JP2017053310A - Vane pump - Google Patents

Vane pump Download PDF

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JP2017053310A
JP2017053310A JP2015179525A JP2015179525A JP2017053310A JP 2017053310 A JP2017053310 A JP 2017053310A JP 2015179525 A JP2015179525 A JP 2015179525A JP 2015179525 A JP2015179525 A JP 2015179525A JP 2017053310 A JP2017053310 A JP 2017053310A
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pressure chamber
discharge port
pump
high pressure
discharge
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JP6454247B2 (en
Inventor
宏美 下野
Hiromi Shimono
宏美 下野
藤田　朋之
Tomoyuki Fujita
朋之 藤田
智行 中川
Satoyuki Nakagawa
智行 中川
弘俊 近藤
Hirotoshi Kondo
弘俊 近藤
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KYB Corp
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KYB Corp
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Priority to JP2015179525A priority Critical patent/JP6454247B2/en
Priority to US15/758,091 priority patent/US20180252215A1/en
Priority to PCT/JP2016/075509 priority patent/WO2017043392A1/en
Priority to CN201680049526.6A priority patent/CN108026918A/en
Priority to EP16844253.1A priority patent/EP3348838A1/en
Priority to MX2018003019A priority patent/MX2018003019A/en
Publication of JP2017053310A publication Critical patent/JP2017053310A/en
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    • 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
    • F04C15/06—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/10—Outer members for co-operation with rotary pistons; Casings
    • F01C21/104—Stators; Members defining the outer boundaries of the working chamber
    • F01C21/108—Stators; Members defining the outer boundaries of the working chamber with an axial surface, e.g. side plates
    • 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

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)

Abstract

PROBLEM TO BE SOLVED: To miniaturize a vane pump.SOLUTION: A vane pump 100 includes a plurality of discharge ports (a first discharge port 9a and a second discharge port 9b) for discharging working fluid from a pump chamber 7, a high pressure chamber 12 formed in a shape of a groove on a bottom of a pump storage recession 10a so that the working fluid is guided through the plurality of the discharge ports (the first discharge port 9a and the second discharge port 9b), and a high pressure passage 19 having an opening 19a opened to the high pressure chamber 12 and guiding the working fluid to the outside of the high pressure chamber 12. One (the first discharge port 9a) of the plurality of the discharge ports (the first discharge port 9a and the second discharge port 9b) is arranged to face the opening 19a of the high pressure passage 19, and a flow passage cross sectional area of the high pressure chamber 12 is smaller than a total flow passage cross sectional area of the plurality of the discharge ports (the first discharge port 9a and the second discharge port 9b).SELECTED DRAWING: Figure 2

Description

本発明は、ベーンポンプに関するものである。   The present invention relates to a vane pump.

特許文献１には、対称となる位置に二つの吐出ポートを有する平衡型のベーンポンプが記載されている。これら二つの吐出ポートから吐出された吐出油は、ハウジング内に設けられた円環状の圧力室を通って流量制御弁につながる流路に流入する。   Patent Document 1 describes a balanced vane pump having two discharge ports at symmetrical positions. The discharge oil discharged from these two discharge ports flows into a flow path connected to the flow control valve through an annular pressure chamber provided in the housing.

特開２００２−１６１８６９号公報JP 2002-161869 A

しかしながら、特許文献１に記載のベーンポンプでは、二つの吐出ポートから吐出された吐出油は、圧力室内で合流した後、流量制御弁につながる流路内へと流入する。この種のベーンポンプにおいては、圧力室内で合流した吐出油の圧力損失を低減するために、圧力室の流路断面積を二つの吐出ポートの流路断面積の合計以上の流路断面積にする必要があった。このため、圧力室の流路断面積を小さくすることが難しく、ベーンポンプを小型化することが難しかった。   However, in the vane pump described in Patent Document 1, the discharge oil discharged from the two discharge ports merges in the pressure chamber and then flows into the flow path connected to the flow control valve. In this type of vane pump, in order to reduce the pressure loss of the discharge oil that merges in the pressure chamber, the flow passage cross-sectional area of the pressure chamber is set to a flow passage cross-sectional area that is greater than or equal to the sum of the cross-sectional areas of the two discharge ports. There was a need. For this reason, it is difficult to reduce the cross-sectional area of the pressure chamber, and it is difficult to reduce the size of the vane pump.

本発明は、上記の問題点に鑑みてなされたものであり、ベーンポンプを小型化することを目的とする。    The present invention has been made in view of the above problems, and an object of the present invention is to reduce the size of a vane pump.

