JP2010185463A - Damper pulley and variable displacement vane pump - Google Patents

Damper pulley and variable displacement vane pump Download PDF

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Publication number
JP2010185463A
JP2010185463A JP2007112454A JP2007112454A JP2010185463A JP 2010185463 A JP2010185463 A JP 2010185463A JP 2007112454 A JP2007112454 A JP 2007112454A JP 2007112454 A JP2007112454 A JP 2007112454A JP 2010185463 A JP2010185463 A JP 2010185463A
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Japan
Prior art keywords
damper pulley
annular member
elastic body
peripheral side
pump
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JP2007112454A
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Japanese (ja)
Inventor
Norikatsu Hoshina
憲克 保科
Yasuhiro Sato
康寛 佐藤
Shoichiro Hashimoto
庄一郎 橋本
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Hitachi Ltd
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Hitachi Ltd
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Priority to JP2007112454A priority Critical patent/JP2010185463A/en
Priority to PCT/JP2008/057624 priority patent/WO2008133212A1/en
Publication of JP2010185463A publication Critical patent/JP2010185463A/en
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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
    • F16H—GEARING
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/32—Friction members
    • F16H55/36—Pulleys
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/18—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber
    • F04C14/22—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members
    • F04C14/223—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members using a movable cam
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0057—Driving elements, brakes, couplings, transmission specially adapted for machines or pumps
    • F04C15/0061—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C2/34—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
    • F04C2/344—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F04C2/3441—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation
    • F04C2/3442—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the working space, being surfaces of revolution
    • 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
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/14—Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers
    • F16F15/1407—Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers the rotation being limited with respect to the driving means
    • F16F15/1414—Masses driven by elastic elements
    • F16F15/1435—Elastomeric springs, i.e. made of plastic or rubber
    • F16F15/1442—Elastomeric springs, i.e. made of plastic or rubber with a single mass
    • 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
    • F16H—GEARING
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/32—Friction members
    • F16H55/36—Pulleys
    • F16H2055/366—Pulleys with means providing resilience or vibration damping

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Pulleys (AREA)
  • Rotary Pumps (AREA)

Abstract

<P>PROBLEM TO BE SOLVED: To provide a damper pulley which can cope with vibrations not only in the radial direction but also in the axial direction of the pulley and is excellent in mounting property of a rubber-like elastic body. <P>SOLUTION: The damper pulley includes a boss 201 connected to a drive shaft 2, a flange 202 which extends in the radial direction from the drive shaft 2, a rim 203 which is provided on the outer peripheral side of the flange 202 and formed in an annular shape, a metal annular member 210 provided at the inside circumferential side of the rim 203, an elastic body 230 which is provided at the inside circumferential side of the annular member 210 and made up of a radial section 232 extending in the radial direction in a cross section and an axial section 233 extending in the axial direction, and a metal mass member 220 provided on inside circumferential side of the elastic body 230. The annular member 210 is provided so as to be exposed to the opening end side of the rim 203. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

本発明は、可変容量型ベーンポンプに備えられるダンパプーリに関する。   The present invention relates to a damper pulley provided in a variable displacement vane pump.

従来、特許文献１に記載されるダンパプーリにあっては、圧入リングを介してゴム状弾性体がプーリに取り付けられている。
特開平５−３３２４１９号公報 Conventionally, in the damper pulley described in Patent Document 1, a rubber-like elastic body is attached to the pulley via a press-fit ring.
JP-A-5-332419

しかしながら上記従来技術にあっては、このゴム状弾性体は断面が矩形状に形成されており、プーリの径方向振動のみに対応したものであり、軸方向振動に対応するものではない。このため、プーリの径方向だけでなく軸方向の振動にも対応し、かつゴム状弾性体の組み付け性に優れたダンパプーリが望まれていた。   However, in the above prior art, this rubber-like elastic body has a rectangular cross section and corresponds only to the radial vibration of the pulley, not to the axial vibration. For this reason, there has been a demand for a damper pulley that can cope with not only the radial direction of the pulley but also the vibration in the axial direction and that is excellent in the ease of assembling the rubber-like elastic body.

本発明は上記問題に着目してなされたもので、その目的とするところは、プーリの径方向だけでなく軸方向の振動にも対応し、かつゴム状弾性体の組み付け性に優れたダンパプーリを提供することにある。   The present invention has been made paying attention to the above-mentioned problems, and the object of the present invention is to provide a damper pulley that can handle not only the radial direction of the pulley but also the vibration in the axial direction and that is excellent in assembling property of the rubber-like elastic body. It is to provide.

上記目的を達成するため、本発明では、駆動軸が接続されるボス部と、前記駆動軸から径方向に設けられるフランジ部と、前記フランジ部の外周側に設けられ、環状に形成されるリム部と、前記リム部の内周側に設けられる金属製の環状部材と、前記環状部材の内周側に設けられ、断面形状が径方向に伸びる径方向部分と、軸方向に伸びる軸方向部分とから構成される弾性体と。前記弾性体の内周側に設けられた金属製のマス部材とを有し、前記環状部材は、前記リム部の開口端側に露出するように設けられることとした。   In order to achieve the above object, in the present invention, a boss portion to which a drive shaft is connected, a flange portion provided radially from the drive shaft, and an annular rim provided on the outer peripheral side of the flange portion. Part, a metal annular member provided on the inner peripheral side of the rim part, a radial part provided on the inner peripheral side of the annular member, and a cross-sectional shape extending in the radial direction, and an axial part extending in the axial direction And an elastic body composed of A metal mass member provided on the inner peripheral side of the elastic body, and the annular member is provided so as to be exposed on the opening end side of the rim portion.

よって、プーリの径方向だけでなく軸方向の振動にも対応し、かつゴム状弾性体の組み付け性に優れたダンパプーリを提供できる。   Therefore, it is possible to provide a damper pulley that can handle not only the radial direction of the pulley but also the vibration in the axial direction and that is excellent in the ease of assembling the rubber-like elastic body.

以下、本発明のダンパプーリを実現する最良の形態を、図面に示す実施例に基づいて説明する。   Hereinafter, the best mode for realizing the damper pulley of the present invention will be described based on an embodiment shown in the drawings.

［ベーンポンプの概要］
図１はベーンポンプ１の軸方向断面図（図２のＩ−Ｉ断面）、図２は径方向断面図（図１のＩＩ−ＩＩ断面）である。図２ではカムリング４が最もｙ軸負方向に位置する場合（偏心量最大）を示す。 [Outline of vane pump]
FIG. 1 is an axial sectional view of the vane pump 1 (II section in FIG. 2), and FIG. 2 is a radial sectional view (II-II section in FIG. 1). FIG. 2 shows the case where the cam ring 4 is located in the most negative y-axis direction (maximum eccentricity).

なお、駆動軸２の軸方向をｘ軸とし、フロントボディ１１、リアボディ１２へ駆動軸が挿入される方向を正方向とする。また、カムリング４の揺動を規制するスプリング７１（図２参照）の軸方向であってカムリング４を付勢する方向をｙ軸負方向、ｘ、ｙ軸と直交する軸であって吸入通路ＩＮ側をｚ軸正方向とする。   The axial direction of the drive shaft 2 is the x axis, and the direction in which the drive shaft is inserted into the front body 11 and the rear body 12 is the positive direction. In addition, the axial direction of a spring 71 (see FIG. 2) that restricts the swinging of the cam ring 4 and the direction in which the cam ring 4 is urged is a negative y-axis direction, an axis orthogonal to the x and y axes, and the suction passage IN. The side is the z-axis positive direction.

