WO2023042530A1 - オイルポンプ - Google Patents

オイルポンプ Download PDF

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Publication number
WO2023042530A1
WO2023042530A1 PCT/JP2022/027076 JP2022027076W WO2023042530A1 WO 2023042530 A1 WO2023042530 A1 WO 2023042530A1 JP 2022027076 W JP2022027076 W JP 2022027076W WO 2023042530 A1 WO2023042530 A1 WO 2023042530A1
Authority
WO
WIPO (PCT)
Prior art keywords
rotor
pump
oil pump
cam profile
chamber
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/JP2022/027076
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
大輔 加藤
浩二 佐賀
暢昭 寒川
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.)
Astemo Ltd
Original Assignee
Hitachi Astemo 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 Astemo Ltd filed Critical Hitachi Astemo Ltd
Priority to CN202280058623.7A priority Critical patent/CN117881890A/zh
Priority to JP2023548140A priority patent/JPWO2023042530A1/ja
Priority to US18/685,353 priority patent/US12286970B2/en
Publication of WO2023042530A1 publication Critical patent/WO2023042530A1/ja
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C2/34—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
    • F04C2/344—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/08—Rotary pistons
    • F01C21/0809—Construction of vanes or vane holders
    • F01C21/0818—Vane tracking; control therefor
    • F01C21/0827—Vane tracking; control therefor by mechanical means
    • F01C21/0836—Vane tracking; control therefor by mechanical means comprising guiding means, e.g. cams, rollers
    • 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
    • F04C14/226—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 by pivoting the cam around an eccentric axis
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/06—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • 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
    • 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 an oil pump.
  • an oil pump for example, an oil pump described in Patent Document 1 below is known.
  • the oil pump of Patent Document 1 includes a housing having a pump housing chamber, a cam ring provided inside the pump housing chamber, a rotor housed on the inner peripheral side of the cam ring, and a rotor that can protrude from the outer peripheral side of the rotor. and a plurality of vanes provided in the.
  • a suction opening is formed in the bottom surface of the pump housing chamber for supplying oil to the working chamber provided between the adjacent vanes.
  • the present invention has been devised in view of the conventional circumstances, and an object thereof is to provide an oil pump capable of suppressing noise caused by vanes falling into the suction opening.
  • the terminating portion of the suction opening includes: a terminating inner peripheral portion; a terminating outer peripheral portion located radially outside the cam profile surface; a curved surface portion connecting the terminating inner peripheral portion and the terminating outer peripheral portion; have. At the intersection where the curved portion intersects the cam profile surface, the radial length of the vane facing the intake opening is less than half the total length of the vane.
  • FIG. 1 is an exploded perspective view of a variable displacement oil pump according to a first embodiment
  • FIG. 1 is a front view of a variable displacement oil pump according to a first embodiment
  • FIG. FIG. 3 is a cross-sectional view of the variable displacement oil pump of the first embodiment cut along line AA in FIG. 2
  • 2 is a partially enlarged plan view of the variable displacement oil pump of the first embodiment
  • FIG. 5 is a schematic cross-sectional view of the housing, vanes and cam ring of the first embodiment taken along line BB of FIG. 4
  • FIG. FIG. 4 is a schematic cross-sectional view of the housing, vanes and cam ring of the first embodiment showing the vanes depressed into the intake port;
  • FIG. 1 is a front view of a variable displacement oil pump according to a first embodiment
  • FIG. 3 is a cross-sectional view of the variable displacement oil pump of the first embodiment cut along line AA in FIG. 2
  • 2 is a partially enlarged plan view of the variable displacement oil pump of the first embodiment
  • FIG. 2 is a partially enlarged plan view of a conventional variable displacement oil pump
  • 1 is a schematic cross-sectional view of a prior art housing, vanes and cam ring showing the vanes depressed into the intake port
  • FIG. FIG. 6 is a partially enlarged plan view of a variable displacement oil pump of a second embodiment
  • FIG. 5 is a schematic cross-sectional view of the housing, vanes and cam ring of the second embodiment
  • variable displacement oil pump as an oil pump of the present invention
  • FIG. 1 is an exploded perspective view of a variable displacement oil pump according to a first embodiment provided in a cylinder block or the like of an internal combustion engine (not shown).
  • FIG. 2 is a front view of the variable displacement oil pump of the first embodiment with the cover member 2 removed. 2, the electromagnetic valve 13 is omitted for the sake of simplification.
