WO2018198451A1 - Variable capacity pump and control system - Google Patents

Variable capacity pump and control system Download PDF

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Publication number
WO2018198451A1
WO2018198451A1 PCT/JP2018/002133 JP2018002133W WO2018198451A1 WO 2018198451 A1 WO2018198451 A1 WO 2018198451A1 JP 2018002133 W JP2018002133 W JP 2018002133W WO 2018198451 A1 WO2018198451 A1 WO 2018198451A1
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WO
WIPO (PCT)
Prior art keywords
variable displacement
pump chamber
opening
discharge
displacement pump
Prior art date
Application number
PCT/JP2018/002133
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French (fr)
Japanese (ja)
Inventor
竹花　憲夫
Original Assignee
株式会社ミクニ
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Filing date
Publication date
Application filed by 株式会社ミクニ filed Critical 株式会社ミクニ
Publication of WO2018198451A1 publication Critical patent/WO2018198451A1/en

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/24—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • 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
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member

Definitions

  • the present invention relates to a variable displacement pump that can inhale, pressurize, and discharge a fluid and change the discharge amount, and more particularly, to an internal gear type variable displacement pump including an inner rotor and an outer rotor, and a control system.
  • a trochoid pump including a housing, an inner rotor, and an outer rotor is known (see, for example, Patent Document 1).
  • the discharge (capacity) characteristics of the pump are determined in accordance with the high load operation region where the most discharge amount is required, such as high-speed rotation. Therefore, in the low load operation region such as medium speed rotation, the oil discharge amount becomes excessive, and the driving force is lost correspondingly.
  • a conventional variable displacement pump in a trochoid pump including a housing, an inner rotor, and an outer rotor, a control space (hydraulic chamber) provided in the housing and an outer rotor to be rotationally displaced by the hydraulic pressure in the control space.
  • a control space hydroaulic chamber
  • an outer rotor to be rotationally displaced by the hydraulic pressure in the control space.
  • a variable capacity mechanism including an adjustment ring disposed on the outer periphery and an OCV disposed outside the housing (see, for example, Patent Document 2).
  • the hydraulic pressure in the control space is appropriately controlled by the OCV, the rotation angle of the adjustment ring is adjusted, and the outer rotor is displaced with respect to the housing, so that the pump capacity is increased according to the engine speed. It is something to change.
  • variable capacity mechanism requires a larger adjustment ring than the outer rotor, the structure becomes complicated, large, and expensive.
  • the present invention has been made in view of the above circumstances, and an object thereof is to provide a variable displacement pump and a control system capable of changing the discharge amount by solving the above-described problems of the conventional technology. There is.
  • variable displacement pump of the present invention exerts suction, pressurization, and discharge pumping action on the suction passage for sucking fluid, the suction port located downstream of the suction passage, and the fluid guided to the suction port.
  • variable displacement pump configured as described above includes a housing having a suction passage and a communication passage, and an inner rotor and an outer rotor disposed in the housing so as to define a pump chamber, and the flow control valve is located in the middle of the communication passage. You may employ
  • the housing may adopt a configuration including the suction port and the discharge port on the wall surface on which the side surfaces of the inner rotor and the outer rotor slide.
  • the housing may adopt a configuration in which the opening is provided on the wall surface on which the side surfaces of the inner rotor and the outer rotor slide.
  • variable displacement pump configured as described above, a configuration may be adopted in which the opening is disposed at a position closed by the side surface of the inner rotor when the inner rotor is in a predetermined rotation angle region.
  • the opening is disposed at a position where the opening is blocked by the side surface of the inner rotor from the middle of the discharge operation by the pump chamber and blocked from the pump chamber during the discharge operation. May be.
  • the opening is disposed at an approximately intermediate angular position in an angular range that defines a partition region in a state immediately before the pump chamber completes the suction action and starts the discharge action.
  • a configuration may be adopted.
  • the inner rotor and the outer rotor may be configured to be trochoidal.
  • a control system of the present invention is a control system for controlling a variable displacement pump having any one of the above-described configurations mounted on an engine to supply oil as a fluid, wherein the oil in the engine or the operation of the engine Based on information relating to the state, it includes a control means for driving and controlling the flow control valve.