ベーンポンプ１は、駆動軸２、ロータ３、カムリング４、アダプタリング５、ポンプボディ１０を有する。駆動軸２はダンパプーリ２００を介して図外のエンジンと接続し、ロータ３と一体回転する。   The vane pump 1 includes a drive shaft 2, a rotor 3, a cam ring 4, an adapter ring 5, and a pump body 10. The drive shaft 2 is connected to an engine (not shown) via a damper pulley 200 and rotates integrally with the rotor 3.

ダンパプーリ２００はボス部２０１、フランジ部２０２、リム部２０３を有する。ボス部２０１は駆動軸２と接続し、外径方向に延在してフランジ部２０２を形成し、最外径部には環状のリム部２０３が設けられてベルトによって図外のエンジンの回転が伝達される。   The damper pulley 200 has a boss portion 201, a flange portion 202, and a rim portion 203. The boss portion 201 is connected to the drive shaft 2 and extends in the outer diameter direction to form a flange portion 202. An annular rim portion 203 is provided at the outermost diameter portion, and the rotation of the engine (not shown) is performed by the belt. Communicated.

リム部２０３の内周側には環状部材２１０が設けられ、さらに内径側にはマス部材２２０が設けられている。この環状部材２１０とマス部材２２０はともに金属部材であって、径方向断面Ｌ字型の弾性体２３０を介して互いに接続される。   An annular member 210 is provided on the inner peripheral side of the rim portion 203, and a mass member 220 is provided on the inner diameter side. The annular member 210 and the mass member 220 are both metal members, and are connected to each other via an elastic body 230 having an L-shaped radial cross section.

ロータ３の外周には軸方向溝である複数のスロット３１が放射状に形成され、各スロット３１にベーン３２が径方向に出没可能に挿入される。また、各スロット３１の内径側端部には背圧室３３が設けられ、作動油が供給されてベーン３２を径方向外側に付勢する。   A plurality of slots 31, which are axial grooves, are formed radially on the outer periphery of the rotor 3, and vanes 32 are inserted into the slots 31 so as to be able to protrude and retract in the radial direction. Further, a back pressure chamber 33 is provided at the inner diameter side end of each slot 31, and hydraulic oil is supplied to urge the vane 32 radially outward.

ポンプボディ１０はフロントボディ１１およびリアボディ１２から形成される。フロントボディ１１はｘ軸正方向側に開口する有底カップ形状であり、底部１１１には円盤状のプレッシャープレート６が収装される。フロントボディ１１内周部であるポンプ要素収容部１１２であってプレッシャープレート６のｘ軸正方向側には、アダプタリング５、カムリング４、およびロータ３が収装される。   The pump body 10 is formed from a front body 11 and a rear body 12. The front body 11 has a bottomed cup shape that opens in the positive direction of the x-axis, and a disc-shaped pressure plate 6 is accommodated in the bottom portion 111. The adapter ring 5, the cam ring 4, and the rotor 3 are housed in the pump element accommodating portion 112 that is the inner peripheral portion of the front body 11 and on the x-axis positive direction side of the pressure plate 6.

リアボディ１２はｘ軸正方向側からアダプタリング５、カムリング４、およびロータ３と液密に当接し、アダプタリング５、カムリング４、およびロータ３はプレッシャープレート６およびリアボディ１２に挟持されることとなる。   The rear body 12 comes into liquid-tight contact with the adapter ring 5, the cam ring 4, and the rotor 3 from the x axis positive direction side, and the adapter ring 5, the cam ring 4, and the rotor 3 are sandwiched between the pressure plate 6 and the rear body 12. .

プレッシャープレート６には貫通孔６６が設けられて駆動軸２が挿入される。また、ｘ軸正方向側面６１およびリアボディ１２のｘ軸負方向側面１２０にはそれぞれ吸入ポート６２，１２１および吐出ポート６３，１２２が設けられ、吸入通路ＩＮ、吐出口ＯＵＴと接続してロータ３とカムリング４の間に形成されるポンプ室Ｂへの作動油の給排を行う。   A through hole 66 is provided in the pressure plate 6 and the drive shaft 2 is inserted. Further, suction ports 62 and 121 and discharge ports 63 and 122 are provided on the x-axis positive side surface 61 and the x-axis negative direction side surface 120 of the rear body 12, respectively, and are connected to the suction passage IN and discharge port OUT to connect with the rotor 3. The hydraulic oil is supplied to and discharged from the pump chamber B formed between the cam rings 4.

この吸入ポート６２，１２１は複数のポンプ室Ｂの容積が増大する領域（吸入領域Ｂｚ＋）に開口し、吐出ポート６３，１２２は複数のポンプ室Ｂの容積が縮小する領域（吐出領域Ｂｚ−）に開口する。   The suction ports 62 and 121 open to a region where the volumes of the plurality of pump chambers B increase (suction region Bz +), and the discharge ports 63 and 122 serve as a region where the volumes of the plurality of pump chambers B decrease (discharge region Bz−). Open to.

アダプタリング５はｙ軸側を長軸、ｚ軸側を短軸とする略楕円状の円環部材であり、外周側においてフロントボディ１１に収装されるとともに、内周側においてカムリング４を収装する。ポンプ駆動時にフロントボディ１１内で回転しないよう、アダプタリング５はピン部材４０ａによりフロントボディ１１に対し回転を規制される。   The adapter ring 5 is a substantially elliptical ring member having a major axis on the y-axis side and a minor axis on the z-axis side. The adapter ring 5 is accommodated in the front body 11 on the outer peripheral side and the cam ring 4 on the inner peripheral side. Disguise. The adapter ring 5 is restricted from rotating with respect to the front body 11 by the pin member 40a so as not to rotate in the front body 11 when the pump is driven.

カムリング４は略真円の円環状部材であり、外周はアダプタリング５の短軸とほぼ同径に設けられている。したがって、略楕円状のアダプタリング５に収装されることにより、アダプタリング５内周とカムリング４外周の間には流体圧室Ａが形成され、カムリング４はアダプタリング５内においてｙ軸方向に揺動可能となる。   The cam ring 4 is a substantially perfect circular ring member, and the outer periphery thereof is provided with substantially the same diameter as the short axis of the adapter ring 5. Therefore, by being accommodated in the substantially elliptical adapter ring 5, a fluid pressure chamber A is formed between the inner periphery of the adapter ring 5 and the outer periphery of the cam ring 4, and the cam ring 4 extends in the y-axis direction within the adapter ring 5. It can swing.

また、アダプタリング内周面５３のｚ軸正方向端部にはシール部材５０（シール部材）が設けられ、ｚ軸負方向端部には揺動支持面が形成される。アダプタリング５はこの揺動支持面においてカムリング４のｚ軸負方向を係止する。   Further, a seal member 50 (seal member) is provided at the z-axis positive end of the adapter ring inner peripheral surface 53, and a swing support surface is formed at the z-axis negative end. The adapter ring 5 locks the cam ring 4 in the negative z-axis direction on the swing support surface.

揺動支持面には板部材４０が設けられ、この板部材４０の揺動支持面とシール部材５０により、カムリング４とアダプタリング５との間の流体圧室Ａはｙ軸負、正方向に画成されて第１、第２流体圧室Ａ１，Ａ２を形成する。   A plate member 40 is provided on the rocking support surface, and the fluid pressure chamber A between the cam ring 4 and the adapter ring 5 is in the y-axis negative and positive directions by the rocking support surface of the plate member 40 and the seal member 50. The first and second fluid pressure chambers A1 and A2 are defined.