  • 3 is a cross-sectional view of the variable displacement oil pump of the first embodiment taken along line AA in FIG. 2.
  • the variable displacement oil pump includes a housing consisting of a housing body 1 and a cover member 2, a drive shaft 3, a rotor 4, a plurality of (seven in this embodiment) vanes 5, a cam ring 6, and a first coil.
  • a spring 7, a pair of ring members 8, first to third seal means 9 to 11, and five fixing means such as a screw member 12, an electromagnetic valve 13, and a relief valve 14 are provided.
  • the housing body 1 is integrally formed of a metal material, such as an aluminum alloy material, and is formed into a cylindrical shape with a bottom so that one end side is open and a pump accommodating chamber 1a recessed in a substantially cylindrical shape is provided therein.
  • the housing body 1 has a first bearing hole 1c, which is a drive shaft insertion hole for rotatably supporting one end of the drive shaft 3, at the center of the bottom surface 1b of the pump housing chamber 1a.
  • the housing body 1 is formed with an annularly continuous flat mounting surface 1d on the outer peripheral side of the opening of the pump accommodating chamber 1a.
  • the mounting surface 1d of the housing body 1 is formed with five screw holes 1e into which the respective screw members 12 are screwed.
  • the cover member 2 is made of a metal material, such as an aluminum alloy material, and is used to close the opening of the housing body 1.
  • the cover member 2 has a flat plate shape and has an outer shape corresponding to the outer shape of the housing body 1 .
  • the cover member 2 is formed with a second bearing hole 2a, which is a drive shaft insertion hole for rotatably supporting the other end of the drive shaft 3, at a position corresponding to the first bearing hole 1c of the housing body 1.
  • a second bearing hole 2a which is a drive shaft insertion hole for rotatably supporting the other end of the drive shaft 3, at a position corresponding to the first bearing hole 1c of the housing body 1.
  • five fixing means through-holes 2b are formed respectively.
  • the housing main body 1 and the cover member 2 constitute a housing that partitions the pump accommodating chamber 1a.
  • This housing is not immersed in the oil provided inside the internal combustion engine. That is, the housing is positioned above the oil level in an oil pan (not shown) provided in the internal combustion engine.
  • the drive shaft 3 passes through the center of the pump housing chamber 1a and is rotatably supported by the housing, and is rotationally driven by a crankshaft (not shown).
  • the drive shaft 3 rotates the rotor 4 in the counterclockwise direction (rotational direction R) in FIG. 2 by the rotational force transmitted from the crankshaft.
  • the rotor 4 has a cylindrical shape and is rotatably accommodated in the pump accommodation chamber 1a. A central portion of the rotor 4 is coupled to the drive shaft 3 . As shown in FIGS. 1 and 2, the rotor 4 is formed with seven slits 4a radially extending from the inner center side of the rotor 4 to the outside in the radial direction. As shown in FIGS. 1 and 2, each slit 4a has a back pressure chamber 4b formed at its inner base end for introducing oil discharged to a discharge port 24, which will be described later. As shown in FIG. 2 , the back pressure chamber 4 b opens into circular recesses 4 c formed on both side surfaces of the rotor 4 .
  • the circular recess 4c has clearances with the bottom surface 1b of the pump housing chamber 1a and with the inner side surface 2d of the cover member 2.
  • Oil from a second chamber 27, which will be described later flows into the back pressure chamber 4b via the discharge port 24, an oil introduction groove (not shown) formed in the bottom surface 1b of the pump housing chamber 1a, and the circular recess 4c.
  • the vanes 5 retractably accommodated in the slits 4a of the rotor 4 are pushed outward by the centrifugal force accompanying the rotation of the rotor 4 and the hydraulic pressure in the back pressure chamber 4b.
  • the vanes 5 are made of metal in the form of thin plates, and are accommodated in the slits 4a of the rotor 4 so as to be retractable. A small gap is formed between the vane 5 and the slit 4a when the vane 5 is accommodated in the slit 4a.
  • the vane 5 has a tip surface slidably contacting the cam profile surface 6a of the cam ring 6 which continues in a circular shape, and an inner end surface of the base end sliding on the outer peripheral surface of the ring member 8. contact as possible.
  • the drive shaft 3, rotor 4, and vanes 5 constitute a pump structure.
