WO2015141466A1 - Pump device - Google Patents

Pump device Download PDF

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Publication number
WO2015141466A1
WO2015141466A1 PCT/JP2015/056337 JP2015056337W WO2015141466A1 WO 2015141466 A1 WO2015141466 A1 WO 2015141466A1 JP 2015056337 W JP2015056337 W JP 2015056337W WO 2015141466 A1 WO2015141466 A1 WO 2015141466A1
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WO
WIPO (PCT)
Prior art keywords
pump
discharge
passage
discharge passage
suction
Prior art date
Application number
PCT/JP2015/056337
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French (fr)
Japanese (ja)
Inventor
浩一朗 赤塚
藤田　朋之
智行 中川
史恭 加藤
裕希 五味
Original Assignee
カヤバ工業株式会社
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Application filed by カヤバ工業株式会社 filed Critical カヤバ工業株式会社
Publication of WO2015141466A1 publication Critical patent/WO2015141466A1/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
    • 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
    • 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
    • F04C11/00—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations
    • F04C11/001—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations of similar working principle
    • 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
    • F04C14/06—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations specially adapted for stopping, starting, idling or no-load operation
    • F04C14/065—Capacity control using a multiplicity of units or pumping capacities, e.g. multiple chambers, individually switchable or controllable
    • 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
    • F04C14/24—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
    • F04C14/26—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves using bypass channels

