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WO2018051673A1 - Pompe à débit variable et système d'alimentation en fluide hydraulique pour moteur à combustion interne - Google Patents

Pompe à débit variable et système d'alimentation en fluide hydraulique pour moteur à combustion interne Download PDF

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Publication number
WO2018051673A1
WO2018051673A1 PCT/JP2017/028361 JP2017028361W WO2018051673A1 WO 2018051673 A1 WO2018051673 A1 WO 2018051673A1 JP 2017028361 W JP2017028361 W JP 2017028361W WO 2018051673 A1 WO2018051673 A1 WO 2018051673A1
Authority
WO
WIPO (PCT)
Prior art keywords
pump
port
control chamber
control
hydraulic oil
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/JP2017/028361
Other languages
English (en)
Japanese (ja)
Inventor
敦 永沼
大西　秀明
渡辺　靖
浩二 佐賀
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Hitachi Astemo Ltd
Original Assignee
Hitachi Automotive Systems Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Hitachi Automotive Systems Ltd filed Critical Hitachi Automotive Systems Ltd
Priority to CN201780056266.XA priority Critical patent/CN109690081A/zh
Priority to US16/333,211 priority patent/US20190219053A1/en
Publication of WO2018051673A1 publication Critical patent/WO2018051673A1/fr
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
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/18—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber
    • F04C14/22—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/06—Control
    • F04B1/07—Control by varying the relative eccentricity between two members, e.g. a cam and a drive shaft
    • 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
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/12—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by varying the length of stroke of the working members
    • F04B49/123—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by varying the length of stroke of the working members by changing the eccentricity of one element relative to another element
    • F04B49/125—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by varying the length of stroke of the working members by changing the eccentricity of one element relative to another element by changing the eccentricity of the actuation means, e.g. cams or cranks, relative to the driving means, e.g. driving shafts
    • 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
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/18—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber
    • F04C14/22—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members
    • F04C14/223—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members using a movable cam
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2210/00—Fluid
    • F04C2210/20—Fluid liquid, i.e. incompressible
    • F04C2210/206—Oil

Definitions

  • the present invention relates to a variable displacement pump.
  • variable displacement pumps are known.
  • the conventional variable displacement pump has room to improve controllability.
  • variable displacement pump preferably includes a control unit that changes the cross-sectional area of the flow path for discharging the hydraulic oil in the control chamber while communicating the discharge unit and the control chamber.
  • FIG. 11 A part of FIG. 11 is enlarged and shown. It is a schematic diagram of the control valve of 2nd Embodiment. The operating state of the pump of 2nd Embodiment is shown. The operating state of the pump of 2nd Embodiment is shown. The operating state of the pump of 2nd Embodiment is shown. It is sectional drawing of a part of pump of 3rd Embodiment.
  • a variable displacement pump (hereinafter referred to as a pump) 2 of the present embodiment is an oil pump used in a hydraulic oil supply system 1 of an internal combustion engine (engine) of an automobile.
  • the pump 2 is installed at the front end of the cylinder block of the engine, etc., and is used for various sliding parts of the engine and variable valve gears (valve timing control devices, etc.) that variably control the operating characteristics of the engine valves.
  • Supply oil hydroaulic oil
  • an engine oil supply system 1 includes an oil pan 400, a passage 4, a pump 2, a pressure sensor (pressure measuring unit) 51, a rotation speed sensor (rotation speed measuring unit) 52, and an engine control unit. (Control unit) 6 is provided.
  • the oil pan 400 is a low pressure part that is located in the lower part of the engine and stores hydraulic oil.
  • the passage 4 is, for example, inside the cylinder block, and includes a suction passage 40, a discharge passage 41, a main gallery 42, a control passage 43, and a relief passage 44. One end of the suction passage 40 is connected to the oil pan 400 via the oil filter 401. The other end of the suction passage 40 is connected to the pump 2. One end of the discharge passage 41 is connected to the pump 2.
  • the other end of the discharge passage 41 is connected to the main gallery 42.
  • An oil filter 410 and a pressure sensor 51 are installed in the discharge passage 41.
  • the main gallery 42 is connected to each sliding portion of the engine, a variable valve operating device, and the like.
  • the relief passage 44 is branched from the discharge passage 41 and connected to the oil pan 400.
  • a relief valve 440 is installed in the relief passage 44.
  • the pump 2 is a vane pump.
  • the pump 2 includes a housing, a shaft (drive shaft) 21, a rotor 22, a plurality of vanes 23, a cam ring 24, a spring (first urging member) 25, a first seal member 261, a second seal member 262, a pin 27, and A control mechanism 3 is provided.
  • the housing has a housing body 20 and a cover.
  • FIG. 2 shows the pump 2 with the cover removed.
  • the housing body 20 includes a pump storage chamber 200, a suction port (suction part) 201, and a discharge port (discharge part) 203 therein.
  • the pump housing chamber 200 has a bottomed cylindrical shape and opens on one side surface of the housing body 20.
  • a hole (shaft housing hole) for housing the drive shaft 21 and a hole (pin hole) for fixing the pin 27 are opened.
  • the cover is attached to one side surface of the housing body 20 with a plurality of bolts, and closes the opening of the pump housing chamber 200.
  • One end of the suction port 201 opens to the outer surface of the housing body 20, and the other end of the suction passage 40 is connected.
  • the other end of the suction port 201 opens to the bottom surface of the pump storage chamber 200 as a suction port 202.
  • the suction port 202 is a groove (concave portion) extending in the direction around the shaft receiving hole and is on the opposite side of the pin hole with respect to the shaft receiving hole.
  • the discharge port 203 opens as a discharge port 204 on the bottom surface of the pump storage chamber 200.
  • the discharge port 204 is a groove (concave portion) extending in the direction around the shaft receiving hole, and is located on the pin hole side with respect to the shaft receiving hole.
  • the other end of the discharge port 203 opens to the outer surface of the housing body 20, and one end of the discharge passage 41 is connected.
  • a groove corresponding to the suction port 202 and the discharge port 204 of the housing body 20 is also provided on the surface of the cover that closes the pump housing chamber 200.
  • the rotor 22, the plurality of vanes 23, the cam ring 24, and the spring 25 are inside the pump housing chamber 200.
  • the drive shaft 21 is rotatably supported by the housing.
  • the drive shaft 21 is connected to the crankshaft by a chain, a gear or the like.
  • the rotor 22 is fixed to the drive shaft 21 in the circumferential direction.
  • the rotor 22 is cylindrical.
  • a concave portion 221 is provided on the surface on one side of the rotor 22 in the axial direction.
  • the outer peripheral surface 220 of the rotor 22 has a convex portion 224 protruding outward in the radial direction.
  • the slit 222 opens in the convex part 224.
  • the vane 23 is accommodated in the slit 222.
  • An annular member 230 is installed in the recess 221.
  • the outer peripheral surface of the member 230 faces the base end of each vane 23.
  • the inner peripheral surface 240 of the cam ring 24 is cylindrical.
  • the outer periphery of the cam ring 24 has four protrusions 241 to 244 that protrude radially outward.
  • a first seal member 261 is installed on the first protrusion 241.
  • a second seal member 262 is installed on the second protrusion 242.
  • the pin 27 is fitted to the third protrusion 243.
  • the first protrusion 241 and the second protrusion 242 are on opposite sides across a straight line passing through the axis of the pin 27 and the center 24P of the cam ring inner peripheral surface 240.
  • One end of a spring 25 is installed on the fourth protrusion 244.
  • the first control chamber 291 includes a space between the first protrusion 241 (first seal member 261) to the third protrusion 243 (pin 27) on the outer peripheral surface 245 of the cam ring 24 and the inner peripheral surface of the housing (pump housing chamber 200). It is a space between.
  • the first control chamber 291 is sealed by the first seal member 261 and the pin 27.
  • a first region 246 between the first seal member 261 and the pin 27 on the cam ring outer peripheral surface 245 faces the first control chamber 291.
  • the second control chamber 292 includes a space between the second protrusion 242 (second seal member 262) and the third protrusion 243 (pin 27) on the cam ring outer peripheral surface 245 and the inner peripheral surface of the housing (pump housing chamber 200). It is a space between.
  • the second control chamber 292 is sealed by the second seal member 262 and the pin 27.
  • a second region 247 between the second seal member 262 and the pin 27 on the cam ring outer peripheral surface 245 faces the second control chamber 292.
  • the area of the second region 247 (the angle occupied by the second region 247 in the circumferential direction of the cam ring 24) is slightly larger than the area of the first region 246 (the angle occupied by the first region 246 in the circumferential direction of the cam ring 24).
  • the radial width of the portion corresponding to the second region 247 in the cam ring 24 corresponds to the portion corresponding to the first region 246 (
  • the width in the radial direction of the cam ring 24 that is continuous with the first region 246 and faces the bottom surface of the pump storage chamber 200 is larger on average in the region adjacent to the discharge port 204 at least in the radial direction.
  • the spring accommodating chamber 293 is formed between the first protrusion 241 (first seal member 261) on the cam ring outer peripheral surface 245 and the second protrusion 242 (second seal member 262) via the fourth protrusion 244 and the housing (pump It is a space between the inner peripheral surface of the storage chamber 200).
  • Spring 25 is a compression coil spring. One end of the spring 25 abuts on the surface of the fourth protrusion 244 on one side in the circumferential direction of the cam ring 24. The surface on the other circumferential side of the cam ring 24 in the fourth protrusion 244 faces the inner peripheral surface of the pump storage chamber 200 (spring storage chamber 293) and can contact the inner peripheral surface. The other end of the spring 25 is installed on the inner peripheral surface of the pump housing chamber 200 (spring housing chamber 293). The spring 25 is in a compressed state, has a predetermined set load in the initial state, and constantly urges the fourth protrusion 244 to the other side in the circumferential direction.