  • a cam ring 6 surrounding this pump structure is integrally formed in a cylindrical shape from sintered metal.
  • One side surface 6b of the cam ring 6 facing the inner side surface 2d of the cover member 2 is formed with an inner peripheral groove 6c extending in an arc shape along the cam profile surface 6a at a position adjacent to the cam profile surface 6a.
  • the circumferential length of the inner circumferential groove 6c is set to be larger than the range including the three vanes 5 adjacent in the rotational direction R of the rotor 4 in the suction region of the variable displacement oil pump. It is As shown in FIG.
  • first side clearance C1 through which oil from an operation chamber 15, which will be described later, can flow.
  • second side clearance C2 is provided between the other side surface 6d of the cam ring 6 and the bottom surface 1b of the pump housing chamber 1a, through which oil from the working chamber 15, which will be described later, can flow.
  • a first coil spring 7 located on the outer circumference of the cam ring 6 is housed inside the housing body 1 and always biases the cam ring 6 in a direction to increase the eccentricity of the cam ring 6 with respect to the rotation center of the rotor 4 .
  • a ring member 8 is slidably arranged in a circular concave portion 4c provided in the rotor 4. As shown in FIG.
  • the first to third seal means 9 to 11 are mounted on the cam ring 6 so as to be slidable on the first to third seal contact surfaces 1g, 1h and 1i, and partition the cam ring 6 and the housing body 1.
  • first and second chambers 26 and 27, which are control hydraulic chambers and will be described later, are fluid-tightly defined between the outer peripheral surface of the cam ring 6 and the inner peripheral surface of the housing body 1 .
  • the first sealing means 9 includes a first sealing member 16 and a first elastic member 17 that biases the first sealing member 16 toward the inner peripheral surface of the housing body 1 .
  • the second seal means 10 also includes a second seal member 18 and a second elastic member 19 that biases the second seal member 18 toward the inner peripheral surface of the housing body 1 .
  • the third sealing means 11 includes a third sealing member 20 and a third elastic member 21 that biases the third sealing member 20 toward the inner peripheral surface of the housing body 1 .
  • a circular support hole 1f for rockably supporting the cam ring 6 via a cylindrical pivot pin 22 is formed at a predetermined position on the inner peripheral wall of the pump housing chamber 1a.
  • cam ring reference line M in FIG. cam ring reference line M”.
  • the inner peripheral wall of the pump accommodating chamber 1a is formed with a first seal contact surface 1g in a region on one side (right side in FIG. 2) of the cam ring reference line M.
  • a first seal member 16 provided on the outer periphery of the cam ring 6 is slidably brought into contact with the first seal contact surface 1g.
  • the first seal contact surface 1g is an arcuate surface having a predetermined radius R1 from the center O2 of the pivot pin 22.
  • the radius R1 is set to a circumferential length that allows the first seal member 16 to always slidably contact within the eccentric swing range of the cam ring 6 .
  • a second seal contact surface 1h is formed on the inner peripheral wall of the pump housing chamber 1a in a region on the other side (left side in FIG. 2) of the cam ring reference line M.
  • a second seal member 18 provided on the outer periphery of the cam ring 6 is slidably brought into contact with the second seal contact surface 1h.
  • the second seal contact surface 1h is an arcuate surface formed from the center O2 of the pivot pin 22 with a predetermined radius R2 smaller than the radius R1.
  • the radius R2 is set to a circumferential length that allows the second seal member 18 to always slidably contact within the eccentric swing range of the cam ring 6 .
  • a third seal contact surface is formed on the inner peripheral wall of the pump housing chamber 1a at a position farther from the pivot pin 22 than the second seal contact surface 1h in the region on the left side of the cam ring reference line M. 1i is formed.
  • a third seal member 20 provided on the outer periphery of the cam ring 6 is slidably brought into contact with the third seal contact surface 1i.
  • the third seal contact surface 1i is an arcuate surface extending from the center O2 of the pivot pin 22 with a predetermined radius R3 larger than the radius R1.
  • the radius R3 is set to a circumferential length that allows the third seal member 20 to always slidably contact within the eccentric swing range of the cam ring 6 .
  • a suction port 23 (indicated by a solid line and a broken line in FIG. 2), which is an arc-shaped suction opening, is provided in the outer peripheral area of the drive shaft 3.
  • a discharge port 24, which is also an arc-shaped discharge opening, is cut out so as to face each other with the drive shaft 3 interposed therebetween.