Definitions

  • the present invention relates to a pump device.
  • JP2010-14101A discloses a multiple vane pump in which the rotors of the first vane pump and the second vane pump are connected in parallel by being connected by a common drive shaft.
  • a switching valve for switching whether the hydraulic oil discharged from the first vane pump is supplied to the hydraulic device or returned to the suction passage is provided in the discharge passage of the first vane pump.
  • the switching valve described in JP2010-14101A has a pump port communicating with the first vane pump, a discharge port communicating with the hydraulic device side, and a suction side port communicating with the suction passage side.
  • the hydraulic fluid in the pump port is supplied to the hydraulic equipment or returned to the suction passage according to the position of the spool of the switching valve.
  • the pump port communicates with both the discharge port and the suction side port, the pressure of the hydraulic oil supplied to the hydraulic equipment will decrease. If the pump port does not communicate with both the discharge port and the suction side port, the internal pressure of the pump port rises and a surge pressure is generated.
  • An object of the present invention is to stably switch a working fluid discharged from a sub pump in a pump device having a main pump and a sub pump.
  • a pump device that supplies a working fluid to a fluid pressure device, the main pump supplying the working fluid to the fluid pressure device through a first discharge passage, and the first discharge passage.
  • a sub-pump that supplies the working fluid to the fluid pressure device through the second discharge passage, and a reverse pump that is provided in the second discharge passage and allows only the flow of the working fluid from the second discharge passage to the first discharge passage.
  • a switching valve having a blocking position for blocking the return path and an opening position for opening the return path.
  • FIG. 1 is a cross-sectional view of a pump device according to an embodiment of the present invention.
  • FIG. 2 is a plan view of a pump cartridge in the pump device according to the embodiment of the present invention.
  • FIG. 3 is a hydraulic circuit diagram of the pump device according to the embodiment of the present invention.
  • the pump device 100 is used as a hydraulic supply source for a hydraulic device mounted on a vehicle, for example, a power steering device or a transmission.
  • This embodiment demonstrates the case where the pump apparatus 100 is the structure where the main pump 101 and the subpump 102 which are two vane pumps were connected in parallel.
  • the rotor 2 of each of the main pump 101 and the sub pump 102 is connected to a common drive shaft 1 to which the power of the engine 22 (see FIG. 3) is transmitted.
  • the rotor 2 is rotated by the rotation of 1.
  • the rotor 2 rotates clockwise in FIG.
  • the hydraulic oil (working fluid) discharged from the main pump 101 is always supplied to the hydraulic equipment (fluid pressure equipment) 21 (see FIG. 3).
  • the hydraulic oil discharged from the sub pump 102 is supplied to the hydraulic equipment 21 or recirculates to the suction side in accordance with the operation of the switching valve 40 (see FIG. 3).
  • the main pump 101 and the sub-pump 102 accommodate a plurality of vanes 3 that are reciprocally movable in the radial direction with respect to the rotor 2, and the vanes 3 on the inner cam surface 4 a as the rotor 2 rotates.
  • tip part slides is provided.
  • slits 16 having openings on the outer peripheral surface are radially formed at predetermined intervals, and the vanes 3 are slidably inserted into the slits 16.
  • a back pressure chamber 17 into which the pump discharge pressure is guided is defined on the base end side of the slit 16.
  • Adjacent back pressure chambers 17 communicate with each other by an arc-shaped groove 2a formed in the rotor 2, and pump discharge pressure is always guided to the groove 2a.
  • the vane 3 is pressed in the direction of coming out of the slit 16 by the pressure of the back pressure chamber 17 and the centrifugal force due to the rotation of the rotor 2, and the tip part comes into contact with the cam surface 4 a on the inner periphery of the cam ring 4.
  • a plurality of pump chambers 7 are defined inside the cam ring 4 by the outer peripheral surface of the rotor 2, the cam surface 4 a of the cam ring, and the adjacent vanes 3.
  • the rotor 2, the vane 3, and the cam ring 4 constitute a pump cartridge 20.
  • the cam ring 4 is an annular member having an inner circumferential cam surface 4 a that is substantially elliptical, and expands the volume of the pump chamber 7 that is partitioned by the vanes 3 that slide on the cam surface 4 a as the rotor 2 rotates.
  • the center plate 5 is disposed between the pump cartridges 20 of the main pump 101 and the sub pump 102, and the side plate 6 is disposed on the side of each pump cartridge 20.
  • the pump cartridge 20 is sandwiched between the center plate 5 and the side plate 6, and the pump chamber 7 is sealed by the center plate 5 and the side plate 6.
  • the center plate 5 is formed with a suction port 8 that opens toward the suction region 4 b of the cam ring 4 and guides hydraulic oil to the pump chamber 7.
  • the side plate 6 is formed with two arc-shaped discharge ports 9 that open toward the discharge region 4c of the cam ring 4 and guide the hydraulic oil discharged from the pump chamber 7.
  • Each pump chamber 7 sucks the working oil through the suction port 8 in the suction region 4 b of the cam ring 4 and makes the sucked hydraulic oil pass through the discharge port 9 in the discharge region 4 c of the cam ring 4 in the process of one rotation of the rotor 2. After that, the hydraulic oil is sucked through the suction port 8 in the suction area 4 b of the cam ring 4, and the sucked hydraulic oil is discharged through the discharge port 9 in the discharge area 4 c of the cam ring 4.
  • each pump chamber 7 expands and contracts with the rotation of the rotor 2, and performs the suction and discharge of the hydraulic oil twice in the process of rotating the rotor 2 once.
  • the drive shaft 1 is rotatably supported by the first pump body 10 and the second pump body 11 via a bush 18.
  • the side plate 6 of the main pump 101 and the pump cartridge 20 are stacked and housed in the pump housing recess 10 a formed in the first pump body 10, and in the pump housing recess 11 a formed in the second pump body 11.
  • the center plate 5 is stacked and accommodated together with the side plate 6 of the sub pump 102 and the pump cartridge 20.
  • the main pump 101 is accommodated in the first pump body 10 and the sub pump 102 is accommodated in the second pump body 11.
  • the first pump body 10 and the second pump body 11 are fastened together with the surfaces having the openings in contact with each other, and the respective pump housing recesses 10a and 11a are sealed.
  • the cam ring 4 and the side plate 6 of the main pump 101 and the sub pump 102 are stopped by two positioning pins 19 that pass through the center plate 5.
  • the positioning pin 19 restricts the relative rotation of the center plate 5 and the side plate 6 with respect to the cam ring 4. Thereby, the positioning of the suction area 4b of the cam ring 4 and the suction port 8 of the center plate 5 and the positioning of the discharge area 4c of the cam ring 4 and the discharge port 9 of the side plate 6 are performed.
  • a high pressure chamber 12 into which hydraulic oil discharged from the discharge port 9 flows is formed.
  • the hydraulic oil in the high pressure chamber 12 is supplied to the hydraulic equipment 21 through the first discharge passage 32 and the second discharge passage 33 (see FIG. 3).
  • the hydraulic oil in the high pressure chamber 12 is guided to the arc-shaped groove 2 a of the rotor 2 through the through hole 6 a formed in the side plate 6 and is guided to each back pressure chamber 17.
  • the suction passage 31 connected to the tank 34 is connected to the suction port 8 of the main pump 101 and the sub pump 102.
  • a first discharge passage 32 is connected to the discharge port 9 of the main pump 101, and a second discharge passage 33 is connected to the discharge port 9 of the sub pump 102.
  • the second discharge passage 33 is provided so as to join the first discharge passage 32.
  • the main pump 101 sucks the hydraulic oil from the tank 34 through the suction passage 31 and supplies the hydraulic oil to the hydraulic device 21 through the first discharge passage 32, and the sub pump 102 passes the hydraulic oil from the tank 34 through the suction passage 31.
  • the hydraulic fluid is supplied to the hydraulic device 21 through the second discharge passage 33.
  • the second discharge passage 33 is provided with a check valve 35 that allows only the flow of hydraulic oil from the second discharge passage 33 to the first discharge passage 32.
  • a return passage 36 is branched and provided upstream of the check valve 35 in the second discharge passage 33.
  • the return passage 36 is for returning the hydraulic oil discharged from the sub pump 102 to the suction side.
  • the return passage 36 is provided with a switching valve 40 for switching whether the hydraulic oil discharged from the sub pump 102 is supplied to the hydraulic equipment 21 or returned to the suction passage 31.
  • the hydraulic oil discharged from the sub pump 102 is selectively guided to either the hydraulic device 21 or the suction passage 31 by switching the switching valve 40.
  • the switching valve 40 has two positions, a blocking position A for blocking the return passage 36 and an opening position B for opening the return passage 36.
  • the switching valve 40 is an electromagnetic switching valve whose position is switched by a control current output from the controller 30.
  • the switching valve 40 is set to the open position B by the biasing force of the spring 42 when the solenoid 41 is not excited, and is set to the blocking position A against the biasing force of the spring 42 when the solenoid 41 is excited.
  • the position of the switching valve 40 is switched according to, for example, the rotational speed of the engine 22 input to the controller 30, that is, the pump rotational speed that is the rotational speed of the rotor 2.
  • the switching valve 40 is not limited to an electromagnetic switching valve, and may be a pilot switching valve that is switched by a pilot hydraulic pressure.
  • the entire amount of hydraulic oil discharged from the main pump 101 is supplied to the hydraulic equipment 21 regardless of the position of the switching valve 40.
  • the switching valve 40 When the switching valve 40 is set to the cutoff position A, the hydraulic oil discharged from the sub pump 102 pushes the check valve 35 open and is supplied to the hydraulic device 21 in its entirety. Thus, even when the switching valve 40 is in the shutoff position A, the check valve 35 is opened, so that the discharge pressure of the sub pump 102 is prevented from increasing and surge pressure is prevented from being generated.
  • the check valve 35 opens, so that the discharge pressure of the sub pump 102 rises and surge pressure is prevented from being generated. Further, since the second discharge passage 33 is provided with a check valve 35 that allows only the flow of hydraulic oil from the second discharge passage 33 to the first discharge passage 32, the hydraulic oil is moved from the main pump 101 side to the sub pump 102 side. Will not flow in. Accordingly, it is possible to prevent the pressure of the hydraulic oil supplied to the hydraulic device 21 from being lowered. As described above, the hydraulic oil discharged from the sub pump 102 can be switched stably.
  • the main pump and the sub pump of the pump device 100 may be configured by one vane pump that performs the suction and discharge of the hydraulic oil twice in the process of rotating the rotor 2 once.
  • the suction region 4b and the discharge region 4c of the cam ring 4 that performs one suction discharge are configured as a main pump
  • the suction region 4b and the discharge region 4c of the cam ring 4 that performs the other suction discharge are configured as a sub pump.
  • the hydraulic circuit same as the hydraulic circuit shown in FIG. 3 can be comprised.
  • the first discharge passage 32 is connected to one discharge port 9 and the second discharge passage 33 is connected to the other discharge port 9.
  • the switching valve 40 is an electromagnetic switching valve having two positions of the cutoff position A and the opening position B.
  • the switching valve 40 may be a linear solenoid valve capable of controlling the flow passage area steplessly between the cutoff position A and the opening position B.
  • the discharge of the sub pump 102 is throttled by the switching valve 40, and the check valve 35 is pushed open by the amount corresponding to the increase of the discharge pressure of the sub pump 102 and flows into the first discharge passage 32 on the main pump 101 side.
  • the flow volume of the hydraulic fluid supplied to the hydraulic equipment 21 can be changed gently, and a pressure fluctuation can be prevented.
  • the generation of surge pressure on the sub pump 102 side can be prevented, and the pressure drop of the hydraulic oil supplied to the hydraulic device 21 can be prevented.

