WO2019013110A1 - ポンプ - Google Patents

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Publication number
WO2019013110A1
WO2019013110A1 PCT/JP2018/025620 JP2018025620W WO2019013110A1 WO 2019013110 A1 WO2019013110 A1 WO 2019013110A1 JP 2018025620 W JP2018025620 W JP 2018025620W WO 2019013110 A1 WO2019013110 A1 WO 2019013110A1
Authority
WO
WIPO (PCT)
Prior art keywords
passage
housing
pump
drive shaft
axis
Prior art date
Application number
PCT/JP2018/025620
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
大輔 加藤
敦 永沼
大西　秀明
Original Assignee
日立オートモティブシステムズ株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 日立オートモティブシステムズ株式会社 filed Critical 日立オートモティブシステムズ株式会社
Priority to US16/629,456 priority Critical patent/US20200141407A1/en
Priority to CN201880043741.4A priority patent/CN110832203A/zh
Publication of WO2019013110A1 publication Critical patent/WO2019013110A1/ja

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C2/34—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
    • F04C2/344—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • 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
    • 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
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/10—Outer members for co-operation with rotary pistons; Casings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/16—Casings; Cylinders; Cylinder liners or heads; Fluid connections
    • 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
    • F04C15/0057—Driving elements, brakes, couplings, transmission specially adapted for machines or pumps
    • 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
    • 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
    • F04C2230/00—Manufacture
    • F04C2230/20—Manufacture essentially without removing material
    • F04C2230/21—Manufacture essentially without removing material by casting
    • 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
    • F04C2240/00—Components
    • F04C2240/30—Casings or housings
    • 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
    • F04C2240/00—Components
    • F04C2240/80—Other components
    • F04C2240/807—Balance weight, counterweight
    • 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
    • F04C2270/00—Control; Monitoring or safety arrangements
    • F04C2270/18—Pressure
    • F04C2270/185—Controlled or regulated
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2201/00—Metals
    • F05C2201/02—Light metals
    • F05C2201/021—Aluminium

Definitions

  • the present invention relates to a pump.
  • Patent Document 1 discloses a pump including a housing, a shaft rotatably supported by the housing, and a pump element accommodated in the housing and coupled to the shaft. Inside the housing of this pump, there are a suction passage for introducing the fluid from the outside of the housing into the pump element, and a discharge passage for discharging the fluid pressurized by the pump element to the outside of the housing.
  • the discharge passage includes a first passage and a second passage.
  • the first passage extends around one straight line.
  • the shape of the cross section of the first passage cut in the direction orthogonal to the straight line changes continuously from the beginning to the end.
  • the second passage is connected to the end of the first passage and opens to the outside of the housing.
  • FIG. 3 It is a circuit diagram of a hydraulic oil supply system of an engine of a 1st embodiment. It is a perspective view of a balancer module to which the pump of a 1st embodiment was attached. It is a side view of the balancer module to which the pump of a 1st embodiment was attached. The IV-IV visual cross section of FIG. 3 is shown. It is a front view of the pump of a 1st embodiment.
  • FIG. 6 is a cross-sectional view taken along line VI-VI of FIG. 5; It is the perspective view which disassembled the pump of 1st Embodiment, and arranged each component on the same axis. It is a front view of the pump which removed the cover of 1st Embodiment.
  • FIG. 10 is a cross-sectional view taken along line XX in FIG. It is a bottom view of a housing main part of a 1st embodiment.
  • the discharge port in the front view of the housing main body of 1st Embodiment and its vicinity are expanded and shown.
  • the XIII-XIII view cross section of FIG. 11 is shown.
  • the XIV-XIV visual cross section of FIG. 11 is shown.
  • the XV-XV visual cross section of FIG. 11 is shown.
  • FIG. 10 shows a cross section taken along line XVI-XVI of FIG. It is a schematic diagram of the discharge passage of 1st Embodiment, and shows the flow of oil with an arrow.
  • FIG. 20 is a cross-sectional view taken along line XX-XX in FIG.
  • FIG. 20 is a cross-sectional view taken along line XXI-XXI of FIG.
  • the pump 1 of the present embodiment is used in a hydraulic oil supply system of an internal combustion engine of a car.
  • the engine is a reciprocating engine and is an in-line multi-cylinder (for example, four cylinders).
  • the pump 1 is an oil pump that supplies oil (hydraulic oil), which is a fluid, to each sliding portion of the engine and a variable valve mechanism.
  • the variable valve mechanism is a valve timing control device or the like, and controls the operating characteristics of the valves of the engine.
  • the pump 1 is a source that generates an oil pressure for lubrication and for operation of the variable valve mechanism. As shown in FIG.
  • the hydraulic oil supply system of the engine includes an oil pan 100, an oil passage, a pump 1, a pressure sensor 18, and a control mechanism.
  • the oil pan 100 is a low pressure portion located in the lower part of the engine and storing hydraulic oil.
  • the passage has a suction passage 11, a discharge passage 12, a relief passage 13 and a main gallery 14.
  • One end of the suction passage 11 is connected to the oil pan 100 via an oil strainer 101.
  • the other end of the suction passage 11 is connected to the suction port 110 of the pump 1.
  • One end of the discharge passage 12 is connected to the discharge port 120 of the pump 1.
  • the other end of the discharge passage 12 is connected to the oil filter 102.
  • the relief passage 13 branches from the discharge passage 12 and can discharge the hydraulic oil to the oil pan 100.
  • a relief valve 16 is installed in the relief passage 13.
  • One end of the main gallery 14 is connected to the oil filter 102.
  • the main gallery 14 can supply hydraulic oil to sliding parts of the engine, variable valve devices, and the like.
  • a pressure sensor 18 is installed in the main gallery 14. The pressure sensor 18 detects the pressure (main gallery pressure) P1 of the main gallery 14.
  • the control mechanism has a control passage 15, a control valve 17, and an engine control unit 19.
  • the control valve 17 is a solenoid valve (solenoid valve) having a valve portion and a solenoid portion, and is a proportional control valve.
  • the valve part is a three-way valve.
  • the valve portion is a spool valve and has a housing, a spool as a valve body, and a spring as a return spring.
  • the housing has an inlet port 171, a pilot port 172, an outlet port 173, and an outlet port 174.
  • the spring biases the spool towards the initial position.
  • the pressure of oil (pilot pressure) supplied from the pilot port 172 to the inside of the housing biases the spool in the direction opposite to the spring.
  • the solenoid generates an electromagnetic force to bias the spool in the direction opposite to the spring.
  • the solenoid unit can continuously change the magnitude of the electromagnetic force in accordance with the value of the supplied current.
  • the control passage 15 has a supply passage 151, a feedback passage 152, a discharge passage 153, and a communication passage 154.
  • the supply passage 151 branches from the main gallery 14 and is connected to the inlet port 171 of the control valve 17.
  • the feedback passage 152 branches from the supply passage 151 and is connected to the pilot port 172 of the control valve 17.
  • the discharge passage 153 is connected to the discharge port 173 of the control valve 17 and is in communication with the oil pan 100.
  • the communication passage 154 connects the outlet port 174 of the control valve 17 and the control chamber 80 of the pump 1.
  • the pump 1 is installed in a balancer module (balancer unit) 2 of the engine. That is, the balancer module 2 is a pump integrated type.
  • the balancer module 2 is a balancer mechanism for canceling secondary vibration generated in the engine, and generates rotation force in the direction to cancel the above-mentioned vibration by rotating the balancer shafts 25 and 26 in synchronization with the crankshaft.
  • the module 2 has a housing, balancer shafts 25 and 26, and a gear.
  • the housing has a lower housing 200 and an upper housing 201.
  • a three-dimensional orthogonal coordinate system is set in the drawings.
  • the z axis is set in the direction in which the axes of the balancer shafts 25 and 26 extend, and the side of the pump 1 with respect to the balancer shafts 25 and 26 is positive.
  • the x-axis is set in the lateral direction orthogonal to the z-axis, and the side of the drive-side shaft 25 with respect to the driven-side shaft 26 is positive.
  • the y-axis is set in the vertical direction (vertical direction) orthogonal to the z-axis, and the side of the upper housing 201 with respect to the lower housing 200 is positive.
  • the z-axis direction In the state where the engine is installed in a vehicle (car), the z-axis direction is horizontal and the y-axis direction is vertical.
  • the y-axis positive direction is vertically upward, and the x-axis negative direction is forward of the vehicle.
  • positioning to a vehicle is not restricted to this.
  • the lower housing 200 has a gear housing portion, a bearing housing portion, and a weight housing portion.
  • Each accommodation portion has a semi-cylindrical shape extending in the z-axis direction, and opens in the surface on the y-axis positive direction side of the lower housing 200.
