21 from expanding, thereby improving the characteristics of the rotary damper. It is possible to improve from the past.
- FIG. 18 is a graph showing the relationship between operating time and load.
- the difference between the example and the comparative example is the shape of the tip of the shaft and the partition wall.
- the shape of the tip of the shaft portion and the partition wall is straight.
- the width of change in operating time caused by a change in load is smaller than in the comparative example.
- the difference between the maximum and minimum operating time in the comparative example was about 1.5 seconds, while the difference in the working example was about 0.5 seconds, which was about one third of the comparative example. This result shows that the working example was able to supply more oil to the valve than the comparative example. This is to demonstrate that it can be prevented.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Fluid-Damping Devices (AREA)
Abstract
Description
1.隔壁を有するシリンダーと、前記隔壁に対向する軸部を有するローターを備え、前記シリンダーが鋳物であり、且つ前記隔壁の先端及び前記軸部がテーパー形状であるロータリーダンパ。
2.隔壁を有するシリンダーと、前記隔壁に対向する軸部を有するローターと、前記軸部から突出するベーンと、前記隔壁又は前記ベーンに形成される第1油路と、第1油路を一方向に通過するオイルの流量を負荷に応じて変化させるバルブを備え、前記シリンダーが鋳物であり、且つ前記隔壁の先端及び前記軸部がテーパー形状であるロータリーダンパ。
3.隔壁を有するシリンダーと、前記隔壁に対向する軸部を有するローターと、前記軸部から突出するベーンと、前記隔壁又は前記ベーンに形成される第1油路と、第1油路を一方向に通過するオイルの流量を負荷に応じて変化させるバルブと、第1油路が形成されていない前記隔壁又は前記ベーンに形成される第2油路と、第2油路に設けられる逆止弁を備え、前記シリンダーが鋳物であり、且つ前記隔壁の先端及び前記軸部がテーパー形状であるロータリーダンパ。
4.隔壁を有するシリンダーと、前記隔壁に対向するテーパー形状の軸部を有するローターを備えるロータリーダンパの製造方法であって、金型を用いて前記シリンダーを鋳造する工程を含み、前記金型の上型が、前記隔壁の先端をテーパー形状に成形するためのテーパー部と、前記テーパー部の表面に形成される窪みを有する方法。
前記2に記載の本発明によれば、上述したように前記隔壁と前記軸部との間に形成される隙間の拡大を防止し得るため、前記バルブに対して前記バルブが機能するのに十分な量のオイルを供給することが可能である。したがって、前記2に記載の本発明によれば、負荷の変化によって生じる動作時間の変化の幅を小さくすることが可能である。
前記3に記載の本発明によれば、上述したように前記隔壁と前記軸部との間に形成される隙間の拡大を防止し得るため、前記ローターを一方向に回転させるときに発生する制動力の低下を防ぐことが可能である。一方、前記ローターを逆方向に回転させるときにオイルが前記隔壁と前記軸部との間に形成される隙間を通過し難くなる。しかしながら、前記3に記載の本発明によれば、前記ローターが逆方向に回転するときにオイルが2つの油路、すなわち、第1油路及び第2油路を通過できるため、前記ローターに作用するオイルの抵抗を低減することが可能である。
前記4に記載の本発明は、隔壁を有するシリンダーを鋳造する工程で使用される金型の上型が、前記隔壁の先端をテーパー形状に成形するためのテーパー部と、前記テーパー部の表面に形成される窪みを有するため、前記窪みに溶湯を注入することによって、前記隔壁の先端面に外引けが発生すること、及び前記隔壁の先端面に外引けによる凹みが形成されることを防ぐことが可能である。したがって、前記隔壁と前記軸部との間に形成される隙間の拡大を防止することが可能である。
11 周壁
12 端壁
13 隔壁
14 フランジ
15 凸部
20 ローター
21 軸部
22 凹部
23 穴
24 ベーン
25 保持部
26 溝
30 蓋
41 第1油室
42 第2油室
43 第3油室
44 第4油室
51 第1油路
52 第2油路
60 バルブ
61 弁体
62 弁座
70 逆止弁
71 弁体
80 上型
81 テーパー部
82 窪み
Claims (4)
- 隔壁を有するシリンダーと、前記隔壁に対向する軸部を有するローターを備え、前記シリンダーが鋳物であり、且つ前記隔壁の先端及び前記軸部がテーパー形状であるロータリーダンパ。
- 前記軸部から突出するベーンと、前記隔壁又は前記ベーンに形成される第1油路と、第1油路を一方向に通過するオイルの流量を負荷に応じて変化させるバルブを備える請求項1に記載のロータリーダンパ。
- 第1油路が形成されていない前記隔壁又は前記ベーンに形成される第2油路と、第2油路に設けられる逆止弁を備える請求項2に記載のロータリーダンパ。
- 隔壁を有するシリンダーと、前記隔壁に対向するテーパー形状の軸部を有するローターを備えるロータリーダンパの製造方法であって、金型を用いて前記シリンダーを鋳造する工程を含み、前記金型の上型が、前記隔壁の先端をテーパー形状に成形するためのテーパー部と、前記テーパー部の表面に形成される窪みを有する方法。