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

Abstract

A pump device comprising: a main pump (101) which supplies a working fluid through a first discharge passage (32) to a fluid pressure apparatus (21); a subpump (102) which supplies the working fluid through a second discharge passage (33) to the fluid pressure apparatus, said second discharge passage merging with the first discharge passage; a check valve (35) which is provided to the second discharge passage and only allows the working fluid to flow from the second discharge passage to the first discharge passage; a return passage (36) for returning the working fluid discharged from the subpump to the intake side, said return passage being provided to the second discharge passage in a manner so as to branch from the upstream side of the check valve; and a switching valve (40) which is provided to the return passage and has a blocking position in which the return passage is blocked and an opening position in which the return passage is opened.

Description

ポンプ装置Pump device
　本発明は、ポンプ装置に関するものである。 The present invention relates to a pump device.
　ＪＰ２０１０－１４１０１Ａには、第１ベーンポンプと第２ベーンポンプのロータが共通の駆動軸にて連結されることによって並列に接続された多連式ベーンポンプが開示されている。その多連式ベーンポンプでは、第１ベーンポンプの吐出通路に、第１ベーンポンプが吐出する作動油を油圧機器へ供給するか又は吸込通路へ戻すかを切り換える切換弁が設けられる。 JP2010-14101A discloses a multiple vane pump in which the rotors of the first vane pump and the second vane pump are connected in parallel by being connected by a common drive shaft. In the multiple vane pump, a switching valve for switching whether the hydraulic oil discharged from the first vane pump is supplied to the hydraulic device or returned to the suction passage is provided in the discharge passage of the first vane pump.
　ＪＰ２０１０－１４１０１Ａに記載の切換弁は、第１ベーンポンプに連通するポンプポートと、油圧機器側に連通する吐出ポートと、吸込通路側に連通する吸込側ポートと、を有する。ポンプポートの作動油は、切換弁のスプールの位置に応じて、油圧機器へ供給されるか又は吸込通路へ戻される。 The switching valve described in JP2010-14101A has a pump port communicating with the first vane pump, a discharge port communicating with the hydraulic device side, and a suction side port communicating with the suction passage side. The hydraulic fluid in the pump port is supplied to the hydraulic equipment or returned to the suction passage according to the position of the spool of the switching valve.
　この種の切換弁では、スプールの位置によっては、ポンプポートが吐出ポートと吸込側ポートの両方に連通するか、或いは、ポンプポートが吐出ポートと吸込側ポートの両方に連通しない瞬間が存在する。 In this type of switching valve, depending on the position of the spool, there is a moment when the pump port communicates with both the discharge port and the suction side port, or when the pump port does not communicate with both the discharge port and the suction side port.
　ポンプポートが吐出ポートと吸込側ポートの両方に連通すると、油圧機器へ供給される作動油の圧力が低下してしまう。また、ポンプポートが吐出ポートと吸込側ポートの両方に連通しないと、ポンプポートの内圧が上昇しサージ圧が発生してしまう。 If the pump port communicates with both the discharge port and the suction side port, the pressure of the hydraulic oil supplied to the hydraulic equipment will decrease. If the pump port does not communicate with both the discharge port and the suction side port, the internal pressure of the pump port rises and a surge pressure is generated.
　本発明は、メインポンプとサブポンプとを有するポンプ装置において、サブポンプから吐出される作動流体の切り換えを安定して行うことを目的とする。 An object of the present invention is to stably switch a working fluid discharged from a sub pump in a pump device having a main pump and a sub pump.
　本発明のある態様によれば、流体圧機器へ作動流体を供給するポンプ装置であって、第１吐出通路を通じて前記流体圧機器へ作動流体を供給するメインポンプと、前記第１吐出通路に合流する第２吐出通路を通じて前記流体圧機器へ作動流体を供給するサブポンプと、前記第２吐出通路に設けられ、前記第２吐出通路から前記第１吐出通路への作動流体の流れのみを許容する逆止弁と、前記第２吐出通路における前記逆止弁の上流側から分岐して設けられ、前記サブポンプから吐出された作動流体を吸込側へと還流させるためのリターン通路と、前記リターン通路に設けられ、前記リターン通路を遮断する遮断位置と前記リターン通路を開通する開通位置とを有する切換弁と、を備える。 According to an aspect of the present invention, there is provided a pump device that supplies a working fluid to a fluid pressure device, the main pump supplying the working fluid to the fluid pressure device through a first discharge passage, and the first discharge passage. A sub-pump that supplies the working fluid to the fluid pressure device through the second discharge passage, and a reverse pump that is provided in the second discharge passage and allows only the flow of the working fluid from the second discharge passage to the first discharge passage. A stop valve, a return passage branched from the upstream side of the check valve in the second discharge passage, and provided in the return passage for returning the working fluid discharged from the sub-pump to the suction side And a switching valve having a blocking position for blocking the return path and an opening position for opening the return path.
図１は、本発明の実施形態に係るポンプ装置の断面図である。FIG. 1 is a cross-sectional view of a pump device according to an embodiment of the present invention. 図２は、本発明の実施形態に係るポンプ装置におけるポンプカートリッジの平面図である。FIG. 2 is a plan view of a pump cartridge in the pump device according to the embodiment of the present invention. 図３は、本発明の実施形態に係るポンプ装置の油圧回路図である。FIG. 3 is a hydraulic circuit diagram of the pump device according to the embodiment of the present invention.
　以下、図面を参照して、本発明の実施形態に係るポンプ装置１００ついて説明する。 Hereinafter, a pump device 100 according to an embodiment of the present invention will be described with reference to the drawings.
　ポンプ装置１００は、車両に搭載される油圧機器、例えば、パワーステアリング装置や変速機等の油圧供給源として用いられるものである。本実施形態では、ポンプ装置１００が２つのベーンポンプであるメインポンプ１０１とサブポンプ１０２が並列に接続された構造である場合について説明する。 The pump device 100 is used as a hydraulic supply source for a hydraulic device mounted on a vehicle, for example, a power steering device or a transmission. This embodiment demonstrates the case where the pump apparatus 100 is the structure where the main pump 101 and the subpump 102 which are two vane pumps were connected in parallel.
