EP3225847A1 - Pompe à palettes à capacité variable - Google Patents

Pompe à palettes à capacité variable Download PDF

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Publication number
EP3225847A1
EP3225847A1 EP15863924.5A EP15863924A EP3225847A1 EP 3225847 A1 EP3225847 A1 EP 3225847A1 EP 15863924 A EP15863924 A EP 15863924A EP 3225847 A1 EP3225847 A1 EP 3225847A1
Authority
EP
European Patent Office
Prior art keywords
cam ring
pressure chamber
rotor
passage
fluid pressure
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Withdrawn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
EP15863924.5A
Other languages
German (de)
English (en)
Other versions
EP3225847A4 (fr
Inventor
Ryouichi Nagasaka
Shiro Suo
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.)
KYB Corp
Original Assignee
KYB 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 KYB Corp filed Critical KYB Corp
Publication of EP3225847A1 publication Critical patent/EP3225847A1/fr
Publication of EP3225847A4 publication Critical patent/EP3225847A4/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Withdrawn legal-status Critical Current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
    • 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
    • F04C14/223—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 using a movable cam
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/24—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C2/34—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
    • F04C2/344—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • 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
    • F04C2/3441—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 one line or continuous surface substantially parallel to the axis of rotation
    • F04C2/3442—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 one line or continuous surface substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the working space, being surfaces of revolution
    • 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
    • F04C2210/00—Fluid
    • F04C2210/20—Fluid liquid, i.e. incompressible
    • F04C2210/206—Oil