  • variable displacement pump and control system configured as described above, it is necessary to appropriately control the flow control valve from fully closed to fully open while achieving simplification, miniaturization, cost reduction, etc.
  • the fluid can be discharged with a discharge amount according to the above. Therefore, it is possible to prevent the discharge of an excessive amount, and it is possible to reduce the loss of driving force accordingly.
  • FIG. 1 is an external perspective view showing an embodiment of a variable displacement pump according to the present invention. It is a disassembled perspective view of the variable displacement pump shown in FIG. It is sectional drawing of the variable displacement pump shown in FIG. It is a block diagram of the variable displacement pump shown in FIG. It is a schematic diagram of the variable displacement pump shown in FIG. It is a block diagram which shows the control system which controls a flow control valve, when the variable displacement pump which concerns on this invention is applied to an engine.
  • FIG. 2 is a view for explaining the operation of the variable displacement pump shown in FIG.
  • FIG. 8 is a view for explaining the operation of the variable displacement pump shown in FIG. 1, and is an operation diagram at a position where the inner rotor is rotated counterclockwise by 15 degrees from the position shown in FIG. 7.
  • FIG. 9 illustrates the operation of the variable displacement pump shown in FIG. 1, and is an operation diagram at a position where the inner rotor rotates 15 degrees counterclockwise from the position shown in FIG. 8.
  • FIG. 10 illustrates the operation of the variable displacement pump shown in FIG. 1, and is an operation diagram at a position where the inner rotor is rotated counterclockwise by 15 degrees from the position shown in FIG. 9.
  • FIG. 11 is a diagram for explaining the operation of the variable displacement pump shown in FIG. 1, and is an operation diagram at a position where the inner rotor is rotated counterclockwise by 15 degrees from the position shown in FIG. 10.
  • FIG. 12 is a view for explaining the operation of the variable displacement pump shown in FIG.
  • FIG. 13 is a diagram for explaining the operation of the variable displacement pump shown in FIG. 1, and is an operation diagram at a position where the inner rotor is rotated counterclockwise by 15 degrees from the position shown in FIG. 12.
  • FIG. 14 illustrates the operation of the variable displacement pump shown in FIG. 1, and is an operation diagram at a position where the inner rotor is rotated counterclockwise by 15 degrees from the position shown in FIG.
  • FIG. 15 is a view for explaining the operation of the variable displacement pump shown in FIG. 1 and is an operation diagram at a position where the inner rotor is rotated 15 degrees counterclockwise from the position shown in FIG. 14.
  • FIG. 16 is a view for explaining the operation of the variable displacement pump shown in FIG. 1, and is an operation diagram at a position where the inner rotor is rotated counterclockwise by 15 degrees from the position shown in FIG. 15.
  • FIG. 17 illustrates the operation of the variable displacement pump shown in FIG. 1, and is an operation diagram at a position where the inner rotor is rotated counterclockwise by 15 degrees from the position shown in FIG. 16. It is a graph which shows the discharge characteristic in the fixed rotation of the variable displacement pump which concerns on this invention. 6 is a graph showing hydraulic characteristics when the flow control valve is controlled in accordance with the engine speed when the variable displacement pump according to the present invention is applied to an engine.
  • variable displacement pump is a trochoidal variable displacement pump VP that supplies oil as a fluid in an application object such as an engine.
  • the variable displacement pump VP includes a housing H, a drive shaft 40 that rotates about an axis S in the direction of arrow R (counterclockwise in FIG. 5), an inner rotor 50, and an outer rotor 60.
  • the flow control valve 70 is provided.
  • the housing H is formed by a three-part structure of the base 10, the rotor case 20, and the cover 30.
  • the variable displacement pump VP includes an introduction passage 1 a and an oil pan 2 connected to a supply destination 1 such as a lubrication region in the engine E in the engine E to be applied.
  • the oil is disposed between the outlet passages 2a connected to the outlet, and the oil guided from the outlet passage 2a is sucked, pressurized and discharged, and supplied from the introduction passage 1a to the supply destination 1.