ロータ３の外径はカムリング内周４１よりも小径に設けられ、カムリング４内周側に収装される。カムリング４が揺動し、ロータ３とカムリング４の相対位置が変化した場合であっても、ロータ３の外周はカムリング内周４１と当接しないよう設けられている。   The outer diameter of the rotor 3 is provided smaller than the inner diameter 41 of the cam ring, and is accommodated on the inner peripheral side of the cam ring 4. Even when the cam ring 4 swings and the relative position between the rotor 3 and the cam ring 4 changes, the outer periphery of the rotor 3 is provided so as not to contact the inner periphery 41 of the cam ring.

また、揺動によりカムリング４が最もｙ軸負方向に位置する場合、カムリング内周４１とロータ３外周との距離はｙ軸負方向側において最大となる。カムリング４が最もｙ軸正方向に位置する場合は、同様に距離Ｌはｙ軸正方向側において最小となる。   Further, when the cam ring 4 is positioned most in the y-axis negative direction due to swinging, the distance between the cam ring inner periphery 41 and the rotor 3 outer periphery is maximum on the y-axis negative direction side. When the cam ring 4 is positioned most in the y-axis positive direction, the distance L is similarly minimum on the y-axis positive direction side.

ベーン３２の径方向長さは距離Ｌの最大値よりも大きく設けられており、そのためベーン３２は、カムリング４とロータ３との相対位置によらず、常にスロット３１に挿入されつつカムリング内周４１に当接した状態を維持することとなる。これにより、ベーン３２は常時背圧室３３から背圧を受け、カムリング内周４１と液密に当接する。   The radial length of the vane 32 is larger than the maximum value of the distance L. Therefore, the vane 32 is always inserted into the slot 31 regardless of the relative position between the cam ring 4 and the rotor 3, and the cam ring inner periphery 41. It will maintain the state contact | abutted to. As a result, the vane 32 constantly receives the back pressure from the back pressure chamber 33 and comes into liquid tight contact with the cam ring inner periphery 41.

したがって、カムリング４とロータ３との間の領域は、隣り合うベーン３２によって常時液密に画成されてポンプ室Ｂを形成する。揺動によりロータ３とカムリング４が偏心状態にあれば、ロータ３の回転に伴って各ポンプ室Ｂの容積が変化する。   Therefore, the region between the cam ring 4 and the rotor 3 is always liquid-tightly defined by the adjacent vanes 32 to form the pump chamber B. If the rotor 3 and the cam ring 4 are in an eccentric state due to the swing, the volume of each pump chamber B changes as the rotor 3 rotates.

プレッシャープレート６およびリアボディ１２に設けられた吸入ポート６２，１２１および吐出ポート６３，１２２は、ロータ３の外周に沿って設けられ、各ポンプ室Ｂの容積変化により作動油の給排が行われる。   The suction ports 62 and 121 and the discharge ports 63 and 122 provided in the pressure plate 6 and the rear body 12 are provided along the outer periphery of the rotor 3, and hydraulic oil is supplied and discharged by the volume change of each pump chamber B.

アダプタリング５のｙ軸正方向端部には径方向貫通孔５１が設けられている。また、フロントボディ１１のｙ軸正方向端部にはプラグ部材挿入孔１１４が設けられ、有底カップ形状のプラグ部材７０が挿入されてフロントボディ１１、リアボディ１２外部との液密を保つ。   A radial through hole 51 is provided at the y-axis positive end of the adapter ring 5. In addition, a plug member insertion hole 114 is provided at the end of the front body 11 in the positive y-axis direction, and a bottomed cup-shaped plug member 70 is inserted to maintain liquid-tightness between the front body 11 and the rear body 12.

このプラグ部材７０の内周にはスプリング７１がｙ軸方向に伸縮可能に挿入され、アダプタリング５の径方向貫通孔５１を貫通してカムリング４に当接し、ｙ軸負方向へ付勢する。   A spring 71 is inserted into the inner periphery of the plug member 70 so as to be expandable and contractible in the y-axis direction, passes through the radial through hole 51 of the adapter ring 5, contacts the cam ring 4, and is biased in the negative y-axis direction.

スプリング７１は揺動量が最大となる方向にカムリング４を付勢し、圧力の安定しないポンプ始動時において吐出量（８ムリング４揺動位置）を安定させるものである。   The spring 71 urges the cam ring 4 in the direction in which the swing amount becomes maximum, and stabilizes the discharge amount (8 m-ring 4 swing position) at the time of pump start when the pressure is not stable.

［ダンパプーリの詳細］
図３はダンパプーリ２００の拡大断面図である。上述のようにリム部２０３内周側には環状部材２１０、弾性体２３０、およびマス部材２２０が設けられている。環状部材２１０はリム部２０３内周に固定され、マス部材２２０は弾性体２３０を介して環状部材２１０に保持される。 [Details of damper pulley]
FIG. 3 is an enlarged cross-sectional view of the damper pulley 200. As described above, the annular member 210, the elastic body 230, and the mass member 220 are provided on the inner peripheral side of the rim portion 203. The annular member 210 is fixed to the inner periphery of the rim portion 203, and the mass member 220 is held by the annular member 210 via the elastic body 230.

環状部材２１０はｘ軸正方向側面２１４がリム部２０３のｘ軸正方向開口端２０４側に露出するように設けられ、組み付け時に環状部材２１０のｘ軸正方向側面２１４を開口端２０４側（ｘ軸正方向側）から押してリム部２０３に挿入・嵌合させる。   The annular member 210 is provided so that the x-axis positive side surface 214 is exposed to the x-axis positive direction opening end 204 side of the rim 203, and the x-axis positive direction side surface 214 of the annular member 210 is attached to the opening end 204 side (x The rim portion 203 is inserted and fitted by pushing from the axial positive direction side).

弾性体２３０およびマス部材２２０を押して挿入・嵌合させる場合は弾性体２３０が変形するため組み付け性がよくないが、金属製の環状部材２１０を押すことで確実に挿入・嵌合させる構成とすることで、組み付け性を向上させる。   When the elastic body 230 and the mass member 220 are pushed and inserted and fitted, the elastic body 230 is deformed so that the assemblability is not good. However, the metal annular member 210 is pushed and inserted and fitted securely. This improves assembly.

また、環状部材２１０の内周側面２１１およびマス部材２２０の外周側面２２１はともに略Ｌ字型に形成され、環状部材２１０とマス部材２２０に挟まれる弾性体２３０も断面略Ｌ字型となる。   Further, the inner peripheral side surface 211 of the annular member 210 and the outer peripheral side surface 221 of the mass member 220 are both formed in an approximately L shape, and the elastic body 230 sandwiched between the annular member 210 and the mass member 220 also has an approximately L shape in cross section.

このため弾性体２３０は断面形状が径方向に伸びる径方向部２３２と、軸方向に伸びる軸方向部２３３とから構成されることとなる。したがって、マス部材２２０は環状部材２１０に対し径方向および軸方向に振動可能となり、ダンパプーリ２００の制振効果が向上する。   For this reason, the elastic body 230 will be comprised from the radial direction part 232 from which a cross-sectional shape extends to radial direction, and the axial direction part 233 which extends to an axial direction. Therefore, the mass member 220 can vibrate in the radial direction and the axial direction with respect to the annular member 210, and the damping effect of the damper pulley 200 is improved.