　図１及び２に示すように、ポンプ装置１００は、エンジン２２（図３参照）の動力が伝達される共通の駆動軸１にメインポンプ１０１及びサブポンプ１０２のそれぞれのロータ２が連結され、駆動軸１の回転によってロータ２が回転するものである。ロータ２は、図２中時計方向に回転する。 As shown in FIGS. 1 and 2, in the pump device 100, the rotor 2 of each of the main pump 101 and the sub pump 102 is connected to a common drive shaft 1 to which the power of the engine 22 (see FIG. 3) is transmitted. The rotor 2 is rotated by the rotation of 1. The rotor 2 rotates clockwise in FIG.
　メインポンプ１０１から吐出される作動油（作動流体）は、常に油圧機器（流体圧機器）２１（図３参照）へ供給される。一方、サブポンプ１０２から吐出される作動油は、切換弁４０（図３参照）の作動に応じて、油圧機器２１へ供給されるか又は吸込側へと還流する。 The hydraulic oil (working fluid) discharged from the main pump 101 is always supplied to the hydraulic equipment (fluid pressure equipment) 21 (see FIG. 3). On the other hand, the hydraulic oil discharged from the sub pump 102 is supplied to the hydraulic equipment 21 or recirculates to the suction side in accordance with the operation of the switching valve 40 (see FIG. 3).
　メインポンプ１０１及びサブポンプ１０２は、ロータ２に対して径方向に往復動自在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 main pump 101 and the sub-pump 102 accommodate a plurality of vanes 3 that are reciprocally movable in the radial direction with respect to the rotor 2, and the vanes 3 on the inner cam surface 4 a as the rotor 2 rotates. The cam ring 4 with which the front-end | tip part slides is provided.
　ロータ２には、外周面に開口部を有するスリット１６が所定間隔をおいて放射状に形成され、ベーン３は、スリット１６に摺動自在に挿入される。 In the rotor 2, slits 16 having openings on the outer peripheral surface are radially formed at predetermined intervals, and the vanes 3 are slidably inserted into the slits 16.
　スリット１６の基端側には、ポンプの吐出圧が導かれる背圧室１７が画成される。隣り合う背圧室１７は、ロータ２に形成された円弧状の溝２ａによって連通し、この溝２ａにはポンプ吐出圧が常時導かれている。ベーン３は、背圧室１７の圧力及びロータ２の回転による遠心力によってスリット１６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の外周面、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。ロータ２、ベーン３、及びカムリング４によってポンプカートリッジ２０が構成される。 A back pressure chamber 17 into which the pump discharge pressure is guided is defined on the base end side of the slit 16. Adjacent back pressure chambers 17 communicate with each other by an arc-shaped groove 2a formed in the rotor 2, and pump discharge pressure is always guided to the groove 2a. The vane 3 is pressed in the direction of coming out of the slit 16 by the pressure of the back pressure chamber 17 and the centrifugal force due to the rotation of the rotor 2, and the tip part comes into contact with the cam surface 4 a on the inner periphery of the cam ring 4. Thus, a plurality of pump chambers 7 are defined inside the cam ring 4 by the outer peripheral surface of the rotor 2, the cam surface 4 a of the cam ring, and the adjacent vanes 3. The rotor 2, the vane 3, and the cam ring 4 constitute a pump cartridge 20.
　カムリング４は、内周のカム面４ａが略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４ｂと、ポンプ室７の容積を収縮する吐出領域４ｃと、を有する。 The cam ring 4 is an annular member having an inner circumferential cam surface 4 a that is substantially elliptical, and expands the volume of the pump chamber 7 that is partitioned by the vanes 3 that slide on the cam surface 4 a as the rotor 2 rotates. A suction region 4b that contracts, and a discharge region 4c that contracts the volume of the pump chamber 7.
　メインポンプ１０１及びサブポンプ１０２のポンプカートリッジ２０の間にはセンタープレート５が配置されると共に、それぞれのポンプカートリッジ２０の側部にはサイドプレート６が配置される。このように、ポンプカートリッジ２０は、センタープレート５とサイドプレート６との間に挟持され、ポンプ室７は、センタープレート５とサイドプレート６とによって密閉される。 The center plate 5 is disposed between the pump cartridges 20 of the main pump 101 and the sub pump 102, and the side plate 6 is disposed on the side of each pump cartridge 20. Thus, the pump cartridge 20 is sandwiched between the center plate 5 and the side plate 6, and the pump chamber 7 is sealed by the center plate 5 and the side plate 6.
　センタープレート５には、カムリング４の吸込領域４ｂに向けて開口し、ポンプ室７に作動油を導く吸込ポート８が形成される。 The center plate 5 is formed with a suction port 8 that opens toward the suction region 4 b of the cam ring 4 and guides hydraulic oil to the pump chamber 7.
　サイドプレート６には、カムリング４の吐出領域４ｃに向けて開口し、ポンプ室７が吐出する作動油が導かれる円弧状の２つの吐出ポート９が形成される。 The side plate 6 is formed with two arc-shaped discharge ports 9 that open toward the discharge region 4c of the cam ring 4 and guide the hydraulic oil discharged from the pump chamber 7.
　各ポンプ室７は、ロータ２が１回転する過程で、カムリング４の吸込領域４ｂにて吸込ポート８を通じて作動油を吸込み、その吸込んだ作動油をカムリング４の吐出領域４ｃにて吐出ポート９を通じて吐出し、その後、カムリング４の吸込領域４ｂにて吸込ポート８を通じて作動油を吸込み、その吸込んだ作動油をカムリング４の吐出領域４ｃにて吐出ポート９を通じて吐出する。このように、各ポンプ室７は、ロータ２の回転に伴って拡縮し、ロータ２が１回転する過程で作動油の吸込吐出を２回行う。 Each pump chamber 7 sucks the working oil through the suction port 8 in the suction region 4 b of the cam ring 4 and makes the sucked hydraulic oil pass through the discharge port 9 in the discharge region 4 c of the cam ring 4 in the process of one rotation of the rotor 2. After that, the hydraulic oil is sucked through the suction port 8 in the suction area 4 b of the cam ring 4, and the sucked hydraulic oil is discharged through the discharge port 9 in the discharge area 4 c of the cam ring 4. As described above, each pump chamber 7 expands and contracts with the rotation of the rotor 2, and performs the suction and discharge of the hydraulic oil twice in the process of rotating the rotor 2 once.
　駆動軸１は、第１ポンプボディ１０及び第２ポンプボディ１１にブッシュ１８を介して回転自在に支持される。第１ポンプボディ１０に形成されたポンプ収容凹部１０ａ内には、メインポンプ１０１のサイドプレート６とポンプカートリッジ２０が積層して収容され、第２ポンプボディ１１に形成されたポンプ収容凹部１１ａ内には、サブポンプ１０２のサイドプレート６とポンプカートリッジ２０と共にセンタープレート５が積層して収容される。このように、第１ポンプボディ１０にはメインポンプ１０１が収容され、第２ポンプボディ１１にはサブポンプ１０２が収容される。 The drive shaft 1 is rotatably supported by the first pump body 10 and the second pump body 11 via a bush 18. The side plate 6 of the main pump 101 and the pump cartridge 20 are stacked and housed in the pump housing recess 10 a formed in the first pump body 10, and in the pump housing recess 11 a formed in the second pump body 11. The center plate 5 is stacked and accommodated together with the side plate 6 of the sub pump 102 and the pump cartridge 20. Thus, the main pump 101 is accommodated in the first pump body 10 and the sub pump 102 is accommodated in the second pump body 11.
