WO2016027308A1 - ベーンポンプ - Google Patents

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Publication number
WO2016027308A1
WO2016027308A1 PCT/JP2014/071640 JP2014071640W WO2016027308A1 WO 2016027308 A1 WO2016027308 A1 WO 2016027308A1 JP 2014071640 W JP2014071640 W JP 2014071640W WO 2016027308 A1 WO2016027308 A1 WO 2016027308A1
Authority
WO
WIPO (PCT)
Prior art keywords
vane
cam ring
rotor
section
pump
Prior art date
Application number
PCT/JP2014/071640
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
大輔 菊地
訓一 兵藤
Original Assignee
東京計器株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 東京計器株式会社 filed Critical 東京計器株式会社
Priority to CN201480081272.7A priority Critical patent/CN106662101B/zh
Priority to PCT/JP2014/071640 priority patent/WO2016027308A1/ja
Priority to JP2016543511A priority patent/JP6307619B2/ja
Publication of WO2016027308A1 publication Critical patent/WO2016027308A1/ja

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Classifications

    • 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

Definitions

  • the present invention relates to a vane pump that performs a pump operation using a vane.
  • a pump that sucks fluid such as hydraulic oil from a tank and discharges it to a load circuit
  • a rotor that is rotatably disposed in a cam ring and a plurality of radially extending portions formed on the outer diameter side of the rotor
  • a vane pump that performs a pump operation by a vane that is slidably disposed in a radial direction in the vane storage groove.
  • suction pressure and discharge pressure are periodically introduced into an under vane chamber formed between the vane and the rotor in the vane storage groove. When pressure is generated in the discharge pressure, the vane jumps out in the outer diameter direction and is pressed against the inner peripheral surface of the cam ring.
  • a variable speed motor such as a servo motor is used to drive the pump, and the pump speed is controlled.
  • the flow rate obtained by multiplying the displacement of the vane pump by the pump speed is supplied to the load device.
  • a method of controlling the flow rate by discharging is known. According to such a vane pump control method, it is possible to control and discharge the flow rate necessary to increase the pressure of the load circuit. Further, the pressure of the load circuit can be kept constant by rotating the rotor at a very low speed and controlling the flow rate to compensate for internal leakage of the load circuit and the vane pump.
  • an intra vane is slidably disposed in an intra vane storage groove formed on an inner diameter side portion of the vane, and the vane is disposed in the intra vane storage groove.
  • a compression coil spring that urges the vane in the outer diameter direction is arranged in the intra vane chamber formed between the vane and the vane so that the vane can be reliably pressed against the cam ring even at low rotation.
  • a vane pump is known (for example, Patent Document 1).
  • the embodiment of the present invention has been made to solve the above-described problems, and can stably control the pressure of the load circuit by preventing the cam ring and the vane from separating during reverse rotation.
  • the object is to provide a vane pump.
  • a vane pump includes a cam ring having an inner peripheral surface shape including a large arc and a small arc, a rotor provided rotatably in the cam ring, and an outer surface of the rotor.
  • a plurality of vanes that are slidable in the radial direction of the rotor with respect to each of the plurality of vane storage grooves extending in the radial direction formed in the radial side portion, the cam ring, the rotor, and the plurality of vanes;
  • a suction port that communicates with a suction compartment whose volume gradually increases in the pump chamber defined by: a discharge port that communicates with a discharge compartment whose volume gradually decreases in the pump chamber; and
  • An under vane chamber into which the pressure of the suction port or the discharge port is introduced is formed between the plurality of vanes, and each of the plurality of vanes
  • a communication hole that communicates with the under vane chamber is formed, and the inner peripheral surface shape
  • FIG. 2 is a cross-sectional view of a principal part taken along line 2-2 in FIG. It is a perspective view of a vane. It is a figure which shows the front, side surface, upper surface, and bottom surface of a vane. It is the schematic which shows the internal peripheral surface shape of a cam ring. It is the schematic which shows the internal peripheral surface shape of the expand
  • FIG. 1 is a cross-sectional view showing the overall configuration of a vane pump according to an embodiment of the present invention.
  • FIG. 2 is a cross-sectional view of the principal part taken along line 2-2 in FIG.
  • the vane pump 10 includes a main body 12 that is fixed to a base or a frame (not shown), a cover 14 that is detachably connected to the main body 12, and the main body 12. And a shaft 16 disposed in the cover 14.