  • the suction port 23 is formed on the bottom surface 1b of the pump housing chamber 1a at a position opposite to the pivot pin 22, and is positioned in the direction of the rotational axis O1 of the rotor 4, and is moved out of the plurality of working chambers 15 as the rotor 4 rotates.
  • the suction port 23 has a tapered end portion 23 a formed at a position where the suction port 23 ends in the rotational direction R of the rotor 4 . Termination portion 23a will be described in detail later.
  • a suction groove 2e having a shape substantially similar to that of the suction port 23 is formed in the inner surface 2d of the cover member 2 at a position corresponding to the suction port 23.
  • the suction groove 2e communicates with a suction hole 2c (see FIG. 1) provided in the cover member 2.
  • a suction hole 2c (see FIG. 1) provided in the cover member 2.
  • the discharge port 24 is located on the side of the pivot pin 22 and opens in a region (discharge region) where the internal volume of the working chamber 15 decreases due to the pump action of the pump structure.
  • a discharge hole 1j having a circular cross section is provided which penetrates the side wall of the housing body 1 and opens to the outside.
  • the oil pressurized by the pumping action and discharged to the discharge port 24 flows from the discharge hole 1j through the discharge passage (not shown) and the main gallery (not shown) to each slide of the internal combustion engine (not shown). parts, valve timing devices, etc.
  • a discharge groove 2f having the same shape as the discharge port 24 is formed in the inner surface 2d of the cover member 2 at a position corresponding to the discharge port 24.
  • a spring housing the first coil spring 7 is provided between the second seal member 18 and the third seal member 20 at a position facing the flat portion 6e provided on the outer circumference of the cam ring 6.
  • a storage chamber 25 is provided in the spring housing chamber 25, the first coil spring 7 compressed by a predetermined set load W1 is elastically in contact with one end wall of the spring housing chamber 25 and the flat portion 6e. In this manner, the first coil spring 7 constantly moves the cam ring 6 through the flat portion 6e in the direction in which the eccentricity increases (counterclockwise direction in FIG. 2) with the elastic force based on the set load W1. energize.
  • the outer peripheral portion of the cam ring 6 has first to third seal surfaces at positions facing the first to third seal contact surfaces 1g to 1i. Portions 6f to 6h protrude respectively.
  • the first to third seal surfaces have predetermined radii slightly smaller than the radii R1, R2, R3 forming the corresponding seal contact surfaces 1g, 1h, 1i from the center O2 of the pivot pin 22. It is composed by A small clearance is formed between each seal surface and each seal contact surface 1g, 1h, 1i.
  • First and second seal holding grooves 6i, 6j and 6k each having a U-shaped cross section are formed along the axial direction of the cam ring 6 on the seal surfaces of the seal holding portions 6f, 6g and 6h, respectively. .
  • first to third seal members 16, 18, 20 contacting the first to third seal contact surfaces 1g, 1h, 1i when the cam ring 6 eccentrically swings are provided. retained respectively.
  • a first chamber 26 is defined in the outer peripheral area of the cam ring 6 by the outer peripheral portion of the substantially circular support wall portion 6m of the cam ring 6 surrounding the pivot pin 22 and the first seal member 16.
  • a second chamber 27 is defined by the seal member 18 and the third seal member 20 .
  • Pump discharge pressure is introduced into the first chamber 26 through an oil passage (not shown), while pump discharge pressure is supplied to the second chamber 27 through an oil passage (not shown) and the solenoid valve 13 .
  • the volume of the first chamber 26 increases when the oil discharged from the discharge port 24 is guided and the cam ring 6 moves in the direction in which the flow rate of the oil discharged from the discharge port 24 decreases.
  • the second chamber 27 is a space that includes the spring housing chamber 25, and is configured so that its volume increases when the cam ring 6 moves in the direction in which the flow rate of the oil discharged from the discharge port 24 increases. ing.
  • the surface adjacent to the first chamber 26 serves as a first pressure receiving surface 6n that receives the pump discharge pressure introduced into the first chamber 26.
  • a surface of the outer peripheral surface of the cam ring 6 adjacent to the second chamber 27 serves as a second pressure receiving surface 6o (including the flat portion 6e) that receives the pump discharge pressure introduced into the second chamber 27.