　第１ポンプボディ１０と第２ポンプボディ１１は、開口部を有する面を互いに当接して一体に締結され、それぞれのポンプ収容凹部１０ａ，１１ａが封止される。 The first pump body 10 and the second pump body 11 are fastened together with the surfaces having the openings in contact with each other, and the respective pump housing recesses 10a and 11a are sealed.
　メインポンプ１０１及びサブポンプ１０２のカムリング４及びサイドプレート６は、センタープレート５を挿通する２つの位置決めピン１９によって回り止めされる。位置決めピン１９によって、カムリング４に対するセンタープレート５とサイドプレート６の相対回転が規制される。これにより、カムリング４の吸込領域４ｂとセンタープレート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４ｃとサイドプレート６の吐出ポート９との位置決めが行われる。 The cam ring 4 and the side plate 6 of the main pump 101 and the sub pump 102 are stopped by two positioning pins 19 that pass through the center plate 5. The positioning pin 19 restricts the relative rotation of the center plate 5 and the side plate 6 with respect to the cam ring 4. Thereby, the positioning of the suction area 4b of the cam ring 4 and the suction port 8 of the center plate 5 and the positioning of the discharge area 4c of the cam ring 4 and the discharge port 9 of the side plate 6 are performed.
　第１ポンプボディ１０及び第２ポンプボディ１１には、吐出ポート９から吐出された作動油が流入する高圧室１２が形成される。高圧室１２の作動油は、第１吐出通路３２及び第２吐出通路３３（図３参照）を通じて油圧機器２１へ供給される。また、高圧室１２の作動油は、サイドプレート６に形成された貫通孔６ａを通じてロータ２の円弧状の溝２ａに導かれて各背圧室１７へ導かれる。 In the first pump body 10 and the second pump body 11, a high pressure chamber 12 into which hydraulic oil discharged from the discharge port 9 flows is formed. The hydraulic oil in the high pressure chamber 12 is supplied to the hydraulic equipment 21 through the first discharge passage 32 and the second discharge passage 33 (see FIG. 3). The hydraulic oil in the high pressure chamber 12 is guided to the arc-shaped groove 2 a of the rotor 2 through the through hole 6 a formed in the side plate 6 and is guided to each back pressure chamber 17.
　次に、図３を参照して、ポンプ装置１００の油圧回路について説明する。 Next, the hydraulic circuit of the pump device 100 will be described with reference to FIG.
　メインポンプ１０１及びサブポンプ１０２の吸込ポート８には、タンク３４に接続された吸込通路３１が接続される。メインポンプ１０１の吐出ポート９には第１吐出通路３２が接続され、サブポンプ１０２の吐出ポート９には第２吐出通路３３が接続される。第２吐出通路３３は第１吐出通路３２に合流して設けられる。 The suction passage 31 connected to the tank 34 is connected to the suction port 8 of the main pump 101 and the sub pump 102. A first discharge passage 32 is connected to the discharge port 9 of the main pump 101, and a second discharge passage 33 is connected to the discharge port 9 of the sub pump 102. The second discharge passage 33 is provided so as to join the first discharge passage 32.
　このように、メインポンプ１０１は、吸込通路３１を通じてタンク３４から作動油を吸い込み、第１吐出通路３２を通じて油圧機器２１へ作動油を供給し、サブポンプ１０２は、吸込通路３１を通じてタンク３４から作動油を吸い込み、第２吐出通路３３を通じて油圧機器２１へ作動油を供給する。 As described above, the main pump 101 sucks the hydraulic oil from the tank 34 through the suction passage 31 and supplies the hydraulic oil to the hydraulic device 21 through the first discharge passage 32, and the sub pump 102 passes the hydraulic oil from the tank 34 through the suction passage 31. The hydraulic fluid is supplied to the hydraulic device 21 through the second discharge passage 33.
　第２吐出通路３３には、第２吐出通路３３から第１吐出通路３２への作動油の流れのみを許容する逆止弁３５が設けられる。 The second discharge passage 33 is provided with a check valve 35 that allows only the flow of hydraulic oil from the second discharge passage 33 to the first discharge passage 32.
　第２吐出通路３３における逆止弁３５の上流側には、リターン通路３６が分岐して設けられる。リターン通路３６は、サブポンプ１０２から吐出された作動油を吸込側へと還流させるためのものである。 A return passage 36 is branched and provided upstream of the check valve 35 in the second discharge passage 33. The return passage 36 is for returning the hydraulic oil discharged from the sub pump 102 to the suction side.
　リターン通路３６には、サブポンプ１０２が吐出する作動油を油圧機器２１に供給するか又は吸込通路３１へ戻すかを切り換える切換弁４０が設けられる。つまり、サブポンプ１０２から吐出される作動油は、切換弁４０の切り換えによって油圧機器２１又は吸込通路３１のいずれかに選択的に導かれる。 The return passage 36 is provided with a switching valve 40 for switching whether the hydraulic oil discharged from the sub pump 102 is supplied to the hydraulic equipment 21 or returned to the suction passage 31. In other words, the hydraulic oil discharged from the sub pump 102 is selectively guided to either the hydraulic device 21 or the suction passage 31 by switching the switching valve 40.
　切換弁４０は、リターン通路３６を遮断する遮断位置Ａとリターン通路３６を開通する開通位置Ｂとの２ポジションを有する。切換弁４０は、コントローラ３０から出力される制御電流によってポジションが切り換えられる電磁式切換弁である。切換弁４０は、ソレノイド４１が非励磁のときにはバネ４２の付勢力によって開通位置Ｂに設定され、ソレノイド４１が励磁したときにはバネ４２の付勢力に抗して遮断位置Ａに設定される。切換弁４０は、例えば、コントローラ３０に入力されるエンジン２２の回転数、つまりロータ２の回転数であるポンプ回転数に応じてポジションが切り換えられる。なお、切換弁４０は電磁式切換弁には限られず、パイロット液圧によって切換作動するパイロット式切換弁でもよい。 The switching valve 40 has two positions, a blocking position A for blocking the return passage 36 and an opening position B for opening the return passage 36. The switching valve 40 is an electromagnetic switching valve whose position is switched by a control current output from the controller 30. The switching valve 40 is set to the open position B by the biasing force of the spring 42 when the solenoid 41 is not excited, and is set to the blocking position A against the biasing force of the spring 42 when the solenoid 41 is excited. The position of the switching valve 40 is switched according to, for example, the rotational speed of the engine 22 input to the controller 30, that is, the pump rotational speed that is the rotational speed of the rotor 2. The switching valve 40 is not limited to an electromagnetic switching valve, and may be a pilot switching valve that is switched by a pilot hydraulic pressure.
　次に、ポンプ装置１００の動作について説明する。 Next, the operation of the pump device 100 will be described.
　メインポンプ１０１から吐出される作動油は、切換弁４０のポジションに関係なく全量が油圧機器２１へ供給される。 The entire amount of hydraulic oil discharged from the main pump 101 is supplied to the hydraulic equipment 21 regardless of the position of the switching valve 40.