Definitions

  • the present invention relates to a variable displacement vane pump used as a fluid pressure source.
  • JP2013-194692A describes a variable displacement vane pump that is capable of changing an amount of working fluid discharged by changing an amount of eccentricity of a cam ring with respect to a rotor.
  • this variable displacement vane pump includes a first fluid pressure chamber and a second fluid pressure chamber that are formed on the outer circumferential side of the cam ring; a metering orifice that is provided in a discharge passage; a control valve that introduces control pressure to the first fluid pressure chamber in accordance with movement of a spool that slides in accordance with a differential pressure between upstream and downstream of the metering orifice; and a cam spring that always biases the cam ring towards the first fluid pressure chamber side from the second fluid pressure chamber.
  • the cam ring is provided so as to be movable between a maximum-eccentric position in which the amount of eccentricity is maximized when the cam ring is moved towards the first fluid pressure chamber side and a minimum-eccentric position in which the amount of eccentricity is minimized.
  • the present invention has been conceived in light of such technical problems, and an object thereof is to provide a variable displacement vane pump capable of preventing the follow-up delay of a cam ring.
  • a variable displacement vane pump includes: a rotor that is linked to a driving shaft; a plurality of vanes provided so as to be movable in a reciprocating manner in the radial direction with respect to the rotor; a cam ring in which tip-end portions of the vanes are in sliding contact with a cam face on an inner circumference of the cam ring with rotation of the rotor arranged in the cam ring, the cam ring being capable of being made eccentric with respect to the rotor; pump chambers that are defined between the rotor and the cam ring by being partitioned by the plurality of vanes; a first fluid pressure chamber and a second fluid pressure chamber that are defined in an accommodating space on an outer circumferential side of the cam ring; a biasing member configured to always bias the cam ring in a direction in which an amount of eccentricity is increased; a restrictor configured to impart resistance to flow of working fluid discharged from the pump chambers; a control valve configured to reduce the amount of eccentric
  • variable displacement vane pump 100 according to a first embodiment of the present invention will be described with reference to FIGs. 1 to 3 .
  • variable displacement vane pump 100 (hereinafter, simply referred to as "the vane pump 100") is used as a hydraulic pressure source for a hydraulic apparatus mounted on a vehicle, such as, for example, a power steering apparatus, a continuously variable transmission, and the like.
  • FIG. 1 in the vane pump 100, motive force from a driving source (not shown) is transmitted to a driving shaft 1, and a rotor 2 that is linked to the driving shaft 1 is rotated.
  • a driving source not shown
  • FIGs. 1 and 3 the rotor 2 is rotated in the counterclockwise direction as indicated by an arrow.
  • the vane pump 100 includes a plurality of vanes 3 that are provided so as to be movable in a reciprocating manner in the radial direction with respect to the rotor 2 and a cam ring 4 in which tip-end portions of the vanes 3 are in sliding contact with a cam face 4a, forming an inner circumference of the cam ring 4, by rotation of the rotor 2 arranged in the cam ring 4.
  • the cam ring 4 is can be made eccentric with respect to the center of the rotor 2.
  • the driving shaft 1 is rotatably supported by a pump body 6 via a bush 5.
  • a pump accommodating recessed portion 6a serving as a recessed portion for accommodating the cam ring 4 is formed in the pump body 6.
  • a seal 7 is provided in an end portion of the pump body 6, for preventing leakage of lubricating oil between an outer circumference of the driving shaft 1 and an inner circumference of the bush 5.
  • a side plate 8 that comes into contact with first side portions of the rotor 2 and the cam ring 4 is arranged on a bottom surface 6b of the pump accommodating recessed portion 6a.
  • An opening portion of the pump accommodating recessed portion 6a is sealed with a pump cover 9 that comes into contact with second side portions of the rotor 2 and the cam ring 4.
  • the pump cover 9 is fastened to the pump body 6 by bolts 10 (see FIG. 1 ).
  • the pump cover 9 and the side plate 8 are arranged so as to sandwich the rotor 2 and the cam ring 4 at both side surfaces thereof.
  • pump chambers 11 are defined between the rotor 2 and the cam ring 4 by being partitioned by the respective vanes 3.
  • the cam ring 4 is an annular member and has a suction region in which volumes of the pump chambers 11 partitioned by and between the respective vanes 3 are expanded by the rotation of the rotor 2 and a discharge region in which the volumes of the pump chambers 11 partitioned by and between the respective vanes 3 are contracted by the rotation of the rotor 2.
  • the pump chambers 11 suck working oil serving as working fluid in the suction region and discharge the working oil in the discharge region.
  • an upper part of the cam ring 4 corresponds to the suction region and a lower part corresponds to the discharge region.
  • An annular adapter ring 12 is fitted to an inner circumferential surface of the pump accommodating recessed portion 6a so as to surround the cam ring 4.
  • the adapter ring 12 is sandwiched by the pump cover 9 and the side plate 8 at both side surfaces thereof in the same way as the rotor 2 and the cam ring 4.
  • a support plate 13 that extends in parallel with the driving shaft 1 is supported on an inner circumferential surface of the adapter ring 12.
  • the cam ring 4 is supported by the support plate 13, and the cam ring 4 swings around inside the adapter ring 12 with the support plate 13 as a supporting point.
  • a groove 12a extending in parallel with the driving shaft 1 is formed at an axisymmetric position to the support plate 13 in the inner circumferential surface of the adapter ring 12.
  • a first hydraulic chamber 16 serving as a first fluid pressure chamber and a second hydraulic chamber 17 serving as a second fluid pressure chamber are defined by the support plate 13 and the seal member 14.
  • a cam spring 18 serving as a biasing member is provided on the second hydraulic chamber 17 side of the outer circumferential surface of the cam ring 4.
  • the cam spring 18 is fitted to a spring plug 19 that is screwed into the pump body 6 from the side and always biases the cam ring 4 towards the first hydraulic chamber 16 side via a through hole 12b formed in the adapter ring 12.
  • the cam ring 4 is always biased by the cam spring 18 in the direction in which an amount of eccentricity is increased.
  • the cam ring 4 swings around with the support plate 13 as the supporting point in such a manner that a differential pressure of the working oil between the first hydraulic chamber 16 and the second hydraulic chamber 17, biasing force exerted by the cam spring 18, and the internal pressure of the cam ring 4 are balanced.