第１の発明は、ベーンポンプであって、駆動軸に連結され外周に複数のベーンを有するロータと、ロータを収容し内部にポンプ室を画成するカムリングと、ロータ及びカムリングが収容されるポンプ収容凹部が形成されたポンプボディと、ロータとポンプボディとの間に設けられるサイドプレートと、サイドプレートに形成され、ポンプ室から作動流体を吐出する複数の吐出ポートと、ポンプ収容凹部の底部に溝状に形成され、複数の吐出ポートを通じて作動流体が導かれる高圧室と、高圧室に開口する開口部を有し作動流体を高圧室の外部へ導く高圧通路と、を備え、複数の吐出ポートのうちの一つは、高圧通路の開口部に対向するように配置され、高圧室の流路断面積は、複数の吐出ポートの流路断面積の合計よりも小さいことを特徴とする。   A first invention is a vane pump, which is a rotor connected to a drive shaft and having a plurality of vanes on the outer periphery, a cam ring that houses the rotor and defines a pump chamber therein, and a pump housing that houses the rotor and the cam ring A pump body in which a recess is formed, a side plate provided between the rotor and the pump body, a plurality of discharge ports formed in the side plate for discharging the working fluid from the pump chamber, and a groove in the bottom of the pump housing recess A high-pressure chamber that is formed in a shape and through which a working fluid is guided through a plurality of discharge ports, and a high-pressure passage that has an opening that opens to the high-pressure chamber and guides the working fluid to the outside of the high-pressure chamber. One of them is disposed so as to face the opening of the high-pressure passage, and the flow passage cross-sectional area of the high-pressure chamber is smaller than the sum of the flow passage cross-sectional areas of the plurality of discharge ports. That.

第１の発明では、複数の吐出ポートのうちの一つは、高圧通路の開口部に対向するように配置される。したがって、複数の吐出ポートのうちの一つから吐出された作動流体は、直接高圧通路に流入する。これにより、高圧室には、残りの吐出ポートから導かれた作動油のみが流れることになるので、高圧室の流路断面積を複数の吐出ポートの流路断面積の合計よりも小さくできる。   In 1st invention, one of several discharge ports is arrange | positioned so as to oppose the opening part of a high voltage | pressure channel | path. Therefore, the working fluid discharged from one of the plurality of discharge ports flows directly into the high pressure passage. As a result, only the hydraulic oil guided from the remaining discharge ports flows through the high pressure chamber, so that the flow path cross-sectional area of the high pressure chamber can be made smaller than the sum of the flow path cross-sectional areas of the plurality of discharge ports.

第２の発明は、複数の吐出ポートは、高圧通路の開口部に対向するように配置される第１吐出ポートと、高圧通路の開口部から離間した位置に配置される第２吐出ポートと、からなり、高圧室は、第２吐出ポートから高圧室に導かれた作動流体が高圧室内において第１高圧室及び第２高圧室の二手に分かれて流れ、その後高圧通路の開口部おいて合流するように環状に形成され、第１高圧室及び第２高圧室の流路断面積の合計は、第２吐出ポートの流路断面積よりも大きいことを特徴とする。   According to a second aspect of the present invention, the plurality of discharge ports are a first discharge port disposed so as to face the opening of the high-pressure passage, a second discharge port disposed at a position separated from the opening of the high-pressure passage, In the high-pressure chamber, the working fluid guided from the second discharge port to the high-pressure chamber flows in the high-pressure chamber in two ways, the first high-pressure chamber and the second high-pressure chamber, and then merges at the opening of the high-pressure passage. The sum of the flow passage cross-sectional areas of the first high-pressure chamber and the second high-pressure chamber is larger than the flow passage cross-sectional area of the second discharge port.

第２の発明では、第１高圧室及び第２高圧室の流路断面積の合計は、第２吐出ポートの流路断面積よりも大きい。これにより、第２吐出ポートを通じて吐出された作動流体の高圧室による圧力損失を低減できる。また、第２吐出ポートから高圧室に導かれた作動流体は、第１高圧室及び第２高圧室の二手に分かれて流れるので、第１高圧室及び第２高圧室それぞれの流路断面積を小さくできる。   In the second aspect of the invention, the sum of the channel cross-sectional areas of the first high-pressure chamber and the second high-pressure chamber is larger than the channel cross-sectional area of the second discharge port. Thereby, the pressure loss by the high pressure chamber of the working fluid discharged through the 2nd discharge port can be reduced. In addition, since the working fluid guided from the second discharge port to the high pressure chamber flows in two ways, the first high pressure chamber and the second high pressure chamber, the cross-sectional area of each of the first high pressure chamber and the second high pressure chamber is determined. Can be small.

本発明によれば、ベーンポンプを小型化することができる。   According to the present invention, the vane pump can be reduced in size.

本発明の実施形態に係るベーンポンプの断面図である。It is sectional drawing of the vane pump which concerns on embodiment of this invention. 本発明の実施形態に係るベーンポンプのポンプ収容凹部の底部を示す平面図である。It is a top view which shows the bottom part of the pump accommodation recessed part of the vane pump which concerns on embodiment of this invention.

以下、図面を参照して、本発明の実施形態に係るベーンポンプ１００について説明する。図１はベーンポンプ１００における駆動軸に平行な断面を示す断面図である。   Hereinafter, a vane pump 100 according to an embodiment of the present invention will be described with reference to the drawings. FIG. 1 is a cross-sectional view showing a cross section parallel to the drive shaft in the vane pump 100.

ベーンポンプ１００は、車両に搭載される流体圧機器、例えば、パワーステアリング装置や変速機等の流体圧供給源として用いられる。作動流体は、オイルやその他の水溶性代替液等である。   The vane pump 100 is used as a fluid pressure supply source for a fluid pressure device mounted on a vehicle, for example, a power steering device or a transmission. The working fluid is oil or other water-soluble alternative liquid.

ベーンポンプ１００は、駆動軸１の端部にエンジン（図示せず）の動力が伝達され、駆動軸１に連結されたロータ２が回転する。   In the vane pump 100, the power of the engine (not shown) is transmitted to the end of the drive shaft 1, and the rotor 2 connected to the drive shaft 1 rotates.