  • the control mechanism 3 has a control passage 43 and a control valve 7.
  • the control passage 43 has a first feedback passage 431 and a second feedback passage 432.
  • One end side of the first feedback passage 431 branches off from the discharge passage 41.
  • the other end of the first feedback passage 431 is connected to the first control chamber 291.
  • the second feedback passage 432 includes a supply passage 433, a communication passage 434, and a discharge passage 435.
  • One end side of the supply passage 433 branches from the first feedback passage 431.
  • the other end of the supply passage 433 is connected to the control valve 7.
  • One end of the communication path 434 is connected to the control valve 7.
  • the other end of the communication path 434 is connected to the second control chamber 292.
  • One end of the discharge passage 435 is connected to the control valve 7.
  • the other end of the discharge passage 435 is connected to the oil pan 400.
  • the control valve 7 is a solenoid valve (solenoid valve) and has a valve portion 8 and a solenoid portion 9.
  • the valve unit 8 includes a cylinder (tubular member) 80, a spool 81, and a spring (second urging member) 82.
  • the solenoid unit 9 includes a case 90, a solenoid, a plunger, and a connector 92.
  • the cylinder 80 is a hollow member (cylindrical member) with an inner peripheral surface 800 having a cylindrical shape, one side in the axial direction is open, and a bottom portion 802 is provided on the other side in the axial direction.
  • a hole 809 passes through the bottom portion 802 in the axial direction.
  • the cylinder 80 has a plurality of ports. These ports are holes that penetrate the cylinder 80 in the radial direction, and open to the inner peripheral surface 800 and the outer peripheral surface 801 of the cylinder 80. These ports function as a part of the second feedback passage 432 together with the space on the inner peripheral side of the cylinder 80.
  • the plurality of ports include a supply port 803, a communication port 804, and an exhaust port 805.
  • the supply port 803, the communication port 804, and the discharge port 805 are arranged in this order from one axial direction to the other side of the cylinder 80.
  • the other end of the supply passage 433 is connected to the supply port 803.
  • the supply port 803 communicates with the discharge port 203 via the supply passage 433 (second feedback passage 432) and the discharge passage 41.
  • the supply port 803 can introduce hydraulic oil discharged from the discharge port 203 into the cylinder 80.
  • One end of a communication path 434 is connected to the communication port 804.
  • the communication port 804 communicates with the second control chamber 292 through the communication path 434.
  • the communication port 804 connects the inside of the cylinder 80 and the second control chamber 292.
  • One end of a discharge passage 435 is connected to the discharge port 805.
  • the discharge port 805 communicates with the oil pan 400 via the discharge passage 435.
  • the discharge port 805 can discharge hydraulic oil from the cylinder 80.
  • the spool 81 is a valve body (valve) on the second feedback passage 432.
  • the spool 81 is inside the cylinder 80 (accommodated in the cylinder 80) and can reciprocate in the axial direction of the cylinder 80 along the cylinder inner peripheral surface 800.
  • the spool 81 includes a first land portion 811, a second land portion 812, and a connection portion 813.
  • the first land portion 811 is at the end on one axial side of the spool 81.
  • the second land portion 812 is at the other end of the spool 81 in the axial direction.
  • the connection portion 813 is between the first land portion 811 and the second land portion 812, and connects both land portions 811 and 812.
  • the diameter of the first land portion 811 and the diameter of the second land portion 812 are the same.
  • the diameters of both land portions 811 and 812 are slightly smaller than the diameter of the cylinder inner peripheral surface 800.
  • the connection portion 813 is a thin shaft portion, and the diameter of the connection portion 813 is smaller than the diameters of both land portions 811 and 812.
  • the land portions 811 and 812 are in sliding contact with the cylinder inner peripheral surface 800.
  • a space 807 is formed between the first land portion 811 and the second land portion 812 as a liquid chamber.
  • a space 808 is defined between the second land portion 812 and the bottom portion 802.
  • the space 807 is between the cylinder inner peripheral surface 800, the outer peripheral surface of the connection portion 813, the surface on the other axial side of the first land portion 811 and the surface on the one axial side of the second land portion 812.
  • the space 807 is cylindrical (annular).
  • the supply port 803 opens in the initial state, and the communication port 804 always opens.
  • a discharge port 805 can be opened in the space 807.
  • the space 808 is between the surface on the other axial side of the second land portion 812 and the bottom portion 802 on the inner peripheral side of the cylinder 80.
  • the discharge port 805 is slightly opened in the initial state.
  • the spring 82 is a compression coil spring and is installed in the space 808.
  • the space 808 functions as a spring chamber that houses the spring 82.
  • One end side of the spring 82 is fitted to the outer peripheral side of the convex portion protruding from the second land portion 812 of the spool 81, and one end of the spring 82 is in contact with the other end surface of the second land portion 812.
  • the other end of the spring 82 is in contact with the bottom 802.
  • the spring 82 is in a compressed state, has a predetermined set load in the initial state, and constantly urges the spool 81 toward one side in the axial direction. Let this spring force be fs.
  • the solenoid unit 9 is coupled to one side in the axial direction of the valve unit 8 and closes the opening on one side in the axial direction of the cylinder 80.
  • the solenoid unit 9 is an electromagnet that receives supply of current through the connector 92.
  • the solenoid and the plunger are accommodated in the case 90.
  • a solenoid (coil) generates electromagnetic force when energized.
  • the plunger (armature) is made of a magnetic material, is located on the inner peripheral side of the solenoid, and is movable in the axial direction. The plunger is biased in the axial direction by the electromagnetic force generated by the solenoid.
  • the first land portion 811 of the spool 81 is integrally coupled to the plunger.
  • the electromagnetic force biases the first land portion 811 (spool 81) toward the other side in the axial direction.
  • This electromagnetic force (solenoid thrust for propelling the spool 81) is defined as fm.
  • the solenoid can continuously change the magnitude of fm according to the value of the supplied current.
  • the solenoid unit 9 is PWM-controlled, and the current value of the solenoid is given by the duty ratio D. fm changes according to the duty ratio D (the current value of the solenoid). When D is less than a predetermined value D1 (dead zone), fm is zero (not generated) regardless of the size of D.
  • fm When D is greater than or equal to D1 and less than the predetermined value D2, fm changes according to D, and the larger D is, the larger fm is.
  • D is equal to or greater than D2
  • fm is the maximum value fmax regardless of the size of D.
  • the pressure sensor 51 detects (measures) the pressure of the hydraulic oil discharged from the discharge port 203 of the pump 2 into the discharge passage 41, in other words, the pressure of the main gallery 42 (main gallery hydraulic pressure P).
  • the rotation speed sensor 52 detects (measures) the rotation speed Ne of the engine (crankshaft).
  • the engine control unit (hereinafter referred to as ECU) 6 controls the opening / closing operation of the control valve 7 (that is, the discharge amount of the pump 2) based on the input information and the built-in program. Thereby, the pressure and flow rate of the hydraulic oil supplied to the engine are controlled.
  • the ECU 6 includes a receiver, a central processing unit (CPU), a read only memory (ROM), a random access memory (RAM), and a drive circuit, and these are mainly microcomputers connected to each other by a bidirectional common bus. To do.
  • the receiving unit receives information related to detection values of the pressure sensor 51 and the rotation speed sensor 52 and other engine operating states (oil temperature, water temperature, engine load, etc.).
  • the ROM is a storage unit that stores control programs, map data, and the like.
  • the CPU is a calculation unit that performs calculation using information input from the reception unit based on the read control program.
  • the CPU performs a value of the current supplied to the control valve 7 (solenoid unit 9) and other calculations.
  • a control signal corresponding to the calculation result is output to the drive circuit.
  • the drive circuit supplies power to the solenoid in accordance with a control signal from the CPU, and controls the supply current to the solenoid.
  • the drive circuit is a PWM control circuit, and changes the pulse width (duty ratio D) of the solenoid drive signal in accordance with the control signal.
  • the control program is executed and the control valve 7 (pump 2) is controlled.
  • the ECU 6 controls the solenoid so that the difference between the main gallery hydraulic pressure P and the predetermined required value P * is within a predetermined range at an arbitrary engine rotational speed Ne in a predetermined engine speed range (Ne ⁇ Ne1). Change the value of the current to be supplied (duty ratio D).
  • Ne1 is a preset rotation speed.
  • the required value P * is the oil pressure required for the operation of the variable valve system, the oil pressure required for cooling the engine piston, the oil pressure required for lubricating the crankshaft bearings, etc. It is set in advance as an ideal value corresponding to.
  • P * is stored as a map for each Ne (depending on the engine operating state). For example, the map can also set discharge pressure, oil temperature, water temperature, engine load, and the like as parameters.
  • the ECU 6 changes D according to Ne based on the map.
  • the ECU 6 detects the main gallery hydraulic pressure P and performs feedback control so as to bring it close to P *.
  • the ECU 6 changes D so that the difference of the detected value with respect to the required value P * of the main gallery hydraulic pressure P is within a predetermined range.
  • the ECU 6 sets D to zero when Ne is less than Ne1.
  • the magnitude of ⁇ P is larger than the preset value ⁇ Pset, D is changed so that the magnitude of ⁇ P becomes smaller until the magnitude of ⁇ P becomes equal to or smaller than ⁇ Pset.
  • ⁇ P is equal to or smaller than ⁇ Pset, D is maintained (the value immediately before ⁇ P is equal to or smaller than ⁇ Pset).
  • the cam ring 24 accommodates the rotor 22 and the plurality of vanes 23 to separate a plurality of pump chambers (working chambers) 28.
  • the rotor 22 and the plurality of vanes 23 function as elements (pump components) constituting the pump 2.