また、弾性体２３０は合成樹脂で形成され、リム部２０３の内周２０５から所定距離離間して設けられている。さらに、弾性体２３０を構成する合成樹脂材料が注入または排出される湯口２３１は、この弾性体２３０の挿入端側の軸方向端面に形成される。   The elastic body 230 is made of synthetic resin and is provided at a predetermined distance from the inner periphery 205 of the rim portion 203. Furthermore, the gate 231 into which the synthetic resin material constituting the elastic body 230 is injected or discharged is formed on the axial end surface of the elastic body 230 on the insertion end side.

リム部２０３の内周２０５から離間させることで、リム部２０３内周面に付着した油等が弾性体２３０を侵すことを防止する。また、湯口２３１部分の弾性体２３０は凹形状となるため湯口２３１部分には油等が溜まり易いが、凹形状がｘ軸方向（水平方向）に開口するように形成される。したがって、湯口２３１に進入した油はｚ軸負方向側（鉛直下方側）に流れ、湯口２３１における油等の滞留が防止される。   By separating from the inner circumference 205 of the rim portion 203, oil or the like adhering to the inner circumference surface of the rim portion 203 is prevented from attacking the elastic body 230. Further, since the elastic body 230 at the gate 231 has a concave shape, oil or the like tends to accumulate in the gate 231, but the concave shape is formed to open in the x-axis direction (horizontal direction). Therefore, the oil that has entered the gate 231 flows to the z-axis negative direction side (vertically below), and oil or the like stays in the gate 231 is prevented.

なお、環状部材２１０は中実金属部材であって、リム部２０３の内周２０５に圧入される。リム部２０３を支持するフランジ部２０２はリム部２０３のｘ軸負方向側のみを支持するため、リム部２０３はｘ軸正方向側の強度が低くなる。そのため、ベルトによってダンパプーリ２００にトルク伝達が行われる際、リム部２０３のｘ軸正方向側が内径側に変形し、ベルトが外れるおそれがある。   The annular member 210 is a solid metal member and is press-fitted into the inner periphery 205 of the rim portion 203. Since the flange portion 202 that supports the rim portion 203 supports only the rim portion 203 on the x-axis negative direction side, the rim portion 203 has low strength on the x-axis positive direction side. For this reason, when torque is transmitted to the damper pulley 200 by the belt, the x-axis positive direction side of the rim portion 203 may be deformed to the inner diameter side, and the belt may come off.

したがって、環状部材２１０を中実部材とし、リム部２０３のｘ軸正方向側から圧入されることで、環状部材２１０によってリム部２０３のｘ軸正方向側を補強し、ベルトの外れを防止する。   Therefore, the annular member 210 is a solid member, and the rim portion 203 is press-fitted from the x-axis positive direction side, thereby reinforcing the rim portion 203 on the x-axis positive direction side and preventing the belt from coming off. .

［実施例１の効果］
（１）ダンパプーリ２００は、駆動軸２に接続されるボス部２０１と、ボス部２０１から駆動軸２の外径方向に延在するフランジ部２０２と、フランジ部２０２の外周側に設けられ、環状に形成されるリム部２０３と、リム部２０３の内周側に設けられる金属製の環状部材２１０と、環状部材２１０の内周側に設けられ、断面形状が径方向に伸びる径方向部分と、軸方向に伸びる軸方向部分とから構成される弾性体２３０と、弾性体２３０の内周側に設けられた金属製のマス部材２２０とを有し、環状部材２１０は、リム部２０３の開口端２０４側に露出するように設けられることとした。 [Effect of Example 1]
(1) The damper pulley 200 is provided on the outer peripheral side of the flange portion 202, the boss portion 201 connected to the drive shaft 2, the flange portion 202 extending from the boss portion 201 in the outer diameter direction of the drive shaft 2, and A rim portion 203 formed on the inner peripheral side of the rim portion 203, a radial portion 210 provided on the inner peripheral side of the annular member 210 and having a cross-sectional shape extending in the radial direction, The elastic member 230 includes an axial portion extending in the axial direction, and a metal mass member 220 provided on the inner peripheral side of the elastic member 230, and the annular member 210 is an opening end of the rim portion 203. It was decided to be exposed to the 204 side.

これにより、弾性体２３０を軸方向と径方向両方向の振動に対応した形状とすることが可能となり。ダンピング効果をより高めることができる。また、環状部材２１０のｘ軸正方向側面２１４がリム部２０３の開口端２０４側に露出するため、組み付けの際は金属製の環状部材２１０を押し込むことにより組み付けが行われる。よって、弾性体２３０またはマス部材２２０を押し込んで組み付ける場合と比べ、組み付け作業性を向上させることができる。   Thereby, it becomes possible to make the elastic body 230 into a shape corresponding to vibrations in both the axial direction and the radial direction. The damping effect can be further enhanced. Further, since the x-axis positive side surface 214 of the annular member 210 is exposed to the opening end 204 side of the rim portion 203, the assembly is performed by pushing in the metal annular member 210 at the time of assembly. Therefore, assembly workability can be improved as compared with the case where the elastic body 230 or the mass member 220 is pushed in and assembled.

（２）ポンプボディ１０と、ポンプボディ１０に軸支された駆動軸２と、ポンプボディ１０内に設けられ、駆動軸２によって回転駆動されるロータ３と、ロータ３の周方向に複数個設けられたスロット３１に出没自在に設けられたベーン３２と、ポンプボディ１０内であって移動可能に設けられるとともに、内周側にロータ３およびベーン３２とともに複数のポンプ室Ｂを形成するカムリング４と、カムリング４の軸方向両側に設けられたリアボディ１２（第１部材）およびプレッシャープレート６（第２部材）と、リアボディ１２またはプレッシャープレート６のうち少なくとも一方側に設けられ、複数のポンプ室Ｂの容積が増大する領域に開口する吸入ポート６２，１２１と、複数のポンプ室Ｂの容積が縮小する領域に開口する吐出ポート６３，１２２と、カムリング４の外周側に設けられ、このカムリング４の外周側空間をポンプ吐出量が増大する側に設けられた第１流体圧室Ａ１と、ポンプ吐出量が減少する側に設けられた第２流体圧室Ａ２とに隔成するシール部材５０と、駆動軸２の一端側に設けられたプーリ２００と
を有する可変容量型ベーンポンプに、上記（１）のダンパプーリ２００を適用することとした。 (2) Pump body 10, drive shaft 2 pivotally supported by pump body 10, rotor 3 provided in pump body 10 and driven to rotate by drive shaft 2, and a plurality in the circumferential direction of rotor 3 A vane 32 that can be freely moved in and out of the slot 31, and a cam ring 4 that is movably provided in the pump body 10 and that forms a plurality of pump chambers B together with the rotor 3 and the vanes 32 on the inner peripheral side, The rear body 12 (first member) and the pressure plate 6 (second member) provided on both sides of the cam ring 4 in the axial direction and the rear body 12 or the pressure plate 6 are provided on at least one side of the plurality of pump chambers B. Suction ports 62 and 121 that open to areas where the volume increases, and discharge ports that open to areas where the volumes of the plurality of pump chambers B decrease 63, 122, provided on the outer peripheral side of the cam ring 4, the outer peripheral side space of the cam ring 4 is provided on the first fluid pressure chamber A1 provided on the side where the pump discharge amount increases, and on the side where the pump discharge amount decreases. The damper pulley 200 of the above (1) is applied to a variable displacement vane pump having a seal member 50 separated from the second fluid pressure chamber A2 and a pulley 200 provided at one end of the drive shaft 2. It was.

