JP2008223911A - Damper structure - Google Patents

Damper structure Download PDF

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Publication number
JP2008223911A
JP2008223911A JP2007063879A JP2007063879A JP2008223911A JP 2008223911 A JP2008223911 A JP 2008223911A JP 2007063879 A JP2007063879 A JP 2007063879A JP 2007063879 A JP2007063879 A JP 2007063879A JP 2008223911 A JP2008223911 A JP 2008223911A
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valve
piezoelectric element
piston
damper structure
rod
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Tatsuhiro Tomari
辰弘 泊
Kiyoshi Nakajima
清志 中島
Yoshi Sukigara
宜 鋤柄
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Honda Motor Co Ltd
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Honda Motor Co Ltd
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Abstract

<P>PROBLEM TO BE SOLVED: To provide a damper structure having a wide variable range of damping force even when a piezoelectric element is used as a drive source. <P>SOLUTION: In the damper structure 11, a cylinder 12 and a rod 13 receiving force such as vibration are combined via a piston 14, a valve 15 is disposed through which fluid pressed by the piston 14 flows, and the piezoelectric element 16 is disposed for applying driving force of a valve 15. The piezoelectric element 16 is connected to a valve element 45 of the valve 15 via a booster mechanism 17. Thereby, a driving amount of the piezoelectric element 16 becomes a large moving amount by the booster mechanism 17 to move the valve element 45. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

本発明は、振動などの力に応じて、減衰力を調節することができるダンパー構造に関するものである。   The present invention relates to a damper structure capable of adjusting a damping force according to a force such as vibration.

ダンパー構造には、シリンダ内の流量を変更するバルブを設け、バルブを圧電素子によって駆動しているものがある（例えば、特許文献１参照。）。
特開平１１−３０２６６号公報（第８頁、図１） Some damper structures are provided with a valve for changing the flow rate in the cylinder, and the valve is driven by a piezoelectric element (see, for example, Patent Document 1).
Japanese Patent Laid-Open No. 11-30266 (page 8, FIG. 1)

次に、特許文献１を簡単に説明する。
図６は、従来の技術（特許文献１）の説明図であり、従来の減衰特性可変型緩衝器２０１は、シリンダ２０２の外部に可変バルブ２０３が設けられ、可変バルブ２０３を背圧室２０４内のパイロット圧で制御する。パイロット圧を形成するパイロット圧室２０５には開閉するパイロット弁２０６が設けられ、パイロット弁２０６（パイロット弁体２０８）の閉方向（図の右）への駆動を圧電セラミック板２０７によって行っている。 Next, Patent Document 1 will be briefly described.
FIG. 6 is an explanatory diagram of a conventional technique (Patent Document 1). In a conventional damping characteristic variable shock absorber 201, a variable valve 203 is provided outside the cylinder 202, and the variable valve 203 is placed in the back pressure chamber 204. The pilot pressure is controlled. A pilot valve 206 that opens and closes is provided in the pilot pressure chamber 205 that forms the pilot pressure, and the piezoelectric valve 206 (pilot valve body 208) is driven in the closing direction (right in the drawing) by the piezoelectric ceramic plate 207.

しかし、特許文献１の減衰特性可変型緩衝器２０１では、減衰特性の可変量が小さいという問題がある。
パイロット弁体２０８は圧電セラミック板２０７によって移動するが、移動量（ストローク量）を圧電セラミック板２０７に対応させると、圧電素子の特性からパイロット弁体２０８の最大の開き量は小さいという問題がある。 However, the damping characteristic variable buffer 201 of Patent Document 1 has a problem that the variable amount of the damping characteristic is small.
The pilot valve body 208 is moved by the piezoelectric ceramic plate 207. However, if the movement amount (stroke amount) is made to correspond to the piezoelectric ceramic plate 207, there is a problem that the maximum opening amount of the pilot valve body 208 is small due to the characteristics of the piezoelectric element. .

可変バルブ２０３を他の緩衝器に採用した場合、必要な流量を確保できず、結果的に、必要な減衰力の可変範囲を得ることができないという問題がある。   When the variable valve 203 is employed in another shock absorber, there is a problem that a necessary flow rate cannot be secured and, as a result, a necessary variable range of damping force cannot be obtained.

