[go: up one dir, main page]

WO2018147081A1 - Pompe à cylindrée variable - Google Patents

Pompe à cylindrée variable Download PDF

Info

Publication number
WO2018147081A1
WO2018147081A1 PCT/JP2018/002094 JP2018002094W WO2018147081A1 WO 2018147081 A1 WO2018147081 A1 WO 2018147081A1 JP 2018002094 W JP2018002094 W JP 2018002094W WO 2018147081 A1 WO2018147081 A1 WO 2018147081A1
Authority
WO
WIPO (PCT)
Prior art keywords
region
drive shaft
suction
variable displacement
diameter portion
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.)
Ceased
Application number
PCT/JP2018/002094
Other languages
English (en)
Japanese (ja)
Inventor
淳 添田
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.)
Hitachi Astemo Ltd
Original Assignee
Hitachi Automotive Systems Ltd
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 Hitachi Automotive Systems Ltd filed Critical Hitachi Automotive Systems Ltd
Publication of WO2018147081A1 publication Critical patent/WO2018147081A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Images

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
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/10—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by changing the positions of the inlet or outlet openings with respect to the working chamber
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/18—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber
    • F04C14/22—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members
    • 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 variable displacement pump.
  • Patent Document 1 discloses a variable displacement pump having a rotor that is rotationally driven by a drive shaft, a plurality of vanes provided on the outer periphery of the rotor, and a cam ring that houses the rotor.
  • the capacity of each pump chamber is variable by swinging the cam ring.
  • variable displacement pump In a variable displacement pump, the suction area and the discharge area of the pump are arranged at symmetrical positions with respect to the drive shaft. For this reason, the variable displacement pump has a problem that the pressure acting on the drive shaft is unbalanced, and the pulsation and vibration of the pump are large.
  • One of the objects of the present invention is to provide a variable displacement pump capable of suppressing pulsation and vibration.
  • the first suction region and the second suction region which are a pair of regions in which the volumes of the plurality of pump chambers increase as the rotor rotates, rotate the drive shaft.
  • a first discharge region and a second discharge region which are a pair of regions that are disposed in a symmetric position with respect to the axis and in which the respective volumes of the plurality of pump chambers are reduced, are disposed in a symmetric position with respect to the rotation axis, and are disposed in the housing.
  • the pressure acting on the drive shaft is balanced, so that pulsation and vibration can be suppressed.
  • FIG. 1 is a schematic diagram of a variable displacement pump 1 according to Embodiment 1.
  • FIG. 1 is an axial sectional view of a variable displacement pump 1 according to Embodiment 1.
  • FIG. It is explanatory drawing which shows the discharge amount at the time of cam non-rotation. It is explanatory drawing which shows the discharge amount at the time of cam rotation.
  • FIG. 6 is a schematic diagram of a main part of a variable displacement pump 51 according to a second embodiment. 6 is a schematic diagram of a variable displacement pump 53 of Embodiment 3.
  • FIG. FIG. 6 is a schematic diagram of a main part of a variable displacement pump 55 according to a fourth embodiment.
  • FIG. 1 is a schematic diagram of a variable displacement pump 1 according to the first embodiment.
  • FIG. 2 is an axial sectional view of the variable displacement pump 1 according to the first embodiment.
  • the variable displacement pump 1 is a pump device applied to a power steering device for a vehicle.
  • the variable displacement pump 1 functions as a fluid pressure generating source that supplies power steering oil (hereinafter referred to as hydraulic fluid) to the power steering device.
  • the power steering apparatus has a power cylinder provided in a steering gear box.
  • the variable displacement pump 1 is driven by an internal combustion engine as a prime mover, sucks hydraulic fluid from a reservoir tank 31, and discharges the hydraulic fluid to a power cylinder.
  • the variable displacement pump 1 has a housing 2.
  • the housing 2 is formed by abutting the front housing 3 and the rear housing 4 together.
  • the housing 2 has a pump element accommodating portion 5 therein.
  • the pump element accommodating portion 5 is a substantially cylindrical space, and the pump element 6 is accommodated therein.
  • the pump element 6 has a rotor 7 and a cam ring 8.
  • the pump element accommodating portion 5 includes an adapter ring portion 9 and a pressure plate 10.
  • the rotor 7 has a drive shaft 11 passing through the center.
  • the rotor 7 and the drive shaft 11 are serrated.
  • the drive shaft 11 is rotationally driven by the crankshaft of the engine.
  • Both ends of the drive shaft 11 are supported by the bearings 12 and 13 and rotate around the rotation axis O (hereinafter also simply referred to as the axis periphery).
  • the bearing 12 is a ball bearing and is disposed in the front housing 3.
  • the bearing 13 is a needle bearing and is disposed in the rear housing 4.
  • An oil seal 14 is disposed in the front housing 3 adjacent to the bearing 12.
  • the oil seal 14 has a function of preventing hydraulic fluid from leaking from the pump element housing 5 side to the bearing 12 side.
  • the rotor 7 has, on its outer periphery, a plurality of slots 7a cut out along a radial direction (hereinafter also simply referred to as a radial direction) in the rotation axis O.
  • the slots 7a are arranged at an equal pitch in the circumferential direction of the rotation axis O (hereinafter also simply referred to as the circumferential direction).
  • a back pressure chamber 7b is formed on the inner peripheral side of each slot 7a.
  • the hydraulic fluid pressurized in the pump chamber 16 is introduced into each back pressure chamber 7b.
  • a substantially flat vane 15 is accommodated so as to be able to protrude and retract in the radial direction of the rotor 7.
  • Each vane 15 is pressed against the inner cam surface 8a of the cam ring 8 by the pressure of the hydraulic fluid introduced into the back pressure chamber 7b.
  • the cam ring 8 is formed in an annular shape surrounding the rotor 7.
  • the cam ring 8 has a substantially elliptical inner cam surface 8a.
  • a plurality of pump chambers 16 are formed by each vane 15 partitioning the annular space between the cam ring 8 and the rotor 7 in the circumferential direction.
  • the adapter ring portion 9 is formed in an annular shape surrounding the cam ring 8.
  • the adapter ring portion 9 holds the cam ring 8 so as to be rotatable around the axis.
  • the adapter ring portion 9 is restricted from rotating around the axis with respect to the housing 2 by a rotation prevention pin 17.
  • a notch groove 20 is formed on the outer periphery of the cam ring 8 over a predetermined angular range in the circumferential direction.
  • the protrusion 18 protrudes into the notch groove 20.
  • the protrusion 18 has a cam seal (first seal member) 19 at its tip.