  • a bearing 18 is fitted into the through hole of the main body 12, and the shaft 16 is pivotally supported by the bearing 18.
  • the main body side end of the shaft 16 is connected to an electric motor (not shown), and the shaft 16 is rotationally driven by the electric motor.
  • a wear plate 20 is accommodated on the cover 14 side, and a pressure plate 22 is accommodated on the main body 12 side, and is sandwiched between the wear plate 20 and the pressure plate 22.
  • the cam ring 24 is stored. Further, the rotor 26 and the vane 28 are accommodated in the internal space.
  • the cam ring 24, the wear plate 20, and the pressure plate 22 are integrally assembled with the cover 14 by bolts (not shown), and are positioned by positioning pins 32 in the cover 14.
  • the wear plate 20 is formed with suction grooves 201a and 203 communicating with the suction port 40 and discharge grooves 202a and 204 communicating with the discharge port 42. Further, the wear plate 20 is formed with a suction groove 201b communicating with the suction port 40 at a position facing the suction groove 201a in the radial direction of the rotor 26, and facing the discharge groove 202a in the radial direction of the rotor 26. A discharge groove 202b communicating with the discharge port 42 is formed at the position. The suction groove 201b and the discharge groove 202b are not shown in FIG.
  • the pressure plate 22 has suction grooves 221 a and 223 communicating with the suction port 40 and discharge grooves 222 a and 224 communicating with the discharge port 42.
  • the pressure plate 22 is formed with a suction groove 221b communicating with the suction port 40 at a position opposed to the suction groove 221a in the radial direction of the rotor 26, and opposed to the discharge groove 222a in the radial direction of the rotor 26.
  • a discharge groove 222b communicating with the discharge port 42 is formed at the position.
  • the suction groove 221b and the discharge groove 222b are not shown in FIG.
  • the cam ring 24 has an internal space with a non-circular cross-sectional outline such as an ellipse or an eccentric circle, and the rotor 26 is rotatably disposed in the internal space.
  • the inner peripheral surface of the rotor 26 is spline-coupled to the outer peripheral surface of the shaft 16 so as not to be relatively rotatable, and the rotor 26 rotates integrally with the shaft 16.
  • the inner circumferential surface of the cam ring 24, the vane 28 adjacent to the rotation direction of the rotor 26, the outer circumferential surface of the rotor 26, the wear plate 20 and the pressure plate 22 define a pump chamber P whose volume is increased or decreased by the rotation of the rotor 26. Made.
  • a plurality of vane storage grooves 26 a are formed radially on the outer diameter side portion of the rotor 26.
  • a vane 28 is slidably disposed in the radial direction of the rotor in each vane storage groove 26a, and each of the vane storage grooves 26a extends in the radial direction and corresponds to the vane 28 in the axial direction of the rotor 26. It is formed over the length.
  • a space defined by the bottom and side surfaces thereof, the inner diameter side end of the vane 28, the wear plate 20, and the pressure plate 22 is an under vane chamber U.
  • the under vane chamber U is provided with a compression coil spring 34 that is an elastic body.
  • the compression coil spring 34 is inserted between the vane 28 and the bottom of the vane storage groove 26 a, one end is supported by the bottom of the vane storage groove 26 a, and the other end is supported at a position facing the under vane chamber U in the vane 28. Is done.
  • the compression coil spring 34 presses the vane 28 against the inner peripheral surface of the cam ring 24 by pressing the vane 28 in a direction that always separates from the bottom of the vane storage groove 26 a.
  • FIG. 3 is a perspective view of the vane.
  • FIG. 4 is a view showing the front, side, top and bottom surfaces of the vane.
  • the axial direction of the shaft is the y direction
  • the sliding direction of the vanes is the z direction
  • the direction orthogonal to the y direction and the z direction is the x direction.
  • 4A is a front view of the vane viewed from the x direction
  • FIG. 4B is a side view of the vane viewed from the y direction
  • FIG. 4C is a view from the cam ring side in the z direction.
  • FIG. 4D is a plan view of the vane as seen
  • FIG. 4D is a bottom view of the vane as seen from the shaft side in the z direction.
  • the vane 28 includes a front end 281a and a rear end 281b, and an end groove 282, a notch 283, a spring receiving portion 284, a communication hole 285, and a side groove 286 are formed. Is done.
  • Both the front end portion 281a and the rear end portion 281b are located at the end portion on the cam ring 24 side in the z direction, and as shown in FIG. 4B, the front end portion 281a is located on the front side in the forward rotation direction of the rotor 26 in the x direction.