  • each pump discharge pressure acts on the corresponding first and second pressure receiving surfaces 6n, 6o of the cam ring 6, so that the urging force based on the hydraulic pressure acting on the first and second pressure receiving surfaces 6n, 6o and the first
  • the amount of eccentricity of the cam ring 6 is controlled by the balance with the biasing force of the coil spring 7 .
  • the pressure receiving area of the first pressure receiving surface 6n is set larger than the pressure receiving area of the second pressure receiving surface 6o, and when hydraulic pressure acts on both pressure receiving surfaces 6n and 6o, the amount of eccentricity decreases as a whole.
  • the cam ring 6 is urged in the direction.
  • the solenoid valve 13 includes a valve portion 28 for supplying and discharging oil according to the axial position in the moving direction of the spool (not shown), and a solenoid portion 29 for controlling the axial position of the spool by energization.
  • the solenoid valve 13 is provided on a regular hexahedral block portion 1k integrally formed on the rear surface of the housing body 1 as shown in FIG. More specifically, the valve portion 28 located on the tip side of the solenoid valve 13 is housed in a control valve housing portion 30 recessed with respect to one surface 1m of the block portion 1k as shown in FIG. A solenoid portion 29 located on the rear end side of 13 protrudes outward from the surface 1m of the block portion 1k.
  • the relief valve 14 is housed in a valve housing hole (not shown) formed in the vicinity of the discharge port 24 in the housing body 1, and opens to discharge when the discharge pressure of the variable displacement oil pump is higher than a predetermined discharge pressure. It functions to release pressure to the outside.
  • the relief valve 14 includes a lid 31 closing the valve housing hole, a spring 32 having one end in contact with the lid 31, and a ball 33 having the other end in contact with the spring 32. As shown in FIG. When the discharge pressure of the variable displacement oil pump is higher than a predetermined discharge pressure, the discharge pressure acts on the ball 33, and when the ball 33 contracts the spring 32 against the lid 31, the back side of the ball 33 The discharge pressure is released to the outside through a relief hole (not shown) provided.
  • FIG. 4 shows a portion of the variable displacement oil pump of the first embodiment when one vane 5 passes through the terminal end 23a of the suction port 23 with the cam ring 6 being most eccentric (see FIG. 2).
  • 2 is a typical enlarged plan view.
  • FIG. 4 illustration of the rotor 4 and the ring member 8 is omitted for convenience of explanation.
  • FIG. 5 is a schematic cross-sectional view of the housing, vanes 5 and cam ring 6 of the first embodiment taken along line BB of FIG.
  • FIG. 6 is a schematic cross-sectional view of the housing, vanes 5 and cam ring 6 of the first embodiment showing vanes 5 depressed into intake port 23 .
  • 5 and 6 show a cross-sectional view of a state where the cover member 2 is attached, and the illustration of the bottom of the intake port 23, the bottom of the intake groove 2e, and the inner peripheral groove 6c is omitted for convenience of explanation.
  • the terminating portion 23a of the intake port 23 includes an inner terminating portion 23b (indicated by a solid line and a dashed line in FIG. 4) and an outer terminating portion 23c (indicated by a dashed line in FIG. 4) positioned outside the inner terminating portion 23b. and a curved surface portion (indicated by solid and broken lines in FIG. 4) 23d connecting the terminal inner peripheral portion 23b and the terminal outer peripheral portion 23c.
  • the terminal inner peripheral portion 23b is located inside the cam profile surface 6a of the cam ring 6.
  • the end inner peripheral portion 23 b is provided so that the inner periphery of the intake port 23 becomes larger radially outward of the rotor 4 as it advances in the rotational direction R of the rotor 4 .
  • the terminal inner peripheral portion 23b is the minor angle among the angles formed by the terminal inner peripheral portion 23b and a line N passing through the rotation axis O1 of the pump component and one end 23e of the terminal inner peripheral portion 23b.
  • the inner circumference of the intake port 23 is linearly inclined radially outward of the rotor 4 so that ⁇ is a predetermined angle, which is about 50° in this embodiment.
  • the terminal outer peripheral portion 23c is located outside the cam profile surface 6a of the cam ring 6. More specifically, the terminal outer peripheral portion 23c has a cam profile surface in a region overlapping the inner peripheral groove 6c of the cam ring 6 when viewed in the direction along the rotation axis O1 of the pump assembly as shown in FIG. It is arranged near 6a.