これにより、可変容量型ベーンポンプにおいても、上記（１）の作用効果を得ることができる。   Thereby, also in the variable displacement vane pump, the effect (1) can be obtained.

（３）弾性体２３０は合成樹脂で形成され、リム部２０３内周面から所定距離離間して設けられることとした。これにより、リム部２０３内周面に付着した油等が弾性体２３０を侵すことを防止することができる。   (3) The elastic body 230 is made of synthetic resin and is provided at a predetermined distance from the inner peripheral surface of the rim portion 203. Thereby, it is possible to prevent oil or the like attached to the inner peripheral surface of the rim portion 203 from invading the elastic body 230.

（５）弾性体２３０は合成樹脂で形成され、かつこの弾性体２３０を構成する合成樹脂材料が注入または排出される湯口２３１は、この弾性体２３０の挿入端側（ｘ軸負方向側）の軸方向端面に形成されることとした。湯口２３１部分の弾性体２３０は凹形状となるため油等が溜まり易いが、凹形状がｘ軸方向に開口するように形成されるため、油等が溜まるのを抑制することができる。   (5) The elastic body 230 is formed of a synthetic resin, and the gate 231 into which the synthetic resin material constituting the elastic body 230 is injected or discharged is on the insertion end side (the negative x-axis side) of the elastic body 230. It was decided to be formed on the end face in the axial direction. The elastic body 230 at the gate 231 has a concave shape, so that oil or the like is easily collected, but the concave shape is formed so as to open in the x-axis direction, so that accumulation of oil or the like can be suppressed.

（１２）環状部材２１０は中実金属部材であって、リム部２０３の内周に圧入されることとした。   (12) The annular member 210 is a solid metal member and is press-fitted into the inner periphery of the rim portion 203.

リム部２０３を支持するフランジ部２０２はリム部２０３の一端側（ｘ軸負方向側）のみを支持するため、リム部２０３の他端側（ｘ軸正方向側）の強度が低くなる。そのため、ベルトによってダンパプーリ２００にトルク伝達が行われる際、リム部２０３のｘ軸正方向側が内径側に変形し、ベルトが外れるおそれがある。したがって、環状部材２１０を中実部材とし、リム部２０３の開口端２０４側（ｘ軸正方向側）から圧入されることで、環状部材２１０によってリム部２０３のｘ軸正方向側を補強し、ベルトの外れを防止することができる。   Since the flange portion 202 that supports the rim portion 203 supports only one end side (x-axis negative direction side) of the rim portion 203, the strength of the other end side (x-axis positive direction side) of the rim portion 203 is reduced. For this reason, when torque is transmitted to the damper pulley 200 by the belt, the x-axis positive direction side of the rim portion 203 may be deformed to the inner diameter side, and the belt may come off. Therefore, the annular member 210 is a solid member, and the rim portion 203 is pressed from the opening end 204 side (x-axis positive direction side) to reinforce the rim portion 203 on the x-axis positive direction side, The belt can be prevented from coming off.

実施例２につき説明する。基本構成は実施例１と同様である。実施例２では環状部材２１０のｘ軸負方向側外周部にテーパを設けた点で異なる。   Example 2 will be described. The basic configuration is the same as that of the first embodiment. The second embodiment is different in that a taper is provided on the outer peripheral portion on the x-axis negative direction side of the annular member 210.

図４は実施例２におけるダンパプーリ２００の拡大断面図である。実施例２においては、環状部材２１０のｘ軸負方向側外周部にテーパ部２１２を設ける。このテーパ部２１２は外周側に向かって環状部材２１０のｘ軸方向幅が狭まるよう設けられ、組み付け時において環状部材２１０をリム部２０３内周側へ容易に挿入可能とする。また、リム部２０３内周面とテーパ部２１２との間に油等を保持可能となるため、弾性体２３０に油が飛散することを防止可能となる。   FIG. 4 is an enlarged cross-sectional view of the damper pulley 200 in the second embodiment. In the second embodiment, a tapered portion 212 is provided on the outer peripheral portion of the annular member 210 on the x-axis negative direction side. The tapered portion 212 is provided so that the width in the x-axis direction of the annular member 210 decreases toward the outer peripheral side, and the annular member 210 can be easily inserted into the inner peripheral side of the rim portion 203 during assembly. In addition, since oil or the like can be held between the inner peripheral surface of the rim portion 203 and the tapered portion 212, it is possible to prevent the oil from scattering on the elastic body 230.

［実施例２の効果］
（４）環状部材２１０はこの環状部材２１０の挿入端側外周側にテーパ部２１２を有することとした。これにより環状部材２１０の挿入性を向上させることができる。また、リム部２０３内周面とテーパ部との間に油等を保持し、弾性体２３０に油が飛散することを防止することができる。 [Effect of Example 2]
(4) The annular member 210 has a tapered portion 212 on the outer peripheral side of the annular member 210 on the insertion end side. Thereby, the insertability of the annular member 210 can be improved. Moreover, oil etc. can be hold | maintained between the rim | limb part 203 internal peripheral surface and a taper part, and it can prevent that oil scatters to the elastic body 230. FIG.

実施例３につき説明する。基本構成は実施例１と同様である。実施例３では、マス部材２２０のｘ軸正方向側内周部にテーパを設けた点で異なる。   Example 3 will be described. The basic configuration is the same as that of the first embodiment. The third embodiment is different in that a taper is provided on the inner peripheral portion of the mass member 220 on the x-axis positive direction side.

図５は実施例３におけるダンパプーリ２００の拡大断面図である。実施例２においてはマス部材２２０のｘ軸正方向側内周部にテーパ部２２２を設ける。このテーパ部２２２は駆動軸２側に向かって縮径し、内径側に向かってマス部材２２０のｘ軸方向幅が狭まるよう設けられている。   FIG. 5 is an enlarged cross-sectional view of the damper pulley 200 in the third embodiment. In Example 2, the taper part 222 is provided in the x-axis positive direction side inner peripheral part of the mass member 220. The taper portion 222 is provided so that the diameter thereof decreases toward the drive shaft 2 and the width of the mass member 220 in the x-axis direction decreases toward the inner diameter side.

これにより弾性体２３０の湯口２３１の凹部に溜まった油が重力によってｚ軸負方向に落下するとき、マス部材２２０のテーパ面に沿って落下しやすくなり、再度油が弾性体２３０側に付着することを防止する。   As a result, when the oil accumulated in the recess of the gate 231 of the elastic body 230 falls in the negative z-axis direction due to gravity, it easily falls along the tapered surface of the mass member 220, and the oil adheres again to the elastic body 230 side. To prevent that.

また、テーパ部２２２はポンプ１本体のフロントボディ１１とマス部材２２０と干渉しない形状に設けられている。互いの干渉を回避するとともにマス部材２２０を可能な限り大きく設定し、減衰させる周波数に対応する自由度を増加させるものである。   The tapered portion 222 is provided in a shape that does not interfere with the front body 11 and the mass member 220 of the pump 1 body. In addition to avoiding mutual interference, the mass member 220 is set as large as possible to increase the degree of freedom corresponding to the frequency to be attenuated.