  • the discharge oil discharged from the discharge port 14 of the variable displacement pump VP is returned to the oil pan 2 through the return passage 3 and the relief valve 4 when an overpressure state of a predetermined level or higher is reached. It is like that.
  • the base 10 is formed in a flat plate shape that defines a joint surface 10a joined to the engine E and a joint surface 10b joined to the rotor case 20 using a material such as steel, cast iron, sintered steel, and an aluminum alloy. Yes.
  • the joint surface 10b also functions as a wall surface on which the side surface 51 of the inner rotor 50 and the side surface 61 of the outer rotor 60 slide.
  • the base 10 includes a bearing hole 11, a suction passage 12, a suction port 13, a discharge port 14, a discharge passage 15, a communication passage 16, a positioning hole 17 for fitting a positioning pin D, and a fastening bolt (not fixed) when fastened to the engine E. It is provided with a circular hole 18 through which it is shown.
  • the bearing hole 11 is formed to support the drive shaft 40 so as to be rotatable about the axis S.
  • the suction passage 12 is formed in a groove shape on the joint surface 10 a so as to connect the outlet passage 2 a of the engine E and the suction port 13.
  • the suction port 13 is formed so as to penetrate from the joint surface 10a to the joint surface 10b so as to face the suction passage 12 and the lead-out passage 2a and to form a substantially crescent-shaped outline indicated by a two-dot chain line in FIG.
  • the discharge port 14 is formed to penetrate from the joint surface 10a to the joint surface 10b so as to face the discharge passage 15 and the introduction passage 1a and to form a substantially crescent-shaped outline indicated by a two-dot chain line in FIG.
  • the discharge passage 15 is formed in a groove shape on the joint surface 10 a so as to connect the introduction passage 1 a of the engine E and the discharge port 14.
  • the communication path 16 forms a part of the communication path that allows the pump chamber PC and the suction path 12 to communicate with each other.
  • the communication path 16 is formed in a cylindrical shape extending in parallel with the axis S, and is connected to the bonding surface 10a side from the bonding surface 10b. It is formed so as to penetrate to the suction passage 12.
  • the rotor case 20 is made of a material such as steel, cast iron, sintered steel, aluminum alloy or the like, and has a substantially annular shape that defines a joining surface 20a joined to the joining surface 10b of the base 10 and a joining surface 20b joined to the cover 30. Is formed.
  • the rotor case 20 has an inner wall 21, a communication path 22, a fitting hole for fitting the positioning pin D, and a screw hole / positioning hole 23 in which a screw hole for screwing the screw B is formed on the same axis, and a fastening bolt.
  • a circular hole 24 is provided.
  • the inner wall surface 21 is a cylindrical surface centered on the center line L2 so as to rotatably support the outer peripheral surface 63 of the outer rotor 60 about the center line L2 deviated from the center line L1 of the inner rotor 50 by a predetermined amount. Is formed.
  • the communication path 22 forms a part of the communication path that allows the pump chamber PC and the suction path 12 to communicate with each other.
  • the communication path 22 extends in parallel with the axis S and is formed in a cylindrical shape coaxially with the communication path 16. It is formed so as to penetrate from the surface 20b to the joint surface 20a.
  • the cover 30 is made of a material such as steel, cast iron, sintered steel, or aluminum alloy, and protrudes like a bowl on the joint surface 30a, the outer surface 30b, and the outer surface 30b that are joined to the joint surface 20b of the rotor case 20. It is formed in a substantially flat plate shape that defines the portion 30c.
  • the joint surface 30a also functions as a wall surface on which the side surface 52 of the inner rotor 50 and the side surface 62 of the outer rotor 60 slide.
  • the cover 30 includes an opening 31, a communication path 32 (32 a, 32 b, 32 c), a fitting recess 33 formed in the middle of the communication path 32, a circular hole 34 for passing a screw B, and a circular hole 35 for passing a fastening bolt. ing.
  • the opening 31 is a joint surface so as to open a communication path 32 a that forms a part of the communication path 32 toward the pump chamber PC defined by the inner rotor 50 and the outer rotor 60. 30a.