  • the cam seal 19 seals between the tip of the protrusion 18 and the notch groove 20.
  • the cam ring 8 can rotate within a predetermined angle range by the relative movement of the protruding portion 18 in the circumferential direction within the cutout groove 20.
  • a portion where the notch groove 20 is formed is a small diameter portion 21.
  • an end portion including one side wall of the notch groove 20 is a first large diameter portion 22, and an end portion including the other side wall is a second large diameter portion 23.
  • the outer diameter of the small diameter portion 21 is smaller than the first large diameter portion 22 and the second large diameter portion 23 by the notch groove 20.
  • the cam ring 8 is connected to the adapter ring portion 9 in a circumferential direction from a state where the projecting portion 18 and the first large diameter portion 22 abut to a state where the projecting portion 18 and the second large diameter portion 23 abut. Relative rotation is possible.
  • the first large diameter portion 22 has a cam seal (second seal member) 24 on its outer periphery.
  • the cam seal 24 seals between the inner peripheral surface of the adapter ring portion 9 and the first large diameter portion 22.
  • a step portion 22 a is formed at the end of the first large diameter portion 22.
  • the stepped portion 22a is thinner than the other portions of the cam ring 8 (the dimension along the rotational axis O (hereinafter, also simply referred to as the axial direction) is small).
  • the space between the inner peripheral surface of the adapter ring portion 9 and the outer peripheral surface of the small diameter portion 21 and the region between the protruding portion 18 and the first large diameter portion 22 is a main cam control chamber 25.
  • a space between the inner peripheral surface of the adapter ring portion 9 and the outer peripheral surface of the small diameter portion 21, and a region between the protruding portion 18 and the second large diameter portion 23 is a sub cam control chamber 26.
  • High pressure or low pressure hydraulic fluid is selectively supplied to the main cam control chamber 25 by a spool type control valve 29 that operates by a differential pressure across the metering orifice 28 formed in the discharge passage 27.
  • the pair of cam seals 19 and 24 prevent the hydraulic fluid in the main cam control chamber 25 from leaking.
  • the main cam control chamber 25 is a space between the pair of cam seals 19 and 24.
  • the discharge passage 27 is formed in the rear housing 4 and discharges the hydraulic fluid pressurized in each pump chamber 16 to the outside.
  • the control valve 29 is accommodated in the housing 2.
  • hydraulic fluid is always supplied from the reservoir tank 31 to the auxiliary cam control chamber 26 via the suction passage 30 formed in the housing 2.
  • the reservoir tank 31 stores the hydraulic fluid in an open state.
  • each vane 15 of the rotor 7 that is driven to rotate inside the inner cam surface 8a is in sliding contact with the cam ring 8, so that the rotation direction of the rotor 7 (counterclockwise direction in FIG. 1) is caused by so-called rotation.
  • Rotation behavior in the same direction is given. That is, when the rotor 7 rotates, the rotational friction of each vane 15 always acts on the cam ring 8. Due to this rotational friction, when the main cam control chamber 25 is in a low pressure state, the cam ring 8 is in a state where the first large-diameter portion 22 constituting the main cam control chamber 25 and the protruding portion 18 are in contact with each other, and the variable displacement pump 1 maintains the maximum discharge rate.
  • the cam ring 8 is connected to each vane 15 in accordance with this pressure increase.
  • the rotor 7 rotates in the opposite direction (the clockwise direction in FIG. 1) against the rotational friction of the rotor 7.
  • the pressure plate 10 is disposed in pressure contact with the front housing 3 side of the pump element 6. On the side opposite to the front housing 3 of the pump element 6, the end surface of the rear housing 4 is pressed as a side plate. Note that the pressure plate 10, the adapter ring portion 9, and the rear housing 4 are integrally assembled and fixed in a state of being positioned in the circumferential direction by an appropriate anti-rotation structure including the anti-rotation pin 17.
  • a pressure chamber 32 is formed on the contact surface of the front housing 3 with the pressure plate 10. The hydraulic fluid pressurized in each pump chamber 16 is supplied to the pressure chamber 32. The pressure plate 10 is pressed against the rotor 7 by the hydraulic fluid supplied to the pressure chamber 32.
  • the pressure plate 10 is formed with a first suction port 33, a second suction port 34, a first discharge port 35 and a second discharge port 36.
  • Each port 33, 34, 35, 36 is formed in an arc shape extending in the circumferential direction, and penetrates the pressure plate 10 in the axial direction.
  • the first suction port 33 and the second suction port 34 have a point-symmetric (two-fold symmetry) shape with a point on the rotation axis O as a symmetry point.
  • the first discharge port 35 and the second discharge port 36 are disposed at positions that are 90 ° out of phase with respect to the first suction port 33 and the second suction port 34.
  • the first discharge port 35 and the second discharge port 36 When viewed from the direction of the rotation axis O, the first discharge port 35 and the second discharge port 36 have a point-symmetric (two-fold symmetry) shape with a point on the rotation axis O as a symmetric point.
  • the first suction port 33 and the second suction port 34 have a capacity of each pump chamber 16 as the rotor 7 rotates in a state where the first large diameter portion 22 of the cam ring 8 is in contact with the protruding portion 18 of the adapter ring portion 9. Open to a pair of first and second suction areas where the gradually increases.
  • the first suction area and the second suction area are set at symmetrical positions with respect to the rotation axis O. That is, when viewed from the direction of the rotation axis O, the first suction region and the second suction region have a point-symmetric (two-fold symmetry) shape with a point on the rotation axis O as a symmetric point.
  • the first suction port 33 and the second suction port 34 are connected to suction passages 30 a and 30 b branched from the suction passage 30.
  • the first discharge port 35 and the second discharge port 36 are connected to the pump chambers 16 as the rotor 7 rotates in a state where the first large diameter portion 22 of the cam ring 8 is in contact with the protruding portion 18 of the adapter ring portion 9. Open to a pair of first discharge area and second discharge area where the volume of the first discharge area gradually decreases.
  • the first discharge region and the second discharge region are disposed at positions that are 90 ° out of phase with respect to the first suction region and the second suction region.
  • the first discharge area and the second discharge area are set at symmetrical positions with respect to the rotation axis O. That is, when viewed from the direction of the rotation axis O, the first discharge area and the second discharge area have a point-symmetric (two-fold symmetry) shape with a point on the rotation axis O as a symmetric point.