本発明は、圧電素子を駆動源に用いても、減衰力の可変範囲が大きいダンパー構造を提供することを課題とする。   An object of the present invention is to provide a damper structure having a large variable range of damping force even when a piezoelectric element is used as a drive source.

請求項１に係る発明は、振動などの力を受けるシリンダとロッドをピストンを介して組合わせ、ピストンで押圧された流体が通るバルブを配置し、バルブの駆動力を付与する圧電素子が配置されているダンパー構造において、バルブの弁体に圧電素子が倍力機構を介して連結されていることを特徴とする。   In the first aspect of the invention, a cylinder and a rod that receive a force such as vibration are combined via a piston, a valve through which a fluid pressed by the piston passes, and a piezoelectric element that provides a driving force for the valve is disposed. In the damper structure, the piezoelectric element is connected to the valve body of the valve via a booster mechanism.

請求項２に係る発明は、圧電素子は、ロッド内にロッドと同軸に配置され、倍力機構は、ピストンの半径方向に伸びて弁体と圧電素子を連結しているレバー部材と、レバー部材の支点を支持する支点支持部と、を備えていることを特徴とする。   According to a second aspect of the present invention, the piezoelectric element is disposed coaxially with the rod in the rod, and the boosting mechanism extends in the radial direction of the piston to connect the valve element and the piezoelectric element, and the lever member And a fulcrum support part for supporting the fulcrum.

請求項３に係る発明は、支点支持部は、ピストンの中央に形成され、レバー部材は、一端が弁体に連結され、他端が支点支持部に連結され、他端の近傍に圧電素子の駆動力を加える力点連結部材を連結したことを特徴とする。   In the invention according to claim 3, the fulcrum support portion is formed at the center of the piston, and the lever member has one end connected to the valve body, the other end connected to the fulcrum support portion, and the piezoelectric element near the other end. A power point connecting member for applying a driving force is connected.

請求項１に係る発明では、振動などの力を受けるシリンダとロッドをピストンを介して組合わせ、ピストンで押圧された流体が通るバルブを配置し、バルブの駆動力を付与する圧電素子が配置されているダンパー構造において、バルブの弁体に圧電素子が倍力機構を介して連結されているので、圧電素子の駆動量が倍力機構によって大きな移動量となって弁体を移動させる。その結果、バルブの流量の範囲が大きくなり、圧電素子を駆動源に用いても、減衰力の可変範囲を大きくすることができるという利点がある。   In the invention according to claim 1, a cylinder and a rod that receive a force such as vibration are combined via a piston, a valve through which a fluid pressed by the piston passes, and a piezoelectric element that provides a driving force for the valve is disposed. In the damper structure, since the piezoelectric element is connected to the valve body of the valve via a booster mechanism, the driving amount of the piezoelectric element is increased by the booster mechanism to move the valve body. As a result, the range of the flow rate of the valve is increased, and there is an advantage that the variable range of the damping force can be increased even when the piezoelectric element is used as a drive source.

請求項２に係る発明では、圧電素子は、ロッド内にロッドと同軸に配置され、倍力機構は、ピストンの半径方向に伸びて弁体と圧電素子を連結しているレバー部材と、レバー部材の支点を支持する支点支持部と、を備えているので、圧電素子をロッドの軸線方向に駆動させ、且つ、ロッドの軸線方向の圧電素子の変位（駆動量）を大きくすることができる。   In the invention according to claim 2, the piezoelectric element is disposed coaxially with the rod in the rod, and the boosting mechanism extends in the radial direction of the piston and connects the valve body and the piezoelectric element, and the lever member Since the piezoelectric element is driven in the axial direction of the rod, the displacement (driving amount) of the piezoelectric element in the axial direction of the rod can be increased.

また、ロッドの軸線方向の圧電素子の変位が倍力機構によって大きな移動量となって弁体を移動させる。従って、減衰力の可変範囲をより大きくすることができるという利点がある。   Further, the displacement of the piezoelectric element in the axial direction of the rod becomes a large movement amount by the boost mechanism, and the valve body is moved. Therefore, there is an advantage that the variable range of the damping force can be increased.