  • the gear storage portion includes a drive gear storage portion 211, a drive-side reverse gear storage portion 212, a driven-side reverse gear storage portion 213, a reduction gear storage portion 214, and a pump drive gear storage portion 215.
  • the bearing housing portion includes a drive side first bearing housing portion 221, a drive side second bearing housing portion 222, a driven side first bearing housing portion 223, and a driven side second bearing housing portion 224.
  • the weight storage portion has a drive-side weight storage portion 231 and a driven-side weight storage portion 232.
  • the reverse gear accommodating portions 212 are arranged in this order from the z-axis positive direction side toward the z-axis negative direction side.
  • the reverse gear accommodating portion 213 is arranged in this order from the z-axis positive direction side toward the z-axis negative direction side.
  • a pump drive gear accommodating portion 215 is adjacent to the drive gear accommodating portion 211 on the z positive side in the z axial positive direction end of the lower housing 200 in the z axial positive direction end.
  • the housing portion 222 and the driven second bearing housing portion 224, and the drive side reverse gear housing portion 212 and the driven side reverse gear housing portion 213 are adjacent to each other in the x-axis direction.
  • Bolt holes 241 penetrating the lower housing 200 in the y-axis direction are adjacent to the respective bearing accommodating portions in the x-axis direction.
  • the upper housing 201 has a gear housing portion, a bearing housing portion, a weight housing portion, and a mounting portion 242.
  • Each housing portion has substantially the same shape and arrangement as the corresponding housing portion in the lower housing 200, and opens in the surface on the y-axis negative direction side of the upper housing 201.
  • the drive gear housing portion 211 also opens in the surface on the y-axis positive direction side of the upper housing 201.
  • the upper housing 201 is fixed to the lower housing 200 by a bolt 202 which passes through a bolt hole 241 of the lower housing 200.
  • the attachment portion 242 is a protrusion which protrudes from the surface on the y-axis positive direction side of the upper housing 201, and has a bolt hole extending in the y-axis direction.
  • the balancer module 2 is attached so as to hang down to the lower portion (y-axis negative direction side) of the cylinder block by a bolt 203 which passes through a bolt hole of the attachment portion 242.
  • the balancer module 2 is housed in an oil pan 100.
  • the balancer shaft has a drive shaft 25 and a driven shaft 26.
  • the drive shaft 25 and the driven shaft 26 are disposed parallel to the crankshaft.
  • the two shafts 25 and 26 are sandwiched between the upper housing 201 and the lower housing 200, arranged side by side in the xz plane, and rotatably supported by the two housings 200 and 201.
  • Both shafts 25 and 26 have balance weights 250 and 260, respectively.
  • Weights 250 and 260 are eccentric weights whose center of gravity is offset with respect to the axial center of both shafts 25 and 26.
  • the gear has a balancer drive gear 27, a reverse gear, and a reduction gear 29.
  • the reversing gear has a driving side reversing gear 281 and a driven side reversing gear 282.
  • the balancer drive gear 27 is fixed to the z-axis positive direction end of the drive side shaft 25.
  • the drive side reversing gear 281 is fixed to the z-axis negative direction end of the drive side shaft 25.
  • the driven side reversing gear 282 is fixed to the z-axis negative direction end of the driven side shaft 26.
  • the reduction gear 29 is fixed to the z-axis positive end of the driven shaft 26. Fixation of these is by press fitting or the like.
  • the balance weight 250 of the drive side shaft 25 is accommodated in the drive side weight accommodation portion 231 of both the housings 200 and 201.
  • the balancer drive gear 27 is accommodated in the drive gear accommodating portion 211 of both the housings 200 and 201.
  • the drive side reverse gear 281 is accommodated in the drive side reverse gear accommodating portion 212 of both the housings 200 and 201.
  • the journal portion between the balance weight 250 and the balancer drive gear 27 in the drive side shaft 25 is supported by the bearing 251 accommodated in the drive side first bearing accommodation portion 221 of both the housings 200 and 201.
  • the journal portion between the balance weight 250 and the drive side reversing gear 281 is supported by a bearing 252 accommodated in the drive side second bearing accommodation portion 222 of both housings 200 and 201.
  • the balance weight 260 of the driven shaft 26 is accommodated in the driven weight accommodating portion 232 of the two housings 200 and 201.
  • the reduction gear 29 is accommodated in the reduction gear accommodating portion 214 of both the housings 200 and 201.
  • the driven side reversing gear 282 is accommodated in the driven side reversing gear accommodating portion 213 of the two housings 200 and 201.
  • the journal portion of the driven shaft 26 between the balance weight 260 and the reduction gear 29 is supported by a bearing 261 accommodated in the driven first bearing accommodating portion 223 of both housings 200 and 201.
  • the journal portion between the balance weight 260 and the driven side reversing gear 282 is supported by a bearing 262 accommodated in the driven side second bearing accommodating portion 224 of both the housings 200 and 201.
  • a part of the outer periphery of the balancer drive gear 27 protrudes from the opening of the upper housing 201 in the positive y-axis direction and meshes with a gear integral with the crankshaft.
  • the gear ratio of the balancer drive gear 27 is set such that the drive side shaft 25 rotates at twice the rotational speed of the crankshaft.
  • the driven side reversing gear 282 meshes with the driving side reversing gear 281. Both shafts 25 and 26 rotate in opposite directions at the same rotational speed.
  • the pump 1 is a variable displacement vane pump.
  • the pump 1 has a housing 3, a bolt 30, a pump drive gear 400, a drive shaft 4, a rotor 5, a plurality of vanes 6, vane rings 61 and 62, a cam ring 7, a seal member 71, a pin 72 and a spring 73.
  • the housing 3 has a housing body (body) 300 and a cover 301.
  • the housing body 300 has a pump element housing 31, a spring housing 32, a passage, and a flange 35. Inside the housing body 300, there are a bearing portion 360, a pin hole 361, a pump element accommodation hole 362, a spring accommodation hole 363, a suction port 110, a discharge port 120, a suction passage 11, a discharge passage 12, and a communication passage 154.
  • the pump element housing portion 31 has a bottomed cylindrical shape and has a bottom portion 310 and a cylindrical peripheral wall 311.
  • the pump element housing portion 31 includes a pump element housing hole 362, a bearing portion 360, a pin hole 361, a suction port 110, and a discharge port 120.
  • the pump element housing hole 362 is a bottomed cylindrical recess extending in the z-axis direction.
  • the hole 362 is closed on the z-axis positive direction side by the bottom portion 310, and the z-axis negative direction side is opened on the surface of the housing main body 300 on the z-axis negative direction side.
  • the bearing portion 360 extends in the z-axis direction around the axis 40 and penetrates substantially the center of the bottom portion 310.
  • Pump element receiving bore 362 extends around axis 40.
  • the pin hole 361 has a bottomed cylindrical shape extending in the z-axis direction, and opens in the surface on the z-axis negative direction side of the bottom 310 (the bottom surface 364 of the pump element receiving hole 362 in the z-axis direction).
  • the pin hole 361 is located at the outer edge of the bottom surface 364 in the x-axis positive direction side and the y-axis positive direction side.
  • the suction port 110 and the discharge port 120 are arc-shaped recesses extending in the circumferential direction of the axis 40 (hereinafter referred to as the circumferential direction), and the surface on the z-axis negative direction side of the bottom portion 310 (bottom surface 364 of the pump element receiving hole 362) Open to The suction port 110 is bottomed.
  • the suction port 110 is between the bearing 360 and the pin hole 361.
  • the discharge port 120 is on the side of the pin hole 361 with respect to the bearing portion 360.
  • a straight line passing through the axis 40 and (the axis of) the pin hole 361 overlaps the two ports 110, 120.
  • the ports 110 and 120 are on opposite sides of a straight line perpendicular to the straight line and passing through the axis 40.
  • the discharge port 120 extends inside the bottom 310 around a first straight line 91.
  • the first straight line 91 is parallel to the axis 40 and extends along the axis 40 (in the z-axis direction).
  • the first straight line 91 passes through the middle in the circumferential direction at the opening of the discharge port 120 to the bottom surface 364.
  • the cross section of the discharge port 120 cut in the direction orthogonal to the first straight line 91 has a flat shape that is long in the circumferential direction.
  • the dimension of the discharge port 120 in the circumferential direction is larger than the dimension of the discharge port 120 in the radial direction of the drive shaft 4.
  • the wall 121 on the rotational direction side of the drive shaft 4 extends along the radial direction of the drive shaft 4 and is slightly inclined with respect to the first straight line 91, z
  • the drive shaft 4 is gradually displaced toward the reverse rotation direction as it goes from the negative direction side of the shaft to the positive direction side.
  • the wall 122 on the reverse rotation direction side of the drive shaft 4 extends along the radial direction of the drive shaft 4 and is inclined with respect to the first straight line 91 and gradually increases from the negative direction side to the positive direction side of the z axis. It is displaced in the rotational direction of the drive shaft 4.