［実施例３の効果］
（６）マス部材２２０の軸方向リム側端部の外周面は、リム側に向かって縮径するテーパ形状（テーパ部２２２）であることとした。弾性体２３０の湯口の凹部に溜まった油が重力によって落下するとき、マス部材２２０のテーパ部２２２に沿って落下しやすくなり、再度油が弾性体２３０側に付着することを防止できる。 [Effect of Example 3]
(6) The outer peripheral surface of the end portion on the axial rim side of the mass member 220 has a tapered shape (tapered portion 222) that decreases in diameter toward the rim side. When the oil collected in the recess of the gate of the elastic body 230 falls due to gravity, it becomes easy to fall along the tapered portion 222 of the mass member 220, and the oil can be prevented from adhering again to the elastic body 230 side.

（１０）マス部材２２０の形状がベーンポンプ１本体のフロントボディ１１と干渉しない形状であることとした。マス部材２２０の形状に対してテーパ部２２２等を設けてフロントボディ１１と干渉させないとともに、マス部材２２０を可能な限り大きくすることで減衰させる周波数に対応する自由度を増すことができる。   (10) The mass member 220 has a shape that does not interfere with the front body 11 of the main body of the vane pump 1. A taper portion 222 or the like is provided to the shape of the mass member 220 so as not to interfere with the front body 11, and the mass member 220 is made as large as possible to increase the degree of freedom corresponding to the frequency to be attenuated.

実施例４につき説明する。基本構成は実施例１と同様である。実施例４では、環状部材２１０のｘ軸正方向側面２１４をより広くリム部２０３の開口端側に露出させるため、弾性体２３０形状を変更する点で異なる。   Example 4 will be described. The basic configuration is the same as that of the first embodiment. The fourth embodiment is different in that the shape of the elastic body 230 is changed to expose the x-axis positive side surface 214 of the annular member 210 to the opening end side of the rim portion 203 more widely.

図６は実施例４におけるダンパプーリ２００の拡大断面図である。略Ｌ字型の弾性体２３０において、ｚ軸方向に延在する径方向部２３２は、ｘ軸方向に延在する軸方向部２３３に対し内径側に延在する。また径方向部２３２は内径側に開口して湯口２３１ｚを形成し、軸方向部２３３はｘ軸正方向側に開口して湯口２３１ｘを形成する。   FIG. 6 is an enlarged cross-sectional view of the damper pulley 200 in the fourth embodiment. In the substantially L-shaped elastic body 230, the radial portion 232 extending in the z-axis direction extends toward the inner diameter side with respect to the axial portion 233 extending in the x-axis direction. The radial direction portion 232 opens to the inner diameter side to form a gate 231z, and the axial direction portion 233 opens to the x-axis positive direction side to form a gate 231x.

したがって実施例４では、環状部材２１０が断面略Ｌ字型、マス部材２２０が断面長方形となり、軸方向部２３３は環状部材２１０において軸方向部２３３よりも外径側に位置することになる。これにより環状部材２１０のｘ軸正方向側面２１４をより広くリム部２０３の開口端２０４側（ｘ軸正方向側）に露出させる。   Therefore, in the fourth embodiment, the annular member 210 has a substantially L-shaped cross section, the mass member 220 has a rectangular cross section, and the axial direction portion 233 is positioned on the outer diameter side of the axial direction portion 233 in the annular member 210. As a result, the x-axis positive side surface 214 of the annular member 210 is more widely exposed to the opening end 204 side (x-axis positive direction side) of the rim portion 203.

［実施例４の効果］
（７）弾性体２３０の軸方向部分は環状部材２１０の外周側に設けられ、弾性体２３０の径方向部分は環状部材２１０の軸方向の挿入端側（ｘ軸負方向側）に設けられることとした。これにより、環状部材２１０をより広くリム部２０３の開口端側に露出させることができる。 [Effect of Example 4]
(7) The axial direction portion of the elastic body 230 is provided on the outer peripheral side of the annular member 210, and the radial direction portion of the elastic body 230 is provided on the insertion end side (x-axis negative direction side) of the annular member 210. It was. Thereby, the annular member 210 can be more widely exposed to the opening end side of the rim portion 203.

実施例５につき図７に基づき説明する。実施例５では、実施例４とは異なりマス部材２２０が断面略Ｌ字型、環状部材２１０が断面長方形となり、軸方向部２３３は環状部材２１０において軸方向部２３３よりも内径側に位置させている。実施例５にあっても、実施例１と同様の作用効果を得ることができる。   Example 5 will be described with reference to FIG. In the fifth embodiment, unlike the fourth embodiment, the mass member 220 has a substantially L-shaped cross section, the annular member 210 has a rectangular cross section, and the axial direction portion 233 is positioned closer to the inner diameter side than the axial direction portion 233 in the annular member 210. Yes. Even in the fifth embodiment, the same effects as those of the first embodiment can be obtained.

実施例６につき説明する。基本構成は実施例１と同様である。実施例１の環状部材２１０は単にリム部２０３内周に挿入。嵌合されるのみであったが、実施例６では環状部材２１０をリム部２０３の端部にカシメ固定する点で異なる。   Example 6 will be described. The basic configuration is the same as that of the first embodiment. The annular member 210 of the first embodiment is simply inserted into the inner periphery of the rim portion 203. The only difference was that the annular member 210 was caulked and fixed to the end of the rim portion 203 in Example 6.

図８は実施例６におけるダンパプーリ２００の拡大断面図、図９は図８における領域Ｄの拡大図である。環状部材２１０をリム部２０３内径側に挿入した後、リム部２０３のｘ軸正方向端部内径側にはカシメ加工が施されて肉がリム内径部２０５よりも内径側に逃げ、カシメ部２０６が形成される。これにより環状部材２１０の脱落が防止される。   FIG. 8 is an enlarged cross-sectional view of the damper pulley 200 in the sixth embodiment, and FIG. 9 is an enlarged view of a region D in FIG. After inserting the annular member 210 on the inner diameter side of the rim portion 203, the rim portion 203 is crimped on the inner diameter side of the positive end portion in the x-axis direction so that the meat escapes to the inner diameter side of the rim inner diameter portion 205. Is formed. This prevents the annular member 210 from falling off.

また、実施例６では環状部材２１０のｘ軸正方向側外周部であってカシメ部２０６と対応する位置が切り欠かれて凹部２１３を形成する。この凹部２１３が存在することにより、カシメ加工によってカシメ部２０６の肉が内径側に張り出した際にもカシメ部２０６と環状部材２１０とが干渉することがなく、リム部２０３のｘ軸方向寸法の大型化は回避される。   Further, in the sixth embodiment, a position corresponding to the caulking portion 206 on the x-axis positive direction outer peripheral portion of the annular member 210 is cut out to form the concave portion 213. Due to the presence of the recess 213, the caulking portion 206 does not interfere with the annular member 210 even when the caulking portion 206 protrudes to the inner diameter side by caulking, and the rim portion 203 has an x-axis dimension. Larger size is avoided.

［実施例６の効果］
（８）リム部２０３はこのリム部２０３の内周面であって環状部材２１０の軸方向の開口端側にカシメ部２０６を有することとした。これにより、環状部材２１０の脱落を確実に防止することができる。 [Effect of Example 6]
(8) The rim portion 203 has a caulking portion 206 on the inner peripheral surface of the rim portion 203 and on the opening end side in the axial direction of the annular member 210. Thereby, the annular member 210 can be reliably prevented from falling off.