請求項３に係る発明では、支点支持部は、ピストンの中央に形成され、レバー部材は、一端が弁体に連結され、他端が支点支持部に連結され、他端の近傍に圧電素子の駆動力を加える力点連結部材を連結したので、支点支持部から力点連結部材までの距離と力点連結部材から弁体までの距離の比が大きくなり、弁体の移動量をより大きくすることができる。従って、減衰力の可変範囲をより大きくすることができるという利点がある。   In the invention according to claim 3, the fulcrum support portion is formed at the center of the piston, and the lever member has one end connected to the valve body, the other end connected to the fulcrum support portion, and the piezoelectric element near the other end. Since the power point connecting member for applying the driving force is connected, the ratio of the distance from the fulcrum support part to the power point connecting member and the distance from the power point connecting member to the valve body is increased, and the amount of movement of the valve body can be further increased. . Therefore, there is an advantage that the variable range of the damping force can be increased.

本発明を実施するための最良の形態を添付図に基づいて以下に説明する。
図１は、本発明のダンパー構造の断面図である。
図２は、本発明のダンパー構造の斜視図である。 The best mode for carrying out the present invention will be described below with reference to the accompanying drawings.
FIG. 1 is a cross-sectional view of the damper structure of the present invention.
FIG. 2 is a perspective view of the damper structure of the present invention.

ダンパー構造１１は、シリンダ１２と、ロッド１３と、ピストン１４と、ピストン１４に設けたバルブ１５と、バルブ１５を駆動する圧電素子１６と、倍力機構１７を備え、例えば、自動車の懸架装置に用いられる。   The damper structure 11 includes a cylinder 12, a rod 13, a piston 14, a valve 15 provided on the piston 14, a piezoelectric element 16 that drives the valve 15, and a booster mechanism 17. Used.

自動車は、走行状態を検出する車両状態検出装置２１と、自動車の全体を制御する制御装置２２を備え、制御装置２２の減衰情報に基づいて圧電素子１６は制御される。
シリンダ１２は、ピストン１４で仕切られてロッド１３が配置されている前室２５と、ロッド１３が配置されていない後室２６を有する。 The automobile includes a vehicle state detection device 21 that detects a traveling state and a control device 22 that controls the entire automobile, and the piezoelectric element 16 is controlled based on attenuation information of the control device 22.
The cylinder 12 has a front chamber 25 that is partitioned by the piston 14 and in which the rod 13 is disposed, and a rear chamber 26 in which the rod 13 is not disposed.

ピストン１４は、シリンダ１２の内径よりわずかに小さい外周面２８を形成し、外周面２８にシートリング３１、３１を取付け、前室２５の壁をなす前壁３２を形成し、後室２６の壁をなす後壁３３を形成し、後壁３３と前壁３２を結合部材３４で結合して、バルブ室３５を形成している。
結合部材３４を用いることで、ピストン１４の軽量化を図ることができる。
前壁３２には、ロッド１３を接続する第１めねじ部が形成されている。 The piston 14 forms an outer peripheral surface 28 that is slightly smaller than the inner diameter of the cylinder 12, seat rings 31, 31 are attached to the outer peripheral surface 28, a front wall 32 that forms the wall of the front chamber 25 is formed, and the wall of the rear chamber 26 A rear wall 33 is formed, and the rear wall 33 and the front wall 32 are coupled by a coupling member 34 to form a valve chamber 35.
By using the coupling member 34, the weight of the piston 14 can be reduced.
A first female thread portion for connecting the rod 13 is formed on the front wall 32.

ロッド１３は、前壁３２の第１めねじ部にねじ込んだおねじ部が切られ、一端３７に嵌合穴４１が深く形成され、嵌合穴４１の端に第２めねじ部が形成されている。   The rod 13 has a male thread portion screwed into the first female thread portion of the front wall 32, a fitting hole 41 is deeply formed at one end 37, and a second female thread portion is formed at the end of the fitting hole 41. ing.

図３は、図１の３−３線断面図である。図１、図２を併用して説明する。
バルブ１５は、ピストン１４内（バルブ室３５）に設けられ、後壁３３に貫通している後流路４３と、前壁３２に向いている後流路４３の角に形成した弁座４４と、弁座４４に、閉じるときに当たる弁体４５と、ピストン１４の前壁３２に貫通させた前流路４６と、を備える。 3 is a cross-sectional view taken along line 3-3 of FIG. This will be described with reference to FIGS.
The valve 15 is provided in the piston 14 (valve chamber 35), and includes a rear passage 43 that penetrates the rear wall 33, and a valve seat 44 that is formed at a corner of the rear passage 43 that faces the front wall 32. The valve seat 44 is provided with a valve body 45 that contacts the valve seat 44 and a front passage 46 that penetrates the front wall 32 of the piston 14.