ベーンポンプ１００は、ロータ２に対して径方向に往復動可能に設けられる複数のベーン３と、ロータ２を収容すると共にロータ２の回転に伴って内周のカム面４ａにベーン３の先端部が摺動するカムリング４と、を備える。   The vane pump 100 accommodates the plurality of vanes 3 provided so as to be capable of reciprocating in the radial direction with respect to the rotor 2 and the tip of the vane 3 on the inner cam surface 4 a as the rotor 2 rotates. A sliding cam ring 4.

ロータ２には、外周面に開口部を有するスリットが所定間隔をおいて放射状に形成され、そのスリットにベーン３が摺動自在に挿入される。スリットの基端側には、ポンプの吐出圧が導かれる背圧室１７が区画される。ベーン３は、背圧室１７の圧力によってスリットから抜け出る方向に押圧され、先端部がカムリング４の内周のカム面４ａに当接する。これにより、カムリング４の内部には、ロータ２の外面、カムリングのカム面４ａ、及び隣り合うベーン３によって複数のポンプ室７が画成される。   In the rotor 2, slits having openings on the outer peripheral surface are radially formed at predetermined intervals, and the vanes 3 are slidably inserted into the slits. A back pressure chamber 17 into which the pump discharge pressure is guided is defined on the base end side of the slit. The vane 3 is pressed in the direction of coming out of the slit by the pressure of the back pressure chamber 17, and the tip part abuts on the cam surface 4 a on the inner periphery of the cam ring 4. As a result, a plurality of pump chambers 7 are defined in the cam ring 4 by the outer surface of the rotor 2, the cam surface 4 a of the cam ring, and the adjacent vanes 3.

カムリング４は、内周のカム面４ａが楕円形状をした環状の部材であり、ロータ２の回転に伴ってカム面４ａを摺動する各ベーン３間によって仕切られるポンプ室７の容積を拡張する吸込領域と、ポンプ室７の容積を収縮する吐出領域と、を有する。各ポンプ室７は、ロータ２の回転に伴って拡縮する。ベーンポンプ１００は、カムリング４が２つの吸込領域と２つの吐出領域とを有する、いわゆる平衡型のベーンポンプである。   The cam ring 4 is an annular member having an inner circumferential cam surface 4 a having an elliptical shape, and expands the volume of the pump chamber 7 partitioned by the vanes 3 that slide on the cam surface 4 a as the rotor 2 rotates. It has a suction area and a discharge area that shrinks the volume of the pump chamber 7. Each pump chamber 7 expands and contracts as the rotor 2 rotates. The vane pump 100 is a so-called balanced vane pump in which the cam ring 4 has two suction regions and two discharge regions.

ロータ２及びカムリング４の一側面（図１では上側）にはポンプカバー５が当接して配置され、他側面（図１では下側）にはサイドプレート６が当接して配置される。このように、ポンプカバー５とサイドプレート６は、ロータ２及びカムリング４の両側面を挟んだ状態で配置され、ポンプ室７を密閉する。   The pump cover 5 is disposed in contact with one side surface (upper side in FIG. 1) of the rotor 2 and the cam ring 4, and the side plate 6 is disposed in contact with the other side surface (lower side in FIG. 1). In this way, the pump cover 5 and the side plate 6 are arranged with the both sides of the rotor 2 and the cam ring 4 sandwiched therebetween, and seal the pump chamber 7.

ポンプカバー５におけるロータ２が摺動する面には、カムリング４の吸込領域に対応して開口し、ポンプ室７に作動流体としての作動油を導く円弧状の２つの吸込ポート８が溝状に形成される。   On the surface of the pump cover 5 on which the rotor 2 slides, two arc-shaped suction ports 8 that open corresponding to the suction region of the cam ring 4 and guide the working oil as the working fluid into the pump chamber 7 are formed in a groove shape. It is formed.

サイドプレート６には、カムリング４の吐出領域に対応して開口し、ポンプ室７が吐出する作動油を高圧室１２へ吐出する円弧状の一対の第１吐出ポート９ａ及び第２吐出ポート９ｂが貫通して形成される。   The side plate 6 has an arc-shaped pair of first discharge port 9 a and second discharge port 9 b that open corresponding to the discharge region of the cam ring 4 and discharge the hydraulic oil discharged from the pump chamber 7 to the high-pressure chamber 12. It is formed through.

各ポンプ室７は、ロータ２の回転に伴って、カムリング４の吸込領域にて吸込ポート８を通じて作動油を吸込み、カムリング４の吐出領域にて第１吐出ポート９ａ及び第２吐出ポート９ｂを通じて作動油を吐出する。このように、各ポンプ室７は、ロータ２の回転に伴う拡縮によって作動油を給排する。   Each pump chamber 7 sucks hydraulic oil through the suction port 8 in the suction region of the cam ring 4 as the rotor 2 rotates, and operates through the first discharge port 9 a and the second discharge port 9 b in the discharge region of the cam ring 4. Discharge the oil. Thus, each pump chamber 7 supplies and discharges hydraulic oil by expansion and contraction accompanying the rotation of the rotor 2.