  • the opening 31 is formed so as to open to the pump chamber PC in the region of the joint surface 30 a removed from the suction port 13 and the discharge port 14 in the rotational direction.
  • the opening 31 is disposed at a position that is opened from the side surface 52 of the inner rotor 50 when the inner rotor 50 is in a predetermined rotation angle region. Further, the opening 31 starts to be blocked by the side surface 52 of the inner rotor 50 in the middle of the discharge action by the pump chamber PC as shown in FIG. 15, and from the pump chamber PC during the discharge action as shown in FIGS. As shown in FIGS.
  • the position where the inner rotor 50 is located is blocked by the side surface 52 of the inner rotor 50 when the inner rotor 50 is in a predetermined rotation angle region.
  • the opening part 31 is an area
  • the opening 31 By arranging the opening 31 at the position as described above, the oil in the pump chamber PC is opened before the oil sucked into the pump chamber PC is discharged by appropriately controlling the flow rate control valve 70. It is possible to efficiently return to the suction passage 12 via the portion 31 and the communication passages 32, 22, 16. Therefore, it is possible to prevent excessive oil from being discharged, and it is possible to reduce loss of useless driving force.
  • the opening 31 has an angular region that defines the partition region of the pump chamber PC in the partition region immediately before the pump chamber PC completes the suction action and starts the discharge action. It may be arranged at a substantially intermediate angular position.
  • the partition region means that the pump chamber PC is connected to the suction port 13 and the discharge port by the joint surfaces 10 b and 30 a of the housing H, the outer peripheral wall surface of the inner rotor 50, and the inner peripheral wall surface of the outer rotor 60.
  • 14 is a region (geometric partition section) that is in a state of being partitioned from 14 and blocked.
  • the opening 31 By arranging the opening 31 at the position as described above, even if the flow rate control valve 70 malfunctions and stops in the open state, when the discharge amount in the closed state is 100%, A discharge amount of 60% or more can be secured.
  • the circular hole was shown as a shape of the opening part 31, as long as it is a shape which opens the communicating path 32 to the pump chamber PC, it is not limited to this, Other shapes and forms are employ
  • the communication path 32 forms part of a communication path that allows the pump chamber PC and the suction path 12 to communicate with each other, and as shown in FIG. 3, the communication path 32 includes a communication path 32a, a communication path 32b, and a communication path 32c.
  • the communication path 32a is formed in a cylindrical shape that extends parallel to the axis S from the joint surface 30a toward the protrusion 30c.
  • the communication path 32b is formed in a cylindrical shape that extends perpendicular to the axis S in the protrusion 30c.
  • the communication path 32c extends in parallel with the axis S from the protrusion 30c toward the joint surface 30a and is formed in a cylindrical shape coaxially with the communication paths 22 and 16.
  • the fitting recess 33 is for fitting and fixing the flow control valve 70, and is formed in the projecting portion 30c at the intersection region of the communication path 32b and the communication path 32c. Then, by fitting the fitting convex portion 72 of the flow control valve 70 into the fitting concave portion 33, the passage area of the communication passage 32 is adjusted in a range from fully closed to fully open according to the operation of the valve body 76. It has come to be.
  • the housing H includes the base 10, the rotor case 20, and the cover 30, and the suction passage 12, the suction port 13, the discharge port 14, and the discharge passage 15 are provided to the base 10.
  • a simple structure in which the communication passage 22 is provided in 20 and the fitting recess 33 for attaching the communication passage 32 and the flow control valve 70 to the cover 30 is provided.
  • a communication path that connects the pump chamber PC and the suction path 12 is formed by the communication path 32 of the cover 30, the communication path 22 of the rotor case 20, and the communication path 16 of the base 10.
  • the communication passages are divided into separate members, that is, the base 10, the rotor case 20, and the cover 30, so that drilling of the communication passages 16, 22, 32 a, 32 b, and 32 c is easy. Can be done.
  • the drive shaft 40 is formed by extending in the axis S direction using steel or the like, and is a fitting portion that is fitted into the coupling portion 41 to which the driving force from the engine E is transmitted and the fitting hole 53 of the inner rotor 50. 42, a through hole 43 provided in the fitting portion 42 and fitted with the detent pin F is provided.