倍力機構１７は、弁体４５に連結しているレバー部材４８と、レバー部材４８に連結している支点支持部５１と、レバー部材４８と圧電素子１６を接続している力点連結部材５２と、力点連結部材５２を圧電素子１６に押圧している弾性部材５３と、圧電素子１６をロッド１３の半径方向に対して支持し、ロッド１３の嵌合穴４１に嵌合している固定カラー５４と、を備える。具体的に説明する。   The booster mechanism 17 includes a lever member 48 connected to the valve body 45, a fulcrum support portion 51 connected to the lever member 48, and a force point connecting member 52 connecting the lever member 48 and the piezoelectric element 16. The elastic member 53 pressing the force point connecting member 52 against the piezoelectric element 16, and the fixed collar 54 that supports the piezoelectric element 16 in the radial direction of the rod 13 and is fitted in the fitting hole 41 of the rod 13. And comprising. This will be specifically described.

レバー部材４８は、一端（先端）に弁体４５がピンで揺動自在（矢印ａ１の方向）に連結され、他端が支点支持部５１にピンで揺動自在（矢印ａ２の方向）に連結され、支点支持部５１側に力点連結部材５２が連結されている。
支点支持部５１から力点連結部材５２までの距離はＬ１で、レバー部材４８の約１／４であり、力点連結部材５２から弁体４５までの距離をＬ２とし、距離Ｌ２は、Ｌ２＞Ｌ１で、Ｌ１の約３倍である。 The lever member 48 is connected to one end (tip) of the valve body 45 so as to be swingable with a pin (in the direction of arrow a1), and the other end is connected to the fulcrum support 51 with a pin so as to be swingable (in the direction of arrow a2). The force point connecting member 52 is connected to the fulcrum support portion 51 side.
The distance from the fulcrum support 51 to the force point connecting member 52 is L1, which is about ¼ of the lever member 48, the distance from the force point connecting member 52 to the valve body 45 is L2, and the distance L2 is L2> L1. , About 3 times L1.

弁体４５は、円錐形に形成され、円錐の底面に連ねてレバー部材４８に連結している取付け部５８を形成している。
支点支持部５１は、後壁３３の内面（前壁３２に向いている面）の中央にボス部６１が形成され、ボス部６１の端部にレバー部材４８を支持する溝部６２が形成されている。 The valve body 45 is formed in a conical shape, and forms a mounting portion 58 connected to the lever member 48 so as to be connected to the bottom surface of the cone.
The fulcrum support portion 51 has a boss portion 61 formed at the center of the inner surface of the rear wall 33 (the surface facing the front wall 32), and a groove portion 62 that supports the lever member 48 at the end portion of the boss portion 61. Yes.

力点連結部材５２は、レバー部材４８に連結している凸部６４が形成され、凸部６４に連ねて円盤部６５が形成され、円盤部６５の中央に素子支持ガイド部材６６が形成され、素子支持ガイド部材６６がロッド１３の嵌合穴４１に、ロッド１３の長手方向（Ｚ軸方向）にスライド自在に嵌合し、素子支持ガイド部材６６の掛止部６７に弾性部材５３の一端を当接するとともに弾性部材５３を嵌合穴４１に収納し、収納した弾性部材５３の他端を蓋部材６８に当接して蓋部材６８をロッド１３の接続めねじ部にねじ込んだものである。   The force point connecting member 52 is formed with a convex portion 64 connected to the lever member 48, a disk portion 65 is formed continuously with the convex portion 64, and an element support guide member 66 is formed at the center of the disk portion 65. The support guide member 66 is slidably fitted in the fitting hole 41 of the rod 13 in the longitudinal direction (Z-axis direction) of the rod 13, and one end of the elastic member 53 is brought into contact with the latching portion 67 of the element support guide member 66. The elastic member 53 is accommodated in the fitting hole 41, and the other end of the accommodated elastic member 53 is brought into contact with the lid member 68, and the lid member 68 is screwed into the connecting female thread portion of the rod 13.