  • the radially inner wall 123 of the drive shaft 4 extends along the circumferential direction and is slightly inclined with respect to the first straight line 91, and gradually radially outward from the negative side to the positive side of the z axis. Displace.
  • the radially outer wall has a portion 124 that bulges radially inward near the pin hole 361.
  • the portion 125 on the reverse rotation direction side of the drive shaft 4 with respect to the above-mentioned bulged portion 124 extends along the circumferential direction.
  • the portion 126 on the rotational direction side of the drive shaft 4 with respect to the above-mentioned bulging portion 124 has a so-called pento-uff shape, and has a portion slightly radially outward with respect to the arc ⁇ .
  • the arc ⁇ is an arc that is centered on the axis 40 and passes through the radially outer end of the start end of the discharge port 120 (in the circumferential direction).
  • the radially outer walls 124, 125, 126 are slightly inclined with respect to the first straight line 91, and are gradually displaced radially inward from the negative side to the positive side of the z-axis.
  • the spring accommodation portion 32 is on the y-axis negative direction side of the pump element accommodation portion 31.
  • the spring accommodating portion 32 has a suction passage 11 and a spring accommodating hole 363.
  • the suction passage 11 and the spring accommodation hole 363 open in the surface on the z-axis negative direction side of the housing main body 300.
  • the suction passage 11 opens in the peripheral wall 311 of the pump element housing hole 362 and is connected to the suction port 110.
  • the suction passage 11 extends from the suction port 110 in the negative x-axis direction and in the negative y-axis direction.
  • the spring receiving hole 363 has a tubular shape extending substantially along the x-axis direction, and intersects the suction passage 11.
  • the passage portion has a discharge passage portion 33 and a communication passage portion 34. As shown in FIGS. 10 and 11, the discharge passage portion 33 extends in the z-axis positive direction from the y-axis positive direction side of the surface on the z-axis positive direction side of the pump element housing portion 31 (bottom portion 310).
  • the discharge passage 33 includes a main body 330, a first bulge 331, and a second bulge 332.
  • the discharge passage portion 33 is a plate-like flat portion that extends along the xz plane. The dimension of the main body 330 in the x-axis direction and the z-axis direction is larger than the dimension of the main body 330 in the y-axis direction.
  • the bulges 331 and 332 have bolt holes 333.
  • the bolt holes 333 extend in the y-axis direction and pass through the bulges 331 and 332.
  • the first bulge portion 331 overlaps the main body portion 330 on the x-axis negative direction side and the z-axis negative direction side of the discharge passage portion 33, and is connected to the bottom portion 310.
  • the second bulge portion 332 overlaps the main body portion 330 on the x-axis positive direction side and the z-axis positive direction side of the discharge passage portion 33, and is connected to the z-axis positive direction side of the main body portion 330.
  • the x-axis positive direction side of the discharge passage portion 33 extends in the z-axis direction.
  • the x-axis negative direction side of the discharge passage portion 33 When viewed from the y-axis direction, the x-axis negative direction side of the discharge passage portion 33 has a shape in which the large arc of the main body 330 is sandwiched by the small arcs of the bulges 331 and 332, and extends obliquely with respect to the x-axis and z-axis.
  • the surface on the y-axis negative direction side of the discharge passage portion 33 is parallel to the xz plane.
  • the surface on the y-axis positive direction side of the discharge passage portion 33 is slightly inclined with respect to the xz plane, and is gradually displaced to the y-axis negative direction as going from the negative direction side to the positive direction of the z-axis.
  • the discharge passage 12 has a first passage 12A and a second passage 12B. Both passages 12A, 12B are inside the body 330. As shown in FIGS. 12-16, the first passage 12A is connected to the discharge port 120 at the start end 12A1 and extends around the second straight line 92 to the end 12A2.
  • the second straight line 92 is parallel to the axis 40 of the drive shaft 4 and extends along the axis 40 (in the z-axis direction).
  • the second straight line 92 passes through the middle of the first passage 12A in the circumferential direction.
  • the cross section of the first passage 12A cut in the direction orthogonal to the second straight line 92 has a flat shape that is long in the circumferential direction.
  • the dimension of the first passage 12A in the circumferential direction is larger than the dimension of the first passage 12A in the radial direction of the drive shaft 4.
  • the first passage 12A (second straight line 92) is biased toward the rotational direction of the drive shaft 4 with respect to the discharge port 120 (first straight line 91).
  • the wall 127 on the rotational direction side of the drive shaft 4 extends along the y-axis direction and is slightly inclined with respect to the first straight line 91 As it goes from the negative direction side to the forward direction side, it is gradually displaced to the reverse rotation direction side of the drive shaft 4.
  • a curved surface portion 127A is on the z-axis negative direction side of the wall 127, and the curved surface portion 127A smoothly continues with the wall 121 of the discharge port 120.
  • the wall 128 on the reverse rotation direction side of the drive shaft 4 has a curved surface shape convex toward the reverse rotation direction of the drive shaft 4 and smoothly with the wall 122 on the reverse rotation direction side of the drive shaft 4 in the discharge port 120 ( Continuously)
  • the wall 128 is slightly inclined with respect to the first straight line 91, and is gradually displaced to the rotational direction side (x-axis positive direction side) of the drive shaft 4 as it goes from the negative direction side to the positive direction side of the z-axis.
  • the radially inner wall of the drive shaft 4 extends along the circumferential direction, and the end portion 123A on the reverse rotation direction side of the drive shaft 4 partially extends in the x-axis direction.
  • the end 123A is smoothly (curved) continuous with the wall 122 of the discharge port 120.
  • the other part is flush with the radially inner wall 123 of the drive shaft 4 at the discharge port 120.
  • the radially inner walls 123, 123A of the drive shaft 4 are slightly inclined with respect to the first straight line 91, and are gradually displaced radially outward from the negative side to the positive side of the z-axis.
  • the radially outer wall of the drive shaft 4 is flush with the radially outer walls 124, 126 of the drive shaft 4 at the discharge port 120.
  • the end (starting end) 124 on the reverse rotation direction side of the drive shaft 4 bulges radially inward near the pin hole 361.
  • the portion 126 excluding the bulging portion 124 has a so-called pent-roof shape, and has a portion slightly bulging radially outward with respect to the arc ⁇ .
  • the radially outer walls 124 and 126 are slightly inclined with respect to the first straight line 91, and are gradually displaced radially inward from the negative direction side to the positive direction side of the z-axis.
  • the z-axis positive end wall 129 extends orthogonal to the z-axis.
  • path 12A mutually continues smoothly (with a curved surface).
  • the shape of the cross section of the first passage 12A cut in the direction orthogonal to the second straight line 92 changes continuously from the start end 12A1 to the end 12A2 of the first passage 12A.
  • the shape of the cross section perpendicular to the axis 40 of the connection between the start end 12A1 and the discharge port 120 changes continuously between the start end 12A1 and the discharge port 120.
  • the area of the cross section of this connection gradually decreases from the discharge port 120 toward the start end 12A1 (from the negative direction to the positive direction along the z-axis).
  • the area of the cross section of the first passage 12A gradually decreases from the beginning 12A1 to the end 12A2 (from the negative side to the positive side along the z-axis).
  • the second passage 12 B is connected to the end 12 A 2 of the first passage 12 A, extends around the third straight line 93 (along the third straight line 93) and opens to the outside of the housing 3.
  • the third straight line 93 extends in the y-axis direction.
  • the second passage 12 ⁇ / b> B opens in the surface on the y-axis negative direction side of the main body 330.
  • the opening is located at a predetermined distance from the bottom 310 (the positive end of the drive shaft 4 in the z-axis direction) in the axial direction (z-axis direction) of the drive shaft 4.
  • the cross section of the second passage 12B cut in the direction orthogonal to the third straight line 93, including the opening, is circular.
  • the area of the opening of the second passage 12B at the end portion 12A2 of the first passage 12A is the area of the first passage 12A cut at the portion ⁇ (z-axis negative direction end; see FIG. 11) closest to the starting end 12A1. It is not more than the area of the cross section, and not less than the area of the cross section of the first passage 12A cut at the portion ⁇ (the end in the positive z-axis direction) farthest from the start end 12A1 of the openings.
  • a member such as a pipe or an oil filter 102 is connected to the opening of the second passage 12B to the outside of the housing 3.
  • Bolts pass through the bolt holes 333 of the two bulges 331 and 332.
  • the bulges 331 and 332, together with the bolts, function as a fixing portion for fixing a member connected to the opening of the second passage 12B.
  • the communication passage portion 34 extends in the x-axis positive direction from the outer surface in the x-axis positive direction side and the y-axis positive direction side of the pump element housing portion 31 (peripheral wall 311).
  • the communication passage portion 34 has a main body portion 340 and boss portions 341 and 342.