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP21945870.0A EP4357636A1 (en) | 2021-06-14 | 2021-06-14 | Rotary damper and method for producing same |
CN202180099331.3A CN117480332A (zh) | 2021-06-14 | 2021-06-14 | 旋转阻尼器及其制造方法 |
PCT/JP2021/022436 WO2022264190A1 (ja) | 2021-06-14 | 2021-06-14 | ロータリーダンパ及びその製造方法 |
JP2023529153A JPWO2022264190A1 (ja) | 2021-06-14 | 2021-06-14 |
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PCT/JP2021/022436 WO2022264190A1 (ja) | 2021-06-14 | 2021-06-14 | ロータリーダンパ及びその製造方法 |
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WO2022264190A1 true WO2022264190A1 (ja) | 2022-12-22 |
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PCT/JP2021/022436 WO2022264190A1 (ja) | 2021-06-14 | 2021-06-14 | ロータリーダンパ及びその製造方法 |
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EP (1) | EP4357636A1 (ja) |
JP (1) | JPWO2022264190A1 (ja) |
CN (1) | CN117480332A (ja) |
WO (1) | WO2022264190A1 (ja) |
Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH1182591A (ja) * | 1997-09-01 | 1999-03-26 | Unisia Jecs Corp | ロータリダンパ |
JPH11336822A (ja) * | 1998-05-26 | 1999-12-07 | Kayaba Ind Co Ltd | ロータリダンパ |
WO2003046405A1 (fr) | 2001-11-27 | 2003-06-05 | Kabushiki Kaisha Somic Ishikawa | Amortisseur rotatif, partie d'automobile comprenant cet amortisseur et mecanisme auxiliaire de mouvement rotatif |
JP2008144779A (ja) * | 2006-12-06 | 2008-06-26 | Fuji Latex Kk | 回転ダンパ−装置 |
WO2012141242A1 (ja) | 2011-04-12 | 2012-10-18 | 株式会社ソミック石川 | ロータリーダンパ |
JP2019082208A (ja) * | 2017-10-31 | 2019-05-30 | 株式会社ソミック石川 | ロータリダンパ |
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2021
- 2021-06-14 WO PCT/JP2021/022436 patent/WO2022264190A1/ja active Application Filing
- 2021-06-14 JP JP2023529153A patent/JPWO2022264190A1/ja active Pending
- 2021-06-14 CN CN202180099331.3A patent/CN117480332A/zh active Pending
- 2021-06-14 EP EP21945870.0A patent/EP4357636A1/en active Pending
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH1182591A (ja) * | 1997-09-01 | 1999-03-26 | Unisia Jecs Corp | ロータリダンパ |
JPH11336822A (ja) * | 1998-05-26 | 1999-12-07 | Kayaba Ind Co Ltd | ロータリダンパ |
WO2003046405A1 (fr) | 2001-11-27 | 2003-06-05 | Kabushiki Kaisha Somic Ishikawa | Amortisseur rotatif, partie d'automobile comprenant cet amortisseur et mecanisme auxiliaire de mouvement rotatif |
JP2008144779A (ja) * | 2006-12-06 | 2008-06-26 | Fuji Latex Kk | 回転ダンパ−装置 |
WO2012141242A1 (ja) | 2011-04-12 | 2012-10-18 | 株式会社ソミック石川 | ロータリーダンパ |
JP2019082208A (ja) * | 2017-10-31 | 2019-05-30 | 株式会社ソミック石川 | ロータリダンパ |
Also Published As
Publication number | Publication date |
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EP4357636A1 (en) | 2024-04-24 |
JPWO2022264190A1 (ja) | 2022-12-22 |
CN117480332A (zh) | 2024-01-30 |
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