圧電素子１６は、既存のもので、電圧を印加するとひずむ。円柱に形成し、且つ、長さＬと直径Ｄの比（Ｌ／Ｄ）を大きく形成している。つまり、細長いものである。そして、圧電素子１６の軸線Ｃをロッド１３と軸線Ｃ１と同軸に配置している。   The piezoelectric element 16 is an existing element and is distorted when a voltage is applied. It is formed in a cylinder and has a large ratio (L / D) between the length L and the diameter D. That is, it is elongated. The axis C of the piezoelectric element 16 is arranged coaxially with the rod 13 and the axis C1.

次に、本発明のダンパー構造の作用を説明する。
図１に示しているダンパー構造１１は、通電していない状態で、通電していないときは、弾性部材５３によって、常時、バルブ１５を全開にしている。
弾性部材５３は、力点連結部材５２を圧電素子１６に押圧し続けているので、力点連結部材５２はレバー部材４８を開限位置Ｋに保持し続け、弁体４５を全開位置Ｍに保持する。 Next, the operation of the damper structure of the present invention will be described.
In the damper structure 11 shown in FIG. 1, the valve 15 is always fully opened by the elastic member 53 when not energized and when not energized.
Since the elastic member 53 continues to press the force point connecting member 52 against the piezoelectric element 16, the force point connecting member 52 continues to hold the lever member 48 in the open limit position K and holds the valve body 45 in the fully open position M.

図４は、本発明のダンパー構造の減衰力の調節機構を説明する図である。図１を併用して説明する。
まず、図４を用いて油７１（点模様で示した）の流れを説明し、引き続き、図４でバルブ１５を絞る機構を説明する。 FIG. 4 is a diagram for explaining a damping force adjusting mechanism of the damper structure according to the present invention. This will be described with reference to FIG.
First, the flow of the oil 71 (shown as a dot pattern) will be described with reference to FIG. 4, and the mechanism for restricting the valve 15 will be described with reference to FIG.

ダンパー構造１１は、図４のように圧縮（矢印ａ３の方向）の荷重が加わると、ピストン１４が移動するので、後室２６内の油７１は、後室２６から後流路４３を矢印ｂ１のように流れ、続けて、前流路４６を矢印ｂ２のように流れて、前室２５に移動する。従って、圧縮荷重（振動）を吸収することができる。   In the damper structure 11, when a compression load (in the direction of arrow a <b> 3) is applied as shown in FIG. 4, the piston 14 moves, so that the oil 71 in the rear chamber 26 moves from the rear chamber 26 to the rear flow path 43 by the arrow b <b> 1. Then, the front channel 46 flows as indicated by the arrow b2 and moves to the front chamber 25. Therefore, a compressive load (vibration) can be absorbed.

逆に、引張りの荷重が加わると、圧縮とは逆方向に油が流れるから、引張り荷重（振動）を吸収することができる。   Conversely, when a tensile load is applied, oil flows in the opposite direction to compression, so that the tensile load (vibration) can be absorbed.

ダンパー構造１１は、制御装置２２によって圧電素子１６に電圧を印加すると、圧電素子１６は、長手方向（Ｚ軸方向）に矢印ｂ３のように伸びて、倍力機構１７を介してバルブ１５を閉じ方向に移動させるので、バルブ１５の移動量を大きくすることができる。
なお、バルブ１５を閉じるので、開度が変化し、ダンパー構造１１の減衰力は変化する。 In the damper structure 11, when a voltage is applied to the piezoelectric element 16 by the control device 22, the piezoelectric element 16 extends in the longitudinal direction (Z-axis direction) as indicated by an arrow b 3, and the valve 15 is closed via the booster mechanism 17. Since it is moved in the direction, the amount of movement of the valve 15 can be increased.
Since the valve 15 is closed, the opening degree changes and the damping force of the damper structure 11 changes.

具体的には、圧電素子１６が長手方向に伸びると、弾性部材５３に抗して、力点連結部材５２を矢印ｂ３のように押すと同時にレバー部材４８を押す。レバー部材４８はピストン１４の中央の支点支持部５１を支点に揺動して、一端に取付けている弁体４５を後流路４３に形成している弁座４４に押圧するので、後流路４３は閉じられる。   Specifically, when the piezoelectric element 16 extends in the longitudinal direction, the lever member 48 is pushed at the same time as the force point connecting member 52 is pushed as shown by the arrow b3 against the elastic member 53. The lever member 48 swings around the fulcrum support 51 at the center of the piston 14 and presses the valve body 45 attached to one end against the valve seat 44 formed in the rear flow path 43. 43 is closed.