（９）環状部材２１０の軸方向の開口端側の外周側であって、カシメ部２０６と対応する位置に凹部２１３を有することとした。凹部２１３を設けることにより、環状部材２１０がカシメ部２０６と干渉することがないため、リム部２０３の軸方向寸法が大型化することがない。   (9) The annular member 210 has a recess 213 at a position corresponding to the caulking portion 206 on the outer peripheral side on the opening end side in the axial direction. By providing the recess 213, the annular member 210 does not interfere with the caulking portion 206, so that the axial dimension of the rim portion 203 does not increase.

実施例７につき説明する。基本構成は実施例１と同様である。実施例７では、弾性体２３０を断面略Ｓ字型にした点で異なる。   Example 7 will be described. The basic configuration is the same as that of the first embodiment. The seventh embodiment is different in that the elastic body 230 has a substantially S-shaped cross section.

図１０は実施例７におけるダンパプーリ２００の拡大断面図である。実施例７の弾性体２３０は断面が複数のカーブＣ１，Ｃ２を有する略Ｓ字型であって、ｘ軸方向に延在する軸方向部２３３およびｚ軸方向に延在する径方向部２３２ａ，２３２ｂにより形成される。   FIG. 10 is an enlarged cross-sectional view of the damper pulley 200 in the seventh embodiment. The elastic body 230 according to the seventh embodiment has a substantially S-shaped cross section having a plurality of curves C1 and C2, and includes an axial portion 233 extending in the x-axis direction and a radial portion 232a extending in the z-axis direction. 232b.

軸方向部２３３によってｘ軸方向振動を吸収し、径方向部２３２ａ，２３２ｂによってｚ軸方向振動を吸収する点では実施例１〜６と同様である。複数のカーブＣ１，Ｃ２を設けて径方向部２３２ａ，２３２ｂを複数としたことにより、減衰させる周波数に対応する自由度を増加させる。   The axial direction part 233 absorbs x-axis direction vibration and the radial direction parts 232a and 232b absorb z-axis direction vibration. By providing a plurality of curves C1 and C2 and a plurality of radial portions 232a and 232b, the degree of freedom corresponding to the frequency to be attenuated is increased.

また、湯口２３１は２つともにｘ軸方向に開口させ、環状部材２１０のｘ軸方向長さを大きく設定する。これによりプーリ２００との圧入長さを大きく取ることができる。   Further, both of the gates 231 are opened in the x-axis direction, and the length of the annular member 210 in the x-axis direction is set large. Thereby, the press-fitting length with the pulley 200 can be taken large.

［実施例７の効果］
（１１）弾性体２３０は複数のカーブを有することとした。弾性体２３０のカーブを複数のカーブＣ１，Ｃ２とすることで、減衰させる周波数に対応する自由度を増加させるとともに、プーリ２００との圧入長さを大きく取ることができる。 [Effect of Example 7]
(11) The elastic body 230 has a plurality of curves. By setting the curve of the elastic body 230 to a plurality of curves C1 and C2, the degree of freedom corresponding to the frequency to be attenuated can be increased and the press-fitting length with the pulley 200 can be increased.

［他の実施例］
以上、本発明を実施するための最良の形態を各実施例に基づいて説明してきたが、本発明の具体的な構成は各実施例に限定されるものではなく、発明の要旨を逸脱しない範囲の設計変更等があっても、本発明に含まれる。

[Other embodiments]
The best mode for carrying out the present invention has been described based on each embodiment, but the specific configuration of the present invention is not limited to each embodiment and does not depart from the gist of the invention. Such design changes are included in the present invention.

実施例１におけるベーンポンプ１の軸方向断面図（図２のＩ−Ｉ断面）である。It is an axial sectional view of the vane pump 1 in Embodiment 1 (II cross section in FIG. 2). 実施例１におけるベーンポンプ１の径方向断面図（図１のＩＩ−ＩＩ断面）である。It is radial direction sectional drawing (II-II cross section of FIG. 1) of the vane pump 1 in Example 1. FIG. 実施例１におけるダンパプーリ２００の拡大断面図である。It is an expanded sectional view of damper pulley 200 in Example 1. 実施例２におけるダンパプーリ２００の拡大断面図である。It is an expanded sectional view of damper pulley 200 in Example 2. 実施例３におけるダンパプーリ２００の拡大断面図である。It is an expanded sectional view of damper pulley 200 in Example 3. 実施例４におけるダンパプーリ２００の拡大断面図である。It is an expanded sectional view of damper pulley 200 in Example 4. 実施例５におけるダンパプーリ２００の拡大断面図である。It is an expanded sectional view of damper pulley 200 in Example 5. 実施例６におけるダンパプーリ２００の拡大断面図である。It is an expanded sectional view of damper pulley 200 in Example 6. 図８における領域Ｄの拡大図である。It is an enlarged view of the area | region D in FIG. 実施例７におけるダンパプーリ２００の拡大断面図である。It is an expanded sectional view of damper pulley 200 in Example 7.

符号の説明Explanation of symbols

１ 可変容量型ベーンポンプ
２ 駆動軸
３ ロータ
４ カムリング
５ アダプタリング
６ プレッシャープレート
７ 制御バルブ
１０ ポンプボディ
１１ フロントボディ
１２ リアボディ
３１ スロット
３２ ベーン
３３ 背圧室
５０ シール部材
６２，１２１ 吸入ポート
６３，１２２ 吐出ポート
１１３ 油路
１２０ ｘ軸負方向側面
１６０ 低圧供給通路
Ａ１，Ａ２ 第１、第２流体圧室
Ｂ ポンプ室 DESCRIPTION OF SYMBOLS 1 Variable displacement type vane pump 2 Drive shaft 3 Rotor 4 Cam ring 5 Adapter ring 6 Pressure plate 7 Control valve 10 Pump body 11 Front body 12 Rear body 31 Slot 32 Vane 33 Back pressure chamber 50 Seal members 62 and 121 Suction ports 63 and 122 Discharge port 113 oil passage 120 x-axis negative side surface 160 low pressure supply passage A1, A2 first and second fluid pressure chamber B pump chamber

Claims (12)