駆動軸１は、ブッシュ２６を介してポンプボディ１０に回転自在に支持される。ポンプボディ１０には、ロータ２、カムリング４、及びサイドプレート６が収容されるポンプ収容凹部１０ａが形成される。   The drive shaft 1 is rotatably supported by the pump body 10 via the bush 26. The pump body 10 is formed with a pump housing recess 10 a in which the rotor 2, the cam ring 4, and the side plate 6 are housed.

ポンプ収容凹部１０ａの底部には環状の溝部１５が形成される。ポンプ収容凹部１０ａの底部にはサイドプレート６が配置され、溝部１５とサイドプレート６によって環状の高圧室１２が区画される。高圧室１２には、第１吐出ポート９ａ及び第２吐出ポート９ｂを通じてポンプ室７から吐出された作動油が導かれる。なお、駆動軸１はサイドプレート６を挿通している。   An annular groove 15 is formed at the bottom of the pump housing recess 10a. The side plate 6 is disposed at the bottom of the pump housing recess 10 a, and the annular high pressure chamber 12 is defined by the groove 15 and the side plate 6. The hydraulic oil discharged from the pump chamber 7 is guided to the high pressure chamber 12 through the first discharge port 9a and the second discharge port 9b. The drive shaft 1 passes through the side plate 6.

ポンプ収容凹部１０ａ内にはサイドプレート６に積層してカムリング４が収容される。ポンプボディ１０の環状のスカート１０ｂの端面１０ｃにはポンプカバー５が締結され、ポンプ収容凹部１０ａはポンプカバー５によって封止される。   The cam ring 4 is housed in the pump housing recess 10a so as to be stacked on the side plate 6. The pump cover 5 is fastened to the end face 10 c of the annular skirt 10 b of the pump body 10, and the pump housing recess 10 a is sealed by the pump cover 5.

サイドプレート６には、カムリング４の外周面に形成された凹部（図示せず）を挿通すると共に、ポンプカバー５のピン穴５ａに挿入される２本の位置決めピン１４が設けられる。位置決めピン１４によって、カムリング４に対するポンプカバー５とサイドプレート６の相対回転が規制され、カムリング４の吸込領域とポンプカバー５の吸込ポート８との位置決め、及びカムリング４の吐出領域とサイドプレート６の第１吐出ポート９ａ、第２吐出ポート９ｂとの位置決めが行われる。   The side plate 6 is provided with two positioning pins 14 that are inserted into a pin hole 5 a of the pump cover 5 while being inserted through a recess (not shown) formed on the outer peripheral surface of the cam ring 4. The relative rotation of the pump cover 5 and the side plate 6 with respect to the cam ring 4 is restricted by the positioning pin 14, the positioning of the suction region of the cam ring 4 and the suction port 8 of the pump cover 5, and the discharge region of the cam ring 4 and the side plate 6. The first discharge port 9a and the second discharge port 9b are positioned.

また、ポンプボディ１０には、吸込ポート８に連通し吸込ポート８に作動油を導く吸込通路１１と、高圧室１２に連通し高圧室１２の作動油を高圧通路１９を通じて外部の油圧機器へと供給する吐出通路１３と、が形成される。   The pump body 10 has a suction passage 11 that communicates with the suction port 8 and guides hydraulic oil to the suction port 8, and a hydraulic fluid that communicates with the high pressure chamber 12 and communicates with the high pressure chamber 12 through the high pressure passage 19 to an external hydraulic device. A discharge passage 13 to be supplied is formed.

吐出通路１３には、油圧機器に供給される作動油の流量を制御する流量制御弁２０（図２参照）が介装される。流量制御弁２０は、ポンプボディ１０に形成された組み付け穴１８に収装される。   A flow rate control valve 20 (see FIG. 2) for controlling the flow rate of hydraulic oil supplied to the hydraulic equipment is interposed in the discharge passage 13. The flow control valve 20 is accommodated in an assembly hole 18 formed in the pump body 10.

高圧室１２の作動油は、ポンプボディ１０に形成された高圧通路１９を通じて流量制御弁２０へと導かれる。高圧通路１９は高圧室１２に開口する開口部１９ａを有し、出口部１９ｂは組み付け穴１８に開口して形成される。   The hydraulic oil in the high pressure chamber 12 is guided to the flow control valve 20 through the high pressure passage 19 formed in the pump body 10. The high pressure passage 19 has an opening 19 a that opens to the high pressure chamber 12, and the outlet 19 b is formed to open to the assembly hole 18.

次に、図２を参照して、高圧室１２及び高圧通路１９について詳しく説明する。図２はポンプボディ１０を図１における矢印Ａの方向から見た平面図であり、ポンプ収容凹部１０ａに何も収容されていない状態を示す図である。   Next, the high pressure chamber 12 and the high pressure passage 19 will be described in detail with reference to FIG. FIG. 2 is a plan view of the pump body 10 viewed from the direction of the arrow A in FIG. 1, and shows a state in which nothing is accommodated in the pump accommodating recess 10a.

図２に示すように、ポンプ収容凹部１０ａの底部には、駆動軸１が挿通する挿通穴１ａの周囲を囲むようにして環状の溝部１５が形成される。なお、溝部１５は円弧状に形成するようにしてもよい。   As shown in FIG. 2, an annular groove 15 is formed at the bottom of the pump housing recess 10a so as to surround the insertion hole 1a through which the drive shaft 1 is inserted. In addition, you may make it form the groove part 15 in circular arc shape.