その際、圧電素子１６が伸びδｐだけ伸びると、倍力機構１７の距離Ｌ１と距離Ｌ２の比によって、弁体４５はストローク（距離）Ｂ（Ｂ＞δｐ）だけ移動するので、弁体４５のストローク量を大きくすることができる。従って、減衰力の可変範囲を大きくすることができる。   At this time, when the piezoelectric element 16 is extended by δp, the valve body 45 is moved by the stroke (distance) B (B> δp) depending on the ratio of the distance L1 and the distance L2 of the booster mechanism 17. Stroke amount can be increased. Therefore, the variable range of the damping force can be increased.

図５は、ダンパーのピストンの速度とダンパーの減衰力の関係を示したグラフであり、横軸をダンパーのピストンの速度とし、縦軸をダンパーの減衰力としたものである。
破線は、比較例で、減衰力を変更できない一般的なダンパーを示し、ピストンの速度が速い領域では減衰力は高く、ピストンの速度が遅い領域では減衰力は低い。 FIG. 5 is a graph showing the relationship between the speed of the damper piston and the damping force of the damper, in which the horizontal axis is the speed of the damper piston and the vertical axis is the damping force of the damper.
A broken line shows a general damper in which the damping force cannot be changed in the comparative example. The damping force is high in a region where the piston speed is high, and the damping force is low in a region where the piston speed is slow.

実線は、実施の形態を示している。
実施の形態のダンパーは、圧電素子１６を用いても弁体４５のストローク量が大きく、上限Ｕと下限Ｗの幅が大きくなり、減衰力の範囲を大きくすることができる。 The solid line indicates the embodiment.
In the damper of the embodiment, even when the piezoelectric element 16 is used, the stroke amount of the valve body 45 is large, the width between the upper limit U and the lower limit W is increased, and the range of the damping force can be increased.

ピストンの速度が極めて低いときに、車両状態検出装置２１に基づいて、圧電素子１６に通電することで、バルブ１５を完全に閉じる（後流路４３の流量をゼロにする）。その結果、ピストンの速度が極めて低いときに、減衰力を付与することができる。   When the speed of the piston is extremely low, the valve 15 is completely closed by energizing the piezoelectric element 16 based on the vehicle state detection device 21 (the flow rate of the rear flow path 43 is made zero). As a result, a damping force can be applied when the speed of the piston is extremely low.

走行状態に応じて、車両状態検出装置２１に基づいて、圧電素子１６への通電量を変化させることで、必要な減衰力を発生させることができる。   A necessary damping force can be generated by changing the energization amount to the piezoelectric element 16 based on the vehicle state detection device 21 according to the traveling state.

尚、本発明のダンパー構造は、実施の形態ではレバー部材４８の他端が支点支持部５１に連結されているが、他端に力点連結部材５２を連結してもよい。その際には、支点支持部５１をレバー部材４８の中央側へ移動して、レバー部材４８の比を設定することで、同様の効果を発揮する。   In the damper structure of the present invention, the other end of the lever member 48 is connected to the fulcrum support 51 in the embodiment, but a force point connecting member 52 may be connected to the other end. In that case, the same effect is demonstrated by moving the fulcrum support part 51 to the center side of the lever member 48, and setting the ratio of the lever member 48. FIG.

バルブ１５は、ピストン１４に流路を４個形成したが数は任意である。すなわち、後流路４３や弁体４５を４個設けたが、４個以下でもよく、４個超えでもよい。   The valve 15 has four flow paths formed in the piston 14, but the number is arbitrary. That is, although the four rear flow paths 43 and the valve bodies 45 are provided, the number may be four or less or may be more than four.

本発明のダンパー構造は、自動車の懸架装置に好適である。   The damper structure of the present invention is suitable for an automobile suspension device.

本発明のダンパー構造の断面図である。It is sectional drawing of the damper structure of this invention. 本発明のダンパー構造の斜視図である。It is a perspective view of the damper structure of the present invention. 図１の３−３線断面図である。FIG. 3 is a sectional view taken along line 3-3 in FIG. 1. 本発明のダンパー構造の減衰力の調節機構を説明する図である。It is a figure explaining the adjustment mechanism of damping force of the damper structure of the present invention. ダンパーのピストンの速度とダンパーの減衰力の関係を示したグラフである。It is the graph which showed the relationship between the speed of the piston of a damper, and the damping force of a damper. 従来の技術（特許文献１）の説明図である。It is explanatory drawing of a prior art (patent document 1).