  • the bosses 341, 342 have bolt holes 343.
  • the bolt holes 343 extend in the y-axis direction and pass through the bosses 341 and 342.
  • the communication passage 154 is inside the communication passage portion 34.
  • the start end portion of the communication passage 154 opens at the surface in the y-axis negative direction at the end in the positive x-axis direction of the main body 340.
  • a member connected to the control valve 17 is connected to the opening of the communication passage 154.
  • the bosses 341 and 342 function as fixing parts for fixing the above-mentioned members connected to the control valve 17.
  • the end of the communication passage 154 opens at the inner peripheral surface of the pump element receiving hole 362.
  • the flange portion 35 is on the z-axis negative direction side of the housing body 300 and surrounds the pump element receiving hole 362 and the opening of the suction passage 11 (spring receiving hole 363).
  • the flange portion 35 has three first bosses 351, three second bosses 352, and one pin hole 354.
  • Each boss 351, 352 has a bolt hole 353.
  • the bolt holes 353 extend in the z-axis direction and pass through the bosses 351 and 352.
  • the pin holes 354 extend in the z-axis direction and pass through the flange portion 35.
  • the three first bosses 351 cross the axis 40 of the drive shaft 4 in the x-axis direction on the side of the flange portion 35 in the y-axis positive direction, and straddle the axis 40 in the y-axis direction. Line up around.
  • the three second bosses 352 are arranged along the spring receiving hole 363 so as to straddle the axis 40 in the x-axis direction on the y-axis negative direction side of the flange portion 35.
  • the cover 301 has a suction passage portion 37, an oil strainer installation portion 38, a relief passage portion 39, and a flange portion 35.
  • a bearing portion 360 Inside the cover 301, there are a bearing portion 360, a pin hole 361, a suction port 110, a discharge port corresponding groove 365, a suction passage 11, and a relief passage 13.
  • the bearing 360, the pin hole 361, the suction port 110, the discharge port corresponding groove 365, and the suction passage 11 respectively correspond to the bearing 360 of the housing body 300, the pin hole 361, the suction port 110, the discharge port 120, and the suction passage 11.
  • the cover 301 is opened at the surface on the z-axis positive direction side at the corresponding position and shape in the z-axis direction.
  • the bearing portion 360 penetrates the cover 301 in the z-axis direction.
  • the pin hole 361 has a bottomed cylindrical shape extending in the z-axis direction.
  • the suction port 110 and the discharge port corresponding groove 365 are bottomed concave portions.
  • the suction passage 11 is inside the suction passage portion 37. One end of the suction passage 11 is connected to the suction port 110. The other end of the suction passage 11 extends in the z-axis direction and is connected to the oil strainer installation portion 38.
  • An oil strainer 101 is installed in the oil strainer installation portion 38.
  • the relief passage 39 extends in the x-axis negative direction and the y-axis negative direction from the outer surface of the cover 301 on the x-axis negative direction side and the y-axis positive direction side.
  • the relief passage 13 is inside the relief passage 39.
  • the start end portion of the relief passage 13 opens at the inner peripheral surface of the discharge port corresponding groove 365.
  • the end of the relief passage 13 opens to the outer surface of the cover 301.
  • a relief valve 16 is installed in the relief passage 13.
  • the relief valve 16 has a ball 160 as a valve body, a spring 161 as a return spring, and a retainer 162 of the spring 161.
  • the flange portion 35 is on the z-axis positive direction side of the cover 301.
  • the flanges 35 have bosses 351 and 352 and pin holes 354 at positions corresponding to the bosses 351 and 352 and the pin holes 354 of the housing main body 300 in the z-axis direction.
  • the relief passage 39 has another boss 352.
  • the bosses 351 and 352 have bolt holes 353.
  • the flange portion 35 has another pin hole 355.
  • the bolt holes 353 extend in the z-axis direction and pass through the bosses 351 and 352.
  • the pin holes 355 extend in the z-axis direction and pass through the flange portion 35.
  • the rotor 5, the plurality of vanes 6, the vane rings 61 and 62, the cam ring 7, the seal member 71, and the pins 72 are installed in the pump element housing hole 362.
  • the spring 73 is installed in the spring receiving hole 363.
  • the z-axis positive direction side of the drive shaft 4 is fitted in the bearing portion 360 of the housing main body 300 and is rotatably supported.
  • the z-axis negative direction side of the drive shaft 4 is fitted in the bearing portion 360 of the cover 301 and supported rotatably.
  • the middle portion of the drive shaft 4 in the z-axis direction is in the pump element receiving hole 362.
  • the pump drive gear 400 is fixed to this end by press-fitting or the like.
  • the pump drive gear 400 meshes with the reduction gear 29 of the balancer module 2.
  • the rotor 5 is cylindrical.
  • the groove 51 (convex portion 52) of the rotor 5 is fitted into the convex portion 42 (groove 41) of the drive shaft 4. That is, the drive shaft 4 and the rotor 5 are coupled by splines so as to be relatively movable in the axial direction.
  • Recesses 53 are provided on both sides of the rotor 5 in the z-axis direction.
  • the vane rings 61 and 62 are installed in the recess 53.
  • the radially outer side of the slit 54 opens at the outer peripheral surface 50 of the rotor 5.
  • a back pressure chamber 55 is connected radially inward of the slit 54.
  • the back pressure chamber 55 is cylindrical and extends in the z-axis direction to penetrate the rotor 5.
  • the vanes 6 are accommodated in the slits 54.
  • the base end of each vane 6 faces the vane rings 61 and 62.
  • Both ends of the pin 72 fit into the pin hole 361 of the housing body 300 and the pin hole 361 of the cover 301, respectively.
  • the inner circumferential surface 700 of the cam ring 7 is cylindrical.
  • the pin groove 74, the seal groove 75, and the arm 76 are provided on the outer periphery of the cam ring 7.
  • the pin groove 74 is semi-cylindrical, extends in the z-axis direction and penetrates the cam ring 7.
  • a part of the outer periphery of the pin 72 fits into the pin groove 74.
  • a seal member 71 is installed in the seal groove 75.
  • the arm portion 76 has a plate shape, and protrudes outward in the radial direction from the outer periphery of the cam ring 7.
  • the arm portion 76 is disposed on the x-axis positive direction side of the spring accommodation hole 363.
  • the surface on the x-axis positive direction side of the arm portion 76 can be in contact with the protrusion 321 on the x-axis positive direction side of the spring accommodation hole 363.
  • a plurality of grooves 77 are provided on both sides of the cam ring 7 in the z-axis direction.
  • Each groove 77 has substantially the same shape as the suction port 110 and the discharge port 120 (discharge port corresponding groove 365) of the housing 3 opposed in the z-axis direction, and is connected to the inner peripheral side of the cam ring 7.
  • the groove 77 has a function of adjusting the force by the pressure acting on the cam ring 7 from both sides in the z-axis direction.
  • the spring 73 is a compression coil spring. One end of the spring 73 is disposed on the surface of the arm 76 on the negative side in the x-axis direction. The other end of the spring 73 is installed on the inner peripheral surface on the x-axis negative direction side of the spring accommodation hole 363. In the xy plane, the axis of the spring 73 is substantially orthogonal to the straight line connecting the axis of the pin 72 and the surface of the protrusion 321 in the negative x-axis direction.
  • the spring 73 is in a compressed state, has a predetermined set load in an initial state in which the cam ring 7 is not operating (rocking), and always biases the arm 76 in the positive x-axis direction.
  • a control chamber 80 is located between the inner surface of the housing 3 and the outer periphery of the cam ring 7.
  • the control chamber 80 is located between the seal member 71 and the pin 72 on the outer peripheral surface 701 of the cam ring 7 (the side not including the arm 76), the inner surface of the pump element housing hole 362, and the cover 301 on the z-axis positive direction side. It is a space surrounded by faces.
  • the control chamber 80 is sealed by the seal member 71 and the pin 72.
  • a communication passage 154 opens in the control chamber 80.
  • the pump chamber (vane chamber) is formed by the outer peripheral surface 50 of the rotor 5, the two adjacent vanes 6, the inner peripheral surface 700 of the cam ring 7, the bottom surface 364 of the pump element housing hole 362, and the surface on the z axis positive direction of the cover 301. ) 81 are defined (defined). At the time of rotation of the rotor 5, the vane 6 emerges from the outer circumferential surface 50 of the rotor 5 such that the tip end of the vane 6 contacts the inner circumferential surface 700 of the cam ring 7. The volume of each vane chamber 81 can be changed as the rotor 5 rotates, and the volume of each vane chamber 81 is increased or decreased by rotation to perform a pump action.
  • the suction port 110 opens to the vane chamber 81 in a range (intake region) where the volume of the vane chamber 81 increases (in accordance with the rotation of the rotor 5).
  • the vane chamber 81 in the suction area sucks in oil from the suction port 110.