  • the terminating outer peripheral portion 23c extends arcuately along the rotation direction R of the rotor 4 from the intersection point P of the terminating outer peripheral portion 23c and the line N to one end 23f of the curved surface portion 23d in parallel with the cam profile surface 6a.
  • the terminal outer peripheral portion 23c extends in a curved shape to one end 23f of the curved surface portion 23d so as to be substantially parallel to the arc-shaped cam profile surface 6a.
  • the terminal outer peripheral portion 23c is located outside the cam profile surface 6a and is smoothly connected via an intersection point P to the port outer peripheral portion 23i of the intake port 23 that extends in an arc parallel to the cam profile surface 6a. .
  • the curved surface portion 23d is provided at the extreme end of the intake port 23 in the rotational direction R of the rotor 4, and extends curvedly from one end 23f to the other end 23g so as to swell in the rotational direction R side.
  • the curved surface portion 23d extends from the outside to the inside of the cam profile surface 6a so as to intersect the cam profile surface 6a at the intersection X.
  • most of the curved surface portion 23d is located inside the crossing portion X, that is, inside the cam profile surface 6a, while the remaining portion of the curved surface portion 23d intersects. It is arranged outside the portion X, that is, outside the cam profile surface 6a. Due to this intersection X, as shown in FIG.
  • the radial length La of the vane 5 facing the intake port 23 is shorter than half the total length L of the vane 5 .
  • the radial length Lb of the vane 5 not facing the intake port 23 is longer than half the total length L of the vane 5 .
  • the curved surface portion 23d has an end portion 23h located slightly inside the crossing portion X and located at the end of the rotation direction R of the rotor 4.
  • a tangent line C (indicated by a phantom line in FIG. 4 ) passing through the terminal end portion 23 h is provided along the radial direction of the rotor 4 , that is, along the direction in which the vanes 5 appear and disappear from the outer peripheral side of the rotor 4 .
  • the first portion 5c of the vane 5 adjacent to the cam ring 6 has a narrow width W1 (the width in the horizontal direction in FIG. 5) of the intake port 23 and the thickness of the cam ring 6. They overlap in the direction T (the direction along the rotation axis O1).
  • the second portion 5d which is the remaining portion of the vane 5 overlaps the housing body 1 and the cover member 2 in the thickness direction T of the cam ring 6 over a width W2 wider than the width W1. Therefore, when the width of the first side clearance C1 becomes narrower than the width of the second side clearance C2 due to, for example, an external input or the like, the relatively high hydraulic pressure of the first side clearance C1 pushes the vanes 5 to the second position.
  • the catch amount Ea is the length along the thickness direction T of the cam ring 6 at the edge portion 5 e of the vane 5 inside the intake port 23 .
  • the edge portion 5 f of the vane 5 on the side opposite to the edge portion 5 e in the thickness direction T of the cam ring 6 contacts the cam profile surface 6 a of the cam ring 6 .
  • the edge portion 5g of the vane 5 on the side opposite to the edge portion 5f in the radial direction of the vane 5 contacts the inner side surface 2d of the cover member 2. As shown in FIG.
  • FIG. 7 is a partially enlarged plan view of the prior art variable displacement oil pump when one vane 5 passes through the terminal end 23a of the intake port 23 with the cam ring 6 being most eccentric.
  • FIG. 7 illustration of a rotor and a ring member is omitted for convenience of explanation.
  • FIG. 8 is a schematic cross-sectional view of a prior art housing, vanes 5 and cam ring 6 showing vanes 5 depressed into intake port 23.
  • FIG. 8 shows a cross-sectional view of a state where the cover member 2 is attached, and the illustration of the bottom of the suction port 23, the bottom of the suction groove 2e, and the inner peripheral groove 6c is omitted.
  • the curved surface portion 23d is located inside the cam profile surface 6a of the cam ring 6, and one end of the terminal outer peripheral portion 23c is located at the crossing portion X , the cam profile surface 6a overlaps the cam ring 6 in the thickness direction.
  • the terminal portion 23a faces the surface.
  • the radial length La of the vane 5 to be turned is longer than half of the total length L of the vane 5 .
  • the radial length Lb of the vane 5 not facing the intake port 23 is shorter than half the total length L of the vane 5 .
  • the first portion 5c of the vane 5 adjacent to the cam ring 6 has a width W3 wider than that of the first embodiment (see FIG. 6). Overlap on T.