　切換弁４０が遮断位置Ａに設定された場合には、サブポンプ１０２から吐出される作動油は、逆止弁３５を押し開いて全量が油圧機器２１へ供給される。このように、切換弁４０が遮断位置Ａであっても、逆止弁３５が開くため、サブポンプ１０２の吐出圧が上昇してサージ圧が発生することが防止される。 When the switching valve 40 is set to the cutoff position A, the hydraulic oil discharged from the sub pump 102 pushes the check valve 35 open and is supplied to the hydraulic device 21 in its entirety. Thus, even when the switching valve 40 is in the shutoff position A, the check valve 35 is opened, so that the discharge pressure of the sub pump 102 is prevented from increasing and surge pressure is prevented from being generated.
　一方、切換弁４０が開通位置Ｂに設定された場合（図３に示す状態）には、サブポンプ１０２から吐出される作動油の全量又は一部は、リターン通路３６を通じて吸込側へと還流する。この際、第１吐出通路３２から第２吐出通路３３への作動流体の流れは逆止弁３５によって遮断されるため、メインポンプ１０１から吐出される作動油が切換弁４０を通じてリターン通路３６へ流入することがなく、油圧機器２１へ供給される作動油の圧力が低下することが防止される。 On the other hand, when the switching valve 40 is set to the opening position B (the state shown in FIG. 3), all or part of the hydraulic oil discharged from the sub pump 102 returns to the suction side through the return passage 36. At this time, the flow of the working fluid from the first discharge passage 32 to the second discharge passage 33 is blocked by the check valve 35, so that the hydraulic oil discharged from the main pump 101 flows into the return passage 36 through the switching valve 40. Thus, the pressure of the hydraulic oil supplied to the hydraulic device 21 is prevented from decreasing.
　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, the following effects are obtained.
　サブポンプ１０２から吐出される作動油の圧力が第１吐出通路３２の圧力よりも大きくなると逆止弁３５が開くため、サブポンプ１０２の吐出圧が上昇してサージ圧が発生することが防止される。また、第２吐出通路３３には第２吐出通路３３から第１吐出通路３２への作動油の流れのみを許容する逆止弁３５が設けられるため、メインポンプ１０１側からサブポンプ１０２側へ作動油が流入することがない。したがって、油圧機器２１へ供給される作動油の圧力が低下することが防止される。以上のように、サブポンプ１０２から吐出される作動油の切り換えを安定して行うことができる。 When the pressure of the hydraulic oil discharged from the sub pump 102 becomes larger than the pressure of the first discharge passage 32, the check valve 35 opens, so that the discharge pressure of the sub pump 102 rises and surge pressure is prevented from being generated. Further, since the second discharge passage 33 is provided with a check valve 35 that allows only the flow of hydraulic oil from the second discharge passage 33 to the first discharge passage 32, the hydraulic oil is moved from the main pump 101 side to the sub pump 102 side. Will not flow in. Accordingly, it is possible to prevent the pressure of the hydraulic oil supplied to the hydraulic device 21 from being lowered. As described above, the hydraulic oil discharged from the sub pump 102 can be switched stably.
　以下に、上記実施形態の変形例について説明する。 Hereinafter, modifications of the above embodiment will be described.
 （１）上記実施形態では、ポンプ装置１００が２つのベーンポンプであるメインポンプ１０１とサブポンプ１０２が並列に接続された構造について説明した。これに代わり、ポンプ装置１００のメインポンプとサブポンプを、ロータ２が１回転する過程で作動油の吸込吐出を２回行う１つのベーンポンプによって構成するようにしてもよい。具体的には、一方の吸込吐出を行うカムリング４の吸込領域４ｂ及び吐出領域４ｃをメインポンプとし、他方の吸込吐出を行うカムリング４の吸込領域４ｂ及び吐出領域４ｃをサブポンプとして構成する。このように構成しても、図３に示す油圧回路と同一の油圧回路を構成することができる。具体的には、ベーンポンプの２つの吐出ポート９のうち、一方の吐出ポート９に第１吐出通路３２が接続され、他方の吐出ポート９に第２吐出通路３３が接続される。 (1) In the above embodiment, the structure in which the main pump 101 and the sub pump 102 in which the pump device 100 is two vane pumps is connected in parallel has been described. Instead of this, the main pump and the sub pump of the pump device 100 may be configured by one vane pump that performs the suction and discharge of the hydraulic oil twice in the process of rotating the rotor 2 once. Specifically, the suction region 4b and the discharge region 4c of the cam ring 4 that performs one suction discharge are configured as a main pump, and the suction region 4b and the discharge region 4c of the cam ring 4 that performs the other suction discharge are configured as a sub pump. Even if comprised in this way, the hydraulic circuit same as the hydraulic circuit shown in FIG. 3 can be comprised. Specifically, of the two discharge ports 9 of the vane pump, the first discharge passage 32 is connected to one discharge port 9 and the second discharge passage 33 is connected to the other discharge port 9.
 （２）上記実施形態では、切換弁４０は、遮断位置Ａと開通位置Ｂとの２ポジションを有する電磁式切換弁である場合について説明した。これに代わり、切換弁４０は、遮断位置Ａと開通位置Ｂの間で流路面積を無段階に制御可能なリニアソレノイド弁であってもよい。その場合には、サブポンプ１０２の吐出が切換弁４０によって絞られ、サブポンプ１０２の吐出圧が上昇した分のみ逆止弁３５を押し開けてメインポンプ１０１側の第１吐出通路３２に流入する。これにより、油圧機器２１へ供給される作動油の流量を緩やかに変化させることができ、圧力変動を防止することができる。この場合でも、サブポンプ１０２側のサージ圧の発生を防止することができると共に、油圧機器２１へ供給される作動油の圧力低下を防止することができる。 (2) In the above embodiment, the case where the switching valve 40 is an electromagnetic switching valve having two positions of the cutoff position A and the opening position B has been described. Instead of this, the switching valve 40 may be a linear solenoid valve capable of controlling the flow passage area steplessly between the cutoff position A and the opening position B. In that case, the discharge of the sub pump 102 is throttled by the switching valve 40, and the check valve 35 is pushed open by the amount corresponding to the increase of the discharge pressure of the sub pump 102 and flows into the first discharge passage 32 on the main pump 101 side. Thereby, the flow volume of the hydraulic fluid supplied to the hydraulic equipment 21 can be changed gently, and a pressure fluctuation can be prevented. Even in this case, the generation of surge pressure on the sub pump 102 side can be prevented, and the pressure drop of the hydraulic oil supplied to the hydraulic device 21 can be prevented.
　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.
　本願は２０１４年３月１９日に日本国特許庁に出願された特願２０１４－０５６１４５に基づく優先権を主張し、この出願の全ての内容は参照により本明細書に組み込まれる。 This application claims priority based on Japanese Patent Application No. 2014-056145 filed with the Japan Patent Office on March 19, 2014, the entire contents of which are incorporated herein by reference.