  • the inner rotor 50 is formed in a substantially star shape that defines a side surface 51 that slides on the joint surface 10b of the base 10 and a side surface 52 that slides on the joint surface 30a of the cover 30 using a material such as steel or sintered steel.
  • the inner rotor 50 includes a fitting hole 53, a pin groove 54, four convex portions (ridges) 55, and four concave portions (valleys) 56, and is formed as an external gear having a tooth shape with a trochoidal curve.
  • the fitting hole 53 is formed so that the fitting portion 42 of the drive shaft 40 is fitted.
  • the pin groove 54 is formed so as to fit both side portions of the detent pin F inserted into the through hole 43 of the drive shaft 40.
  • the inner rotor 50 rotates integrally with the drive shaft 40 in the counterclockwise direction in FIG. 5 with the center line L1 coaxial with the axis S as the center of rotation.
  • the outer rotor 60 is formed in an annular shape that defines a side surface 61 that slides on the joint surface 10b of the base 10 and a side surface 62 that slides on the joint surface 30a of the cover 30 using a material such as steel or sintered steel. ing.
  • the outer rotor 60 includes a circular outer peripheral surface 63 centering on the center line L2, five convex portions 64, and five concave portions 65, and is formed as an internal gear having a tooth shape that can mesh with the inner rotor 50.
  • the outer peripheral surface 63 is formed so as to be rotatably supported in contact with the inner wall surface 21 of the rotor case 20.
  • the five convex portions 64 and the five concave portions 65 are formed so as to partially mesh with the four convex portions 55 and the four concave portions 56 of the inner rotor 50.
  • the outer rotor 60 rotates counterclockwise in FIG. 5 with the center line L2 as the rotation center at a slower speed than the inner rotor 50 while interlocking with the rotation of the inner rotor 50 rotating about the center line L1. Rotate. Further, when the inner rotor 50 and the outer rotor 60 are partially meshed with each other, a pump chamber PC that continuously exerts suction, pressurization, and discharge actions is defined between them.
  • the flow control valve 70 includes a case 71, a fitting convex portion 72 continuous with the case 71, an exciting coil 73, an iron core 74, a rod 75 connected to the iron core 74, and a rod 75.
  • the connected valve body 76 and a spring 77 that biases the valve body 76 in the valve closing direction are provided.
  • the case 71 is formed in a cylindrical shape covering the whole with a magnetic metal material or the like.
  • the fitting convex portion 72 is formed in a cylindrical shape with a diameter smaller than that of the case 71, and is firmly fitted into the fitting concave portion 33 of the cover 30.
  • the fitting projection 72 includes a valve seat 72a in which the valve element 76 is seated, an opening 72b communicating with the communication passage 32b on the outer peripheral surface, and an opening 72c communicating with the communication passage 32c on the end surface.
  • the flow control valve 70 configured as described above is an electromagnetic valve that operates the iron core 74 using the magnetomotive force of the exciting coil 73 as a drive source.
  • the flow control valve 70 operates as follows by appropriately controlling the energization of the coil 73. That is, when the coil 73 is not energized, the urging force of the spring 77 causes the valve body 76 to be seated on the valve seat 72a and shut off the communication passages 32b and 32c. On the other hand, in a state where the coil 73 is appropriately energized, the valve element 76 separates from the valve seat 72a and opens the communication passages 32b and 32c against the urging force of the spring 77.
  • the lift amount of the valve body 76 is appropriately adjusted, and the flow rate of oil flowing through the communication passage 32 is adjusted.
  • the flow control valve 70 is a normally closed electromagnetic valve that is set to a closed state that fully closes the communication path 32 when the coil 73 is not energized, the closed state is maintained even if energization failure occurs. The required maximum discharge amount can be satisfied.
  • a normally open solenoid valve that maintains a valve open state in the case of poor energization may be employed.
  • the attachment method of the flow rate control valve 70 is not limited to the method of firmly fitting and fixing the fitting convex portion 72 to the fitting concave portion 33, and the method of fixing the flange or the like provided in the case 71 to the cover 30 with screws. Other techniques can be employed. Further, the mounting direction of the flow control valve 70 is not limited to the direction protruding from the cover 30 in the direction of the axis S, but can be changed together with the path of the communication path 32 so as to satisfy the layout constraint.