  • the working chamber 28 is defined (defined) by the outer peripheral surface 220 of the rotor 22, the two adjacent vanes 23, the cam ring inner peripheral surface 240, the bottom surface of the pump housing chamber 200, and the side surface of the cover.
  • the volume of the working chamber 28 can change with rotation, and it makes a pump action because the volume of the working chamber 28 increases / decreases by rotation.
  • the volume of the working chamber 28 increases in a range (suction region) overlapping with the suction port 202, and the working chamber 28 sucks the working oil from the suction port 202.
  • the volume of the working chamber 28 decreases in a range (discharge region) overlapping the discharge port 204, and the working chamber 28 discharges hydraulic oil to the discharge port 204.
  • the theoretical discharge amount (discharge amount per rotation) of the pump 2, that is, the capacity is determined by the difference between the maximum volume and the minimum volume of the working chamber 28.
  • the rotation of the crankshaft is transmitted to the drive shaft 21 of the pump 2 by the chain and gear.
  • the drive shaft 21 drives the rotor 22 to rotate.
  • the rotor 22 rotates counterclockwise in FIG.
  • the pump structure including the rotor 22 is driven to rotate, and discharges hydraulic oil guided from the suction port 201 from the discharge port 203.
  • the discharge pressure is introduced into the back pressure chamber 223, and the vane 23 is pushed out from the slit 222, so that the liquid tightness of the working chamber 28 is improved.
  • the annular member 230 pushes the vane 23 out of the slit 222, so that the liquid tightness of the working chamber 28 is improved.
  • the pump 2 sucks hydraulic oil from the oil pan 400 through the suction passage 40 and discharges the hydraulic oil to the discharge passage 41.
  • the pump 2 pumps hydraulic oil to each part of the engine via the discharge passage 41 and the main gallery 42.
  • the relief valve 440 opens when the pressure of the discharge passage 41 (discharge pressure) reaches a predetermined high pressure, and discharges hydraulic oil from the discharge passage 41 via the relief passage 44.
  • the amount of change in the volume of the working chamber 28 (the difference between the maximum volume and the minimum volume) is variable.
  • the cam ring 24 is a member (movable member) that can move inside the pump storage chamber 200, and can rotate and swing around the pin 27.
  • the pin 27 functions as a pivot portion (fulcrum) inside the pump storage chamber 200.
  • the increase / decrease amount (volume change amount) of each of the plurality of working chambers 28 during rotation of the rotor 22 and the plurality of vanes 23 is changed. That is, the pump 2 is of a variable capacity type, and it is possible to increase ⁇ by increasing ⁇ and decrease the capacity by decreasing ⁇ . Further, the volume of the first control chamber 291 and the second control chamber 292 can change when the cam ring 24 moves.
  • the cam ring 24 is urged by the spring 25 to one side in the rotational direction around the pin 27 (the side where the volume of each of the plurality of working chambers 28 increases and decreases and the eccentric amount ⁇ increases). Let this spring force be Fs.
  • the cam ring 24 receives the pressure of the hydraulic oil in the first control chamber 291.
  • the first region 246 of the cam ring outer peripheral surface 245 functions as a pressure receiving surface that receives the pressure of the first control chamber 291.
  • the cam ring 24 is urged to the other side in the rotational direction around the pin 27 (the side on which ⁇ decreases) by the hydraulic pressure.
  • the force (hydraulic pressure) by this oil pressure is Fp1.
  • the volume of the first control chamber 291 increases when the cam ring 24 moves to the other side in the rotational direction (the direction against the urging force Fs of the spring 25).
  • the cam ring 24 receives the pressure (control oil pressure) p of hydraulic oil in the second control chamber 292.
  • the second region 247 of the cam ring outer peripheral surface 245 functions as a pressure receiving surface that receives the control hydraulic pressure p.
  • the cam ring 24 is biased to one side in the rotational direction by the control hydraulic pressure p.
  • the force (hydraulic pressure) by the control oil pressure p is Fp2.
  • the volume of the second control chamber 292 increases when the cam ring 24 moves to one side in the rotational direction (the same direction as Fs).
  • the rotational direction position (the amount of eccentricity ⁇ , that is, the capacity) of the cam ring 24 is mainly determined by Fp1, Fp2, and Fs.
  • Fp1 becomes larger than the sum of Fp2 and Fs (Fp2 + Fs)
  • Fp2 + Fs the cam ring 24 swings to the other side in the rotational direction, and ⁇ (capacity) becomes small.
  • Fp1 becomes smaller than (Fp2 + Fs)
  • the cam ring 24 swings to one side in the rotational direction, and ⁇ (capacity) increases.
  • the hydraulic oil discharged from the discharge port 203 (the hydraulic pressure P of the main gallery 42) is introduced into the first control chamber 291 via the first feedback passage 431.
  • the hydraulic oil (main gallery hydraulic pressure P) discharged from the discharge port 203 can be introduced into the second control chamber 292 via the second feedback passage 432 (supply passage 433, control valve 7, communication passage 434).
  • the hydraulic oil inside the second control chamber 292 can be discharged through the discharge passage 435.
  • the control valve 7 can control introduction of hydraulic oil into the second control chamber 292 and discharge of hydraulic oil from the second control chamber 292.
  • the spool 81 switches the connection state of the passage by moving. Specifically, the first land portion 811 changes the opening area of the supply port 803, and the second land portion 812 changes the opening area of the discharge port 805.
  • the opening of the communication port 804 is not blocked by both land portions.
  • the space 807 serves as a hydraulic oil passage.
  • connection and disconnection between the communication passage 434 and the supply passage 433, or connection and disconnection between the communication passage 434 and the discharge passage 435 are switched.
  • the communication path 434 is basically communicated with both the supply path 433 and the discharge path 435.
  • the second land portion 812 opens the discharge port 805 into the space 807 while the first land portion 811 partially closes the opening of the supply port 803 in the space 807.
  • the first land portion 811 opens the supply port 803 into the space 807 with the second land portion 812 partially closing the opening of the discharge port 805 in the space 807.
  • the opening of the communication port 804 in the space 807 is always fully open. It should be noted that at the time of switching (temporarily at a predetermined position of the spool 81), the space 807 may have a state where the supply port 803 and the discharge port 805 are simultaneously open. The maximum opening area of the supply port 803 in the space 807 and the maximum opening area of the discharge port 805 in the space 807 do not have to be the same.
  • the position of the spool where the opening area of the supply port 803 in the space 807 starts to decrease and the position of the spool where the discharge port 805 starts to open in the space 807 must be the same, or the opening area of the discharge port 805 in the space 807 It is not necessary that the position of the spool at which the supply port 803 begins to decrease and the position of the spool at which the supply port 803 starts to open in the space 807 be the same. These are determined by tuning.
  • the spool 81 switches the communication state between the discharge port 203 and the second control chamber 292 (via the communication passage 434 and the supply passage 433) by switching the connection state of the passages, and (the communication passage 434 and the discharge passage).
  • the communication between the second control chamber 292 and the oil pan 400 (via 435) is switched.
  • the communication path 434 and the supply path 433 are connected without limitation (with a maximum flow path cross-sectional area).
  • the discharge port 203 and the second control chamber 292 are in maximum communication with each other, and the amount of hydraulic oil discharged from the discharge port 203 and introduced into the second control chamber 292 is maximized.
  • the communication passage 434 and the discharge passage 435 are connected with the largest restriction (with the smallest flow passage cross-sectional area).
  • the second control chamber 292 and the oil pan 400 are in a state where they communicate with each other at a minimum, and the amount of hydraulic oil that can be discharged from the second control chamber 29 is minimized. More specifically, both the passages 434 and 435 are blocked, the second control chamber 292 and the oil pan 400 are not in communication, and hydraulic oil is not discharged from the inside of the second control chamber 29.
  • this is referred to as a first state. As shown in FIG.
  • the communication passage 434 and the discharge passage 435 are connected with a restriction (with a non-maximum flow passage cross-sectional area).
  • the second control chamber 292 and the oil pan 400 are in partial communication with each other, and hydraulic oil can be discharged from the second control chamber 292. Further, the communication path 434 and the supply path 433 are connected with restrictions.
  • the discharge port 203 and the second control chamber 292 are in a partially communicated state, and the hydraulic oil discharged from the discharge port 203 can be introduced into the second control chamber 292. Hereinafter, this is referred to as a second state.
  • the communication path 434 and the discharge path 435 are connected with smaller restrictions.
  • the second control chamber 292 and the oil pan 400 are more communicated with each other, and the amount of hydraulic oil that can be discharged from the second control chamber 292 increases.
  • the communication passage 434 and the supply passage 433 are connected with greater restrictions.
  • the discharge port 203 and the second control chamber 292 communicate with each other less, and the amount of hydraulic oil that can be discharged from the discharge port 203 and introduced into the second control chamber 292 is reduced.
  • this is referred to as a third state.
  • the communication passage 434 and the discharge passage 435 are connected without limitation.
  • the second control chamber 292 and the oil pan 400 are in maximum communication with each other, and the amount of hydraulic oil that can be discharged from the second control chamber 292 is maximized.
  • the communication passage 434 and the supply passage 433 are connected with the greatest restriction.
  • the discharge port 203 and the second control chamber 292 are in a state of being in communication with each other at a minimum, and the amount of hydraulic oil discharged from the discharge port 203 and introduced into the second control chamber 292 is minimized. More specifically, both the passages 433 and 434 are blocked, the discharge port 203 and the second control chamber 292 are not in communication, and no hydraulic oil is introduced into the second control chamber 29.
  • this is referred to as a fourth state.
  • the solenoid unit 9 can move the spool 81 to an arbitrary position according to the control signal (duty ratio D).
  • the position of the spool 81 is proportional to the duty ratio D on average.