  • the first discharge port 35 and the second discharge port 36 are connected to the discharge passage 27 via discharge passages 39 and 40 formed in the housing 2.
  • the small-diameter portion 21 of the cam ring 8 overlaps the boundary between the second discharge region and the first suction region in the circumferential direction, and the boundary between the first suction region and the first discharge region and the first discharge region. It is provided at a position that does not overlap the boundary between the two suction areas and the second discharge area.
  • one of the pump chambers 16 is between the first suction port 33 and the first discharge port 35 and communicates with both the first suction port 33 and the first discharge port 35.
  • the area that does not exist is defined as the first confinement area.
  • An area where one of the pump chambers 16 is between the second suction port 34 and the second discharge port 36 and does not communicate with either the second suction port 34 or the second discharge port 36. Is the second confinement region.
  • the first suction port 33 is disposed adjacent to the first confinement region.
  • the second suction port 34 is disposed adjacent to the second confinement region.
  • the hydraulic fluid flowing into the suction passage 30 from the reservoir tank 31 passes through the suction passage 30 and the suction passages 30a and 30b, and is sucked into the pump chambers 16 from the first suction port 33 and the second suction port 34.
  • the hydraulic fluid introduced into each pump chamber 16 is sequentially compressed according to the movement of each vane 15, passes through the discharge passages 39 and 40 and the discharge passage 27 from the first discharge port 35 and the second discharge port 36, It is discharged to the outside.
  • a suction pressure introduction passage 41 is formed in the rear housing 4. One end side of the suction pressure introduction passage 41 is connected to the suction passage 30a. The other end side of the suction pressure introduction passage 41 is connected to the sub cam control chamber 26.
  • the opening end 41 a of the suction pressure introduction passage 41 in the sub cam control chamber 26 is disposed at a position where the second large diameter portion 23 is not blocked by the second large diameter portion 23 even when the second large diameter portion 23 is in contact with the protruding portion 18.
  • the control valve 29 is disposed in the front housing 3.
  • the control valve 29 has a valve hole 42, a spool 43 and a spring 44.
  • the valve hole 42 extends in a direction orthogonal to the rotation axis O.
  • an upstream pressure introduction passage 45 connected to the valve hole 42 is formed in the housing 2.
  • the upstream pressure introduction passage 45 is connected to the upstream pressure introduction passage 9 a formed in the adapter ring portion 9.
  • the upstream pressure introduction passage 9 a passes through the adapter ring portion 9 in the radial direction and opens into the main cam control chamber 25.
  • the spool 43 is a spool valve body having a substantially bottomed cylindrical shape.
  • the spring 44 is a compression coil spring and urges the spool 43 toward one axial side (left side in FIG. 1).
  • the valve hole 42 is partitioned into a high pressure chamber 46, an intermediate pressure chamber 47 and a low pressure chamber 48 by a spool 43.
  • the high pressure chamber 46 is connected to the upstream side of the metering orifice 28 of the discharge passage 27.
  • the intermediate pressure chamber 47 is connected to the downstream side of the metering orifice 28 of the discharge passage 27.
  • the low pressure chamber 48 is arranged in the middle of the suction passage 30.
  • the spool 43 moves in the axial direction in accordance with the pressure difference between the intermediate pressure chamber 47 and the high pressure chamber 46.
  • the spool 43 maintains a state where it abuts against the end surface 42a of the valve hole 42 by the urging force of the spring 44.
  • the upstream pressure introduction passage 45 is in communication with the low pressure chamber 48, and the working fluid of the low pressure chamber 48 is introduced into the main cam control chamber 25.
  • the spool 43 moves to the other side in the axial direction (the right side in FIG.
  • the upstream pressure introduction passage 45 is in communication with the high pressure chamber 46, and the working fluid of the high pressure chamber 46 is introduced into the main cam control chamber 25. That is, the hydraulic fluid in the low pressure chamber 48 or the high pressure chamber 46 is selectively introduced into the main cam control chamber 25 according to the differential pressure across the metering orifice 28. On the other hand, hydraulic fluid is always introduced from the low pressure chamber 48 into the sub cam control chamber 26 regardless of the differential pressure across the metering orifice 28.
  • a relief valve 49 is formed inside the spool 43.
  • the relief valve 49 performs a relief operation when the pressure in the intermediate pressure chamber 47, that is, the pressure of the hydraulic fluid supplied to the power steering device becomes more than necessary, and allows the intermediate pressure chamber 47 and the low pressure chamber 48 to communicate with each other.
  • the working fluid is refluxed to the suction passage 30.
  • a bearing holding portion 9b is formed on the inner circumference of the adapter ring portion 9 over a predetermined angular range in the circumferential direction.
  • the bearing holding portion 9b is a notch groove, and is disposed in a region between the pair of cam seals 19, 24 with respect to the rotation axis O, that is, at a position opposite to the main cam control chamber 25.
  • a bearing 50 is accommodated in the bearing holding portion 9b.
  • the bearing 50 is a needle bearing.
  • the bearing 50 aims to reduce the positional deviation of the cam ring 8 and the friction during rotation, and supports a predetermined angular range on the outer periphery of the cam ring 8 so as to be rotatable about an axis.
  • the circumferential width of the bearing 50 is set longer than the circumferential width of the main cam control chamber 25 when the main cam control chamber 25 has the maximum volume.
  • the bearing 50 is located on the opposite side of the main cam control chamber 25 with respect to the rotation axis O regardless of the volume of the main cam control chamber 25.
  • the second suction port 34 has an extension 34a that extends radially outward.
  • the extension portion 34a is connected to the bearing holding portion 9b, that is, the region between the cam ring 8 and the bearing 50.
  • variable displacement pump 1 of the first embodiment The hydraulic fluid sucked into the pump chambers 16 from the first suction port 33 and the second suction port 34 is compressed in the pump chambers 16 as the rotor 7 rotates, and the first discharge port 35 and the second discharge port 36 side. Sent to.
  • the hydraulic fluid discharged from the first discharge port 35 and the second discharge port 36 is discharged from the discharge passage 27 to the outside of the housing 2.