  • variable displacement pump VP having the above configuration
  • a base 10 a rotor case 20, a cover 30, a drive shaft 40, an inner rotor 50, an outer rotor 60, a flow control valve 70, three screws B, three positioning pins D, and one detent pin F are prepared.
  • the rotor case 20 is joined to the base 10 while the positioning pins D are press-fitted into the positioning holes 17 and the screw holes / positioning holes 23.
  • the inner rotor 50 and the outer rotor 60 are fitted inside the rotor case 20.
  • the rotation prevention pin F is inserted into the through hole 43 of the drive shaft 40, and the fitting portion 42 is fitted into the fitting hole 53 while the driving shaft 40 is passed through the fitting hole 53 and the bearing hole 11.
  • the stop pin F is fitted into the pin groove 54.
  • the drive shaft 40 is rotated integrally with the inner rotor 50.
  • the connection part 41 of the drive shaft 40 is larger than a shaft diameter, the procedure in which the drive shaft 40 is inserted from the joint surface 10a side of the base 10 and then the detent pin F is inserted may be used.
  • the cover 30 is joined to the joint surface 20 b of the rotor case 20, and the three screws B are screwed into the screw hole / positioning hole 24 while passing through the circular hole 34. Then, the flow control valve 70 is fitted into the fitting recess 33 of the cover 30 and fixed. Thus, the assembly of the variable displacement pump VP is completed.
  • the above assembling procedure is an example, and other procedures can be adopted.
  • variable displacement pump VP when the variable displacement pump VP is attached to the engine E as an application object, the joint surface 10a of the base 10 is attached to the engine E while the connecting portion 41 of the drive shaft 40 is connected to the rotational drive portion of the engine E. Contact the joint surface. Thereafter, the fastening bolt is passed through the circular holes 35, 24, and 18 and screwed into the screw holes of the engine E, whereby the mounting operation is completed.
  • the variable displacement pump VP having the above configuration is driven and controlled by a control system as shown in FIG.
  • the control system includes a control unit 100 as control means, an ECU 110 mounted on a vehicle to control the entire system, a battery 120, and a detection circuit 130.
  • the control unit 100 includes a microcomputer 101 that performs control, a drive circuit 102 that drives a flow control valve 70 based on a control signal of the microcomputer 101, and an I / F (interface) that transmits and receives signals between the microcomputer 101 and the ECU 110 by communication. )
  • a circuit 103 and a power supply circuit 104 for guiding the power supply to the microcomputer 101 are provided.
  • the microcomputer 101 appropriately calculates the magnitude of the energization current of the coil 73 in order to control the opening / closing operation of the flow control valve 70 based on detection information of the detection circuit 130, for example, oil pressure, oil temperature, engine speed, and the like. It is supposed to be.
  • the detection circuit 130 detects the pressure and temperature of oil in the lubrication region, the rotation speed of the engine E, and the like based on output signals from the hydraulic sensor E1, the oil temperature sensor E2, the engine rotation sensor E3, and the like.
  • the flow control valve 70 is appropriately driven and controlled by the control unit 100 via the ECU 110. That is, the control unit 100 controls the drive of the flow control valve 70 based on the oil in the engine E or information related to the operating state of the engine E.
  • the oil pressure and the oil temperature are shown as the information related to the oil, but the present invention is not limited to this, and the viscosity of the oil, the dirt state of the oil, and the like can be applied as the information.
  • the engine speed is shown as information related to the operating state of the engine E, the present invention is not limited to this, and it is possible to apply information specifying the throttle opening, the coolant temperature, and other operating states. it can.
  • FIGS. 7 to 17 show time-series operation states when the drive shaft 40 rotates counterclockwise every 15 degrees.
  • a description will be given focusing on the front side in the rotation direction R of one convex portion 55 (with a black circle mark) of the inner rotor 50.