  • the discharge port 120 opens to the vane chamber 81 in a range (discharge region) in which the volume of the vane chamber 81 decreases (according to the rotation of the rotor 5).
  • the vane chamber 81 in the discharge area discharges the oil to the discharge port 120.
  • the rotation of the crankshaft is transmitted to the balancer shafts 25, 26 via the gear 27 and the like.
  • the rotation of the balancer shafts 25, 26 is transmitted to the drive shaft 4 of the pump 1 via the gears 29, 40.
  • the gear ratio of the gears 29 and 40 is set such that the drive shaft 4 rotates at 1 ⁇ 2 of the rotational speed of the driven shaft 26. As a result, the rotational speed of the drive shaft 4 becomes
  • the drive shaft 4 rotates the rotor 5 in the counterclockwise direction of FIG.
  • Parts (pump elements) such as the rotor 5 and the vanes 6 constituting the pump chamber pressurize the oil introduced from the suction port 110 by rotating and introduce the oil to the discharge port 120.
  • the axis 40 of the drive shaft 4 coincides with the axis of rotation of the pump element.
  • the direction around the axis 40 is the direction of rotation of the drive shaft 4, ie the direction of rotation of the pump element.
  • the pressure of the discharge port 120 is introduced into the back pressure chamber 55. Thus, the vanes 6 are pushed out of the slits 54.
  • the pump 1 sucks the oil from the oil pan 100 via the suction passage 11 and discharges the oil to the discharge passage 12.
  • the pump 1 pumps hydraulic fluid to each part of the engine through the main gallery 14 connected to the discharge passage 12.
  • the relief valve 16 opens when the pressure (discharge pressure) of the discharge passage 12 reaches a predetermined high pressure, and discharges oil from the discharge passage 12 via the relief passage 13.
  • the difference between the maximum volume and the minimum volume of the vane chamber 81 determines the theoretical discharge amount (discharge amount per rotation) of the pump 1, that is, the capacity.
  • This volume difference (the amount of change in volume of the vane chamber 81) is variable.
  • the cam ring 7 is a movable member (movable member) inside the pump element receiving hole 362, and can swing in the rotational direction about the pin 72. By swinging the cam ring 7, the difference (the amount of eccentricity) between the shaft center 40 of the rotor 5 and the shaft center 78 of the cam ring inner circumferential surface 700 changes.
  • the amount of change (volume change amount) of the volume of each of the plurality of vane chambers 81 at the time of rotation of the rotor 5 changes.
  • the cam ring 7 has one side in the rotational direction centering on the pin 72 by the spring 73 (counterclockwise direction in FIG. 8, the amount of eccentricity increases, and the volume change amount of each of the plurality of vane chambers 81 increases) ). Let this spring force be Fs.
  • the oil supplied from the discharge port 120 to the main gallery 14 can be introduced into the control chamber 80 via the control passage 15.
  • the cam ring 7 receives the pressure of oil in the control chamber 80.
  • the cam ring 7 is rotated by the hydraulic pressure on the other side in the rotational direction about the pin 72 (clockwise in FIG.
  • the control valve 17 can control the introduction of oil to the control chamber 80 and the discharge of oil from the control chamber 80.
  • the communication between the outlet port 174 (communication passage 154) and the inlet port 171 (supply passage 151) is blocked, and the outlet port 174 and the discharge port 173 (discharge passage 153) communicate.
  • the oil can be discharged from the inside of the control chamber 80 of the pump 1 through the communication passage 154 and the discharge passage 153.
  • the spool moves from the initial position in the direction opposite to the biasing force of the spring, the communication between the outlet port 174 and the discharge port 173 is interrupted, and the outlet port 174 and the inlet port 171 communicate.
  • oil can be supplied from the main gallery 14 to the inside of the control chamber 80 through the supply passage 151 and the communication passage 154.
  • the pressure in the main gallery 14 acts on the spool as a pilot pressure via the feedback passage 152.
  • the position of the spool is feedback controlled to adjust the amount of eccentricity (volume). That is, when the pressure (pilot pressure) of the main gallery 14 rises, the spool moves in the direction opposite to the biasing force of the spring.
  • oil is supplied to the control chamber 80, the pressure in the control chamber 80 rises, Fp increases, and the amount of eccentricity decreases.
  • the solenoid section changes the pressure of the main gallery 14 when the spool starts moving by changing the magnitude of the electromagnetic force.
  • the electromagnetic force assists the pilot pressure by biasing the spool in the opposite direction to the spring. Therefore, as the electromagnetic force increases, the spool moves in the direction opposite to the biasing force of the spring at a lower pressure (pilot pressure) of the main gallery 14, and oil is supplied to the control chamber 80. Thereby, the pressure of the main gallery 14 is controlled to a lower constant value (within a predetermined range centered on).
  • the engine control unit 19 calculates the necessary pressure of the main gallery 14 according to the operating conditions such as the engine speed, load, oil temperature and water temperature.
  • the control unit 19 changes the value (the magnitude of the electromagnetic force) of the current supplied to the solenoid unit based on the information input from the pressure sensor 18 and the like and the built-in program. As a result, the pressure of the main gallery 14 can be feedback controlled to the above required value. The pressure of the main gallery 14 can be controlled continuously, so to speak, in a stepless manner. For this reason, the fuel consumption of the vehicle can be improved.
  • the manufacturing process includes a first step of casting the housing main body 300 and the cover 301, a second step of machining the housing main body 300 and the cover 301, and pump elements (such as the rotor 5) in the pump element receiving hole 362 of the housing main body 300. And a fourth step of connecting the cover 301 and the housing main body 300.
  • the housing body 300 is cast by die casting of aluminum alloy. There are three molds. After pouring, “the first mold that forms the discharge passage 33 and the like together with the pump element housing 31” is extracted to one side (z-axis positive direction side) of the drive shaft 4 in the axial direction.
  • the second type in which the pump element housing hole 362 and the discharge port 120 are formed inside the pump element housing portion 31 and the first passage 12A is formed inside the discharge passage portion 33” is the axial direction of the drive shaft 4 To the other side of the (z-axis negative direction side).
  • the “third type forming the second passage 12B in the discharge passage portion 33” is extracted from the discharge passage portion 33 in the axial direction (the y-axis negative direction side) of the second passage 12B.
  • the surface on the y-axis negative direction side of the discharge passage portion 33 is parallel to the xz plane, while the surface on the y-axis positive direction side of the discharge passage portion 33 is one side in the axial direction of the drive shaft 4 (z-axis positive direction side)
  • the second mold can be easily removed because it is configured to be gradually displaced in the negative y-axis direction as it goes to the side. Since the cross-sectional area of the first passage 12A and the discharge port 120 is gradually reduced toward one side (z-axis positive direction side) in the axial direction of the drive shaft 4, the work of removing the second mold is easy.
  • the second passage 12B is opened at one side surface (the surface on the y-axis negative direction side) of the discharge passage portion 33, the work of removing the third mold is easy.
  • the bearing portion 360 in the housing main body 300, the surface on the y-axis negative direction side of the discharge passage portion 33, and the inner peripheral surface of the second passage 12B are machined.
  • the connectivity (sealability and the like) of the member to the opening of the second passage 12B is improved. it can.
  • the cover 301 is attached to the surface of the housing main body 300 in the negative z-axis direction with the bolt 30 at the first boss 351.
  • Pins 356 can be inserted into both pin holes 354 and 354 so that the cover 301 can be positioned relative to the housing body 300.
  • the cover 301 is integrated with the housing body 300 by being tightened by a bolt 30.
  • the surface on the z-axis positive direction side of the cover 301 closes the opening of the pump element receiving hole 362.
  • the cover 301 of the housing 3 is joined to the lower housing 200 or the upper housing 201 of the balancer module 2 or joined across the two housings 200 and 201.
  • the housing 3 is attached to the front end surface (surface on the z-axis positive direction side) of the housing 200 (201) by the bolt 30 at the second boss portion 352 of the housing main body 300 and the second boss portion 352 of the cover 301.
  • the bolt 30 also has a function of tightening the bosses 352 and 352.
  • a pin 357 can be inserted into the pin hole 355, whereby the housing 3 can be positioned relative to the balancer module 2.
  • the first end 12A1 of the first passage 12A of the discharge passage 12 is connected to the discharge port 120.
  • the first passage 12A extends around the second straight line 92 to the end 12A2.
  • the second passage 12 B is connected to the end 12 A 2 and opens to the outside of the housing 3.
  • the second passage 12 ⁇ / b> B is located at the end of the discharge passage 12 and functions as a discharge port for discharging the fluid to the outside of the housing 3.
  • FIG. 18 in the discharge passage 12, when the cross-sectional shape of the passage cut in a direction perpendicular to the axis of the passage changes discontinuously, that is, when there is a step in the inner wall of the passage at a right angle, Vortices can occur at this step.