  • the cam ring 4 swings around with the support plate 13 as the supporting point, the amount of eccentricity of the cam ring 4 with respect to the rotor 2 is changed.
  • a pump displacement volume per rotation of the rotor 2 is changed.
  • the pump cover 9 is provided with a suction port 20 having an arc-shaped opening so as to correspond to the suction region of the pump chambers 11.
  • the side plate 8 is provided with a discharge port 21 having an arc-shaped opening so as to correspond to the discharge region of the pump chambers 11.
  • the suction port 20 is formed so as to communicate with a suction passage 22 formed in the pump cover 9 and guides the working oil in the suction passage 22 to the suction region of the pump chambers 11.
  • the discharge port 21 is formed so as to communicate with a high-pressure chamber 23 formed in the pump body 6 and guides the working oil discharged from the discharge region of the pump chambers 11 to the high-pressure chamber 23.
  • the high-pressure chamber 23 is defined by closing a groove portion 6c, which is formed so as to open at the bottom surface 6b of the pump accommodating recessed portion 6a, with the side plate 8.
  • the working oil in the high-pressure chamber 23 is guided to an external hydraulic apparatus of the vane pump 100 through a discharge passage 24 (see FIG. 3 ) formed in the pump body 6.
  • the pump body 6 is provided with a low-pressure chamber 25, serving as a first guiding passage, that is formed at a position corresponding to the suction region of the pump chambers 11 on the bottom surface 6b of the pump accommodating recessed portion 6a.
  • the low-pressure chamber 25 is defined by closing a groove portion 6d, which is formed so as to open at a position corresponding to the suction region of the pump chambers 11, with the side plate 8.
  • the low-pressure chamber 25 is formed in a straight line parallel to the driving shaft 1, and its back-most end portion communicates with a boundary between the bush 5 and the seal 7.
  • the low-pressure chamber 25 is always connected to the second hydraulic chamber 17, and the working oil that has leaked out between the outer circumference of the driving shaft 1 and the inner circumference of the bush 5 is recovered and returned to the pump chambers 11 in the suction region.
  • the pump body 6 is provided with a valve accommodating hole 26 that is formed in the direction perpendicular to the axial direction of the driving shaft 1.
  • a control valve 27 that controls the working oil pressures in the first hydraulic chamber 16 and the second hydraulic chamber 17 is accommodated.
  • the valve accommodating hole 26 is sealed by a plug 28.
  • the control valve 27 includes a spool 29 that is slidably inserted into the valve accommodating hole 26, a first pilot chamber 30 that faces one end of the spool 29, a second pilot chamber 31 that faces the other end of the spool 29, and a return spring 32 that is accommodated in the second pilot chamber 31 and biases the spool 29 in the direction in which the volume of the second pilot chamber 31 is expanded.
  • the spool 29 includes a first land portion 29a and a second land portion 29b that slide along an inner circumferential surface of the valve accommodating hole 26, an annular groove 29c that is formed between the first land portion 29a and the second land portion 29b, a first rod portion 29d that is connected to the first land portion 29a and extends within the first pilot chamber 30, and a second rod portion 29e that is connected to the second land portion 29b and extends within the second pilot chamber 31.
  • the first rod portion 29d comes into contact with the plug 28 when the spool 29 is moved in the direction in which the volume of the first pilot chamber 30 is contracted.
  • the second rod portion 29e comes into contact with an end surface of the valve accommodating hole 26 on the opposite side from the plug 28.
  • the return spring 32 surrounds the second rod portion 29e and is received in the second pilot chamber 31.
  • a first passage 35 and a second passage 36 which serves as a guiding passage, that communicate with the first hydraulic chamber 16 and the second hydraulic chamber 17, respectively; a first pressure guiding passage 38 that guides to the first pilot chamber 30 the working oil that has been discharged from the high-pressure chamber 23 to the upstream side of an orifice 37 serving as a restrictor; and a second pressure guiding passage 39 that guides to the second pilot chamber 31 the working oil that has been discharged from the high-pressure chamber 23 to the downstream side of the orifice 37 are connected to the control valve 27.
  • a drain passage 40 that is always in communication with the suction passage 22 is connected to the second hydraulic chamber 17.
  • the first passage 35 and the second passage 36 are formed so as to open at the valve accommodating hole 26 and to open at the first hydraulic chamber 16 and the second hydraulic chamber 17, respectively, by penetrating through the adapter ring 12.
  • the spool 29 slides to a position at which the thrust force exerted by the differential pressure between the first pilot chamber 30 and the second pilot chamber 31, which face the respective ends of the spool 29, is balanced with the biasing force exerted by the return spring 32.
  • the first passage 35 is opened/closed by the first land portion 29a, and the working oil in the first hydraulic chamber 16 is supplied/discharged depending on the position of the spool 29.
  • the second passage 36 always opens to the annular groove 29c regardless of the position of the spool 29.
  • the spool 29 is moved against the biasing force exerted by the return spring 32.
  • the first passage 35 is shifted into an open state, communicates with the first pilot chamber 30, and communicates with the first pressure guiding passage 38 through the first pilot chamber 30.
  • the second passage 36 is held in the open state and communicates with the annular groove 29c.
  • the second hydraulic chamber 17 communicates with the suction passage 22 through the drain passage 40, as the pressure in the first hydraulic chamber 16 is increased, the amount of eccentricity of the cam ring 4 is reduced.
  • the cam ring 4 is moved in the direction in which the amount of eccentricity with respect to the rotor 2 is reduced.
  • the working oil at the upstream side and the downstream side of the orifice 37 serving as the restrictor, which is interposed in the discharge passage 24 and imparts resistance to the flow of the working oil, is respectively guided to the first pilot chamber 30 and the second pilot chamber 31.
  • the working oil in the high-pressure chamber 23 is guided directly to the first pilot chamber 30 through the first pressure guiding passage 38 without passing through the orifice 37, and is also guided to the second pilot chamber 31 through the orifice 37. Therefore, the spool 29 is moved in accordance with the differential pressure between upstream and downstream of the orifice 37.
  • FIGs. 4 to 6 are hydraulic circuit diagrams of the vane pump 100 and respectively show states in which the amount of eccentricity of the cam ring 4 with respect to the rotor 2 is at maximum, intermediate, and minimum levels.
  • the working oil is sucked from the suction passage 22 through the suction port 20 into the pump chambers 11 whose spaces are expanded between the respective vanes 3 with the rotation of the rotor 2.