サイドプレート６は、ポンプ収容凹部１０ａの底部外縁の環状段部１０ｄ上に載置されて溝部１５を封止し、高圧室１２を区画する。サイドプレート６の第１吐出ポート９ａ及び第２吐出ポート９ｂは、高圧室１２に開口し、ポンプ室７から吐出された作動油を高圧室１２に導く。第１吐出ポート９ａ及び第２吐出ポート９ｂは、駆動軸１を挟んで対向するように形成される。第１吐出ポート９ａ及び第２吐出ポート９ｂを通じて高圧室１２に導かれた作動油は、開口部１９ａから高圧通路１９へと流入する。   The side plate 6 is placed on the annular step 10d on the outer edge of the bottom of the pump housing recess 10a, seals the groove 15, and partitions the high-pressure chamber 12. The first discharge port 9 a and the second discharge port 9 b of the side plate 6 open to the high pressure chamber 12 and guide the hydraulic oil discharged from the pump chamber 7 to the high pressure chamber 12. The first discharge port 9a and the second discharge port 9b are formed to face each other with the drive shaft 1 interposed therebetween. The hydraulic fluid guided to the high pressure chamber 12 through the first discharge port 9a and the second discharge port 9b flows into the high pressure passage 19 from the opening 19a.

図２に示すように、第１吐出ポート９ａ及び第２吐出ポート９ｂのうち第１吐出ポート９ａが高圧通路１９の開口部１９ａと対向するように配置される。このように第１吐出ポート９ａが配置されることによって、第１吐出ポート９ａから高圧室１２に導かれた作動油は、高圧室１２を横切って直接高圧通路１９に流入する。一方、第２吐出ポート９ｂは、高圧通路１９の開口部１９ａから離間した位置に配置される。このように、第２吐出ポート９ｂが配置されることによって、第２吐出ポート９ｂから高圧室１２に導かれた作動油は、図２において第２吐出ポート９ｂと高圧通路１９の開口部１９ａとを周方向に沿って左側から連通する第１高圧室１２ａと右側から連通する第２高圧室１２ｂとの二手に分かれて流れる。第１高圧室１２ａ及び第２高圧室１２ｂ内を流れる作動油は、その後高圧通路１９の開口部１９ａにおいて合流し、高圧通路１９に流入する。このように、高圧室１２には、第２吐出ポート９ｂから吐出された作動油のみが流れることになる。このため、第１高圧室１２ａ及び第２高圧室１２ｂの流路断面積の合計は、第２吐出ポート９ｂを通じて吐出された作動油の高圧室１２による圧力損失を低減できるように、第２吐出ポート９ｂの流路断面積よりも大きな流路断面積が確保されていればよい。したがって、高圧室１２の流路断面積を第１吐出ポート９ａ及び第２吐出ポート９ｂの流路断面積の合計よりも小さくすることができる。   As shown in FIG. 2, the first discharge port 9 a out of the first discharge port 9 a and the second discharge port 9 b is disposed so as to face the opening 19 a of the high-pressure passage 19. By arranging the first discharge port 9 a in this way, the hydraulic oil guided from the first discharge port 9 a to the high pressure chamber 12 flows directly into the high pressure passage 19 across the high pressure chamber 12. On the other hand, the second discharge port 9 b is disposed at a position separated from the opening 19 a of the high-pressure passage 19. As described above, by arranging the second discharge port 9b, the hydraulic oil guided from the second discharge port 9b to the high-pressure chamber 12 can be obtained from the second discharge port 9b and the opening 19a of the high-pressure passage 19 in FIG. The first high pressure chamber 12a communicated from the left side along the circumferential direction and the second high pressure chamber 12b communicated from the right side. The hydraulic oil flowing in the first high pressure chamber 12 a and the second high pressure chamber 12 b then merges at the opening 19 a of the high pressure passage 19 and flows into the high pressure passage 19. Thus, only the hydraulic oil discharged from the second discharge port 9b flows into the high pressure chamber 12. For this reason, the sum of the channel cross-sectional areas of the first high pressure chamber 12a and the second high pressure chamber 12b is the second discharge so that the pressure loss of the hydraulic oil discharged through the second discharge port 9b by the high pressure chamber 12 can be reduced. It is sufficient that a flow path cross-sectional area larger than that of the port 9b is ensured. Therefore, the flow passage cross-sectional area of the high-pressure chamber 12 can be made smaller than the sum of the flow passage cross-sectional areas of the first discharge port 9a and the second discharge port 9b.

なお、高圧室１２が円弧状、例えば、高圧室１２が第１高圧室１２ａのみで構成される場合には、高圧室１２（第１高圧室１２ａ）の流路断面積は、第２吐出ポート９ｂの流路断面積よりも大きな流路断面積が確保されていればよい。   When the high pressure chamber 12 has an arc shape, for example, when the high pressure chamber 12 is configured only by the first high pressure chamber 12a, the flow path cross-sectional area of the high pressure chamber 12 (first high pressure chamber 12a) is the second discharge port. It is only necessary that a channel cross-sectional area larger than the channel cross-sectional area 9b is secured.

以上の実施形態によれば、以下に示す効果を奏する。   According to the above embodiment, there exist the effects shown below.

