EP1857679A1 - Pompe a palettes - Google Patents

Pompe a palettes Download PDF

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Publication number
EP1857679A1
EP1857679A1 EP06728664A EP06728664A EP1857679A1 EP 1857679 A1 EP1857679 A1 EP 1857679A1 EP 06728664 A EP06728664 A EP 06728664A EP 06728664 A EP06728664 A EP 06728664A EP 1857679 A1 EP1857679 A1 EP 1857679A1
Authority
EP
European Patent Office
Prior art keywords
plate
rotor
side plate
side plates
vane pump
Prior art date
Legal status (The legal status 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 status listed.)
Withdrawn
Application number
EP06728664A
Other languages
German (de)
English (en)
Inventor
Yoshikazu Ishii
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Toyota Motor Corp
Original Assignee
Toyota Motor Corp
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 Toyota Motor Corp filed Critical Toyota Motor Corp
Publication of EP1857679A1 publication Critical patent/EP1857679A1/fr
Withdrawn legal-status Critical Current

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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
    • F04C2/3446—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along more than one line or surface
    • 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
    • F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
    • F04C15/0023—Axial sealings for working fluid

Definitions

  • the present invention relates to a vane pump that has a pair of side plates, each side plate being disposed on opposite sides of a rotor.
  • Pumps that generate a fluid pressure include, for example, trochoidal pumps, gear pumps, and piston pumps.
  • a vane pump which is known as one mode of such a pump, is used, for example, as a pump for supplying a pressurized fluid to the power steering apparatus of an automobile.
  • this vane pump includes a cam ring that has an elliptical through hole formed therein.
  • a rotor that is rotated due to a drive shaft is accommodated inside the cam ring.
  • a plurality of radially disposed vane grooves is provided in this rotor, and a vane is accommodated in each of the vane grooves so as to be able to slide.
  • the vanes When the rotor rotates, the vanes are urged in a radial direction by, for example, centrifugal force, and rotate along with the rotor while in contact with the cam surface on the inner circumference of the cam ring.
  • the volume of the working chamber changes, this working chamber being defined by adjacent vanes and the cam surface on the inner circumference of the cam ring.
  • side plates that form a portion of the working chamber may be disposed on opposite sides the rotor and the vanes.
  • side clearance In order to generate a high pressure by using a vane pump of this type, it is important to reduce and maintain the gaps between the rotor and vanes and these side plates (referred to as "side clearance").
  • various technologies have been proposed that have the object of reducing and maintaining this side clearance.
  • Patent Document 1 the following technology has been proposed.
  • a pressurized fluid having a pressure Pout that is discharged from the working chamber is caused to flow, at the pump intake section, into the vane back pressure chambers that are provided at the bottom of each vane groove.
  • the pressurized fluid having this pressure Pout is further pressurized to a pressure Pv when each of the vanes in the pump discharge section is pressed against the inner circumferential surface of the cam ring. Subsequently, the pressurized fluid having this pressure Pv flows into a back pressure chamber that is formed by the movable side plate.
  • Patent Document 1 Japanese Patent Application Publication No. 6-207587
  • a stationary side plate may be deformed due to the pressure inside the pump during the operation of the pump.
  • the side clearances increase due to this deformation, the amount of leakage of the pressurized fluid increases.
  • the pump cannot supply a fluid that has been highly pressurized.
  • the vane pump according to the present invention is provided, inside a case, with a cam ring, a rotor that is disposed inside the cam ring so as to be freely rotatable, a plurality of vanes that is accommodated in a plurality of vane grooves that is radially formed in the rotor and slides along the cam surface of the cam ring accompanying the rotation of the rotor, and side plates that are disposed on opposite sides of the rotor and the vanes, and is characterized in that the side plates have an identical rigidity and are disposed symmetrically with respect to the rotor.
  • the side plates that are fastened to opposite side surfaces of the rotor and the vanes have a symmetrical structure that encloses the rotor.
  • minute deformations in proximity to the axial center that occur when fastened by bolts to the side surface of the cam ring and deformations that are caused by pressure inside the pump become symmetrical because the rotor is enclosed between side plates.
  • the symmetry between the side plates can be ensured in this manner, it is possible to maintain a pressure distribution of the pressurized fluid that is applied to opposite side surfaces of the rotor and the vanes to be symmetrical. Therefore, it is possible to suppress advantageously the deformation of the rotor and the vanes, and it is possible to suppress scorching due to a high surface pressure state that is produced by the rotor and the vanes coming into contact with the side plates.