  • the control valve 7 functions as a proportional control valve.
  • the control valve 7 can continuously change the position of the spool 81 and can stop the spool 81 at an arbitrary position.
  • the axial position of the spool 81 with respect to the cylinder 80 is mainly determined by the spring force fs and the electromagnetic force fm.
  • the solenoid can change fm continuously. By changing the size of fm, movement of the spool 81, in other words, transition between the above states (state transition) becomes possible.
  • the spool 81 moves to the other side in the axial direction and realizes a state transition from the first state side to the fourth state side.
  • the spool 81 moves to one side in the axial direction and realizes a state transition from the fourth state side to the first state side.
  • fm varies with D.
  • the solenoid functions as a proportional electromagnet that can control fm steplessly according to D (current value). Basically, increasing D increases fm, and the position of the spool 81 (land portions 811 and 812) is determined according to D. As shown in FIG.
  • the opening area Si of the supply port 803 and the opening area Sd of the discharge port 805 in the space 807 are proportional to D, respectively.
  • Si is the maximum value Smax regardless of the size of D.
  • Si changes according to D, and Si increases as D increases.
  • Si is the minimum value Smin (zero in this embodiment) regardless of the size of D.
  • Sd is the minimum value Smin (zero in this embodiment) regardless of the size of D.
  • Sd is the maximum value Smax regardless of the size of D.
  • Each value of Ds, De, Smin, and Smax may be different between Si and Sd. De at which Si is Smin is larger than Ds at which Sd is Smin. That is, Si and Sd intersect between Ds and De.
  • fs acts on the spool 81 in the left direction and fm acts on the spool 81 in the right direction. If D is less than Ds and fm is equal to or less than fs (set load of the spring 82), the spool 81 is at the initial position closest to one side in the axial direction as shown in FIG.
  • the opening area Si of the supply port 803 in the space 807 is the maximum value Smax on the setting.
  • the opening of the discharge port 805 in the space 807 is completely closed by the second land portion 812, and the opening area Sd becomes a set minimum value Smin (zero).
  • the hydraulic pressure P introduced into the space 807 from the supply passage 433 is introduced into the second control chamber 292 without pressure loss.
  • the space 807 functions as a communication chamber through which hydraulic oil flows. Since (Fp2 + Fs (the set load of the spring 25)) is larger than Fp1 acting on the cam ring 24, the cam ring 24 is at the position most oscillated on one side in the rotational direction, and maintains the maximum amount of eccentricity ⁇ .
  • the spool 81 slightly moves from the initial position to the other side in the axial direction as shown in FIG.
  • the opening of the supply port 803 in the space 807 is partially blocked by the first land portion 811 and the opening area Si is smaller than Smax.
  • the discharge port 805 partially opens in the space 807, and the opening area Sd becomes larger than Smin (zero). That is, the connection destination of the communication path 434 (second control chamber 292) is switched from only the supply port 803 to both the supply port 803 and the discharge port 805.
  • the hydraulic oil is discharged from the space 807 through the discharge passage 435. Therefore, the hydraulic oil can be discharged from the communication path 434 (second control chamber 292) through the space 807.
  • the hydraulic oil can be discharged from the supply passage 433 through the space 807, a flow of the hydraulic oil from the supply passage 433 to the space 807 through the supply port 803 occurs.
  • the supply port 803 in which the opening area Si is reduced functions as an orifice, and the hydraulic pressure in the space 807 is lower than the hydraulic pressure P in the supply passage 433. Therefore, since the pressure reduced from the hydraulic pressure P is introduced into the second control chamber 292 from the space 807, the control hydraulic pressure p decreases.
  • the control valve 7 can change the control hydraulic pressure p and the eccentric amount ⁇ (capacity) by changing the position of the spool 81 in accordance with the duty ratio D, thereby controlling the hydraulic pressure P or the discharge flow rate.
  • the control oil pressure p is a maximum value pmax (corresponding to the main gallery oil pressure P) regardless of the magnitude of D when D is less than Ds.
  • p changes according to D, and as D increases, p decreases.
  • p is the minimum value pmin regardless of the size of D.
  • the eccentricity ⁇ is the maximum value ⁇ max regardless of the size of D when D is less than Ds.
  • ⁇ changes according to D, and as D increases, ⁇ decreases.
  • ⁇ is the minimum value ⁇ min regardless of the size of D.
  • the main gallery hydraulic pressure P is the maximum value Pmax (at the engine speed Ne at that time) regardless of the magnitude of D when D is less than Ds.
  • P changes according to D, and P increases as D increases.
  • P is the minimum value Pmin (at Ne at that time).
  • the ECU 6 changes the duty ratio D according to the stored map so that the difference ⁇ P of the detected value with respect to the required value P * of the main gallery hydraulic pressure P is within a predetermined range in the region of the engine speed Ne equal to or greater than Ne1.
  • the characteristic of the hydraulic pressure P with respect to Ne as shown by the thick solid line in FIG. 11 is realized.
  • the engine 6 will be described by taking the low speed region as an example. In the region where Ne is less than Ne1, D is set to 0% (no current is supplied to the solenoid).
  • the hydraulic oil discharged from the discharge port 203 is guided to the second control chamber 292, while the hydraulic oil is not discharged from the second control chamber 292 to the oil pan 400.
  • the ECU 6 Since the magnitude of ⁇ P is equal to or smaller than ⁇ Pset in the region where Ne is equal to or larger than Ne2 and smaller than Ne3, the ECU 6 maintains D at D3 (which is a value immediately before the magnitude of ⁇ P becomes equal to or smaller than ⁇ Pset).
  • D changes according to Ne at a constant gradient according to the capacity corresponding to D3.
  • P increases (decreases) as Ne increases (decreases).
  • the ECU 6 increases (decreases) D in response to an increase (decrease) in Ne, as in the region from Ne1 to less than Ne2, since ⁇ P is larger than ⁇ Pset in an area where Ne is Ne3 or more. Therefore, regardless of Ne, P is maintained (controlled to be constant) at P2 and its vicinity. This is repeated a plurality of times according to the change in Ne, thereby realizing the step-like characteristics.
  • the solenoid can change the magnitude of the electromagnetic force fm that urges the spool 81 in the axial direction according to the duty ratio D (value of the supplied current). Therefore, the main gallery hydraulic pressure P and the discharge flow rate can be freely changed (controlled) by changing D according to Ne.
  • the characteristics of P and discharge flow rate with respect to Ne can be easily approximated to desired characteristics. Thereby, it is possible to improve fuel efficiency by suppressing power loss due to unnecessary increase in discharge pressure (increase in flow rate).
  • the characteristics are expressed in steps for explanation. However, in actual control, the number of steps is increased innumerably, that is, P is controlled steplessly according to Ne, and P is required hydraulic pressure P *. It is possible to control substantially continuously along the line.
  • the control valve 7 and the cam ring 24 operate so that the characteristic of the discharge pressure P according to the change in the engine speed Ne approaches the required characteristic.
  • the feedback control makes it possible to accurately control the characteristics of P while avoiding the influence of leakage (leakage of hydraulic oil) due to clearance between members in the pump 2.
  • the method for feedback control of P to P * is not limited to the above, and is arbitrary. By setting ⁇ Pset to be smaller, the stepped steps can be changed more finely and continuously. ⁇ Pset may be zero. Control hunting can be suppressed by setting ⁇ Pset to a non-zero value and not changing D when ⁇ P is equal to or smaller than ⁇ Pset.
  • the control valve 7 can change the position of the spool 81 continuously. Therefore, since the spool 81 can be moved to an arbitrary position, the control hydraulic pressure p, the eccentricity ⁇ (capacity), and the main gallery hydraulic pressure P can be controlled to arbitrary values.
  • the control valve 7 can stop the spool 81 at an arbitrary position. Therefore, since the spool 81 can be fixed at an arbitrary position, the control hydraulic pressure p and the eccentric amount ⁇ (capacity) can be fixed at arbitrary values. Therefore, it is possible to realize control for fixing the inclination when the hydraulic pressure P increases or decreases according to the change in the engine speed Ne.
  • the control valve 7 has a solenoid portion 9 that can generate an electromagnetic force fm that urges the spool 81. Therefore, the solenoid 81 can move the spool 81 to an arbitrary position.
  • the spool 81 is integrally connected to the plunger of the solenoid unit 9. Therefore, even if a force by hydraulic pressure acts on the spool 81 from one side or the other side in the axial direction, the spool 81 can be prevented from moving.
  • p, ⁇ , and P are less likely to be affected by disturbance, so that the control performance can be improved. Note that the control of p, ⁇ , and P is performed by opening and closing the port of the control valve 7, and thus is not affected by the spring constant of the spring 25 of the cam ring 24.
  • the control valve 7 is on the second feedback passage 432, and the hydraulic oil in the second control chamber 292 is discharged to the oil pan 400 while the discharge port 203 and the second control chamber 292 are in communication with each other by the movement of the spool 81.
  • the cross-sectional area Sd of the flow path is changed.
  • the amount of hydraulic oil discharged from the space 807 (second control chamber 292) is changed (adjusted) by changing the flow path cross-sectional area Sd.
  • the eccentric amount ⁇ (capacity) and the main gallery hydraulic pressure P are controlled by changing (controlling) the control hydraulic pressure p.
  • the control valve 7 reduces the cross-sectional area Si of the flow path for introducing the hydraulic oil from the discharge port 203 to the second control chamber 292 by the movement of the spool 81 toward the other side in the axial direction (in the first direction). 2 Increase the cross-sectional area Sd of the flow path for discharging the hydraulic oil in the control chamber 292 to the oil pan 400. Therefore, since the discharge port 203 and the space 807 (second control chamber 292) are in communication at the same time as increasing Sd, the amount of discharge from the second control chamber 292 with respect to the movement of the spool 81 is moderately increased. Become. Therefore, the decrease gradient of P with respect to the change (increase) of D can be made gentle.