ベーンポンプ１００では、第１吐出ポート９ａが高圧通路１９の開口部１９ａと対向するように配置される。これにより、第１吐出ポート９ａから高圧室１２に導かれた作動油は、高圧室１２を横切って直接高圧通路１９に流入する。このため、高圧室１２には、第２吐出ポート９ｂから導かれた作動油のみが流れることになるので、高圧室１２の流路断面積を第１吐出ポート９ａ及び第２吐出ポート９ｂの流路断面積の合計よりも小さくできる。これにより、従来のベーンポンプに比べて、溝部１５の深さを浅くして高圧室１２の流路断面積を小さくしても、高圧室１２の必要な流路断面積を確保することができるので、ベーンポンプ１００を小型化することができる。   In the vane pump 100, the first discharge port 9 a is disposed so as to face the opening 19 a of the high-pressure passage 19. As a result, the hydraulic fluid guided from the first discharge port 9 a to the high pressure chamber 12 flows directly into the high pressure passage 19 across the high pressure chamber 12. For this reason, only the hydraulic oil guided from the second discharge port 9b flows into the high-pressure chamber 12, so that the flow passage cross-sectional area of the high-pressure chamber 12 is changed to the flow of the first discharge port 9a and the second discharge port 9b. It can be made smaller than the total road cross-sectional area. Thereby, compared with the conventional vane pump, even if the depth of the groove part 15 is made shallow and the flow path cross-sectional area of the high-pressure chamber 12 is reduced, the necessary flow cross-sectional area of the high-pressure chamber 12 can be secured. The vane pump 100 can be reduced in size.

また、高圧室１２が環状に形成された場合には、第２吐出ポート９ｂから高圧室１２に導かれた作動油は、第１高圧室１２ａ及び第２高圧室１２ｂの二手に分かれて流れるので、高圧室１２が円弧状に（第１高圧室１２ａのみで）形成された場合に比べて、第１高圧室１２ａ及び第２高圧室１２ｂそれぞれの流路断面積を小さくできる。これにより、ベーンポンプをより小型化できる。   In addition, when the high pressure chamber 12 is formed in an annular shape, the hydraulic oil guided from the second discharge port 9b to the high pressure chamber 12 flows in two ways, the first high pressure chamber 12a and the second high pressure chamber 12b. As compared with the case where the high pressure chamber 12 is formed in an arc shape (only the first high pressure chamber 12a), the cross-sectional areas of the first high pressure chamber 12a and the second high pressure chamber 12b can be reduced. Thereby, a vane pump can be reduced more in size.

以上のように構成された本発明の実施形態の構成、作用、及び効果をまとめて説明する。   The configuration, operation, and effect of the embodiment of the present invention configured as described above will be described together.

ベーンポンプ１００は、駆動軸１に連結され外周に複数のベーン３を有するロータ２と、ロータ２を収容し内部にポンプ室７を画成するカムリング４と、ロータ２及びカムリング４が収容されるポンプ収容凹部１０ａが形成されたポンプボディ１０と、ロータ２とポンプボディ１０との間に設けられるサイドプレート６と、サイドプレート６に形成され、ポンプ室７から作動流体を吐出する複数の吐出ポート（第１吐出ポート９ａ及び第２吐出ポート９ｂ）と、ポンプ収容凹部１０ａの底部に溝状に形成され、複数の吐出ポート（第１吐出ポート９ａ及び第２吐出ポート９ｂ）を通じて作動流体が導かれる高圧室１２と、高圧室１２に開口する開口部１９ａを有し作動流体を高圧室１２の外部へ導く高圧通路１９と、を備え、複数の吐出ポート（第１吐出ポート９ａ及び第２吐出ポート９ｂ）のうちの一つ（第１吐出ポート９ａ）は、高圧通路１９の開口部１９ａに対向するように配置され、高圧室１２の流路断面積は、複数の吐出ポート（第１吐出ポート９ａ及び第２吐出ポート９ｂ）の流路断面積の合計よりも小さいことを特徴とする。   The vane pump 100 is connected to a drive shaft 1 and has a rotor 2 having a plurality of vanes 3 on the outer periphery, a cam ring 4 that houses the rotor 2 and defines a pump chamber 7 inside, and a pump that houses the rotor 2 and the cam ring 4. The pump body 10 in which the housing recess 10 a is formed, the side plate 6 provided between the rotor 2 and the pump body 10, and a plurality of discharge ports (which are formed in the side plate 6 and discharge the working fluid from the pump chamber 7 ( The first discharge port 9a and the second discharge port 9b) are formed in a groove shape at the bottom of the pump housing recess 10a, and the working fluid is guided through the plurality of discharge ports (first discharge port 9a and second discharge port 9b). A high-pressure chamber 12 and a high-pressure passage 19 having an opening 19 a that opens to the high-pressure chamber 12 and guiding the working fluid to the outside of the high-pressure chamber 12. One of the first discharge port 9a and the second discharge port 9b (the first discharge port 9a) is disposed so as to oppose the opening 19a of the high-pressure passage 19, and the cross-sectional area of the flow path of the high-pressure chamber 12 Is characterized by being smaller than the sum of the cross-sectional areas of the plurality of discharge ports (the first discharge port 9a and the second discharge port 9b).