  • the spool 43 of the control valve 29 is maintained in contact with the end surface 42a by the urging force of the spring 44. Accordingly, low pressure hydraulic fluid is introduced into the main cam control chamber 25 from the suction passage 30 as in the case of the sub cam control chamber 26, and no pressure difference is generated between the main cam control chamber 25 and the sub cam control chamber 26. Therefore, the cam ring 8 maintains the state in which the first large diameter portion 22 is in contact with the protruding portion 18 by the rotational friction of each vane 15. At this time, as shown in FIG. 3, the discharge amount of the hydraulic fluid from the first discharge port 35 and the second discharge port 36 is maximum. When the rotational speed of the drive shaft 11 rises from this state, the discharge amount increases in proportion to the rotational speed.
  • variable displacement pump 1 the first suction region, the second suction region, the first discharge region, and the second discharge region are arranged at symmetrical positions with respect to the rotation axis O. Therefore, since a bending force due to a lateral load does not act on the drive shaft 11, a pressure balance with respect to the drive shaft 11 can be achieved, and pulsation and vibration can be suppressed. Further, since the drive shaft 11 is not subjected to bending force, the shaft diameter of the drive shaft 11 and the bearings 12 and 13 can be reduced, and the variable displacement pump 1 can be reduced in size.
  • variable displacement pump 1 In the variable displacement pump 1, the first discharge port 35 and the second discharge port 36, the first suction port 33 and the second suction port in each pump chamber 16 when the cam ring 8 rotates according to the increase in the rotation speed of the drive shaft 11.
  • the discharge amount By changing the relative position of the port 34 and the pump volume, the discharge amount can be made variable. For this reason, useless power loss can be suppressed in supplying hydraulic fluid to the power steering device.
  • the variable displacement pump 1 has a bearing 50 that supports the cam ring 8 on the opposite side of the region (main cam control chamber 25) between the pair of cam seals 19, 24 with respect to the rotation axis O in the radial direction.
  • the cam ring 8 is urged in the direction of the bearing 50 by a pair of cam seals 19, 24 and high-pressure hydraulic fluid introduced into the main cam control chamber 25, and is supported by the bearing 50 so as to be rotatable about the axis. Thereby, positional deviation (eccentricity) of the cam ring 8 and friction during rotation can be reduced, and the cam ring 8 can be smoothly rotated.
  • the bearing 50 is located on the opposite side of the main cam control chamber 25 with respect to the rotation axis O regardless of the volume of the main cam control chamber 25.
  • the bearing 50 when the circumferential width of the main cam control chamber 25 is a half of the maximum width, the bearing 50 is located at a symmetrical position with respect to the rotation axis O at the central position in the circumferential direction of the main cam control chamber 25. ing. Since the bearing 50 is disposed at a well-balanced position with respect to both the state in which the main cam control chamber 25 has the maximum volume and the state in which the main volume reaches the minimum volume, the rotation controllability of the cam ring 8 in the entire operation region can be improved. Further, the bearing 50 overlaps with the axis along the direction of the combined vector of the forces that the pressure of the main cam control chamber 25 acts on the small diameter portion 21 and the first large diameter portion 22 of the cam ring 8. As a result, the force of the main cam control chamber 25 acting on the cam ring 8 can be appropriately received by the bearing 50.
  • the small-diameter portion 21 of the cam ring 8 overlaps the boundary between the second discharge region and the first suction region in the circumferential direction, and the boundary between the first suction region and the first discharge region and the first discharge region. It is provided at a position that does not overlap the boundary between the two suction areas and the second discharge area. That is, the small diameter portion 21 is provided in a portion where the inner diameter of the cam ring 8 is small, and the small diameter portion 21 is not provided in a portion where the inner diameter of the cam ring 8 is large. Therefore, there is no portion in which the radial thickness (wall thickness) of the cam ring 8 becomes extremely small, and the rigidity of the cam ring 8 can be ensured.
  • the housing 2 opens to the sub cam control chamber 26 which is a space between the second large diameter portion 23 of the cam ring 8 and the protruding portion 18 of the adapter ring portion 9, and introduces suction pressure for introducing the working fluid of the suction passage 30.
  • a passage 41 is provided.
  • the pressure of the hydraulic fluid supplied to the main cam control chamber 25 can be set lower than when no hydraulic fluid is introduced. The leakage of hydraulic fluid from the cam control chamber 25 can be suppressed.
  • the opening end 41a of the suction pressure introduction passage 41 in the sub cam control chamber 26 is disposed at a position where it is not blocked by the second large diameter portion 23 even when the sub cam control chamber 26 has a minimum volume. If the open end 41a is closed by the second large diameter portion 23, when the volume of the sub cam control chamber 26 is increased again, the pressure in the sub cam control chamber 26 becomes negative, and the controllability of the cam ring 8 is reduced. May be exacerbated. Therefore, even in a state where the sub cam control chamber 26 has the minimum volume, at least a part of the opening end 41a opens into the sub cam control chamber 26, so that the controllability of the cam ring 8 can be suppressed.
  • the rotation direction of the cam ring 8 and the rotation direction of the drive shaft 11 when the volume of the main cam control chamber 25 increases are opposite directions.
  • the direction in which the cam ring 8 rotates in the direction in which the volume of the main cam control chamber 25 decreases coincides with the direction in which the drive shaft 11 rotates.
  • the main cam control chamber 25 has a stepped portion 22a that abuts against the protruding portion 18 when the volume is minimum and forms a space between the first large diameter portion 22 and the protruding portion 18. If the volume of the main cam control chamber 25 becomes 0, when the volume of the main cam control chamber 25 is increased again, the pressure in the main cam control chamber 25 becomes negative and the controllability of the cam ring 8 may be deteriorated. is there. Therefore, even when the main cam control chamber 25 has a minimum volume, the controllability of the cam ring 8 can be prevented from decreasing by keeping the volume of the main cam control chamber 25 from becoming zero.
  • the first suction port 33 is provided adjacent to a first confinement region where one of the pump chambers 16 does not communicate with either the first suction port 33 or the first discharge port 35.
  • the second suction port 34 is provided adjacent to a second confinement region in which one of the pump chambers 16 does not communicate with either the second suction port 34 or the second discharge port 36. .
  • the hydraulic fluid in the first confinement region and the second confinement region may be in a compressed state.
  • the compressed hydraulic fluid is not easily removed, the compressed state continues, leading to a drive loss of the pump.