  • the pressure loss increases inside the pump 1 and the discharge efficiency decreases.
  • the decrease in the discharge efficiency of the pump 1 leads to the deterioration of fuel consumption.
  • the shape of the cross section of the first passage 12A cut in the direction orthogonal to the second straight line 92 changes continuously from the start end 12A1 to the end 12A2. That is, in the inner wall of the first passage 12A (including the start end portion 12A1 and the end portion 12A2), there is no portion (step difference at right angles) discontinuously changing in the extending direction (axial direction of the flow path) of the first passage 12A. Therefore, the pressure loss due to the step (the generation of the vortex due to the step) can be suppressed.
  • a “continuous" change is one in which the change is not intermittent, and along the flow path, the shape of the cross section of the passage changes gradually (smoothly) rather than abruptly.
  • the degree of change may not be constant. Also, there may be a section in which the shape of the cross section is constant.
  • the area of the cross section of the first passage 12A decreases from the beginning 12A1 to the end 12A2 (from the beginning 12A1 to the end 12A2). Therefore, it can suppress that the flow velocity falls in the 1st channel 12A.
  • the area of the cross section of the first passage 12A gradually decreases from the beginning 12A1 to the end 12A2. In other words, the cross-sectional area of the first passage 12A gradually decreases from the start 12A1 to the end 12A2.
  • the degree of decrease may not be constant. Also, there may be a section in which the cross-sectional area is constant. Even if there is a portion where the shape of the cross section changes discontinuously, the change should be sufficiently small.
  • the shape of the cross section of the discharge port 120 continuously changes from the side of the pump element (vane chamber 81) toward the start end 12A1 of the first passage 12A. Also, the area of the cross section of the discharge port 120 gradually decreases from the side of the pump element toward the start end 12A1. Therefore, in the discharge port 120, the same effect as that of the first passage 12A can be obtained. Similarly, the shape of the cross section of the connection between the discharge port 120 and the start end 12A1 of the first passage 12A changes continuously between the discharge port 120 and the start end 12A1. That is, since there is no discontinuously changing portion in the axial direction of the flow path in the inner wall of the connection portion, it is possible to suppress the pressure loss due to the step.
  • the discharge passage 12 can also be viewed as starting from any position in the z-axis direction of the discharge port 120, or as the discharge port 120 continues to any position in the z-axis direction at the start end 12A1 of the discharge passage 12 Is also possible.
  • the housing 3 has a housing body 300 and a cover 301.
  • the housing body 300 has a discharge port 120, a first passage 12A, and a second passage 12B. That is, the discharge port 120, the first passage 12A, and the second passage 12B are integrally formed in the housing main body 300. Therefore, since it is not necessary to install a seal member for improving liquid tightness between the discharge port 120 and the first passage 12A and between the first passage 12A and the second passage 12B, it is possible to increase the number of parts or Complexity of the structure can be suppressed. Further, the configuration in which the connection between the discharge port 120 and the first passage 12A and the shape of the cross section of the first passage 12A continuously change (or the cross-sectional area gradually decreases) can be realized more easily.
  • the cross-sectional area of the first passage 12A before reaching the second passage 12B is equal to or larger than the area of the cross section orthogonal to the third straight line 93 of the second passage 12B. Therefore, by securing the cross-sectional area of the first passage 12A, the fluid flow in the first passage 12A can be facilitated to form an efficient flow.
  • the area of the opening of the second passage 12B at the end portion 12A2 of the first passage 12A is equal to or less than the area of the cross section of the first passage 12A cut at a portion ⁇ closest to the starting end 12A1 among the openings. It is equal to or larger than the area of the cross section of the first passage 12A cut at a portion ⁇ farthest from the start end 12A1.
  • the area of the cross section of the end portion 12A2 of the first passage 12A is substantially the same as the area of the opening of the second passage 12B. Therefore, since it is suppressed that the cross-sectional area of a flow path changes rapidly in the connection part of both the passages 12A and 12B, the pressure loss resulting from the change of a cross-sectional area can be suppressed.
  • the first passage 12A extends around the second straight line 92
  • the second passage 12B extends around the third straight line 93 (along the third straight line 93).
  • the first passage 12A and the second passage 12B extend linearly, respectively. Therefore, the number of inflection points of the flow passage in the discharge passage 12 is at most one (between the first passage 12A and the second passage 12B). Since the inflection point can be reduced as much as possible, it is possible to suppress the pressure loss due to the refraction of the passage (the generation of a vortex due to it). Moreover, the process and cost for forming the discharge passage 12 can be reduced. This is the same as in the example shown in FIG. 18 where there is a step on the inner wall.
  • the discharge port 120 extends around the first straight line 91, and the first straight line 91 is parallel to the second straight line 92. Therefore, the inflection point between the discharge port 120 and the first passage 12A can also be eliminated.
  • the second straight line 92 may not be along the axis 40 of the drive shaft 4.
  • the first passage 12A may extend around a straight line not parallel to the axis 40.
  • the first passage 12A (the second straight line 92) extends along the axis 40 (parallel to the axis 40). Therefore, the dimension of the housing 3 can be suppressed from increasing in the radial direction of the drive shaft 4.
  • the first straight line 91 may not be along the axis 40.
  • the discharge port 120 (first straight line 91) extends along the axis 40. Therefore, the dimension of the housing 3 can be suppressed from increasing in the radial direction of the drive shaft 4.
  • the housing body 300 comprises a pump element receiving hole 362.
  • the pump element receiving hole 362 is a recess for receiving the pump element.
  • the cover 301 closes the opening of the pump element receiving hole 362.
  • the pump element accommodation hole 362 is a bottomed cylindrical shape extending around the axis 40 of the drive shaft 4, and the discharge port 120 opens at the bottom surface 364 of the pump element accommodation hole 362 in the axial direction of the drive shaft 4. Therefore, as compared with the case where the discharge port 120 opens in the peripheral wall 311 of the pump element accommodation hole 362, an increase in the size of the housing main body 300 in the radial direction of the drive shaft 4 can be suppressed.
  • the first passage 12A extending along the axis 40 is formed by casting the first passage 12A together with the pump element receiving hole 362 so as to open at the bottom surface 364 of the pump element receiving hole 362 through the discharge port 120. Is easy. Further, the direction in which the fluid introduced from the pump element to the discharge port 120 flows inside the discharge port 120 is mainly along the axis 40. This is the same as the flow direction (axial direction of the flow path) of the fluid in the first passage 12A. Therefore, it is possible to suppress the occurrence of a refraction point of the flow passage at the connection portion between the discharge port 120 and the first passage 12A (start end 12A1).
  • the discharge port 120 (extending along the axis 40 of the drive shaft 4) is larger in the rotational direction of the drive shaft 4 than in the radial direction of the drive shaft 4.
  • the cross section of the discharge port 120 orthogonal to the first straight line 91 (parallel to the rotational axis of the pump element) has a flat shape that is long in the rotational direction of the pump element. Therefore, it is possible to secure the area of the cross section of the discharge port 120 and to improve the discharge efficiency while suppressing the dimension of the housing 3 from increasing in the radial direction of the drive shaft 4.
  • the first passage 12 ⁇ / b> A (extending along the axis 40 of the drive shaft 4) is larger in the rotational direction of the drive shaft 4 than in the radial direction of the drive shaft 4.
  • the cross section of the first passage 12A orthogonal to the second straight line 92 (parallel to the rotational axis of the pump element) has a flat shape elongated in the rotational direction of the pump element. Therefore, it is possible to secure the area of the cross section of the first passage 12A and to improve the discharge efficiency while suppressing the dimension of the housing 3 from increasing in the radial direction of the drive shaft 4.
  • the cross section of the connecting portion between the discharge port 120 and the first passage 12A (start end 12A1)
  • a configuration in which the shape changes continuously (or the cross-sectional area gradually decreases) can be realized more easily.
  • the first passage 12A (the second straight line 92) is biased toward the rotational direction of the drive shaft 4 with respect to the discharge port 120 (the first straight line 91). Therefore, the discharge efficiency can be improved. That is, the amount of fluid introduced from the pump element to the discharge port 120 is larger on the rotational direction side (termination side of the discharge port 120) than on the reverse rotation direction side of the drive shaft 4 (the start end side of the discharge port 120). Further, the fluid guided from the pump element to the discharge port 120 and flowing inside the discharge port 120 includes a component in the rotational direction of the drive shaft 4 (inertial energy in the rotational direction).
  • the center (first straight line 91) of the discharge port 120 is not limited to the center of the opening, but may be the center of the cross section of the discharge port 120 cut at an arbitrary position in the z-axis direction. It may be.