Claims (4)

  1. 　流体圧機器へ作動流体を供給するポンプ装置であって、
    　第１吐出通路を通じて前記流体圧機器へ作動流体を供給するメインポンプと、
    　前記第１吐出通路に合流する第２吐出通路を通じて前記流体圧機器へ作動流体を供給するサブポンプと、
    　前記第２吐出通路に設けられ、前記第２吐出通路から前記第１吐出通路への作動流体の流れのみを許容する逆止弁と、
    　前記第２吐出通路における前記逆止弁の上流側から分岐して設けられ、前記サブポンプから吐出された作動流体を吸込側へと還流させるためのリターン通路と、
    　前記リターン通路に設けられ、前記リターン通路を遮断する遮断位置と前記リターン通路を開通する開通位置とを有する切換弁と、
    を備えるポンプ装置。     A pump device for supplying a working fluid to a fluid pressure device,
    A main pump for supplying a working fluid to the fluid pressure device through a first discharge passage;
    A subpump for supplying a working fluid to the fluid pressure device through a second discharge passage that merges with the first discharge passage;
    A check valve provided in the second discharge passage and allowing only a flow of the working fluid from the second discharge passage to the first discharge passage;
    A return path that is branched from the upstream side of the check valve in the second discharge path, and returns the working fluid discharged from the sub pump to the suction side;
    A switching valve provided in the return passage, having a shut-off position for blocking the return passage and an opening position for opening the return passage;
    A pump device comprising:
  2. 　請求項１に記載のポンプ装置であって、
    　前記メインポンプ及び前記サブポンプは、それぞれのロータが共通の駆動軸にて連結されることによって並列に接続された２つのベーンポンプであるポンプ装置。     The pump device according to claim 1,
    The main pump and the sub pump are pump devices that are two vane pumps connected in parallel by connecting respective rotors with a common drive shaft.
  3. 　請求項１に記載のポンプ装置であって、
    　前記メインポンプ及び前記サブポンプは、ロータが１回転する過程で作動油の吸込吐出を２回行う１つのベーンポンプによって構成され、
    　前記メインポンプは、一方の吸込吐出を行うカムリングの吸込領域及び吐出領域によって構成され、
    　前記サブポンプは、他方の吸込吐出を行うカムリングの吸込領域及び吐出領域によって構成されるポンプ装置。     The pump device according to claim 1,
    The main pump and the sub pump are constituted by one vane pump that performs suction and discharge of hydraulic oil twice in the course of one rotation of the rotor,
    The main pump is constituted by a suction region and a discharge region of a cam ring that performs one suction and discharge,
    The said sub pump is a pump apparatus comprised by the suction area | region and discharge area | region of the cam ring which performs the other suction discharge.
  4. 　請求項１に記載のポンプ装置であって、
    　前記切換弁は、リニアソレノイド弁であって、前記遮断位置と前記開通位置の間で流路面積を無段階に制御可能であるポンプ装置。     The pump device according to claim 1,
    The said switching valve is a linear solenoid valve, Comprising: The pump apparatus which can control a flow path area continuously between the said interruption | blocking position and the said opening position.
PCT/JP2015/056337 2014-03-19 2015-03-04 Pump device WO2015141466A1 (en)