  • each of combination side plates may be formed by identical materials and by identical shapes. Thereby, it is possible to further increase the symmetry between a pair of first plates that is deformed due to the pressure inside the pump.
  • the side plates may be a combination side plate made by a first plate and a second plate, and a back pressure chamber into which the pressurized fluid is caused to flow may be provided between the first plate and the second plate.
  • the vane pump according to the present invention is provided, in a case, with a cam ring, a rotor that is disposed inside the cam ring so as to be freely rotatable, a plurality of vanes that is accommodated in a plurality of vane grooves that is radially disposed in the rotor and slides along the cam surface of the cam ring accompanying the rotation of the rotor, and side plates that are disposed on opposite sides of the rotor and the vanes, characterized in that a bolt is inserted into a center hole in at least one of the side plates.
  • the present invention it is possible to apply a compression force on the first plate by tightening a linking bolt that fastens the first plate and the second plate.
  • a linking bolt that fastens the first plate and the second plate.
  • each of the side plates may be a linked combination side plate in which a first plate and a second plate are held together by a linking bolt, the linking bolt is inserted into a center hole in the second plate, and fastened in an internal thread that is formed in a center hole in the first plate.
  • a linking bolt is inserted into a center hole in the second plate, and fastened in an internal thread that is formed in a center hole in the first plate.
  • the linking bolt may be a hollow bolt.
  • a back pressure chamber into which pressurized fluid is caused to flow may be provided between the first plate and the second plate.
  • the linked combination side plates and the cam ring may be fastened by fastening bolts that are disposed in the outer circumferential portion thereof, and a compression force may be applied in advance to the center hole vicinity of the first plate by tightening the linking bolt.
  • a compression force may be applied in advance to the center hole vicinity of the first plate by tightening the linking bolt.
  • both of the side plates may be linked combination side plates.
  • these side plates have a symmetrical structure that encloses the rotor.
  • one of the side plates may be the linked combination side plate, and the other may be the combination side plate.
  • the linking bolt by tightening the linking bolt in advance by an amount of tightening that allows for the deformation of the other combination side plate, it is possible to ensure the symmetry of the distribution of the fluid pressure that is applied to opposite sides of the rotor and the vanes. Thereby, it is possible to suppress advantageously the deformation of the rotor and the vanes, and it is possible to suppress scorching due to a high surface pressure state that is produced by the rotor and the vanes coming into contact with each of the first plates.
  • one of the side plates may be a linked combination side plate, and the other may be a movable side plate that freely slides in an axial direction.
  • the deflection of the flatness of the contact face of this movable side plate with the rotor and the vanes is possible to set the deflection of the flatness of the contact face of this movable side plate with the rotor and the vanes.
  • one of the side plates may be the movable combination side plate that freely slides in an axial direction, and the other may be the combination side plate. Due to this structure, similar to the linked combination side plate, this movable combination side plate can suppress the deformation of the first plate by increasing the rigidity in proximity to a shaft center. Furthermore, it is possible to set the deflection of the flatness of the contact face of this movable combination side plate with the rotor and the vanes.
  • one of the side plates may be the movable combination side plate that freely slides in an axial direction, and the other may be the linked combination side plate.
  • the other may be the linked combination side plate.
  • one of the side plates may be the movable combination side plate that freely slides in an axial direction, and the other may be the movable side plate. In this case, furthermore, it is possible to set the deflection of the flatness of the contact face with the rotor and the vanes.
  • one of the side plates may be the movable combination side plate the freely slides in an axial direction.
  • these side plates have a symmetrical structure that encloses the rotor, it is possible to maintain the symmetry of the pressure distribution of the fluid that is applied to the opposite side surfaces of the rotor and the vanes.
  • a vane pump that can suppress to a minimum the bending of the side plates during assembly, can suppress to a minimum the deformation of the side plates even during the operation of the pump, and can maintain the side clearances advantageously.
  • FIG. 1 is an external view of a vane pump 100.