  • the orifice diameter of the supply port 803 is reduced by reducing Si. That is, the supply port 803 functions as a variable orifice. Therefore, the hydraulic pressure in the space 807 (that is, the control hydraulic pressure p) can be sufficiently reduced with respect to the hydraulic pressure P in the supply passage 433 without greatly increasing the discharge amount from the space 807. Therefore, an increase in the discharge amount can be suppressed, and a decrease in the efficiency of the pump 2 can be suppressed. Further, when the discharge amount from the second control chamber 292 is increased, the amount of hydraulic oil that can be introduced into the second control chamber 292 is decreased by decreasing Si. Therefore, since it is possible to sufficiently reduce the control oil pressure p when it is desired to lower it, it is possible to widen the range (lower limit) of the control oil pressure p. Therefore, the control performance is improved.
  • the control valve 7 decreases the channel cross-sectional area Sd while increasing the channel cross-sectional area Si by the movement of the spool 81 in one axial direction (in the second direction). Therefore, since the discharge port 203 and the space 807 (second control chamber 292) are communicated with each other while reducing Sd, the amount of discharge from the second control chamber 292 with respect to the movement of the spool 81 is moderately reduced. Become. Therefore, the rising gradient of P with respect to the change (decrease) of D can be made gentle. Further, when the discharge amount from the second control chamber 292 is decreased, the amount of hydraulic oil that can be introduced into the second control chamber 292 is increased by increasing Si.
  • the control mechanism 3 decreases the amount of hydraulic fluid discharged from the second control chamber 292 when the amount of hydraulic fluid discharged from the discharge port 203 and introduced into the second control chamber 292 increases.
  • the amount of hydraulic oil discharged from the discharge port 203 and introduced into the second control chamber 292 decreases, the amount of hydraulic oil discharged from the second control chamber 292 is increased. Therefore, the control hydraulic pressure p can be changed (controlled) in a wide range from low pressure to high pressure. Further, the operation of the cam ring 24 is stabilized, and the discharge pressure P is stabilized.
  • the cylinder 80 of the control valve 7 is connected to the supply port 803 as the first port communicating with the discharge port 203, the communication port 804 as the second port communicating with the second control chamber 292, and the oil pan 400.
  • a discharge port 805 as a third port that communicates, and these ports 803 to 805 open to the inner periphery.
  • the discharge port 805 only needs to communicate with the low pressure portion, and is not limited to the oil pan 400 (atmospheric pressure), and may be communicated with, for example, the suction port 201 side (where negative suction pressure is generated).
  • the spool 81 of the control valve 7 is movable inside the cylinder 80, and the first land portion 811 as the first large diameter portion that can change the area of the opening of the supply port 803, and the discharge port 805 described above. It has the 2nd land part 812 as a 2nd large diameter part which can change the area of opening. With such a simple configuration of the spool valve, the valve unit 8 can control the control oil pressure p.
  • the ports 803 to 805 can be simultaneously opened at least partially within the range (space 807) between the first land portion 811 and the second land portion 812 on the inner periphery of the spool 81.
  • the first land portion 811 and the second land portion 812 are arranged. Therefore, the supply port 803 (discharge port 203) and the communication port 804 (second control chamber 292) are communicated with each other via the space 807, and at the same time, the communication port 804 (second control chamber 292) and the discharge port 805 (oil pan) 400) can communicate.
  • the movement of the spool 81 causes the supply port 803 (discharge port 203) and the communication port 804 (second control chamber 292) to communicate with each other, while the opening area of the discharge port 805 in the space 807 (operation in the second control chamber 292).
  • the cross-sectional area (Sd) of the flow path for discharging oil to the oil pan 400 can be changed.
  • the first land portion 811 is connected to the supply port 803 and the communication port 804.
  • the cross-sectional area of the flow path between can be changed.
  • the second land portion 812 can change the cross-sectional area of the flow path between the communication port 804 and the discharge port 805.
  • the first land portion 811 can change the area of the opening of the supply port 803.
  • the second land portion 812 can change the area of the opening of the discharge port 805.
  • the opening area of the supply port 803 in the space 807 increases while Sd Decrease. Due to the movement of the spool 81 in the other axial direction, Sd increases while Si decreases.
  • the spool 81 has a first land portion 811, a second land portion 812, and a connection portion 813.
  • the connection portion 813 connects the first land portion 811 and the second land portion 812.
  • the first land portion 811 is disposed on the supply port 803 side and is urged toward the one axial side by the solenoid portion 9.
  • the second land portion 812 is disposed on the discharge port 805 side and is urged toward the other side in the axial direction by the spring 82.
  • the spring 82 and the solenoid portion 9 are different in the direction in which the spool 81 is urged, and fm and fs act in opposite directions. Therefore, the controllability of the spool 81 by the solenoid unit 9 is good.
  • the spring 82 functions as a return spring for the spool 81 (plunger of the solenoid unit 9). Even when the solenoid portion 9 fails, the eccentric amount ⁇ can be maximized by urging the spool 81 by the spring 82 toward the other side in the axial direction (toward the initial position). Therefore, the discharge pressure P can be increased with a maximum gradient in accordance with the increase in the engine speed Ne.
  • the area of the first region 246 facing the first control chamber 291 and the area of the second region 246 facing the second control chamber 292 on the cam ring outer peripheral surface 245 may be equal, or the area of the second region 247 May be smaller than the area of the first region 246.
  • the area (pressure receiving area) of the second region 247 is larger than the area (pressure receiving area) of the first region 246. Therefore, a stable hydraulic pressure P can be supplied while the pump 2 is operating at high speed. That is, when the engine speed Ne (pump speed) increases, bubbles may be generated in the hydraulic oil.
  • the volume of the first control chamber 291 increases when the cam ring 24 moves in a direction against the urging force Fs of the spring 25. That is, Fp1 acts in the opposite direction to Fs.
  • the volume of the second control chamber 292 increases when the cam ring 24 moves in the same direction as Fs. That is, Fp2 acts in the same direction as Fs and assists Fs.
  • the operation of the cam ring 24 is determined by the magnitude relationship between Fp1 and (Fp2 + Fs). Therefore, since the cam ring 24 is operated in the direction in which the amount of eccentricity ⁇ increases, Fs can be small. The load of the spring 25 can be reduced. Therefore, Fp1 can be small in order to operate the cam ring 24 in the direction in which ⁇ decreases.
  • the discharge pressure when the cam ring 24 operates in the direction in which ⁇ decreases can be reduced.
  • low-pressure hydraulic oil can be discharged.
  • the cam ring 24 can swing around a fulcrum inside the pump storage chamber 200. Therefore, the range in which the cam ring 24 operates can be made compact, and the pump 2 can be downsized.
  • the pressure in the second control chamber 292 When the pressure in the second control chamber 292 is lowered, the difference from the pressure in the discharge port 204 is increased. For this reason, there is a risk that the amount of hydraulic oil leaking through the gap between the axial side surface of the cam ring 24 and the bottom surface of the pump storage chamber 200 may increase.
  • the radial width in the second region 247 of the cam ring 24 is larger than the radial width in the first region 246. Therefore, since the sealing performance is improved on the second control chamber 292 side than on the first control chamber 291 side, the leakage can be suppressed.
  • the discharge pressure is always introduced into the first control chamber 291 and the difference from the pressure of the discharge port 204 is small. Therefore, only the second control chamber 292 side improves the sealing performance (increases the radial width), thereby suppressing unnecessary weight increase.
  • the cylinder 80C has a bottom portion 802 on one side in the axial direction and opens on the other side in the axial direction.
  • the opening of the communication port 804C is between the opening of the supply port 803 and the opening of the discharge port 805.
  • the dimension of the opening of the communication port 804C is larger than the dimensions of the openings of the supply port 803 and the discharge port 805.
  • the spool 81C includes a first land portion 814, a second land portion 814, and a connection portion 813.
  • the dimension in the axial direction of the first land portion 814 is smaller than the dimension of the opening of the communication port 804C.
  • the first land portion 814 is disposed in a region overlapping with the communication port 804C and in the vicinity thereof.
  • the discharge port 805 is always open, and the communication port 804C can be opened.
  • the supply port 803 is always open, and the communication port 804C is open in the initial state.
  • One end of the spring 82C is fitted to the outer peripheral side of the convex portion protruding from the first land portion 814 of the spool 81C, and one end of the spring 82C is in contact with one end face of the first land portion 814.
  • the other end of the spring 82C contacts the bottom 802.
  • the spring force fs of the spring 82C biases the first land portion 814 (spool 81C) toward the other side in the axial direction.
  • the solenoid unit 9 is coupled to the other axial side of the valve unit 8 and closes the opening on the other axial side of the cylinder 80C.
  • the second land portion 815 of the spool 81C is integrally coupled to the plunger.
  • the electromagnetic force fm of the solenoid portion 9 biases the second land portion 815 (the spool 81C and the first land portion 814) to one side in the axial direction. Since other configurations are the same as those of the first embodiment, the same reference numerals are given to corresponding components and description thereof is omitted.
  • the first land portion 814 can change the opening area of the communication port 804C.
  • the communication port 804C opens at least partially in the space 808C.
  • the opening of the supply port 803 communicates with the opening of the communication port 804C through the space 808C.
  • the space 808C serves as a hydraulic oil passage.
  • the opening of the discharge port 805 communicates with the opening of the communication port 804C through the space 807C.
  • the space 807C serves as a hydraulic oil passage.
  • the communication port 804C opens on both axial sides of the first land portion 814, and the communication port 804C is partially in both the space 807C and the space 808C. Open.