  • the second suction port 34 has an extension 34a that extends to a region between the cam ring 8 and the bearing 50 in the radial direction.
  • the adapter ring portion 9 has a bearing holding portion 9b that is recessed radially outward on the inner peripheral surface thereof, the arrangement of the bearing 50 that is a needle bearing is easy.
  • FIG. 5 is a schematic diagram of a main part of the variable displacement pump 51 of the second embodiment.
  • the variable displacement pump 1 of the second embodiment is different from the first embodiment in that a spring (elastic member) 52 is provided between the second large diameter portion 23 and the protruding portion 18 in the circumferential direction.
  • the spring 52 is a compression coil spring. The spring 52 biases the cam ring 8 in the direction in which the volume of the sub cam control chamber 26 increases.
  • the cam ring 8 when the discharge amount of the variable displacement pump 1 is increased, the cam ring 8 is rotated by the rotational friction of each vane 15.
  • the cam ring 8 when the discharge amount of the variable displacement pump 51 is increased, the cam ring 8 is rotated counterclockwise in FIG. 5 by the rotational friction of each vane 15 and the biasing force of the spring 52. .
  • the responsiveness at the time of increasing the discharge amount can be improved as compared with the first embodiment.
  • FIG. 6 is a schematic diagram of the variable displacement pump 53 of the third embodiment.
  • the first suction port 33 and the second suction port 34 are connected to the suction passage 30.
  • the hydraulic fluid flowing into the suction passage 30 from the reservoir tank 31 passes through the suction passage 30 and is sucked into the pump chambers 16 from the first suction port 33 and the second suction port 34.
  • the hydraulic fluid introduced into each pump chamber 16 is sequentially compressed according to the movement of each vane 15, passes through the discharge passages 39 and 40 and the discharge passage 27 from the first discharge port 35 and the second discharge port 36, and moves to the housing 2. It is discharged to the outside.
  • a downstream pressure introduction passage 54 connected to the valve hole 42 is formed.
  • the downstream pressure introduction passage 54 is connected to the downstream pressure introduction passage 9c formed in the adapter ring portion 9.
  • the downstream pressure introduction passage 9 c passes through the adapter ring portion 9 in the radial direction and opens into the sub cam control chamber 26.
  • the downstream pressure introduction passage 54 is in communication with the intermediate pressure chamber 47, and the hydraulic fluid in the intermediate pressure chamber 47 is introduced into the sub cam control chamber 26.
  • the spool 43 moves to the other side in the axial direction (the right side in FIG. 6) against the urging force of the spring 44.
  • the upstream pressure introduction passage 45 is in communication with the high pressure chamber 46, and the working fluid of the high pressure chamber 46 is introduced into the main cam control chamber 25.
  • the downstream pressure introduction passage 54 is in communication with the low pressure chamber 48, and the working fluid is discharged from the sub cam control chamber 26 to the low pressure chamber 48.
  • variable displacement pump 53 of the third embodiment When the rotational speed of the drive shaft 11 is less than the predetermined rotational speed, the pressure loss of the metering orifice 28 is very small, so the pressure difference between the high pressure chamber 46 and the intermediate pressure chamber 47 is less than the predetermined pressure difference. Therefore, the spool 43 of the control valve 29 is maintained in contact with the end surface 42a by the urging force of the spring 44. Therefore, the low pressure hydraulic fluid is introduced into the main cam control chamber 25 from the suction passage 30. On the other hand, medium pressure hydraulic fluid is introduced into the secondary cam control chamber 26 from the downstream side of the metering orifice 28 of the discharge passage 27.
  • the cam ring 8 Since the pressure difference between the main cam control chamber 25 and the sub cam control chamber 26 is large, the cam ring 8 maintains the state where the first large diameter portion 22 is in contact with the protruding portion 18 against the rotational friction of each vane 15. To do. At this time, the discharge amount of the hydraulic fluid from the first discharge port 35 and the second discharge port 36 is maximum. When the rotational speed of the drive shaft 11 rises from this state, the discharge amount increases in proportion to the rotational speed.
  • the cam ring 8 rotates, the amount of hydraulic fluid discharged from the first discharge port 35 and the second discharge port 36 decreases.
  • the pressure difference between the high pressure chamber 46 and the intermediate pressure chamber 47 is less than the predetermined pressure difference, so that the spool 43 moves to one side in the axial direction (left side in FIG. 6) by the urging force of the spring 44. Therefore, the main cam control chamber 25 communicates with the suction passage 30 and the pressure in the main cam control chamber 25 decreases.
  • the secondary cam control chamber 26 communicates with the downstream side of the metering orifice 28 in the discharge passage 27, and the pressure in the secondary cam control chamber 26 increases.
  • the housing 2 has a downstream pressure introduction passage 54 that opens into the sub cam control chamber 26 that is a space between the second large diameter portion 23 and the protruding portion 18 and that introduces pressure downstream of the metering orifice 28. .
  • a downstream pressure introduction passage 54 that opens into the sub cam control chamber 26 that is a space between the second large diameter portion 23 and the protruding portion 18 and that introduces pressure downstream of the metering orifice 28.
  • the control valve 29 controls the pressure in the main cam control chamber 25 and holds the position of the cam ring 8. That is, the control valve 29 controls the pressure in the main cam control chamber 25 so as to balance the rotational torque of the cam ring 8 generated by the rotational friction of each vane 15. As a result, highly accurate position control of the cam ring 8 can be realized while effectively using the rotational friction of each vane 15 for drive control of the cam ring 8.
  • FIG. 7 is a schematic diagram of a main part of the variable displacement pump 55 of the fourth embodiment.
  • the variable displacement pump 1 according to the fourth embodiment is different from the third embodiment in that a spring (elastic member) 56 is provided between the second large diameter portion 23 and the protruding portion 18 in the circumferential direction.
  • the spring 56 is a compression coil spring. The spring 56 biases the cam ring 8 in the direction in which the volume of the sub cam control chamber 26 increases.
  • the cam ring 8 when the discharge amount of the variable displacement pump 53 is increased, the cam ring 8 is rotated by a pressure difference between the high pressure chamber 46 and the intermediate pressure chamber 47.