  • At least a part of the outer wall in the radial direction of the drive shaft 4 in the rotational direction of the drive shaft 4 is an arc centered on the axis 40 of the drive shaft 4
  • the arc ⁇ passing through the outer end in the radial direction of the drive shaft 4 is outside in the radial direction of the drive shaft 4.
  • the outside of the discharge port 120 bulges outward with respect to the arc ⁇ . Therefore, the discharge efficiency and the manufacturing efficiency can be improved.
  • the amount of fluid introduced from the pump element to the discharge port 120 is larger outside the radial inside of the drive shaft 4.
  • the fluid led from the pump element to the discharge port 120 and flowing inside the discharge port 120 includes a component (radial inertial energy) directed radially outward of the drive shaft 4.
  • the radially outward expansion of the discharge port 120 can efficiently guide the fluid from the pump element to the first passage 12A through the discharge port 120.
  • pressure loss can be reduced because the discharge port 120 can easily receive radial inertial energy. More specifically, of the radially outer wall of the discharge port 120, a part of the wall 126 on the rotational direction side of the drive shaft 4 is radially outward with respect to the arc ⁇ .
  • fluid can be more efficiently guided from the pump element through the discharge port 120 to the first passage 12A to receive inertial energy.
  • the discharge port 120 since the discharge port 120 is expanded in the radial direction, the area of the opening of the discharge port 120 in the housing 3 (bottom surface 364 of the pump element accommodation hole 362) (area of the discharge port 120 viewed from the axial direction of the drive shaft 4) Can be increased. Therefore, it is easy to form the discharge port 120 by casting. From this point of view, the discharge port 120 may bulge radially inward.
  • the first passage 12 ⁇ / b> A is inside the discharge passage portion 33.
  • the discharge passage portion 33 is a plate-like flat portion. Therefore, when the cross section of the first passage 12A has a flat shape, the thickness around the first passage 12A can be reduced, and the housing 3 can be miniaturized and miniaturized. Note that at least a part of the first passage 12A may be inside the discharge passage portion 33. In the present embodiment, substantially all of the first passage 12A is inside the discharge passage portion 33. Thus, the above effect can be maximized.
  • the second passage 12 B is inside the discharge passage portion 33.
  • the second passage 12B is opened at one side surface (on the y-axis negative direction side) of the discharge passage portion 33.
  • the length of the second passage 12B that is, the dimension from the first passage 12A (end portion 12A2) to the opening of the second passage 12B can be shortened.
  • the third straight line 93 extends in the direction perpendicular to the second straight line 92 (in the y-axis direction). Therefore, when the one side surface of the discharge passage portion 33 extends along the second straight line 92 (xz plane), the second passage 12B can be effectively shortened. Further, the formation of the first passage 12A and the second passage 12B can be facilitated. Further, the second passage 12B can prevent the housing 3 from being enlarged in the direction of the second straight line 92 (the axial direction of the drive shaft 4).
  • the discharge passage portion 33 has a bolt hole 333.
  • a bolt for fixing a member connected to the opening of the second passage 12 B to the discharge passage portion 33 passes through the hole 333.
  • the bulges 331 and 332 around the hole 333 function as bosses. Therefore, since a part of the discharge passage 33 can be used as a boss (a fixing portion for fixing a member), it is not necessary to separately provide the housing 3 with a boss (a fixing portion). As a result, the housing 3 can be downsized or downsized.
  • the cross section of the second passage 12B orthogonal to the third straight line 93 is circular. Therefore, the pressure loss (friction loss on the wall surface) in the second passage 12B can be suppressed. Further, by making the cross section of the second passage 12B circular, the opening of the second passage 12B on the outer surface of the housing 3 can be easily made circular. By making the opening circular, continuity with the passage in the external member can be easily ensured.
  • the second passage 12B opens to the outside of the housing 3 at a position away from the drive shaft 4 in the axial direction (z-axis direction) of the drive shaft 4. Therefore, interference between the drive shaft 4 and the member connected to the opening of the second passage 12B can be suppressed, and connection of the members can be facilitated.
  • the second passage 12B opens to the outer surface of the housing 3 on the side (the y-axis negative direction side) of the drive shaft 4 with respect to the first passage 12A. Therefore, the said effect can be acquired more effectively.
  • the (z-axis negative direction) end of the drive shaft 4 opposite to the (z-axis positive direction) end of the drive shaft 4 adjacent to the opening of the second passage 12B in the axial direction of the drive shaft 4 is from the housing 3 It projects and power is transmitted from the drive source. That is, the opposite end is connected to a member for driving the drive shaft 4. Therefore, the freedom of design can be secured. That is, interference between the member connected to the opening of the second passage 12B and the member for driving the drive shaft 4 can be suppressed. Further, the size and position of the opening of the second passage 12B, in other words, the length of the first passage 12A can be freely set by the amount that can suppress this interference.
  • the first passage 12A is formed as deep as possible in the axial direction of the drive shaft 4 as long as the discharge port (the opening of the second passage 12B) having a predetermined size is provided. This depth can be reduced. In other words, the area of the opening of the second passage 12B can be increased while suppressing an increase in the size of the housing 3 in the axial direction of the drive shaft 4.
  • the housing 3 (flange portion 35) has a first boss portion 351 and a second boss portion 352 at a position different from the first boss portion 351.
  • a bolt 30 for connecting the cover 301 to the housing main body 300 passes through the first boss 351.
  • a bolt 30 for connecting the housing 3 to another member (the housings 200 and 201 of the balancer module 2) passes through the second boss portion 352. Therefore, since assembly and attachment (to another member) of the pump 1 are realized by separate bosses (fixed parts) 351 and 352, the workability of assembly and attachment can be improved.
  • the coupling strength between the cover 301 and the housing body 300 can be improved.
  • the first bosses 351 are arranged around the pump element accommodation hole 362 so as to straddle the axis 40 of the drive shaft 4 in the x-axis direction and the y-axis direction.
  • the second bosses 352 are two or more (three in the present embodiment). Therefore, the attachment strength of the housing 3 (pump 1) to another member (balancer module 2) can be improved.
  • the second boss portion 352 straddles the axis 40 in the x-axis direction. Therefore, the pump 1 can be attached more firmly.
  • the method of manufacturing the pump 1 has a first step of integrally forming the housing body 300 by casting.
  • the discharge port 120 is opened to the pump element receiving hole 362 which is a recess capable of rotatably receiving the pump element, and extends along the rotation axis 40 of the pump element, and is a cross section orthogonal to the axis 40
  • the first port 12A extending along the rotational axis 40 of the pump element, the discharge port 120 being a flat shape elongated in the rotational direction of the pump element, and the first passage 12A extending along the rotational axis 40 of the pump element
  • the long and flat first passage 12A can be easily formed integrally with the "pump element receiving hole 362".
  • the machining process can be reduced and the sealing plug is not necessary.
  • the configuration by which the shape of the cross section of the discharge port 120, the connection portion between the discharge port 120 and the first passage 12A, and the first passage 12A changes continuously (or the cross sectional area gradually decreases) by casting is easy Can be realized.
  • the inner walls of both 120 and 12A can be continuously (smoothly) It is easy to form.
  • a configuration in which the cross-sectional areas of the discharge port 120 and the first passage 12A gradually decrease can be easily realized by the draft of the (second) die.
  • the discharge passage 33 has a main body 330, a second passage 334, a first boss 335, and a second boss 336.
  • the main body 330 is the same as in the first embodiment.
  • the second passage portion 334 is cylindrical and extends in the x-axis negative direction from the x-axis negative direction side of the main body portion 330.
  • the first passage 12A is inside the main body 330, and the second passage 12B is inside the second passage 334.
  • the first passage 12A has the same configuration as that of the first embodiment.
  • the second passage 12B is cylindrical and extends in the x-axis direction (perpendicular to the second straight line 92).
  • the second passage 12B opens to the wall of the first passage 12A on the negative side in the x-axis direction, and opens to the surface on the negative side in the x-axis direction of the second passage portion 334.
  • the first boss portion 335 has a plate shape extending from the x-axis negative direction end of the second passage portion 334 in the y-axis positive direction side and the z-axis negative direction side and extending along the yz plane.
  • the second boss portion 336 is connected to the y-axis negative direction side and the z-axis positive direction side at the x-axis negative direction end of the second passage portion 334 and is opposite to the first boss portion 335 with the second passage portion 334 interposed therebetween. It is in.
  • Each boss portion 335, 336 has a bolt hole 337.
  • the bolt holes 337 of the first boss portion 335 extend in the x-axis direction and pass through the first boss portion 335.
  • the bolt holes 337 of the second boss portion 336 have a bottom extending in the x-axis direction.
  • the bosses 335 and 336, together with the bolts, function as fixing portions for fixing members connected to the opening of the second passage 12B.
  • the other configuration is the same as that of the first embodiment.