  • the first land portion 814 communicates with the area Si of the communication port 804C communicating with the opening of the supply port 803 and the opening of the discharge port 805 by moving within the axial range of the communication port 804C.
  • the area Sd of the opening of the communication port 804C is changed.
  • the first land portion 814 closes the opening of the communication port 804C in the space 807C and opens the communication port 804C in the space 808C. Is the maximum Smax.
  • the first state similar to that in FIG. 4 is realized, and the maximum amount of eccentricity ⁇ is maintained.
  • the first land portion 814 opens the communication port 804C in the space 808C and opens the communication port 804C in the space 807C.
  • a second state similar to FIG. 5 is realized.
  • the opening area Si is smaller than Smax.
  • the hydraulic oil can be discharged from the communication path 434 (second control chamber 292) through the space 807C. Further, since the hydraulic oil can be discharged from the communication port 804C through the space 807C, a flow of hydraulic oil from the supply passage 433 (space 808C) to the space 807C through the communication port 804C is generated. In this flow, the communication port 804C with the reduced opening area Si functions as an orifice, and the hydraulic pressure in the communication passage 434 (communication port 804C) is lower than the hydraulic pressure P in the supply passage 43 (space 808C). Therefore, the control hydraulic pressure p introduced into the second control chamber 292 decreases, and the eccentric amount ⁇ decreases. As shown in FIG.
  • the first land portion 814 reduces the opening area Sd of the communication port 804C in the space 807C. While increasing the size, the opening area Si of the communication port 804C in the space 808C is decreased.
  • a third state similar to FIG. 6 is realized. As Sd increases, the amount of hydraulic oil discharged from the space 807C through the discharge passage 435 increases. Therefore, the amount of hydraulic oil that can be discharged from the communication path 434 (second control chamber 292) via the space 807C increases.
  • the decrease in Si reduces the orifice diameter of the communication port 804C, and the hydraulic pressure in the communication passage 434 becomes even lower than the hydraulic pressure P in the supply passage 433. Therefore, the control oil pressure p further decreases, and the eccentricity ⁇ further decreases.
  • fs acts on the spool 81C in the right direction and fm acts on the left direction.
  • fm becomes larger than fs
  • the spool 81C moves to one side in the axial direction, and realizes a state transition from the first state side to the third state side.
  • fm becomes smaller than fs
  • the spool 81C moves to the other side in the axial direction, and realizes a state transition from the third state side to the first state side.
  • the amount of hydraulic oil discharged from the communication port 804C (second control chamber 292) is changed (adjusted) by changing the flow path cross-sectional area Sd.
  • the control hydraulic pressure p is changed (controlled).
  • the discharge port 203 and the communication port 804C (second control chamber 292) are connected at the same time when Sd is changed, the amount of hydraulic oil discharged from the second control chamber 292 relative to the movement of the spool 81C is reduced. Change will be gradual.
  • the control valve 7 moves in the second control chamber 292 while reducing the cross-sectional area Si of the flow path for introducing the hydraulic oil from the discharge port 203 to the second control chamber 292 by the movement of the spool 81C in one axial direction.
  • the cross-sectional area Sd of the flow path for discharging the hydraulic oil to the oil pan 400 is increased.
  • the movement of the spool 81C to the other side in the axial direction decreases the flow path cross-sectional area Sd while increasing the flow path cross-sectional area Si.
  • the opening of the communication port 804C (second port) is between the opening of the supply port 803 (first port) and the opening of the discharge port 805 (third port).
  • the spool 81C has a first land portion 814 that is biased to one side by the solenoid portion 9 and biased to the other side by the spring 82C.
  • the first land portion 814 changes the area Si of the opening of the communication port 804C communicating with the opening of the supply port 803 and the area Sd of the opening of the communication port 804C communicating with the opening of the discharge port 805. Therefore, the valve portion 8 can control the control oil pressure p with a simpler configuration of the spool valve.
  • Other functions and effects are the same as those of the first embodiment. Note that the configuration of the present embodiment can be applied to embodiments other than the first embodiment.
  • the movement of the cam ring 24A is a slide type.
  • the pump 2 does not have the first seal member 261, the second seal member 262, and the pin 27 of the first embodiment.
  • the inner peripheral surface of the pump housing chamber 200A of the housing body 20A has flat surfaces 205 to 207. These planes 205 to 207 extend parallel to the axis 22AP of the rotor 22A.
  • the planes 205 and 206 are parallel to each other, and the plane 207 extends in a direction perpendicular to the planes 205 and 206.
  • the outer periphery of the cam ring 24A has four protrusions 246 to 249 that protrude radially outward.
  • the first protrusion 246 and the second protrusion 247 are on opposite sides of the cam ring inner peripheral surface 240A with the shaft center 24AP interposed therebetween, and the third protrusion 248 and the fourth protrusion 249 are on the opposite side of the shaft center 24AP.
  • the first protrusion 246, the second protrusion 247, and the third protrusion 248 have a plane, and these planes extend in parallel with the axis 24AP.
  • the plane of the first protrusion 247 and the plane of the second protrusion 247 are parallel to each other.
  • the distance between the two planes is slightly shorter than the distance between the planes 205 and 206 of the housing body 20A.
  • the plane of the first protrusion 246 and the plane of the second protrusion 247 face the planes 205 and 206, respectively.
  • the plane of the third protrusion 248 extends in a direction orthogonal to the plane of the first protrusion 247 (second protrusion 247) and faces the plane 207 of the inner peripheral surface of the pump housing chamber 200A.
  • One end of a spring 25A is installed on the fourth protrusion 249.
  • the first control chamber 291A is a space between the first protrusion 246 on the cam ring outer peripheral surface 245A and the second protrusion 247 via the third protrusion 248 and the inner peripheral surface of the pump storage chamber 200A.
  • the second control chamber 292A is a space between the first protrusion 246, the fourth protrusion 249, and the second protrusion 247 on the cam ring outer peripheral surface 245A, and the inner peripheral surface of the pump housing chamber 200A.
  • the spring accommodating chamber 293A has a bottomed cylindrical shape integrated with the second control chamber 292A, and the other end side of the spring 25A is installed.
  • the first control chamber 291A Since the gap between the plane of the first projection 246 and the plane 205 of the pump storage chamber 200A and the gap between the plane of the second projection 247 and the plane 206 of the pump storage chamber 200A are small, the first control chamber 291A. And the second control chamber 292A (spring accommodating chamber 293A) are sealed.
  • the valve unit 8 has a retainer 83 and a stopper 84 as shown in FIG.
  • the solenoid unit 9 has a rod 91.
  • the rod 91 is coupled to the plunger.
  • the cylinder 80A has an inner peripheral surface 800 that is cylindrical, and both axial ends open.
  • the retainer 83 has a bottomed cylindrical shape, and has a hole 830 in the bottom portion 831.
  • the retainer 83 is at the other end of the cylinder 80A in the axial direction.
  • the cylindrical portion 832 of the retainer 83 is fitted to the inner periphery of the cylinder 80A.
  • the stopper 84 has an annular shape and has a hole 840 at the center.
  • the stopper 84 is at the other end in the axial direction of the cylinder 80A, and partially closes the opening of the cylinder 80A.
  • the surface on the one axial side of the stopper 84 faces the bottom portion 831 of the retainer 83.
  • One end of the rod 91 projects to the inner peripheral side of the cylinder 80A, and is coupled to the other axial end of the spool 81A (first land portion 811A).
  • the rod 91 functions as a member for the solenoid to urge the spool 81A in the axial direction.
  • the rod 91 is integral with the spool 81A (not separated).
  • a space 808A is defined between the second land portion 812A and the retainer 83 inside the cylinder 80A.
  • One end of the spring 82A is fitted to the inner peripheral side of the retainer 83, and one end of the spring 82A is in contact with the bottom 831 of the retainer 83.
  • the other end of the spring 82A is in contact with the end surface on one axial side of the spool 81A (second land portion 812A). Since other configurations are the same as those of the first embodiment, the same reference numerals are given to corresponding components and description thereof is omitted.
  • the rotor 22A rotates in the clockwise direction in FIG.
  • the cam ring 24A can be slid along the planes 205 and 206 (moved linearly in the radial direction of the rotor 22) inside the pump housing chamber 200A.
  • the planes 205 and 206 function as the above-described movement guides (guides) inside the pump storage chamber 200A.
  • the difference (eccentricity ⁇ ) between the axis (rotation center) 22AP of the rotor 22A and the axis (center) 24AP of the cam ring inner peripheral surface 240A changes.
  • the volumes of the first control chamber 291A and the second control chamber 292A can change when the cam ring 24A moves.
  • the position of the cam ring 24A (the amount of eccentricity ⁇ ) is determined by the force Fp1 due to the pressure in the first control chamber 291A, the force Fp2 due to the pressure in the second control chamber 292A, and the biasing force Fs of the spring 25A.
  • Fp1 becomes larger than (Fp2 + Fs)
  • the cam ring 24A moves to the side where ⁇ (capacity) becomes smaller.
  • Fp1 becomes smaller than (Fp2 + Fs) the cam ring 24A moves to the side where ⁇ (capacity) becomes larger. If fm is equal to or less than fs, as shown in FIG.
  • the spool 81A is in the initial position, and the supply port 803A communicates with the communication port 804A.
  • the amount of eccentricity ⁇ is maximized by the hydraulic oil (control hydraulic pressure pmax) introduced into the second control chamber 292A. If fm is larger than fs, as in FIGS. 5 and 6, the spool 81 moves from the initial position to the other side in the axial direction, and the discharge port 805A communicates with the communication port 804A (along with the supply port 803A). Since hydraulic oil is discharged from the second control chamber 292A, ⁇ decreases.