  • the cam ring 8 when the discharge amount of the variable displacement pump 55 is increased, the cam ring 8 is rotated clockwise in FIG. 7 by the pressure difference between the high pressure chamber 46 and the intermediate pressure chamber 47 and the biasing force of the spring 56. Rotate in the direction of. Thereby, it is possible to improve the responsiveness when increasing the discharge amount as compared with the third embodiment.
  • the bearing 50 may be a bimetal type.
  • the embodiment of the present invention can be applied to a pump used as a fluid pressure generation source in a pressure fluid utilization device other than a power steering device.
  • variable displacement pump includes a housing having a pump element accommodating portion therein, a drive shaft that is pivotally supported by the housing, and a rotor that is rotationally driven by the drive shaft, the drive shaft A rotor having a plurality of slots provided in a direction around a rotation axis of the rotor, a plurality of vanes provided in each of the slots of the rotor, and the rotor and the plurality of vanes provided in the pump element accommodating portion.
  • An encircling annular cam ring wherein the cam ring, the rotor, and the plurality of vanes form a plurality of pump chambers, and each volume of the plurality of pump chambers increases as the rotor rotates.
  • a first discharge region that is a pair of regions in which the respective volumes of the plurality of pump chambers are reduced.
  • the second discharge region, the first suction region and the second suction region are arranged symmetrically with respect to the rotation axis of the drive shaft, and the first discharge region and the second discharge region are The volumes of the plurality of pump chambers in the first suction region and the second suction region are arranged in symmetrical positions, and the cam ring is rotated in a direction around the rotation axis of the drive shaft with respect to the housing.
  • a cam ring that changes a ratio between an increase amount and a decrease amount of the volume of the plurality of pump chambers in the first discharge region and the second discharge region; and the housing, the first suction region and the second suction region A suction passage that opens to a region and supplies hydraulic fluid to the first suction region and the second suction region; and the housing, the first discharge region and the second discharge region.
  • a discharge passage that opens to a region and discharges hydraulic fluid from the first discharge region and the second discharge region to the outside of the housing; and the pump element housing portion and the cam ring in a radial direction of the rotation axis of the drive shaft
  • a first seal member and a second seal member which are a pair of seal members provided between the outer peripheral sides of the first and second seal members, and a main cam control chamber is formed between the first seal member and the second seal member.
  • a bearing provided between the first seal member, the second seal member, and the outer peripheral side of the cam ring in the radial direction of the rotation axis of the drive shaft, the rotation axis of the drive shaft
  • a bearing provided on the opposite side of the first seal member or the second seal member, and a control valve for controlling the pressure in the main cam control chamber.
  • the bearing is located on the opposite side of the region between the first seal member and the second seal member with respect to the rotation axis of the drive shaft.
  • the bearing has a circumferential width in the rotation axis of the drive shaft of the main cam control chamber that is half the maximum width, It is located at a symmetrical position of the central position of the main cam control chamber with respect to the rotation axis.
  • the protrusion is provided on the housing, and includes a protrusion that protrudes inward in the radial direction of the rotation axis of the drive shaft, and the cam ring includes A small diameter portion having a first outer diameter as an outer diameter that is a distance from a rotation axis of the drive shaft to an outer peripheral edge of the cam ring, and provided on both sides of the small diameter portion in a direction around the rotation axis of the drive shaft.
  • a first large diameter portion and a second large diameter portion which are a pair of large diameter portions having a second outer diameter whose outer diameter is larger than the first outer diameter, and the protrusion is a rotation of the drive shaft Arranged between the first large diameter portion and the second large diameter portion in the direction around the axis, and the main cam control chamber is provided in a region between the first large diameter portion and the protrusion, The bearing is in relation to the small diameter portion and the first large diameter portion.
  • Serial pressure main cam control chamber overlaps the axis along the direction of the resultant vector of the force acting.
  • the protrusion is provided on the housing, and includes a protrusion that protrudes inward in the radial direction of the rotation axis of the drive shaft, and the cam ring includes A small diameter portion having a first outer diameter as an outer diameter that is a distance from a rotation axis of the drive shaft to an outer peripheral edge of the cam ring, and provided on both sides of the small diameter portion in a direction around the rotation axis of the drive shaft.
  • a first large diameter portion and a second large diameter portion which are a pair of large diameter portions having a second outer diameter whose outer diameter is larger than the first outer diameter, and the protrusion is a rotation of the drive shaft Arranged between the first large diameter portion and the second large diameter portion in the direction around the axis, and the main cam control chamber is provided in a region between the first large diameter portion and the protrusion,
  • a first suction region, a second suction region, and the first discharge are arranged in the order of the first suction region, the first discharge region, the second suction region, and the second discharge region along the rotation direction of the rotor, In a direction around the rotation axis of the drive shaft, the boundary between the second discharge region and the first suction region overlaps, and the boundary between the first suction region and the first discharge region and the first It is provided at a position that does not overlap the boundary between the two suction areas and the second discharge area.
  • the protrusion is provided on the housing, and includes a protrusion that protrudes inward in the radial direction of the rotation axis of the drive shaft, and the cam ring includes A small diameter portion having a first outer diameter as an outer diameter that is a distance from a rotation axis of the drive shaft to an outer peripheral edge of the cam ring, and provided on both sides of the small diameter portion in a direction around the rotation axis of the drive shaft.
  • a first large diameter portion and a second large diameter portion which are a pair of large diameter portions having a second outer diameter whose outer diameter is larger than the first outer diameter, and the protrusion is a rotation of the drive shaft Arranged between the first large diameter portion and the second large diameter portion in the direction around the axis, and the main cam control chamber is provided in a region between the first large diameter portion and the protrusion,