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JP6672560B2 (en) * 2016-04-06 2020-03-25 株式会社 神崎高級工機製作所 Hydraulic pump unit for clutch hydraulic oil supply
KR102112756B1 (en) * 2018-11-05 2020-05-20 명화공업주식회사 Hydraulic pump device
US11519407B2 (en) * 2020-10-23 2022-12-06 Hamilton Sundstrand Corporation Dual vane pump with pre-pressurization passages

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2833285B2 (en) * 1991-09-17 1998-12-09 トヨタ自動車株式会社 Variable displacement pump
JP2002070757A (en) * 2000-08-31 2002-03-08 Tokico Ltd Variable displacement gear pump
JP2009203811A (en) * 2008-02-26 2009-09-10 Toyota Industries Corp Variable displacement type gear pump
JP2009236074A (en) * 2008-03-28 2009-10-15 Shimadzu Corp Double gear pump
JP2010014101A (en) * 2008-06-05 2010-01-21 Kayaba Ind Co Ltd Multiple vane pump

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2003028335A (en) * 2001-07-11 2003-01-29 Aisin Seiki Co Ltd Linear solenoid valve

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2833285B2 (en) * 1991-09-17 1998-12-09 トヨタ自動車株式会社 Variable displacement pump
JP2002070757A (en) * 2000-08-31 2002-03-08 Tokico Ltd Variable displacement gear pump
JP2009203811A (en) * 2008-02-26 2009-09-10 Toyota Industries Corp Variable displacement type gear pump
JP2009236074A (en) * 2008-03-28 2009-10-15 Shimadzu Corp Double gear pump
JP2010014101A (en) * 2008-06-05 2010-01-21 Kayaba Ind Co Ltd Multiple vane pump

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