  • the second passage 12B extends in the x-axis direction, so that the second passage 12B opens to the outer surface of the housing 3 at a position horizontal to the first passage 12A. Therefore, the layout of the member connected to the opening of the second passage 12B, in other words, the layout of the pump 1 with respect to the member can be improved. In addition, with the same configuration as that of the first embodiment, the same function and effect as the first embodiment can be obtained.
  • the counterpart member to which the pump (housing) is attached is not limited to the balancer module, but may be a cylinder block or the like.
  • the pump is not limited to the engine, and may be applied to a hydraulic oil supply system such as a brake device or a power steering device.
  • the pump is not limited to the vane pump, but may be a gear pump or the like. In addition, it may be a fixed capacity type.
  • the specific method of casting the housing body is optional. Not limited to die casting, casting using a sand mold may be employed.
  • the material of the housing body is not limited to the aluminum alloy, and may be another material.
  • the pump which sucks in and discharges the fluid is, in one aspect thereof, With the housing, A drive shaft rotatably supported by the housing; A pump element housed in the housing and rotated by the drive shaft; Inside the housing: A suction passage into which the fluid from the outside of the housing is introduced; An inlet port for directing the fluid from the inlet passage to the pump element; A discharge port into which the fluid pressurized by the pump element is introduced; A discharge passage for discharging the fluid from the discharge port to the outside of the housing; The discharge passage is A first passage having a start end connected to the discharge port and an end end, the first passage extending around a straight line to the end; A second passage connected to the end of the first passage and opening to the outside of the housing; The shape of the cross section of the first passage cut in the direction orthogonal to the straight line changes continuously from the start end to the end.
  • the shape of the cross section of the connection between the discharge port and the start end changes continuously between the discharge port and the start end.
  • the straight line extends along the axis of the drive shaft.
  • the housing is A bottomed cylindrical recess extending around the axis of the drive shaft, the housing body having a recess for receiving the pump element; And a cover closing the opening of the recess.
  • the discharge port opens at the bottom surface of the recess in the axial direction of the drive shaft.
  • the discharge port extends along the axis of the drive shaft.
  • the dimension of the discharge port in the rotational direction of the drive shaft is larger than the dimension of the discharge port in the radial direction of the drive shaft
  • the dimension of the first passage in the rotational direction of the drive shaft is larger than the dimension of the first passage in the radial direction of the drive shaft.
  • the first passage is disposed forward of the discharge port in the rotational direction of the drive shaft.
  • the housing comprises a plate-like flat portion, A portion of the first passage and the second passage are located inside the flat portion, The second passage opens at one side surface of the flat portion, The flat portion is provided with a fixing portion for fixing a member connected to the opening of the second passage.
  • the second passage opens to the outside of the housing at a position away from the drive shaft in the axial direction of the drive shaft.
  • the second end of the drive shaft opposite to the first end of the drive shaft adjacent to the opening of the second passage in the axial direction of the drive shaft protrudes from the housing, and the drive It is connected to a member for driving the shaft.
  • the second passage extends along a straight line.
  • the area of the cross section of the first passage decreases from the beginning toward the end.
  • the second passage extends in a direction different from a direction in which the first passage extends.
  • the area of the opening of the second passage at the end of the first passage is: The area of the cross section of the first passage cut at a portion closest to the start end of the first passage among the openings of the second passage at the end of the first passage, It is not less than the area of the cross section of the first passage cut at a portion farthest from the starting end of the first passage among the openings of the second passage at the end of the first passage.
  • the housing is A housing body with a recess for receiving the pump element; A cover closing the opening of the recess; A first fixing portion for fixing the cover to the housing body; And a second fixing portion for fixing the housing to another member at a position different from the first fixing portion.
  • the pump for pressurizing and discharging the sucked fluid is: With the housing, A shaft rotatably supported by the housing; A pump element housed in the housing and coupled to the shaft; Inside the housing: A suction passage for introducing the fluid into the pump element from outside the housing; A discharge passage for discharging the fluid pressurized by the pump element to the outside of the housing;
  • the discharge passage is A first passage extending around a straight line and comprising a starting end on the side of the pump element and an end, the area of the cross section orthogonal to the straight line going from the starting end to the end The decreasing first passage, And a second passage connected to the end of the first passage and open to the outside of the housing.
  • the pump for pressurizing and discharging the sucked fluid is: With the housing, And a pump element rotatably housed in the housing.
  • the housing is An intake port for directing the fluid to the pump element; A discharge port extending around a first straight line parallel to the axis of rotation of the pump element and into which the fluid pressurized by the pump element is introduced, wherein the flat shape is elongated in the rotational direction of the pump element A discharge port having a cross section orthogonal to the first straight line; A discharge passage for discharging the fluid introduced into the discharge port to the outside of the housing;
  • the discharge passage is A first passage connected to the discharge port and extending around a second straight line parallel to the axis of rotation of the pump element, the second straight line being of a flat shape elongated in the direction of rotation of the pump element A first passage having an orthogonal cross section; And a second passage connected to the first passage and extending around a third straight line and opening at an outer surface of the housing.
  • the pump is rotatably supported on the housing and comprises a drive shaft for rotating the pump element,
  • the second passage opens on the outer surface of the housing on the side of the drive shaft with respect to the first passage, A second end opposite to the first end adjacent to the opening of the second passage in the drive shaft protrudes from the housing, and power is transmitted from the drive source.
  • the housing is A housing body comprising a recess for receiving the pump element, the discharge port, the first passage, and the second passage; And a cover closing the opening of the recess.
  • the cross section of the second passage orthogonal to the third straight line is circular.
  • a method of manufacturing a pump according to one aspect thereof A recess rotatably receiving the pump element; An intake port opening at the recess; An outlet port opening in the recess and extending along the axis of rotation of the pump element, the outlet port having a flat shape elongated in the direction of rotation of the pump element and having a cross section orthogonal to the axis of rotation of the pump element
  • a first passage having Forming integrally by casting a housing body having a second passage connected to the first passage and extending linearly and opening at an outer surface of the housing; Installing the pump element in the recess; Closing the opening of the recess with a cover.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Rotary Pumps (AREA)
  • Details Of Reciprocating Pumps (AREA)
PCT/JP2018/025620 2017-07-11 2018-07-06 ポンプ WO2019013110A1 (ja)

Priority Applications (2)

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US16/629,456 US20200141407A1 (en) 2017-07-11 2018-07-06 Pump
CN201880043741.4A CN110832203A (zh) 2017-07-11 2018-07-06 泵

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JP2017-135504 2017-07-11
JP2017135504A JP2019019673A (ja) 2017-07-11 2017-07-11 ポンプ

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JP7222860B2 (ja) * 2019-09-18 2023-02-15 日立Astemo株式会社 可変容量形オイルポンプおよびオイルポンプの製造方法
DE102021105822A1 (de) 2021-03-10 2022-09-15 Nidec Gpm Gmbh Gerotorpumpe mit Kupplung
DE102021105814A1 (de) 2021-03-10 2022-09-15 Nidec Gpm Gmbh Gerotorpumpe mit verbesserter Lagerung

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5258106A (en) * 1975-11-07 1977-05-13 Kayaba Ind Co Ltd Noise-preventive device in hydraulic pump
JPH1193862A (ja) * 1997-09-19 1999-04-06 Jidosha Kiki Co Ltd 可変容量形ポンプ
JP2005139909A (ja) * 2003-11-04 2005-06-02 Hitachi Ltd オイルポンプ
JP2008524486A (ja) * 2004-12-16 2008-07-10 ローベルト ボツシユ ゲゼルシヤフト ミツト ベシユレンクテル ハフツング ベーンポンプ
JP2015068181A (ja) * 2013-09-26 2015-04-13 アイシン精機株式会社 電動ポンプ

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2005068181A (ja) * 2003-08-22 2005-03-17 Three M Innovative Properties Co 微細構造体前駆ペースト、微細構造体及びその製造方法
JP4287322B2 (ja) * 2004-04-19 2009-07-01 朝日興業株式会社 ポンプ
JP5258106B2 (ja) * 2009-04-01 2013-08-07 学校法人鶴学園 鋼製柱梁接合部用の制振補強金物及びその制振補強金物を用いた鋼製柱梁の制振接合構造

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5258106A (en) * 1975-11-07 1977-05-13 Kayaba Ind Co Ltd Noise-preventive device in hydraulic pump
JPH1193862A (ja) * 1997-09-19 1999-04-06 Jidosha Kiki Co Ltd 可変容量形ポンプ
JP2005139909A (ja) * 2003-11-04 2005-06-02 Hitachi Ltd オイルポンプ
JP2008524486A (ja) * 2004-12-16 2008-07-10 ローベルト ボツシユ ゲゼルシヤフト ミツト ベシユレンクテル ハフツング ベーンポンプ
JP2015068181A (ja) * 2013-09-26 2015-04-13 アイシン精機株式会社 電動ポンプ

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