駆動軸に接続されるボス部と、
前記ボス部から前記駆動軸の外径方向に延在するフランジ部と、
前記フランジ部の外周側に設けられ、環状に形成されるリム部と、
前記リム部の内周側に設けられる金属製の環状部材と、
前記環状部材の内周側に設けられ、断面形状が径方向に伸びる径方向部分と、軸方向に伸びる軸方向部分とから構成される弾性体と、
前記弾性体の内周側に設けられた金属製のマス部材と
を有し、
前記環状部材は、前記リム部の開口端側に露出するように設けられること
を特徴とするダンパプーリ。 A boss connected to the drive shaft;
A flange portion extending from the boss portion in the outer diameter direction of the drive shaft;
A rim portion provided on the outer peripheral side of the flange portion and formed in an annular shape;
A metal annular member provided on the inner peripheral side of the rim part;
An elastic body that is provided on the inner peripheral side of the annular member, and that is configured by a radial portion whose cross-sectional shape extends in the radial direction and an axial portion that extends in the axial direction;
A metal mass member provided on the inner peripheral side of the elastic body,
The damper pulley, wherein the annular member is provided so as to be exposed to an opening end side of the rim portion. ポンプボディと、
前記ポンプボディに軸支された駆動軸と、
前記ポンプボディ内に設けられ、前記駆動軸によって回転駆動されるロータと、
前記ロータの周方向に複数個設けられたスロットに出没自在に設けられたベーンと、
前記ポンプボディ内であって移動可能に設けられるとともに、内周側に前記ロータおよび前記ベーンとともに複数のポンプ室を形成するカムリングと、
前記カムリングの軸方向両側に設けられた第１部材および第２部材と、
前記第１部材または前記第２部材のうち少なくとも一方側に設けられ、前記複数のポンプ室の容積が増大する領域に開口する吸入ポートと、複数のポンプ室の容積が縮小する領域に開口する吐出ポートと、
前記カムリングの外周側に設けられ、このカムリングの外周側空間をポンプ吐出量が増大する側に設けられた第１流体圧室と、ポンプ吐出量が減少する側に設けられた第２流体圧室とに隔成するシール部材と、
前記駆動軸の一端側に設けられたダンパプーリと
を有する可変容量型ベーンポンプにおいて、
前記ダンパプーリは、
前記駆動軸に接続されるボス部と、
前記駆動軸から径方向に設けられるフランジ部と、
前記フランジ部の外周側に設けられ、環状に形成されるリム部と、
前記リム部の内周側に設けられる金属製の環状部材と、
前記環状部材の内周側に設けられ、断面形状が径方向に伸びる径方向部分と、軸方向に伸びる軸方向部分とから構成される弾性体と。
前記弾性体の内周側に設けられた金属製のマス部材と
を有し、
前記環状部材は、前記リム部の開口端側に露出するように設けられること
を特徴とする可変容量型ベーンポンプ。 A pump body;
A drive shaft pivotally supported by the pump body;
A rotor provided in the pump body and driven to rotate by the drive shaft;
A vane provided so as to freely appear and disappear in a plurality of slots provided in a circumferential direction of the rotor;
A cam ring that is movably provided in the pump body, and forms a plurality of pump chambers together with the rotor and the vane on the inner peripheral side;
A first member and a second member provided on both axial sides of the cam ring;
A suction port that is provided on at least one side of the first member or the second member and opens to a region where the volumes of the plurality of pump chambers increase, and discharge that opens to a region where the volumes of the plurality of pump chambers decrease Port,
A first fluid pressure chamber provided on the outer peripheral side of the cam ring, and a second fluid pressure chamber provided on a side where the pump discharge amount decreases and a first fluid pressure chamber provided on the side where the pump discharge amount increases. A sealing member that is separated into
In the variable displacement vane pump having a damper pulley provided on one end side of the drive shaft,
The damper pulley is
A boss connected to the drive shaft;
A flange portion provided radially from the drive shaft;
A rim portion provided on the outer peripheral side of the flange portion and formed in an annular shape;
A metal annular member provided on the inner peripheral side of the rim part;
An elastic body that is provided on the inner peripheral side of the annular member and includes a radial portion whose cross-sectional shape extends in the radial direction and an axial portion that extends in the axial direction.
A metal mass member provided on the inner peripheral side of the elastic body,
The variable displacement vane pump, wherein the annular member is provided so as to be exposed to an opening end side of the rim portion. 請求項１に記載のダンパプーリにおいて、
前記弾性体は合成樹脂で形成され、前記リム部内周面から所定距離離間して設けられること
を特徴とするダンパプーリ。 The damper pulley according to claim 1,
The damper pulley according to claim 1, wherein the elastic body is formed of a synthetic resin and is provided at a predetermined distance from the inner peripheral surface of the rim portion. 請求項１に記載のダンパプーリにおいて、
前記環状部材はこの環状部材の挿入端側外周側にテーパ部を有すること
を特徴とするダンパプーリ。 The damper pulley according to claim 1,
The damper pulley according to claim 1, wherein the annular member has a tapered portion on an outer peripheral side of an insertion end side of the annular member. 請求項１に記載のダンパプーリにおいて、
前記弾性体は合成樹脂で形成され、かつこの弾性体を構成する合成樹脂材料が注入または排出される湯口は、この弾性体の挿入端側の軸方向端面に形成されること
を特徴とするダンパプーリ。 The damper pulley according to claim 1,
The elastic body is formed of a synthetic resin, and a gate for pouring or discharging a synthetic resin material constituting the elastic body is formed on an axial end surface on the insertion end side of the elastic body. . 請求項５に記載のダンパプーリにおいて、
前記マス部材の軸方向前記リム側端部の外周面は、前記駆動軸側に向かって縮径するテーパ形状であること
を特徴とするダンパプーリ。 The damper pulley according to claim 5,
The damper pulley according to claim 1, wherein an outer peripheral surface of the rim side end portion in the axial direction of the mass member has a tapered shape whose diameter is reduced toward the drive shaft side. 請求項１に記載のダンパプーリにおいて、
前記弾性体の軸方向部分は前記環状部材の外周側に設けられ、前記弾性体の径方向部分は前記環状部材の軸方向の挿入端側に設けられること
を特徴とするダンパプーリ。 The damper pulley according to claim 1,
The damper pulley according to claim 1, wherein an axial portion of the elastic body is provided on an outer peripheral side of the annular member, and a radial portion of the elastic body is provided on an insertion end side in the axial direction of the annular member. 請求項７に記載のダンパプーリにおいて、
前記リム部はこのリム部の内周面であって前記環状部材の軸方向の開口端側にカシメ部を有すること
を特徴とするダンパプーリ。 The damper pulley according to claim 7,
The damper pulley according to claim 1, wherein the rim portion includes a caulking portion on an inner peripheral surface of the rim portion and on an opening end side in an axial direction of the annular member. 請求項８に記載のダンパプーリにおいて、
前記環状部材の軸方向の開口端側の外周側であって、前記カシメ部と対応する位置に凹部を有すること
を特徴とするダンパプーリ。 The damper pulley according to claim 8,
A damper pulley having a recess at a position corresponding to the caulking portion on the outer peripheral side of the annular member on the opening end side in the axial direction. 請求項１に記載のダンパプーリは、
ポンプの振動を低減するダンパプーリであって、
前記マス部材の形状が前記ポンプ本体と干渉しない形状であること
を特徴とするダンパプーリ。 The damper pulley according to claim 1 is:
A damper pulley that reduces pump vibration,
The damper pulley, wherein the mass member has a shape that does not interfere with the pump body. 請求項１に記載のダンパプーリにおいて、
前記弾性体は複数のカーブを有すること
を特徴とするダンパプーリ。 The damper pulley according to claim 1,
The damper pulley, wherein the elastic body has a plurality of curves. 請求項１ないし請求項１１のいずれか１項に記載のダンパプーリにおいて、
前記環状部材は中実金属部材であって、前記リム部の内周に圧入されること
を特徴とするダンパプーリ。 The damper pulley according to any one of claims 1 to 11,
The damper pulley according to claim 1, wherein the annular member is a solid metal member and is press-fitted into an inner periphery of the rim portion.
JP2007112454A 2007-04-23 2007-04-23 Damper pulley and variable displacement vane pump Pending JP2010185463A (en)

Priority Applications (2)

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JP2007112454A JP2010185463A (en) 2007-04-23 2007-04-23 Damper pulley and variable displacement vane pump
PCT/JP2008/057624 WO2008133212A1 (en) 2007-04-23 2008-04-18 Damper pulley, method of producing damper pulley, and variable displacement vane pump

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
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JPS63147948U (en) * 1986-10-31 1988-09-29
JPH029363U (en) * 1988-06-30 1990-01-22
JPH02261953A (en) * 1989-03-31 1990-10-24 Tokai Rubber Ind Ltd Rotor with damper
JPH04503104A (en) * 1989-08-04 1992-06-04 ウイザーズ，グラハム・レックス elastic vibration damper
JPH058355Y2 (en) * 1989-11-29 1993-03-02
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