符号の説明Explanation of symbols

１１…ダンパー構造、１２…シリンダ、１３…ロッド、１４…ピストン、１５…バルブ、１６…圧電素子、１７…倍力機構、４５…弁体、４８…レバー部材、５１…支点支持部、５２…力点連結部材。   DESCRIPTION OF SYMBOLS 11 ... Damper structure, 12 ... Cylinder, 13 ... Rod, 14 ... Piston, 15 ... Valve, 16 ... Piezoelectric element, 17 ... Booster mechanism, 45 ... Valve body, 48 ... Lever member, 51 ... Supporting point part, 52 ... Power point connecting member.

Claims (3)

振動などの力を受けるシリンダとロッドをピストンを介して組合わせ、該ピストンで押圧された流体が通るバルブを配置し、該バルブの駆動力を付与する圧電素子が配置されているダンパー構造において、
前記バルブの弁体に前記圧電素子が倍力機構を介して連結されていることを特徴とするダンパー構造。 In a damper structure in which a cylinder and a rod that receive a force such as vibration are combined via a piston, a valve through which a fluid pressed by the piston passes, and a piezoelectric element that applies driving force of the valve is arranged,
A damper structure, wherein the piezoelectric element is connected to a valve body of the valve via a booster mechanism. 前記圧電素子は、前記ロッド内にロッドと同軸に配置され、
前記倍力機構は、前記ピストンの半径方向に伸びて前記弁体と前記圧電素子を連結しているレバー部材と、該レバー部材の支点を支持する支点支持部と、を備えていることを特徴とする請求項１記載のダンパー構造。 The piezoelectric element is disposed coaxially with the rod in the rod,
The booster mechanism includes a lever member that extends in a radial direction of the piston and connects the valve body and the piezoelectric element, and a fulcrum support portion that supports a fulcrum of the lever member. The damper structure according to claim 1. 前記支点支持部は、前記ピストンの中央に形成され、
前記レバー部材は、一端が前記弁体に連結され、他端が前記支点支持部に連結され、前記他端の近傍に前記圧電素子の駆動力を加える力点連結部材を連結したことを特徴とする請求項２記載のダンパー構造。 The fulcrum support is formed at the center of the piston,
One end of the lever member is connected to the valve body, the other end is connected to the fulcrum support, and a force point connecting member for applying a driving force of the piezoelectric element is connected in the vicinity of the other end. The damper structure according to claim 2.
JP2007063879A 2007-03-13 2007-03-13 Damper structure Pending JP2008223911A (en)

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Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2013011812A1 (en) * 2011-07-17 2013-01-24 本田技研工業株式会社 Damper with variable damping force
JP2013024268A (en) * 2011-07-17 2013-02-04 Honda Motor Co Ltd Damping force variable damper
KR20160131310A (en) * 2015-05-06 2016-11-16 현대자동차주식회사 Variable damper
KR20190048541A (en) * 2017-10-31 2019-05-09 충북대학교 산학협력단 Linear type one-way damper
DE102019210578A1 (en) * 2019-07-18 2021-01-21 Zf Friedrichshafen Ag Adjustable damping valve device with a piezo actuator

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2013011812A1 (en) * 2011-07-17 2013-01-24 本田技研工業株式会社 Damper with variable damping force
JP2013024268A (en) * 2011-07-17 2013-02-04 Honda Motor Co Ltd Damping force variable damper
JP5617038B2 (en) * 2011-07-17 2014-10-29 本田技研工業株式会社 Variable damping force damper
US9126467B2 (en) 2011-07-17 2015-09-08 Honda Motor Co., Ltd. Damper with variable damping force
KR20160131310A (en) * 2015-05-06 2016-11-16 현대자동차주식회사 Variable damper
KR101683503B1 (en) * 2015-05-06 2016-12-07 현대자동차 주식회사 Variable damper
KR20190048541A (en) * 2017-10-31 2019-05-09 충북대학교 산학협력단 Linear type one-way damper
KR101993645B1 (en) * 2017-10-31 2019-06-26 충북대학교 산학협력단 Linear type one-way damper
DE102019210578A1 (en) * 2019-07-18 2021-01-21 Zf Friedrichshafen Ag Adjustable damping valve device with a piezo actuator

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