  • the working oil is discharged through the discharge port 21 to the high-pressure chamber 23 from the pump chambers 11 whose spaces are contracted between the respective vanes 3.
  • the working oil that has been discharged to the high-pressure chamber 23 is supplied to the hydraulic apparatus through the discharge passage 24.
  • the differential pressure is generated between upstream and downstream of the orifice 37, which is interposed in the discharge passage 24, and the pressures at the upstream and downstream sides of the orifice 37 are guided to the first pilot chamber 30 and the second pilot chamber 31, respectively.
  • the spool 29 of the control valve 27 slides to the position at which the thrust force exerted by the differential pressure between the first pilot chamber 30 and the second pilot chamber 31 is balanced with the biasing force exerted by the return spring 32.
  • the rotation speed of the rotor 2 is low and a pump discharge flow amount is small at a pump starting time at which the rotation speed of the rotor 2 is equal to or lower than a predetermined rotation speed
  • the differential pressure between upstream and downstream of the orifice 37 is small, and the thrust force exerted by the differential pressure between the first pilot chamber 30 and the second pilot chamber 31 is small. Therefore, the biasing force exerted by the return spring 32 is greater than the thrust force exerted by the differential pressure between the first pilot chamber 30 and the second pilot chamber 31, and the return spring 32 is in an elongated state.
  • the amount of eccentricity of the cam ring 4 with respect to the rotor 2 is maximized to cause the pump displacement volume per rotation of the rotor 2 to be maximized, and the pump discharge flow amount of the vane pump 100 becomes the flow amount substantially in proportion to the rotation speed of the rotor 2. Therefore, even when the rotation speed of the rotor 2 is low, it is possible to supply the working oil to the hydraulic apparatus at a sufficient flow amount.
  • the differential pressure between upstream and downstream of the orifice 37 is increased, and thereby, the thrust force exerted by the differential pressure between the first pilot chamber 30 and the second pilot chamber 31 is balanced with or becomes slightly greater than the biasing force exerted by the return spring 32.
  • the spool 29 starts to move against the biasing force exerted by the return spring 32.
  • the pump discharge flow amount of the vane pump 100 becomes substantially constant.
  • the pump discharge flow amount is reduced and the differential pressure between upstream and downstream of the orifice 37 is reduced.
  • the pump discharge flow amount When the pump discharge flow amount is increased, the differential pressure between upstream and downstream of the orifice 37 is increased, and the spool 29 is moved so as to compress the return spring 32, and thereby, the first passage 35 and the second passage 36 are again shifted into the open state. As described above, because a control is performed such that the first passage 35 is opened/closed to make the differential pressure between upstream and downstream of the orifice 37 constant, the pump discharge flow amount becomes substantially constant.
  • the spool 29 is moved in accordance with the change in the rotation speed of the rotor 2 and the first passage 35 is opened/closed by the movement of the spool 29, and thereby, the pump discharge flow amount is adjusted. More specifically, at the pump starting time at which the rotation speed of the rotor 2 is equal to or lower than the predetermined rotation speed, because the first passage 35 is closed by the spool 29, the amount of eccentricity of the cam ring 4 with respect to the rotor 2 is maximized, and the pump discharge flow amount is increased along with the increase in the rotation speed of the rotor 2.
  • the second passage 36 opens at the valve accommodating hole 26 and opens at the inner circumferential surface of the adapter ring 12 in the second hydraulic chamber 17 by penetrating through the adapter ring 12, it is possible to shorten a distance between the control valve 27, which is arranged radially outside of the adapter ring 12 so as to be adjacent to the adapter ring 12, and the second hydraulic chamber 17.
  • variable displacement vane pump 200 according to a second embodiment of the present invention will be described with reference to FIGs. 7 and 8 .
  • variable displacement vane pump 200 in this embodiment differs from that in the first embodiment in a configuration of a second passage 136, and other points are the same as those in the first embodiment. Therefore, components that are the same as those in the first embodiment are assigned the same reference signs, and descriptions thereof shall be omitted.
  • the second passage 36 is formed so as to open at the valve accommodating hole 26 and to open at the second hydraulic chamber 17 by penetrating through the adapter ring 12 in the first embodiment, whereas in this embodiment, the second passage 136 serving as a guiding passage is constituted of the low-pressure chamber 25 and a straight passage 101, which serves as a second guiding passage that connects the back-anost end portion of the low-pressure chamber 25 and the annular groove 29c of the control valve 27 in a straight line.
  • the second passage 136 opens at the bottom surface 6b of the pump accommodating recessed portion 6a in the suction region in which the volumes of the pump chambers 11 are expanded, a through hole needs not be provided in the adapter ring 12, which defines an accommodating space on the outer circumferential side of the cam ring 4.
  • the adapter ring 12 defines an accommodating space on the outer circumferential side of the cam ring 4.
  • the second passage 136 is constituted of the low-pressure chamber 25 that is formed in a straight line parallel to the driving shaft 1 and the straight passage 101 that connects the back-most end portion of the low-pressure chamber 25 and the annular groove 29c of the control valve 27 in a straight line, it is possible to form the second passage 136 in the pump body 6 only by providing two straight passages. Therefore, it is possible to improve the ease of processing for providing the second passage 136 and to reduce the manufacturing cost.
  • the second passage 136 is constituted of the low-pressure chamber 25, it is possible to form the second passage 136 only by providing the straight passage 101. Therefore, it is possible to further improve the ease of processing for providing the second passage 136 and to further reduce the manufacturing cost.
  • the configuration is not limited thereto, and at least one of the low-pressure chamber 25 and the straight passage 101 may be formed to have a curved shape or a shape having a bent portion at an intermediate position.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Rotary Pumps (AREA)
EP15863924.5A 2014-11-26 2015-11-24 Pompe à palettes à capacité variable Withdrawn EP3225847A4 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2014239200A JP6375212B2 (ja) 2014-11-26 2014-11-26 可変容量型ベーンポンプ
PCT/JP2015/082937 WO2016084804A1 (fr) 2014-11-26 2015-11-24 Pompe à palettes à capacité variable