  • a case of the vane pump 100 is formed such that a head flange cover 10 is fastened to a center case 11, for example, by press fitting or a bolt fastening, and a case rear cover 12 is fastened to the center case 11 by fastening bolts 13.
  • FIG. 2 is a cross-sectional drawing of the vane pump 100 that is shown in FIG. 1.
  • the vane pump 100 accommodates a pressurized portion inside the case.
  • FIG. 3 is a cross-sectional drawing of this pressurized portion that isolates and shows the portion that is enclosed by the circle in FIG. 2.
  • a front combination side plate 3 a and a rear combination side plate 7a are disposed on the sides of a cam ring 18.
  • a front cover 15 is disposed on the side surface of a front combination side plate 3a.
  • a rear cover 16 is disposed on the side surface of a rear combination side plate 7a.
  • the front combination side plate 3a is structured by a first front plate 1a and a second front plate 2a.
  • the rear combination side plate 7a is structured by a first rear plate 5a and a second rear plate 6a.
  • a plurality of concentrically disposed through holes is formed in the outer circumferential portion, and furthermore, internal threading is formed in the through holes in the front cover 15.
  • the pressurized portion that is shown in FIG. 3 is integrally formed by inserting a fastening bolt 17 into a through hole from the front cover 15 side and fastening the fastening bolt 17 to the rear cover 16.
  • a rotor 19 and vanes 20 are accommodated inside the cam ring 18.
  • FIG. 4 is a cross-sectional drawing along line A-A of the pressurized portion that is shown in FIG. 3.
  • the cam ring 18 has a through hole that is elliptically formed, and the rotor 19 is accommodated inside the cam ring 18.
  • a plurality of radially formed grooves that extend in a radial direction is arranged at equal intervals in the circumferential direction on the outer circumferential surface of the rotor 19.
  • the vanes 20, which can slide in a radial direction, are accommodated in respective grooves, and are continuously pressed against the inner circumferential surface of the cam ring 18 by being urged in the radial direction by, for example, centrifugal force.
  • the rotor 19 is linked to a drive shaft 21 by fitting the drive shaft 21, which includes a corresponding spline shaft, into a spline hole that is formed at the center of rotation of the rotor 19.
  • the drive shaft 21 rotates due to the drive force of an internal combustion engine or the like.
  • Working chambers 23 are formed in the spaces that are enclosed by two adjacent vanes 20 and the cam ring 18. As shown in FIG. 3, the wall surfaces of each working chamber 23 in the axial direction are the first front plate 1a and the first rear plate 5a.
  • the volume of the working chamber 23 expands and contracts accompanying the rotation because the inner circumferential surface of the elliptically shaped through hole of the cam ring 18 forms a portion of the wall surface of the working chamber 23.
  • intake ports 24 that each draw the fluid into the vane pump and discharge ports 25 that discharge the pressurized fluid to the outside are formed in the first rear plate 5a.
  • the first front plate 1a is also structured similarly.
  • the intake ports 24 are formed at positions in the circumferential direction, at which a suction force is generated due to the volume of the working chambers 23 expanding, and in the radial direction, that correspond to the working chambers 23.
  • the discharge ports 25 are formed at positions in the circumferential direction, at which a pressure is generated due to the volume of the working chambers 23 contracting, and in the radial direction, that correspond to working chambers 23.
  • the volume of the working chamber 23 expands and contracts accompanying this rotation.
  • a suction force is generated accompanying the expansion of the volume, and the working chamber 23 draws the fluid from the outside portion through the intake port 24 that is formed in a side plate.
  • the vane 20 that is disposed toward the back with respect to the direction of the rotation passes by the intake port 24 and the working chamber 23 become a closed space.
  • the working chamber 23 reaches a volume contraction step, and the fluid is pressurized accompanying the contraction of the volume.
  • the vanes 20 that form the working chamber 23 when the vane 20 that is disposed toward the front with respect to the direction of rotation passes by the discharge port 25, the fluid, which has become highly pressurized, is discharged from the discharge port 25 to the outside portion.
  • the front combination side plate 3a and the rear combination side plate 7a are each fastened by the fastening bolts 17 to the side faces of the cam ring 18, due to the fastening force, as shown in FIG. 5(a), a center hole vicinity 26 of the first front plate 1a may be deformed toward the rotor side. This is similar in the first rear plate 5a as well.
  • the first front plate 1a and the first rear plate 5a may also deform due to the internal pressure of the pump.
  • the front combination side plate 3 a and the rear combination side plate 7a are symmetrically structured so as to enclose the rotor 19. Furthermore, these combination side plates are formed so as to have identical shapes and have the same rigidity by using identical members.