この構成では、第１吐出ポート９ａ及び第２吐出ポート９ｂのうちの第１吐出ポート９ａは、高圧通路１９の開口部１９ａに対向するように配置される。したがって、第１吐出ポート９ａから吐出された作動流体は、直接高圧通路１９に流入する。これにより、高圧室１２には、第２吐出ポート９ｂから導かれた作動油のみが流れることになるので、高圧室１２の流路断面積を第１吐出ポート９ａ及び第２吐出ポート９ｂの流路断面積の合計よりも小さくできる。よって、ベーンポンプ１００を小型化することができる。   In this configuration, the first discharge port 9 a out of the first discharge port 9 a and the second discharge port 9 b is disposed to face the opening 19 a of the high-pressure passage 19. Accordingly, the working fluid discharged from the first discharge port 9 a flows directly into the high pressure passage 19. As a result, only the hydraulic oil guided from the second discharge port 9b flows into the high pressure chamber 12, so that the flow passage cross-sectional area of the high pressure chamber 12 is changed to the flow of the first discharge port 9a and the second discharge port 9b. It can be made smaller than the total road cross-sectional area. Therefore, the vane pump 100 can be reduced in size.

また、ベーンポンプ１００では、複数の第１吐出ポート９ａ及び第２吐出ポート９ｂは、高圧通路１９の開口部１９ａに対向するように配置される第１吐出ポート９ａと、高圧通路１９の開口部１９ａから離間した位置に配置される第２吐出ポート９ｂと、からなり、高圧室１２は、第２吐出ポート９ｂから高圧室１２に導かれた作動流体が高圧室１２内において第１高圧室１２ａ及び第２高圧室１２ｂの二手に分かれて流れ、その後高圧通路１９の開口部１９ａおいて合流するように環状に形成され、第１高圧室１２ａ及び第２高圧室１２ｂの流路断面積の合計は、第２吐出ポート９ｂの流路断面積よりも大きいことを特徴とする。   In the vane pump 100, the plurality of first discharge ports 9 a and second discharge ports 9 b include a first discharge port 9 a disposed so as to face the opening 19 a of the high-pressure passage 19 and an opening 19 a of the high-pressure passage 19. And the second discharge port 9b disposed at a position spaced from the second discharge port 9b. The high-pressure chamber 12 includes the first high-pressure chamber 12a and the working fluid guided from the second discharge port 9b to the high-pressure chamber 12 in the high-pressure chamber 12. The second high-pressure chamber 12b is divided into two flows, and then formed into an annular shape so as to merge at the opening 19a of the high-pressure passage 19, and the total flow passage cross-sectional area of the first high-pressure chamber 12a and the second high-pressure chamber 12b is The second discharge port 9b is larger than the cross-sectional area of the flow path.

この構成では、第１高圧室１２ａ及び第２高圧室１２ｂの流路断面積の合計は、第２吐出ポート９ｂの流路断面積よりも大きい。これにより、第２吐出ポート９ｂを通じて吐出された作動油の高圧室１２による圧力損失を低減できる。また、第２吐出ポート９ｂから高圧室１２に導かれた作動流体は、第１高圧室１２ａ及び第２高圧室１２ｂの二手に分かれて流れるので、第１高圧室１２ａ及び第２高圧室１２ｂそれぞれの流路断面積を小さくできる。これにより、ベーンポンプ１００をより小型化することができる。   In this configuration, the total of the cross-sectional areas of the first high-pressure chamber 12a and the second high-pressure chamber 12b is larger than the cross-sectional area of the second discharge port 9b. Thereby, the pressure loss by the high pressure chamber 12 of the hydraulic fluid discharged through the 2nd discharge port 9b can be reduced. In addition, since the working fluid led from the second discharge port 9b to the high pressure chamber 12 flows in two ways, the first high pressure chamber 12a and the second high pressure chamber 12b, the first high pressure chamber 12a and the second high pressure chamber 12b respectively. The cross-sectional area of the channel can be reduced. Thereby, the vane pump 100 can be further reduced in size.

以上、本発明の実施形態について説明したが、上記実施形態は本発明の適用例の一部を示したに過ぎず、本発明の技術的範囲を上記実施形態の具体的構成に限定する趣旨ではない。   The embodiment of the present invention has been described above. However, the above embodiment only shows a part of application examples of the present invention, and the technical scope of the present invention is limited to the specific configuration of the above embodiment. Absent.

例えば、複数の吐出ポートは、一つが高圧通路１９に対向するように配置されていれば、三つ以上であってもよい。また、上記実施形態では、ベーンポンプ１００は流量制御弁２０を備えているが、ベーンポンプ１００は流量制御弁２０を備えていない構成であってもよい。   For example, the number of the plurality of discharge ports may be three or more as long as one is arranged so as to face the high-pressure passage 19. In the above embodiment, the vane pump 100 includes the flow control valve 20, but the vane pump 100 may not include the flow control valve 20.