  • the pump 2 has a first protrusion 241B and a second protrusion with respect to a straight line passing through the axis of the pin 27B and the center 24BP of the cam ring inner peripheral surface 240B when viewed from the axial direction of the cam ring 24B.
  • 242B is on the same side.
  • the first protrusion 241B is located between the second protrusion 242B and the third protrusion 243B (pin 27B).
  • the first protrusion 241B and the second protrusion 242B are on the opposite side of the fourth protrusion 244B across the straight line.
  • the first control chamber 291B is a space between the first protrusion 241B (first seal member 261B) to the third protrusion 243B (pin 27B) on the cam ring outer peripheral surface 245B and the inner peripheral surface of the pump storage chamber 200B. It is.
  • a discharge port 204B (a part thereof) and a discharge port 203B are opened on the bottom surface of the pump storage chamber 200B facing the first control chamber 291B.
  • the second control chamber 292B is formed between the first protrusion 241B (first seal member 261B) to the second protrusion 242B (second seal member 262B) on the cam ring outer peripheral surface 245B and the inner peripheral surface of the pump housing chamber 200B. It is a space between.
  • a second region 247B between the first seal member 261B and the second seal member 262B on the cam ring outer peripheral surface 245B faces the second control chamber 292.
  • the second control chamber 292B is sealed by the first seal member 261B and the second seal member 262B.
  • the other end of the communication path 434 opens on the bottom surface of the pump storage chamber 200B facing the second control chamber 292B.
  • the spring accommodating chamber 293B is provided between the third protrusion 243B (pin 27B) on the cam ring outer peripheral surface 245B and the second protrusion 242B (second seal member 262B) via the fourth protrusion 244B, and in the pump accommodating chamber 200B. This is the space between the surrounding surface.
  • a suction port 202B (a part thereof) and a suction port 201B are opened on the bottom surface of the pump storage chamber 200B facing the spring storage chamber 293B.
  • the discharge port 204B communicates with both the working chamber 28B and the first control chamber 291B and functions as the first feedback passage 431.
  • the end of one side in the axial direction of the cylinder 80B is not opened but is closed.
  • One end of the spring 82 abuts on the end of the cylinder 80B.
  • the discharge port 805B, the communication port 804B, the supply port 803B, and the second discharge port 806 are arranged in this order from one axial side to the other side of the cylinder 80B.
  • the discharge port 805B opens in an initial state.
  • the communication port 804B is always open, and the supply port 803B can be opened.
  • a space 808 is defined between the second land portion 812B and the end portion on the other axial side of the cylinder 80B.
  • the supply port 803B opens in the initial state, and the second discharge port 806 always opens.
  • Second discharge port 806 communicates with oil pan 400 via discharge passage 435. Since other configurations are the same as those of the first embodiment, the corresponding components are denoted by the same reference numerals and description thereof is omitted.
  • the rotor 22B rotates in the clockwise direction in FIG.
  • the cam ring 24B is urged to one side in the rotational direction around the pin 27B (the side where the amount of increase / decrease in the volume of each of the plurality of working chambers 28B increases and the eccentricity ⁇ increases) by the spring force Fs of the spring 25. Is done.
  • the cam ring 24B has a pin 27B formed by a force Fp1 due to the hydraulic pressure P in the first control chamber 291B received by the first region 246B of the outer peripheral surface 245B and a force Fp2 due to the hydraulic pressure p in the second control chamber 292B received by the second region 247B.
  • the first land portion 811B of the spool 81B changes the opening area of the discharge port 805B
  • the second land portion 812B changes the opening area of the supply port 803B. If fm is less than fs (set load of the spring 82B), as shown in FIG. 22, the spool 81B is in the initial position, and the second land portion 812 closes the opening of the supply port 803B in the space 807B.
  • the first land portion 811B opens the discharge port 805B into the space 807B.
  • the discharge port 805B communicates with the communication port 804B. Since the hydraulic oil is discharged from the second control chamber 292B, Fp2 becomes small.
  • the communication passage 434 and the supply passage 433 are connected, and hydraulic oil discharged from the discharge port 203B is introduced into the second control chamber 292B.
  • Fp2 is increased by the hydraulic pressure p introduced into the second control chamber 292B. If (Fp1 + Fp2) becomes larger than Fs, ⁇ decreases.
  • the present invention can be applied to the pump 2 having a configuration that acts in the direction of reducing the size of the pump 2.
  • the characteristic of the main gallery hydraulic pressure P with respect to the engine speed Ne can be easily approximated to a desired characteristic. Moreover, controllability can be improved. Other functions and effects are the same as those of the first embodiment. Note that the configuration of the present embodiment can be applied to embodiments other than the first embodiment.
  • the basic configuration is the same as that of the first embodiment (FIG. 2), but it has only the first control chamber 291 and does not have the second control chamber 292. Specifically, the second protrusion 242 and the second seal member 262 are not provided.
  • the basic configuration is the same as that of the fourth embodiment (FIG. 21).
  • the control passage 43 the basic configuration is the same as that of the first embodiment (FIG. 1), but only the first feedback passage 431 branched from the discharge passage 41 is provided, and the second feedback passage 432 is not provided.
  • the first feedback passage 431 includes a supply passage 433, a communication passage 434, and a discharge passage 435.
  • One end side of the supply passage 433 branches from the discharge passage 41, and the other end of the supply passage 433 is connected to the supply port 803 ⁇ / b> B of the control valve 7.
  • One end of the communication path 434 is connected to the communication port 804 B of the control valve 7, and the other end of the communication path 434 is connected to the first control chamber 291.
  • One end of the discharge passage 435 is connected to the discharge port 805 of the control valve 7, and the other end of the discharge passage 435 is connected to the oil pan 400.
  • the cam ring 24 receives the pressure (control oil pressure) p of the hydraulic oil in the first control chamber 291.
  • the first region 246 of the cam ring outer peripheral surface 245 functions as a pressure receiving surface that receives the control hydraulic pressure p. Since other configurations are the same as those of the first embodiment, the corresponding components are denoted by the same reference numerals and description thereof is omitted.
  • the cam ring 24 is urged to one side in the rotational direction around the pin 27 (the side where the increase / decrease amount of each of the plurality of working chambers 28 increases and the eccentricity ⁇ increases) by the spring force Fs of the spring 25. Is done.
  • the cam ring 24 is urged to the other side in the rotational direction around the pin 27 (the side on which ⁇ decreases) by increasing or decreasing the volume of each of the plurality of working chambers 28 by the force Fp1 caused by the control hydraulic pressure p. .
  • Fp1 becomes larger than Fs
  • the cam ring 24 swings to the other side in the rotational direction, so ⁇ (capacity) becomes small.
  • the present invention can also be applied to the pump 2 having a configuration in which the control mechanism 3 (control valve 7) controls the pressure in the first control chamber 291.
  • the characteristic of the main gallery hydraulic pressure P with respect to the engine speed Ne can be easily approximated to a desired characteristic. Moreover, controllability can be improved.
  • Other functions and effects are the same as those of the first embodiment. Note that the configuration of the present embodiment can be applied to embodiments other than the first embodiment.
  • the pump may be a variable displacement type, and a member other than the vane may be used as the pump structure.
  • a member other than the cam ring may be used as the movable member that changes the amount of increase / decrease in the volume of each of the plurality of working chambers during rotation of the pump structure.
  • the pump may be a trochoid gear pump.
  • the outer rotor which is a circumscribed gear, is arranged so as to be movable eccentrically, and a control chamber and a spring are arranged on the outer peripheral side thereof, so that a variable displacement type can be obtained (the outer rotor corresponds to a movable member).
  • the calculation unit and the reception unit of the ECU are realized by software in the microcomputer in the embodiment, but may be realized by an electronic circuit.
  • the calculation means not only mathematical calculation but also general processing on software.
  • the receiving unit may be a microcomputer interface or software in the microcomputer.
  • the control signal may relate to the current value or may relate to the thrust of the solenoid.
  • the method of controlling the supply current to the solenoid is not limited to PWM control.
  • a current value corresponding to the engine speed may be set in advance using a map.
  • the characteristic information for changing the control signal of the solenoid in accordance with the change in the engine speed may be realized by calculation instead of being realized by the map in the microcomputer.
  • variable displacement pump in one embodiment thereof, A housing having a pump housing chamber therein; A pump structure that is disposed in the pump housing chamber, the volumes of the plurality of working chambers can be changed with rotation, and discharges the working oil guided from the suction portion by being driven to rotate from the discharge portion; A movable member that is disposed in the pump housing chamber and separates the plurality of working chambers by housing the pump component, wherein the center of the inner periphery of the movable member is relative to the rotation center of the pump component.
  • a movable member that changes the amount of increase / decrease in the volume of each of the plurality of working chambers during rotation of the pump structure by moving so that the amount of eccentricity changes.
  • a first biasing member that is disposed in the pump housing chamber in a state in which a set load is applied, and biases the movable member in a direction in which the increase / decrease amount of each volume of the plurality of working chambers increases;
  • a first control chamber that is disposed between the pump housing chamber and the movable member and into which hydraulic oil discharged from the discharge portion is introduced, wherein the movable member is subjected to an urging force of the first urging member.
  • the cross-sectional area of the flow path for discharging the hydraulic oil in the second control chamber to the low-pressure portion is changed while the discharge portion and the second control chamber are in communication with each other by being moved on the passage.
  • a control valve is
  • the control valve reduces hydraulic oil in the second control chamber while reducing a cross-sectional area of a flow path for introducing hydraulic oil from the discharge portion to the second control chamber by movement of the valve body in the first direction.
  • the cross-sectional area of the flow path discharged to the low pressure part is increased.
  • the control valve increases hydraulic oil in the second control chamber while increasing a cross-sectional area of a flow path for introducing hydraulic oil from the discharge portion to the second control chamber by movement of the valve body in the second direction.