  • the minute deformations of the center hole vicinities 26 of the front combined side plate 3a and the rear combination side plate 7a that occur when the they are fastened to the side surface of the cam ring 18 by the fastening bolts 17 and the deformations that are caused by the pressure inside the pump become symmetric as the rotor is enclosed by both of the combined side plates.
  • a stepped through hole is formed in the inner circumferential surface in the second front plate 2a.
  • a front back pressure chamber 4 is formed by the cylindrical space that is defined by the step of this inner circumferential surface and the wall surface on the second front plate 2a side of the first front plate 1a.
  • a stepped through hole is also formed in the second rear plate 6a, and a cylindrical rear back pressure chamber 8 is thereby formed.
  • the front back pressure chamber 4 and the rear back pressure chamber 8 communicate, via communication ducts (not illustrated), with each of the discharge ports 25 that are shown in FIG. 4, and pressurized fluid that has attained a high pressure is caused to flow toward each of the back pressure chambers.
  • these combination side plates can each be manufactured separately as two parts, the first front plate 1a and the second front plate 2a, and the first rear plate 5a and the second rear plate 6a, respectively.
  • the side plates that form the back pressure chambers easily and inexpensively.
  • FIG. 6 is a cross-sectional drawing of the pressurized portion, and the present embodiment can be accommodated in the portion that is enclosed by the circle in FIG. 2 in place of the pressurized portion that is shown in FIG. 3.
  • a front combination side plate 3b is structured by a first front plate 1b and a second front plate 2b.
  • a rear combination side plate 7b is structured by a first rear plate 5b and the second rear plate 6b.
  • a stepped through hole is formed in the inner circumferential surface of the second front plate 2b.
  • the cylindrical space that is defined by the step in the inner circumferential surface and the wall surface on the second front plate 2b side of the first front plate 1b forms a front back pressure chamber 4.
  • a stepped through hole is also formed in the second rear plate 6b, and a cylindrical rear back pressure chamber 8 is formed.
  • the front back pressure chamber 4 and the rear back pressure chamber 8 communicate by a communication ducts (not illustrated) with each of the discharge ports that are shown in FIG. 4, and a pressurized fluid that has attained a high pressure is caused to flow into each of the back pressure chambers.
  • Through holes are formed in the first front plate 1b and the first rear plate 5b at their respective axial centers, and furthermore, internal threads 14 are formed in these through holes.
  • a counter bore 32 that accommodates the bolt head of a linking bolt 9 is formed at the axial center of the side surface of the second front plate 2b on the front cover 15 side.
  • a counter bore 32 that accommodates the bolt head of a linking bolt 9 is formed at the axial center of the side surface of the second rear plate 6b on the rear cover 16 side.
  • the linking bolt 9 links together the first front plate 1b and the second front plate 2b.
  • the linking bolt 9 links together the first rear plate 5b and the second rear plate 6b.
  • the linking bolts 9 that are used are hollow, and the drive shaft 21 is accommodated inside the linking bolts 9.
  • the center hole vicinities 26 of the first front plate 1b and the first rear plate 5b may each deform toward the rotor 19 side, similar to the deformation that is shown in FIG. 5(a), due to the fastening force.
  • the symmetry of the fluid pressure that is applied to opposite sides of the rotor 19 and the vanes 20 may be broken, and as a result, the rotor 19 and the vanes 20, for which the center hole vicinities 26 serve as a supporting point, may break down.
  • the plate thickness of the side plates is changed, the material is changed, or the shape is changed.
  • the present embodiment can also ensure a symmetrical distribution of the fluid pressure that is applied to opposite side surfaces of the rotor 19 and the vanes 20, and it can prevent thereby scorching of the rotor.
  • the first front side plate 3b can be separated into two members, the first front plate 1b and the second front plate 2b, the parts manufacturing for forming the front back pressure chamber 4 is simple.
  • the first rear side plate 7b is identical in this respect. Thus, the parts manufacturing is inexpensive and suitable for mass production.
  • the front combination side plate 3b and the rear combination side plate 7b may be identical members and have identical rigidity.
  • the linking bolts 9 that are used need not be hollow, and may be any suitable bolt.
  • the pressurized portion that is shown in FIG. 7 is a cross-sectional drawing of a pressurized portion that is provided with a front combination side plate 3b for one among the pair of side plates.
  • This pressurized portion can be accommodated in the portion that is enclosed by the circle in FIG. 2 in place of the pressurized portion that is shown in FIG. 3.
  • this pressurized portion is one in which the front combination side plate 3 a of the pressurized portion that is shown in FIG. 3 is replaced by the front combination side plate 3b of the pressurized portion described in the second embodiment.