Publications (2)

Publication Number Publication Date
EP3225847A1 true EP3225847A1 (fr) 2017-10-04
EP3225847A4 EP3225847A4 (fr) 2018-07-18

Family

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EP15863924.5A Withdrawn EP3225847A4 (fr) 2014-11-26 2015-11-24 Pompe à palettes à capacité variable

Country Status (5)

Country Link
US (1) US20170321696A1 (fr)
EP (1) EP3225847A4 (fr)
JP (1) JP6375212B2 (fr)
CN (1) CN107002672A (fr)
WO (1) WO2016084804A1 (fr)

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US20180135625A1 (en) * 2015-04-09 2018-05-17 Hitachi Automotive Systems, Ltd. Variable capacity oil pump
JP7042099B2 (ja) 2018-02-06 2022-03-25 日立Astemo株式会社 ポンプ装置
MX2021014215A (es) 2019-05-20 2022-01-06 Stackpole Int Engineered Products Ltd Valvula de carrete utilizada en una bomba de paletas de desplazamiento variable.
CN113994094B (zh) * 2019-05-29 2023-06-20 皮尔伯格泵技术有限责任公司 可变排量润滑剂泵
DE112020007530T5 (de) * 2020-08-21 2023-09-07 Pierburg Pump Technology Gmbh Schmiermittelpumpe mit variabler Verdrängung

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US8444395B2 (en) * 2006-01-31 2013-05-21 Magna Powertrain, Inc. Variable displacement variable pressure vane pump system
JP5216397B2 (ja) * 2008-04-15 2013-06-19 カヤバ工業株式会社 可変容量型ベーンポンプ
JP5116546B2 (ja) * 2008-04-23 2013-01-09 カヤバ工業株式会社 可変容量型ベーンポンプ
JP2010255551A (ja) * 2009-04-27 2010-11-11 Kayaba Ind Co Ltd 可変容量型ベーンポンプ
JP2010255552A (ja) * 2009-04-27 2010-11-11 Kayaba Ind Co Ltd 可変容量型ベーンポンプ
JP5926993B2 (ja) * 2012-03-21 2016-05-25 Ｋｙｂ株式会社 可変容量型ベーンポンプ
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JP6375212B2 (ja) 2018-08-15
CN107002672A (zh) 2017-08-01
US20170321696A1 (en) 2017-11-09
WO2016084804A1 (fr) 2016-06-02
JP2016098802A (ja) 2016-05-30
EP3225847A4 (fr) 2018-07-18

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