  • the housing includes the second large diameter portion and the protruding portion. Open to is spatial sub cam control chamber, having a suction pressure introduction passage for introducing the working fluid of the suction passage.
  • the opening on the side of the sub cam control chamber of the suction pressure introduction passage is configured to have the second large diameter even when the volume of the sub cam control chamber is minimized. It is provided at a position that is not blocked by the part.
  • the rotation direction of the cam ring and the rotation direction of the drive shaft when the volume of the main cam control chamber increases are opposite to each other.
  • the protrusion is provided on the housing, and includes a protrusion that protrudes inward in the radial direction of the rotation axis of the drive shaft, and the cam ring includes A small diameter portion having a first outer diameter as an outer diameter that is a distance from a rotation axis of the drive shaft to an outer peripheral edge of the cam ring, and provided on both sides of the small diameter portion in a direction around the rotation axis of the drive shaft.
  • a first large diameter portion and a second large diameter portion which are a pair of large diameter portions having a second outer diameter whose outer diameter is larger than the first outer diameter, and the protrusion is a rotation of the drive shaft Arranged between the first large diameter portion and the second large diameter portion in the direction around the axis, and the main cam control chamber is provided in a region between the first large diameter portion and the protrusion, Step portion provided on the first large diameter portion or the protruding portion When the volume of the main cam control chamber is minimized, the stepped portion comes into contact with the first large diameter portion or the protruding portion, so that the first large diameter portion and the first large diameter portion in a region other than the stepped portion. It further has a step part which forms a space between the protrusions.
  • the first suction area, the second suction area, the first discharge area, and the second discharge area are arranged along the rotation direction of the rotor.
  • the suction region, the first discharge region, the second suction region, and the second discharge region are arranged in this order, and the suction passage is provided in the first suction port that opens to the first suction region, and the second suction region.
  • a region between one of the first suction port and the first discharge port and not communicating with either the first suction port or the first discharge port is defined as a first confinement region.
  • a plurality of pump chambers When one of the regions is between the second suction port and the second discharge port and does not communicate with either the second suction port or the second discharge port, the second confinement region
  • the first suction port is provided adjacent to the first confinement region
  • the second suction port is provided adjacent to the second confinement region.
  • the first suction area, the second suction area, the first discharge area, and the second discharge area are arranged along the rotation direction of the rotor.
  • the suction region, the first discharge region, the second suction region, and the second discharge region are arranged in this order, and the suction passage is provided in the first suction port that opens to the first suction region, and the second suction region.
  • a second suction port that opens to the first discharge region; a second discharge port that opens to the second discharge region; and the second suction port. Is formed so as to extend to a region between the cam ring and the bearing in the radial direction of the rotation axis of the drive shaft.
  • a protrusion provided in the housing the protrusion projecting inward in the radial direction of the rotation axis of the drive shaft, and the discharge passage.
  • a metering orifice provided, and the cam ring includes a small-diameter portion having a first outer diameter whose outer diameter is a distance from a rotation axis of the drive shaft to an outer peripheral edge of the cam ring, and rotation of the drive shaft.
  • a first large-diameter portion and a second large-diameter portion which are a pair of large-diameter portions provided on both sides of the small-diameter portion in a direction around the axis and having a second outer diameter that is larger than the first outer diameter.
  • the projecting portion is disposed between the first large diameter portion and the second large diameter portion in a direction around the rotation axis of the drive shaft, and the main cam control chamber has the first large diameter In the area between the The pressure upstream of the metering orifice is introduced, and the housing opens into a secondary cam control chamber, which is a space between the second large diameter portion and the protruding portion, and more than the metering orifice.
  • a downstream pressure introduction passage for introducing downstream pressure is provided.
  • the control valve controls the pressure in the main cam control chamber to maintain the position of the cam ring.
  • the housing includes an annular adapter ring portion that surrounds the cam ring, and the adapter ring portion extends from a rotation axis of the drive shaft to the adapter ring portion.
  • the inner diameter of the adapter ring portion which is the distance to the inner peripheral surface, is larger in the region where the bearing is provided than in the region where the first seal member is in sliding contact with the inner peripheral surface of the adapter ring portion. It has the bearing holding part formed in the area
  • the protrusion is provided on the housing, and includes a protrusion that protrudes inward in the radial direction of the rotation axis of the drive shaft, and the cam ring includes A small diameter portion having a first outer diameter as an outer diameter that is a distance from a rotation axis of the drive shaft to an outer peripheral edge of the cam ring, and provided on both sides of the small diameter portion in a direction around the rotation axis of the drive shaft.
  • a first large diameter portion and a second large diameter portion which are a pair of large diameter portions having a second outer diameter whose outer diameter is larger than the first outer diameter, and the protrusion is a rotation of the drive shaft Arranged between the first large diameter portion and the second large diameter portion in the direction around the axis, and the main cam control chamber is provided in a region between the first large diameter portion and the protrusion,
  • the cam in the direction of decreasing the volume of the main cam control chamber Ring and the rotation direction of the drive shaft and the direction of rotation are matched.
  • this invention is not limited to the above-mentioned Example, Various modifications are included.
  • the above-described embodiments have been described in detail for easy understanding of the present invention, and are not necessarily limited to those having all the configurations described.
  • a part of the configuration of one embodiment can be replaced with the configuration of another embodiment, and the configuration of another embodiment can be added to the configuration of one embodiment.