  • a rear ring 29a that can accommodate a front plate 5c is provided on the side surface of the cam ring 18 instead of the rear combination side plate 7a that is shown in FIG. 7, and the first rear plate 5c is accommodated inside the rear ring 29a.
  • This first rear plate 5c is a movable side plate that freely slides in an axial direction.
  • a second rear plate 6c is provided to the rear ring 29a on a side away from the cam ring 18.
  • the second rear plate 6c is a cylindrical member, and a step is formed on the inner circumferential surface thereof.
  • a rear back pressure chamber 8 is formed by the space that is defined by the step of this inner circumferential surface and the wall surface of the second rear plate 6c that is opposite to the rotor, and pressurized fluid is caused to flow in through communication ducts (not illustrated).
  • the second rear plate 6c accommodates a movable side plate set spring 27a inside the cylinder. Due to this movable side plate set spring 27a and the pressure of the pressurized fluid, the first rear plate 5c is urged toward the rotor 19 side.
  • the pressurized portion that is shown in FIG. 9 provides a rear ring 29b that can accommodate one among a pair of side plates, and the movable combination side plate 7d is accommodated inside this rear ring 29b.
  • This movable rear combination side plate 7d freely slides the combination side plate 7b in an axial direction.
  • This combination side plate 7b is that of the pressurized portion that is shown in FIG. 6 to FIG. 8 and described above.
  • the pressurized portion that is shown in FIG. 9 can be accommodated in the portion that is enclosed by the circle in FIG. 2 in place of the pressurized portion that is shown in FIG. 3.
  • the movable rear combination side plate 7d that is provided in the pressurized portion that is shown in FIG. 9 is formed by using the linking bolt 9 to fasten together the first rear plate 5d and the second rear plate 6d.
  • the third rear plate 31 is a cylindrical member that forms a rear back pressure chamber 8 inside thereof and accommodates a movable side plate set spring 27b. Communication ducts (not illustrated) cause the pressurized fluid to flow into this rear back pressure chamber 8. Due to this pressure of the pressurized fluid and the movable side plate set spring 27b, the movable rear combination side plate 7d is urged toward the rotor 19 side.
  • this pressurized portion as well, similar to the pressurized portion in FIG. 7, by increasing the rigidity, it is possible to suppress the deformation of the second rear plate 5d that is caused by pressure inside the pump.
  • by allowing for the deformation of the first front plate 1a and the first rear plate 5d on the sides of the rotor 19 when tightening the linking bolt 9 by a suitable amount similarly, it is possible to ensure the symmetry of the distribution of the fluid pressure that is applied to opposite side surfaces of the rotor 19 and the vanes 20.
  • the movable rear combination side plate 7d that can move in the axial direction, it is possible to set the deflection of the flatness of the contact face with the rotor 19 and the vanes 20.
  • the pressurized portion that is shown in FIG. 10 is provided with the movable rear combination side plate 7d on one side and is provided with the front combination side plate 3b, which has been described above, on the other side.
  • this pressurized portion it is possible to suppress the deformation of the first front plate 1b, which is similar to the deformation that is shown in FIG. 5(a).
  • the pressurized portion that is shown in FIG. 11 is provided with a movable front combination side plate 3d on one side, and is provided with the first rear plate 5c, which is a movable side plate, on the other side.
  • This movable front combination side plate 3d has a structure that is identical to that of the movable rear combination side plate 7d of the pressurized portion that is shown in FIG. 10.
  • the pressurized portion that is shown in FIG. 12 is one in which the pair of plates that encloses the rotor 19 are both formed as movable combination side plates. As shown in FIG. 12, these side plates are the movable front combination side plate 3d and the movable rear combination side plate 7d. In the case of this pressurized portion as well, by increasing the rigidity, it is possible to suppress the deformation of the first front plate 1d and the first rear plate 5d that is caused by pressure inside the pump.
  • the pair of side plates that enclose the rotor 19 is symmetrical, the symmetry of the distribution of the fluid pressure that is applied to the opposite sides of the rotor 19 and the vanes 20 can be further ensured. Therefore, it is possible to suppress the deformation of the rotor 19 and the vanes 20 advantageously, and it is possible to suppress scorching due to a high surface pressure state that is produced by the rotor 19 and the vanes 20 coming into contact with each of the combination side plates 3d and 7d.
  • an identical material may be used for and an identical shape may be applied to these combination side plates 3d and 7d, and they may be formed so as to have an identical rigidity.
  • a vane pump that can suppress to a minimum the bending of the side plates during installation, that can suppress to a minimum the deformation of the side plates even during the operation of the pump, and that can advantageously maintain side clearances.