１００・・・ベーンポンプ、１・・・駆動軸、２・・・ロータ、３・・・ベーン、４・・・カムリング、５・・・ポンプカバー、６・・・サイドプレート、７・・・ポンプ室、 ９ａ・・・第１吐出ポート、９ｂ・・・第２吐出ポート、１０・・・ポンプボディ、１０ａ・・・ポンプ収容凹部、 １２・・・高圧室、１２ａ・・・第１高圧室、１２ｂ・・・第２高圧室、１３・・・吐出通路、１９・・・高圧通路、１９ａ・・・開口部 DESCRIPTION OF SYMBOLS 100 ... Vane pump, 1 ... Drive shaft, 2 ... Rotor, 3 ... Vane, 4 ... Cam ring, 5 ... Pump cover, 6 ... Side plate, 7 ... Pump Chamber, 9a ... first discharge port, 9b ... second discharge port, 10 ... pump body, 10a ... pump housing recess, 12 ... high pressure chamber, 12a ... first high pressure chamber , 12b ... second high pressure chamber, 13 ... discharge passage, 19 ... high pressure passage, 19a ... opening

Claims (2)

駆動軸に連結され外周に複数のベーンを有するロータと、
前記ロータを収容し内部にポンプ室を画成するカムリングと、
前記ロータ及び前記カムリングが収容されるポンプ収容凹部が形成されたポンプボディと、
前記ロータと前記ポンプボディとの間に設けられるサイドプレートと、
前記サイドプレートに形成され、前記ポンプ室から作動流体を吐出する複数の吐出ポートと、
前記ポンプ収容凹部の底部に溝状に形成され、前記複数の吐出ポートを通じて作動流体が導かれる高圧室と、
前記高圧室に開口する開口部を有し作動流体を前記高圧室の外部へ導く高圧通路と、を備え、
前記複数の吐出ポートのうちの一つは、前記高圧通路の前記開口部に対向するように配置され、
前記高圧室の流路断面積は、前記複数の吐出ポートの流路断面積の合計よりも小さいことを特徴とするベーンポンプ。 A rotor connected to the drive shaft and having a plurality of vanes on the outer periphery;
A cam ring that houses the rotor and defines a pump chamber therein;
A pump body in which a pump housing recess for housing the rotor and the cam ring is formed;
A side plate provided between the rotor and the pump body;
A plurality of discharge ports formed in the side plate for discharging working fluid from the pump chamber;
A high-pressure chamber that is formed in a groove shape at the bottom of the pump housing recess and into which a working fluid is guided through the plurality of discharge ports;
A high-pressure passage having an opening that opens to the high-pressure chamber and guiding the working fluid to the outside of the high-pressure chamber,
One of the plurality of discharge ports is disposed to face the opening of the high-pressure passage,
The vane pump according to claim 1, wherein a flow passage cross-sectional area of the high-pressure chamber is smaller than a sum of flow passage cross-sectional areas of the plurality of discharge ports. 前記複数の吐出ポートは、前記高圧通路の前記開口部に対向するように配置される第１吐出ポートと、前記高圧通路の前記開口部から離間した位置に配置される第２吐出ポートと、からなり、
前記高圧室は、前記第２吐出ポートから前記高圧室に導かれた作動流体が前記高圧室内において第１高圧室及び第２高圧室の二手に分かれて流れ、その後前記高圧通路の前記開口部おいて合流するように環状に形成され、
前記第１高圧室及び前記第２高圧室の流路断面積の合計は、前記第２吐出ポートの流路断面積よりも大きいことを特徴とする請求項１に記載のベーンポンプ。 The plurality of discharge ports include: a first discharge port disposed to face the opening of the high-pressure passage; and a second discharge port disposed at a position spaced from the opening of the high-pressure passage. Become
In the high-pressure chamber, the working fluid led from the second discharge port to the high-pressure chamber flows in the high-pressure chamber in two ways, the first high-pressure chamber and the second high-pressure chamber, and then the opening portion of the high-pressure passage is opened. And is formed in an annular shape to merge,
2. The vane pump according to claim 1, wherein the total of the cross-sectional areas of the first high-pressure chamber and the second high-pressure chamber is larger than the cross-sectional area of the second discharge port.
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US15/758,091 US20180252215A1 (en) 2015-09-11 2016-08-31 Vane pump
PCT/JP2016/075509 WO2017043392A1 (en) 2015-09-11 2016-08-31 Vane pump
CN201680049526.6A CN108026918A (en) 2015-09-11 2016-08-31 Vane pump
EP16844253.1A EP3348838A1 (en) 2015-09-11 2016-08-31 Vane pump
MX2018003019A MX2018003019A (en) 2015-09-11 2016-08-31 Vane pump.

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JPH04148092A (en) * 1990-10-11 1992-05-21 Toyoda Mach Works Ltd Vane pump
JP2002161869A (en) * 2000-11-27 2002-06-07 Toyoda Mach Works Ltd Pump device

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JPH08226389A (en) * 1995-02-20 1996-09-03 Jidosha Kiki Co Ltd Vane pump
JPH10184563A (en) * 1996-12-24 1998-07-14 Aisin Seiki Co Ltd Vane pump
US6422845B1 (en) * 2000-12-01 2002-07-23 Delphi Technologies, Inc. Rotary hydraulic vane pump with improved undervane porting
JP2007162554A (en) * 2005-12-13 2007-06-28 Kayaba Ind Co Ltd Vane pump
JP2007278258A (en) * 2006-04-12 2007-10-25 Kayaba Ind Co Ltd Vane pump
JP5372582B2 (en) * 2009-04-17 2013-12-18 カヤバ工業株式会社 Vane pump

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JPH04148092A (en) * 1990-10-11 1992-05-21 Toyoda Mach Works Ltd Vane pump
JP2002161869A (en) * 2000-11-27 2002-06-07 Toyoda Mach Works Ltd Pump device

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US20180252215A1 (en) 2018-09-06
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EP3348838A1 (en) 2018-07-18
MX2018003019A (en) 2018-05-02

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