  • the cross-sectional area of the flow path discharged to the low pressure part is reduced.
  • the control valve can continuously change the position of the valve body.
  • the control valve can stop the valve body at an arbitrary position.
  • the control valve includes a solenoid portion that can generate an electromagnetic force that urges the valve body.
  • the solenoid unit can move the valve body to an arbitrary position according to a control signal.
  • the valve body is integrally connected to the plunger of the solenoid unit.
  • the control valve is a hollow member that accommodates the valve body, and has a first port communicating with the discharge unit, a second port communicating with the second control chamber, and a third port communicating with the low pressure unit.
  • the first port, the second port, and the third port include a hollow member that opens to the inner periphery.
  • the control valve includes a solenoid unit capable of generating an electromagnetic force that urges the valve body,
  • the valve body is A first land portion disposed on the first port side and biased to one side by the solenoid portion; A second land portion disposed on the third port side and biased to the other side by a second biasing member; A connecting portion connecting the first land portion and the second land portion.
  • the first land portion changes the area of the opening of the first port
  • the second land portion changes the area of the opening of the third port.
  • the control valve includes a solenoid unit capable of generating an electromagnetic force that urges the valve body,
  • the opening of the second port is disposed between the opening of the first port and the opening of the third port;
  • the valve body includes a land portion biased to one side by the solenoid portion and biased to the other side by a second biasing member, The land portion changes an area of the opening of the second port communicating with the opening of the first port and an area of the opening of the second port communicating with the opening of the third port. .
  • the volume of the second control chamber increases when the movable member moves in the same direction as the urging force of the first urging member.
  • the movable member has a first pressure receiving surface facing the first control chamber and a second pressure receiving surface facing the second control chamber and having a larger pressure receiving area than the first pressure receiving surface.
  • the movable member can swing around a fulcrum in the pump housing chamber.
  • the movable member is capable of translational movement in the pump housing chamber.
  • the volume of the second control chamber increases when the movable member moves in a direction against the urging force of the first urging member.
  • variable displacement pump is, in one embodiment thereof, A housing having a pump housing chamber therein; A pump structure that is disposed in the pump housing chamber, the volumes of the plurality of working chambers can be changed with rotation, and discharges the working oil guided from the suction portion by being driven to rotate from the discharge portion; A movable member that is disposed in the pump housing chamber and separates the plurality of working chambers by housing the pump component, wherein the center of the inner periphery of the movable member is relative to the rotation center of the pump component. A movable member that changes the amount of increase / decrease in the volume of each of the plurality of working chambers during rotation of the pump structure by moving so that the amount of eccentricity changes.
  • a first control chamber disposed between the pump housing chamber and the movable member, to which hydraulic oil discharged from the discharge portion is guided, wherein the first control chamber is moved when the movable member moves to one side;
  • a first control chamber that increases in volume;
  • a second control chamber that is disposed between the pump housing chamber and the movable member and into which the hydraulic oil discharged from the discharge section is introduced through a passage; and when the movable member moves, A second control room in which the volume of the two control rooms is variable;
  • a hollow cylindrical member that opens to the inner periphery;
  • a control valve comprising a spool movable inside the tubular member, and a solenoid part for moving the spool; Is provided.
  • the spool includes a first large diameter portion capable of changing an area of the opening of the first port, and a second large diameter portion capable of changing an area of the opening of the third port.
  • the first large-diameter portion and the second large-diameter portion are within the range sandwiched between the first large-diameter portion and the second large-diameter portion of the inner periphery of the cylindrical member.
  • the second port and the third port are arranged so that they can be opened at least partially simultaneously.
  • a hydraulic oil supply system for an internal combustion engine in one embodiment thereof, The movable member with respect to the center of rotation of the pump structure is moved by guiding the hydraulic oil discharged from the pump structure to a control chamber around the movable member that houses the pump structure.
  • a variable displacement pump that can change the pressure of hydraulic oil discharged from the pump component to the internal combustion engine, A pressure measuring unit for measuring the pressure of the hydraulic oil discharged from the pump component; A rotational speed measurement unit for measuring the rotational speed of the internal combustion engine; The pressure difference between the pressure measured by the pressure measurement unit and the hydraulic oil pressure required for the internal combustion engine at the rotation number measured by the rotation number measurement unit is calculated, and the rotation number is set in advance.
  • the pressure difference is greater than a preset pressure difference, while introducing hydraulic oil into the control chamber until the pressure difference becomes equal to or less than the preset pressure difference, the control chamber And a control unit that changes the amount of hydraulic fluid discharged from the engine to the low-pressure unit.
  • control unit does not discharge hydraulic oil from the control chamber to the low-pressure unit when the rotation number is less than the preset rotation number.
  • control unit has the pressure difference larger than the set pressure difference when the rotation speed is equal to or higher than the preset rotation speed and the pressure difference is equal to or less than the set pressure difference. Until then, the amount of hydraulic oil discharged from the control chamber to the low pressure part is controlled to a predetermined amount.
  • 1 hydraulic oil supply system 2 variable displacement pump, 20 housing body, 200 pump storage chamber, 201 suction port (suction part), 203 discharge port (discharge part), 22 rotor (pump structure), 23 vane (pump structure) ), 24 cam ring (movable member), 25 spring (first urging member), 28 working chamber, 291 first control chamber, 292 second control chamber, 3 control mechanism, 4 passage, 400 oil pan (low pressure part), 6 Engine control unit (control part), 7 control valve, 8 valve part, 81 spool (valve element), 9 solenoid part

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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)

Abstract

L'invention a pour but de pourvoir à une pompe à débit variable permettant d'améliorer la commandabilité. À cet effet, la pompe à débit variable est munie d'une chambre de commande et d'un clapet de commande. La chambre de commande est disposée entre une chambre de logement de pompe et un élément mobile, et le volume de la chambre de commande peut être modifié lors du déplacement de l'élément mobile. Un fluide hydraulique évacué hors d'une partie d'évacuation est introduit dans la chambre de commande. Le clapet de commande est disposé sur un circuit et, en raison du déplacement d'un corps de clapet, il modifie la surface de section transversale d'un circuit d'écoulement servant à évacuer le fluide hydraulique à l'intérieur de la chambre de commande vers une partie à basse pression, permettant en même temps la communication entre la partie d'évacuation et la chambre de commande.
PCT/JP2017/028361 2016-09-16 2017-08-04 Pompe à débit variable et système d'alimentation en fluide hydraulique pour moteur à combustion interne Ceased WO2018051673A1 (fr)

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CN201780056266.XA CN109690081A (zh) 2016-09-16 2017-08-04 可变容量泵以及内燃机的工作油供给系统
US16/333,211 US20190219053A1 (en) 2016-09-16 2017-08-04 Variable capacity pump and working oil supply system for internal combustion engine

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JP2016-181736 2016-09-16
JP2016181736A JP2018044523A (ja) 2016-09-16 2016-09-16 可変容量ポンプ及び内燃機関の作動油供給システム

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US11486277B2 (en) * 2021-02-26 2022-11-01 Deere & Company Work vehicle engine with split-circuit lubrication system
US12448967B2 (en) 2021-09-08 2025-10-21 Hitachi Astemo, Ltd. Variable displacement oil pump
CN114151331A (zh) * 2021-12-31 2022-03-08 富奥汽车零部件股份有限公司 供油泵及缓速器系统

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS51128009A (en) * 1975-04-16 1976-11-08 Rexroth Gmbh G L Adjustable vane pumps
JPH0276904A (ja) * 1988-06-29 1990-03-16 Hitachi Constr Mach Co Ltd 油圧駆動装置及びその制御方法
US20080038117A1 (en) * 2003-09-12 2008-02-14 Giacomo Armenio Pumping System Employing a Variable-Displacement Vane Pump
WO2012149929A2 (fr) * 2011-05-05 2012-11-08 Ixetic Bad Homburg Gmbh Pompe à cylindrée variable
JP2014178028A (ja) * 2013-03-14 2014-09-25 Husco Automotive Holdings Llc 流体ポンプアウトレット圧調整のためのシステム及び方法

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102012210899A1 (de) * 2012-06-26 2014-01-02 Mahle International Gmbh Hydraulikfördereinrichtung und Hydrauliksystem
JP2014066178A (ja) * 2012-09-26 2014-04-17 Hitachi Automotive Systems Ltd 可変容量型ポンプ
EP2917585B1 (fr) * 2012-11-08 2018-09-26 Pierburg Pump Technology GmbH Pompe à lubrifiant à déplacement variable
JP2016104967A (ja) * 2014-12-01 2016-06-09 日立オートモティブシステムズ株式会社 可変容量形オイルポンプ
JP6410591B2 (ja) * 2014-12-18 2018-10-24 日立オートモティブシステムズ株式会社 可変容量形オイルポンプ
JP2016118112A (ja) * 2014-12-19 2016-06-30 日立オートモティブシステムズステアリング株式会社 ポンプ装置

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS51128009A (en) * 1975-04-16 1976-11-08 Rexroth Gmbh G L Adjustable vane pumps
JPH0276904A (ja) * 1988-06-29 1990-03-16 Hitachi Constr Mach Co Ltd 油圧駆動装置及びその制御方法
US20080038117A1 (en) * 2003-09-12 2008-02-14 Giacomo Armenio Pumping System Employing a Variable-Displacement Vane Pump
WO2012149929A2 (fr) * 2011-05-05 2012-11-08 Ixetic Bad Homburg Gmbh Pompe à cylindrée variable
JP2014178028A (ja) * 2013-03-14 2014-09-25 Husco Automotive Holdings Llc 流体ポンプアウトレット圧調整のためのシステム及び方法

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