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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)
EP06728664A 2005-03-08 2006-03-06 Pompe a palettes Withdrawn EP1857679A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2005063960A JP2006249944A (ja) 2005-03-08 2005-03-08 ベーンポンプ
PCT/JP2006/304245 WO2006095673A1 (fr) 2005-03-08 2006-03-06 Pompe a palettes

Publications (1)

Publication Number Publication Date
EP1857679A1 true EP1857679A1 (fr) 2007-11-21

Family

ID=36953267

Family Applications (1)

Application Number Title Priority Date Filing Date
EP06728664A Withdrawn EP1857679A1 (fr) 2005-03-08 2006-03-06 Pompe a palettes

Country Status (5)

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US (1) US20080159898A1 (fr)
EP (1) EP1857679A1 (fr)
JP (1) JP2006249944A (fr)
CN (1) CN101137847A (fr)
WO (1) WO2006095673A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2011149334A (ja) * 2010-01-21 2011-08-04 Showa Corp 車両の油圧制御装置
JP6163111B2 (ja) * 2014-01-21 2017-07-12 株式会社ショーワ ベーンポンプユニット
JP2016109029A (ja) * 2014-12-05 2016-06-20 株式会社デンソー ベーン式ポンプ、及び、それを用いる燃料蒸気漏れ検出装置
US9902251B2 (en) * 2016-01-26 2018-02-27 Deere & Company Recess-mounted hydraulic pump cartridge and work vehicle drivetrain therewith

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1728050A1 (de) * 1968-08-19 1975-08-28 Otto Eckerle Spiel- und verschleissausgleichende hochdruck-zahnradpumpe bzw. -motor
JPS52106602U (fr) * 1977-02-10 1977-08-13
JPS62116189U (fr) * 1986-01-16 1987-07-23
EP0910746B1 (fr) * 1997-04-15 2003-03-05 LuK Fahrzeug-Hydraulik GmbH & Co. KG Pompe a cellules semi-rotative
JP2000145664A (ja) * 1998-09-08 2000-05-26 Ebara Corp ベーン式回転機械

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2006095673A1 *

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WO2006095673A1 (fr) 2006-09-14
JP2006249944A (ja) 2006-09-21
US20080159898A1 (en) 2008-07-03
CN101137847A (zh) 2008-03-05

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