Landscapes

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

Abstract

L'invention concerne une pompe à cylindrée variable (1) comportant des première et seconde zones d'admission, qui sont une paire de zones dans lesquelles le volume de chacune des chambres d'une pluralité de chambres (16) de pompe augmente après la rotation d'un rotor (7), qui sont disposées dans des positions symétriques par rapport à un axe de rotation O. En outre, des première et seconde zones de d'évacuation, qui forment une paire de zones dans lesquelles le volume de chacune des chambres la pluralité de chambres (16) de pompe diminue après la rotation du rotor (7), sont disposées dans des positions symétriques par rapport à l'axe de rotation O. Le rapport de l'ampleur de l'augmentation du volume de la pluralité de chambres (16) de pompe dans les première et seconde zones d'admission à l'ampleur de la diminution du volume de la pluralité de chambres (16) de pompe dans les première et seconde zones d'évacuation est modifié par rotation d'une came circulaire (8) dans un sens autour de l'axe de rotation O par rapport à un boîtier (2).
PCT/JP2018/002094 2017-02-10 2018-01-24 Pompe à cylindrée variable Ceased WO2018147081A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2017-022687 2017-02-10
JP2017022687A JP6711528B2 (ja) 2017-02-10 2017-02-10 可変容量形ポンプ

Publications (1)

Publication Number Publication Date
WO2018147081A1 true WO2018147081A1 (fr) 2018-08-16

Family

ID=63107453

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2018/002094 Ceased WO2018147081A1 (fr) 2017-02-10 2018-01-24 Pompe à cylindrée variable

Country Status (2)

Country Link
JP (1) JP6711528B2 (fr)
WO (1) WO2018147081A1 (fr)

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2012082762A (ja) * 2010-10-13 2012-04-26 Unisia Jkc Steering System Co Ltd 可変容量形ベーンポンプ
JP2014005781A (ja) * 2012-06-25 2014-01-16 Toyota Industries Corp タンデム式ベーン型圧縮機
JP2014163267A (ja) * 2013-02-22 2014-09-08 Kayaba Ind Co Ltd 可変容量型ベーンポンプ

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2012082762A (ja) * 2010-10-13 2012-04-26 Unisia Jkc Steering System Co Ltd 可変容量形ベーンポンプ
JP2014005781A (ja) * 2012-06-25 2014-01-16 Toyota Industries Corp タンデム式ベーン型圧縮機
JP2014163267A (ja) * 2013-02-22 2014-09-08 Kayaba Ind Co Ltd 可変容量型ベーンポンプ

Also Published As

Publication number Publication date
JP6711528B2 (ja) 2020-06-17
JP2018127983A (ja) 2018-08-16

Similar Documents

Publication Publication Date Title
JP5174720B2 (ja) 可変容量形ポンプ
JP5216397B2 (ja) 可変容量型ベーンポンプ
JP5116546B2 (ja) 可変容量型ベーンポンプ
JP5897945B2 (ja) ベーンポンプ
EP3321478A1 (fr) Appareil de commande de temporisation d'ouverture/de fermeture de soupape
CN105074216B (zh) 可变容量式叶片泵
WO2013141001A1 (fr) Pompe à palettes à capacité variable
JP5499151B2 (ja) 可変容量形ポンプ
JP5371795B2 (ja) 可変容量型ベーンポンプ
US9611848B2 (en) Variable displacement vane pump having connection groove communicating with suction-side back pressure port thereof
WO2013141010A1 (fr) Pompe à palettes à capacité variable
JP2012163040A (ja) ベーンポンプ
JP5583492B2 (ja) 可変容量型ベーンポンプ
JP6711528B2 (ja) 可変容量形ポンプ
JP5475701B2 (ja) ベーンポンプ
WO2023248695A1 (fr) Pompe à palettes
WO2019049660A1 (fr) Dispositif de type pompe
JP5412342B2 (ja) ベーンポンプ
JP7421601B2 (ja) ベーンポンプ
WO2019155758A1 (fr) Dispositif de type pompe
JP2010255551A (ja) 可変容量型ベーンポンプ
JP5555071B2 (ja) ベーンポンプ
JP2011127556A (ja) 可変容量形ベーンポンプ
JP5412341B2 (ja) ベーンポンプ
JP2015059523A (ja) 可変容量形ベーンポンプ

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 18751508

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 18751508

Country of ref document: EP

Kind code of ref document: A1