  • the second portion 5d of the vane 5 overlaps the housing body 1 and the cover member 2 in the thickness direction T of the cam ring 6 over a width W4 narrower than the width W2 of the first embodiment. For this reason, due to, for example, the hydraulic pressure difference between the first and second side clearances C1 and C2, the edge portion 5e of the vane 5 moves into the terminal portion 23a with the edge portion 1q of the intake port 23 as a fulcrum, as shown in FIG.
  • the hooking amount Eb of the vane 5 becomes larger than that in the first embodiment (see FIG. 6).
  • the edge portion 5 f of the vane 5 opposite to the edge portion 5 e in the thickness direction T of the cam ring 6 strongly contacts the cam profile surface 6 a of the cam ring 6 .
  • the edge portion 5g of the vane 5 opposite to the edge portion 5f in the radial direction of the vane 5 strongly contacts the inner surface 2d of the cover member 2. As shown in FIG. Therefore, there is a problem that noise is generated due to the contact between the vane 5 and the cam ring 6 and the contact between the vane 5 and the cover member 2 .
  • the terminal end portion 23a of the intake port 23 is composed of a terminal inner peripheral portion 23b, a terminal outer peripheral portion 23c located radially outside the cam profile surface 6a of the cam ring 6, and a terminal inner peripheral portion 23c. and a curved surface portion 23d that connects the peripheral portion 23b and the terminal outer peripheral portion 23c.
  • the radial length La of the vane 5 facing the intake port 23 is shorter than half the total length L of the vane 5.
  • the vane 5 when the edge portion 5e of the vane 5 falls into the intake port 23 with the edge portion 1q of the intake port 23 as a fulcrum due to, for example, the hydraulic pressure difference between the first and second side clearances C1 and C2, the vane 5 becomes smaller. Conversely, when the edge portion 5e of the vane 5 falls into the intake port 23, the long area corresponding to the radial length Lb of the vane 5 not facing the intake port 23 is formed between the housing body 1 and the cover member 2. and held by As a result, the edge portion 5f of the vane 5 contacts the cam profile surface 6a of the cam ring 6 relatively weakly, and the edge portion 5g of the vane 5 contacts the inner surface 2d of the cover member 2, as compared with the conventional oil pump. abuts relatively weakly on the Therefore, compared with the oil pump of the prior art, the noise caused by the contact between the vane 5 and the cam ring 6 and the contact between the vane 5 and the cover member 2 can be suppressed.
  • the oil pump has the cam ring 6 having the cam profile surface 6a and the first chamber 26 provided between the cam ring 6 and the peripheral wall of the pump housing chamber 1a.
  • the terminal outer peripheral portion 23c extends in an arc shape so as to be parallel to the cam profile surface 6a. Therefore, since the shape of the terminal end outer peripheral portion 23c is determined based on the cam profile surface 6a of the existing cam ring 6, the shape of the terminal end portion 23a of the intake port 23 can be easily designed.
  • the cam ring 6 has an inner circumferential groove 6c formed on one side surface 6b of the cam ring 6 and adjacent to the cam profile surface 6a.
  • the termination outer peripheral portion 23c is provided at a position closer to the cam profile surface 6a in the region overlapping the inner peripheral groove 6c. Therefore, a wider width of the cam ring 6 adjacent to the first chamber 26, i.e., a wider sealing width for the first chamber 26, is ensured than when the terminal outer peripheral portion 23c is not provided at a position closer to the cam profile surface 6a. Therefore, the cam ring 6 can be efficiently controlled by the oil in the first chamber 26 .
  • the terminal end portion 23a further has a curved surface portion 23d at the terminal end of the intake port 23 passing through the crossing portion X, and a tangent line C passing through the terminal portion 23h in the rotational direction R of the curved surface portion 23d. are provided along the direction in which the vanes 5 protrude from the outer peripheral side of the rotor 4 .
  • the length of the vanes 5 facing the suction port 23 is longer than the case where the vanes 5 protrude and disappear in the radial direction.
  • the edge portion 5e of the vane 5 tends to fall into the suction port 23.
  • the vanes 5 appear and disappear in the radial direction with respect to the rotation axis O1 of the rotor 4 . Therefore, the radial length La of the vane 5 facing the suction port 23 is shorter than when the vane 5 is tilted more than the radial direction. It becomes difficult to fall inside. Therefore, noise generated by the contact between the vane 5 and the cam ring 6 and the contact between the vane 5 and the cover member 2 can be suppressed.