  • the rear end portion 282b is located on the rear side in the forward rotation direction of the rotor 26 in the x direction.
  • the end groove 282 is formed over the substantially entire region in the y direction between the front end portion 281a and the rear end portion 281b at the cam ring 24 side end portion in the z direction.
  • each notch 283 is formed at the shaft side end in the z direction.
  • the spring receiving portion 284 is provided corresponding to each of the three notches 283, and each spring receiving portion 284 is a compression coil spring 34 at the cam ring 24 side end portion of the notch 283 in the z direction. It is formed in a circular shape so that one end of it can be supported.
  • the communication hole 285 is provided corresponding to each of the three spring receiving portions 284, and each communication hole 285 penetrates from the spring receiving portion 284 to the end groove 282. It is formed as a cylindrical hole.
  • the side grooves 286 are formed over substantially the entire z direction at both ends of the vane 28 in the y direction.
  • the spring receiving portion 284 receives the restoring force of the compression coil spring 34 and a part of the pressure introduced into the under vane chamber U.
  • the side groove 286 on the wear plate 20 side and the wear plate 20 define a through hole that discharges fluid from the under vane chamber U to the pump chamber P.
  • the side groove 286 on the pressure plate 22 side and pressure Through holes are defined by the plate 22.
  • the under vane chamber U and the pump chamber P communicate with each other through these through holes and the communication hole 285.
  • the cam ring 24 is configured such that either the front end 281a or the rear end 281b is always separated.
  • FIG. 5 is a schematic view showing the shape of the inner peripheral surface of the cam ring.
  • FIG. 6 is a schematic view showing the inner peripheral surface shape of the developed cam ring.
  • the shape of the inner peripheral surface of the cam ring 24 is composed of a large arc, a small arc, and a cam curve connecting them, and is formed in a substantially elliptical shape with a period of 180 degrees.
  • the points A to A ′ are formed as sections not defining the pump chamber P, and the points Y to S are The distance from the shaft center 16a of the shaft 16 to the inner peripheral surface of the cam ring 24, that is, the volume of the pump chamber P is gradually increased in the forward rotation direction and is formed as a suction section that opens to the suction port 40.
  • the volume of the pump chamber P is gradually reduced in the forward rotation direction and is formed as a pre-compression section that does not open to either the suction port 40 or the discharge port 42.
  • the discharge section is gradually reduced to the discharge port 42 and opens to the discharge port 42.
  • the suction grooves 201a, 221a, 201b, and 221b are formed at positions corresponding to the suction sections, and the discharge grooves 202a, 222a, 202b, and 222b are formed at positions corresponding to the discharge sections.
  • the precompression section is formed so that the volume of the pump chamber P is constant from the point S to the point P.
  • the precompression section of the cam ring 24 starts the precompression section during normal rotation. From the point S that is the position to the point P that is the end position of the pre-compression section during forward rotation, it is formed so as to be gradually reduced with a gradient that satisfies a predetermined condition.
  • the predetermined condition relates to the shape of the vane 28. Specifically, during forward rotation, only the front end 281a hits the cam ring 24 before the rear end 281b of the vane 28 passes through the point S. It is to touch.
  • the rear end portion 281b of the vane 28 is separated from the cam ring 24 in the precompression section during reverse rotation, and the under vane chamber U, the pump chamber P, and the like.
  • a pressure difference is generated in the air and the vane 28 is pushed up.
  • the value of the actual pressure at the time of reverse rotation is stabilized, and separation between the cam ring 24 and the vane 28 can be prevented.
  • the problem of the vane pump 10 due to the separation is improved.
  • the gradient from the S point to the P point is a minimum gradient that can push up the vane 28 to a position in contact with the cam ring 24 during reverse rotation while satisfying the above-described conditions.
  • Fu is the pressure applied to the under vane chamber U added to the restoring force of the compression coil spring 34 applied to the vane 28
  • Fp is the pressure applied to the vane 28 from the pump chamber P side
  • E is applied to one vane 28.
  • the coefficient increases as the restoring force of the compression coil spring 34 disposed increases.

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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)
PCT/JP2014/071640 2014-08-19 2014-08-19 ベーンポンプ WO2016027308A1 (ja)

Priority Applications (3)

Application Number Priority Date Filing Date Title
CN201480081272.7A CN106662101B (zh) 2014-08-19 2014-08-19 叶片泵
PCT/JP2014/071640 WO2016027308A1 (ja) 2014-08-19 2014-08-19 ベーンポンプ
JP2016543511A JP6307619B2 (ja) 2014-08-19 2014-08-19 ベーンポンプ

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2014/071640 WO2016027308A1 (ja) 2014-08-19 2014-08-19 ベーンポンプ

Publications (1)

Publication Number Publication Date
WO2016027308A1 true WO2016027308A1 (ja) 2016-02-25

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ID=55350288

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2014/071640 WO2016027308A1 (ja) 2014-08-19 2014-08-19 ベーンポンプ

Country Status (3)

Country Link
JP (1) JP6307619B2 (zh)
CN (1) CN106662101B (zh)
WO (1) WO2016027308A1 (zh)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2020026410A1 (ja) * 2018-08-02 2020-02-06 株式会社ショーワ ベーンポンプ装置

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109026681B (zh) * 2018-06-14 2019-09-17 武汉船用机械有限责任公司 一种叶片泵定子

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5135703U (zh) * 1974-09-10 1976-03-17
JPS60256580A (ja) * 1984-02-03 1985-12-18 Toyoda Mach Works Ltd ベ−ンポンプ
JP2004232465A (ja) * 2003-01-28 2004-08-19 Hitachi Unisia Automotive Ltd 双方向形のベーンポンプ及びベーンモータ
JP2012002183A (ja) * 2010-06-18 2012-01-05 Jtekt Corp ベーンポンプ
JP2014001636A (ja) * 2012-06-15 2014-01-09 Hitachi Automotive Systems Steering Ltd 可変容量形ベーンポンプ

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN2156317Y (zh) * 1993-03-18 1994-02-16 南京液压件厂 单叶片式中高压叶片泵
JP2002276563A (ja) * 2001-03-21 2002-09-25 Honda Motor Co Ltd ベーンポンプ
JP2005035117A (ja) * 2003-07-18 2005-02-10 Fuji Xerox Co Ltd メンテナンス装置及び記録装置
CN101566149A (zh) * 2009-05-07 2009-10-28 宁波威克斯液压有限公司 子母叶片泵及定子减压方法

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5135703U (zh) * 1974-09-10 1976-03-17
JPS60256580A (ja) * 1984-02-03 1985-12-18 Toyoda Mach Works Ltd ベ−ンポンプ
JP2004232465A (ja) * 2003-01-28 2004-08-19 Hitachi Unisia Automotive Ltd 双方向形のベーンポンプ及びベーンモータ
JP2012002183A (ja) * 2010-06-18 2012-01-05 Jtekt Corp ベーンポンプ
JP2014001636A (ja) * 2012-06-15 2014-01-09 Hitachi Automotive Systems Steering Ltd 可変容量形ベーンポンプ

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2020026410A1 (ja) * 2018-08-02 2020-02-06 株式会社ショーワ ベーンポンプ装置

Also Published As

Publication number Publication date
JPWO2016027308A1 (ja) 2017-06-01
CN106662101B (zh) 2018-12-04
JP6307619B2 (ja) 2018-04-04
CN106662101A (zh) 2017-05-10

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