  • the pump assembly further comprises an annular ring member 8 that is accommodated in the circular recess 4c and biases the plurality of vanes 5.
  • annular ring member 8 that is accommodated in the circular recess 4c and biases the plurality of vanes 5.
  • the housing that accommodates the pump assembly is not immersed in the oil in the oil pan provided in the internal combustion engine, and noise is likely to occur. Noise can be suppressed by the configuration having the termination outer peripheral portion 23c located radially outside of the profile surface 6a.
  • FIG. 9 is a partially enlarged plan view of the variable displacement oil pump of the second embodiment.
  • illustration of the rotor 4 and the ring member 8 is omitted for convenience of explanation.
  • FIG. 10 is a schematic cross-sectional view of the housing, vanes 5 and cam ring 6 of the second embodiment.
  • FIG. 10 shows a cross-sectional view of a state where the cover member 2 is attached, and the illustration of the bottom of the suction port 23, the bottom of the suction groove 2e, and the inner circumferential groove 6c is omitted.
  • a termination outer peripheral portion 23c of the termination portion 23a and a port outer peripheral portion 23i of the suction port 23 connected to the termination outer peripheral portion 23c are provided. , is provided inside the cam profile surface 6 a of the cam ring 6 . Therefore, as shown in FIG. 10, the port outer peripheral portion 23i of the intake port 23 is provided inside the cam profile surface 6a of the cam ring 6. As shown in FIG. In other words, the portion 1r of the housing body 1 adjacent to the port outer peripheral portion 23i protrudes radially inward from the cam profile surface 6a. 9, the vane 5 is arranged so as to straddle the suction port 23 as shown in FIG.
  • the edge portion 5e of the first portion 5c of the vane 5 is placed on the portion 1r of the housing body 1, while the second portion 5d of the vane 5 is placed on the portion 1r. , on the portion of the housing body 1 including the edge 1q.
  • the terminating end portion 23a of the suction port 23 is provided with a terminating inner peripheral portion 23b and a terminating outer peripheral portion located outside the terminating inner peripheral portion 23b and positioned radially inward of the cam profile surface 6a. It has a portion 23c and a port outer peripheral portion 23i which is connected to the end outer peripheral portion 23c and positioned radially inward of the inner periphery of the cam profile surface 6a. Therefore, the portion 1r of the housing body 1 protrudes radially inward from the cam profile surface 6a, and the edge portion 5e of the vane 5 is supported by the portion 1r of the housing body 1. As shown in FIG. Therefore, since the edge portion 5e of the vane 5 is prevented from falling into the intake port 23, the noise caused by the contact between the vane 5 and the cam ring 6 and the contact between the vane 5 and the housing body 1 is suppressed. be able to.
  • variable displacement oil pump an example of a variable displacement oil pump has been described, but the present invention can also be applied to a fixed displacement oil pump.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
PCT/JP2022/027076 2021-09-14 2022-07-08 オイルポンプ Ceased WO2023042530A1 (ja)

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JP2023548140A JPWO2023042530A1 (https=) 2021-09-14 2022-07-08
US18/685,353 US12286970B2 (en) 2021-09-14 2022-07-08 Oil pump

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Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS61134589U (https=) * 1985-02-08 1986-08-22
JP2003074725A (ja) * 2001-08-30 2003-03-12 Showa Corp リリーフ弁

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH05223064A (ja) * 1992-02-07 1993-08-31 Nippondenso Co Ltd 可変容量型ロ−タリベーンポンプ
JP2008128024A (ja) * 2006-11-17 2008-06-05 Hitachi Ltd 可変容量形ベーンポンプ
MX2018006924A (es) * 2016-12-09 2018-08-15 Stackpole Int Engineered Products Ltd Bomba de paletas con una o mas paletas menos limitadas, sistemas y metodos.
DE112017007488B4 (de) * 2017-04-28 2024-03-14 Mikuni Corporation Flügelzellenpumpe
JP2019019673A (ja) 2017-07-11 2019-02-07 日立オートモティブシステムズ株式会社 ポンプ

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS61134589U (https=) * 1985-02-08 1986-08-22
JP2003074725A (ja) * 2001-08-30 2003-03-12 Showa Corp リリーフ弁

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JPWO2023042530A1 (https=) 2023-03-23

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