  • the opening 31 is completely closed by the side surface 52. That is, in the process from the state shown in FIG. 15 to the state shown in FIG. 16, the opening 31 is closed by the side surface 52 of the inner rotor 50 in the middle of the pressurizing and discharging action by the pump chamber PC, and the pressurizing and discharging action. It will be in the state where it was cut off from inside pump room PC. Therefore, after the opening 31 is completely closed, only the oil discharge operation from the pump chamber PC toward the discharge port 14 is performed even if the flow control valve 70 is in the open state.
  • the opening 31 is open from the side surface 52 of the inner rotor 52 when it is in the rotation angle region as shown in FIGS. 11 to 15, and the state shown in FIG.
  • the opening 31 is in a state of being closed by the side surface 52 of the inner rotor 52 when it is in the rotation angle region.
  • the flow rate control valve is in a state where the opening 31 is opened and in the rotation angle region of suction action to pressurization and discharge action.
  • the valve 70 By appropriately opening the valve 70, it is possible to efficiently return the unfilled oil filled in the pump chamber PC to the suction passage 12. Thereby, the loss of the driving force for discharging excess oil can be reduced.
  • the flow control valve 70 is appropriately controlled to open the oil, and the oil is directly sucked into the pump chamber PC from the suction passage 12. Can do. Thereby, generation
  • the flow control valve 70 is appropriately controlled to be opened and closed in a use region where the discharge amount set as the fixed discharge performance is not required, so that the pump before discharge By returning the fluid (oil) sucked into the chamber PC to the suction passage 12 through the communication passages 32, 22, and 16, the discharge pressure can be lowered and the driving load can be reduced as shown in FIG. .
  • the flow rate control valve 70 is set by the control unit 100 when the engine E is in the medium speed rotation region as shown in FIG.
  • the drive can be controlled so that the valve is opened at a predetermined opening.
  • the control unit 100 performs drive control to open the flow rate control valve 70 with a predetermined opening, thereby It is possible to suppress or prevent the occurrence of cavitation by suppressing the negative pressure of the chamber PC.
  • the flow control valve 70 is appropriately controlled between fully closed and fully opened while achieving simplification of structure, size reduction, cost reduction, and the like.
  • the fluid can be discharged with a discharge amount as required. Therefore, an excessive amount of discharge can be prevented, and the loss of driving force can be reduced accordingly, and the negative pressure in the pump chamber PC can be suppressed to suppress or prevent the occurrence of cavitation.
  • the trochoid pump containing the inner rotor 50 and the outer rotor 60 which make a trochoid tooth profile was shown as a pump action member which demarcates the pump chamber PC, it is not limited to this.
  • the present invention may be applied to a configuration including an inner rotor and an outer rotor having involute teeth, or an inner rotor and an outer rotor having other tooth shapes.
  • the inner rotor 50 and the outer rotor 60 are configured with the trochoidal four-leaf five-node, but the present invention is not limited to this, and a configuration with other numbers may be adopted. .
  • a trochoid pump is shown as a pump.
  • the present invention is not limited to this, and a vane pump or other positive displacement type may be used as long as it defines a pump chamber that exerts suction, pressurization, and discharge. You may employ
  • the flow control valve 70 including the valve body 76 that reciprocates in the axial direction is shown as the flow control valve.
  • the flow control valve 70 is not limited to this, and is not limited to this. You may employ
  • the present invention is adopted in the configuration in which the housing H is separated into the base 10, the rotor case 20, and the cover 30 is shown.
  • the present invention is not limited to this.
  • a configuration having a body shape may be adopted, and in this portion, a communication path that allows the pump chamber and the suction path to communicate with each other, and an opening that opens the communication path in the pump chamber may be provided.
  • variable displacement pump VP is applied to an engine mounted on an automobile or the like.
  • the present invention is not limited to this and is applied to a transmission and other lubrication systems.
  • the present invention may be applied to an apparatus using a fluid other than oil.

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Abstract

This variable capacity pump is provided with the following: an intake passage (12) that takes in a fluid; an intake opening (13) that is located downstream of the intake passage; a pump chamber (PC) that pumps the fluid guided into the intake opening by taking in, pressurizing, and discharging the fluid; a discharge opening (14) that is located downstream of the pump chamber; a communication path (32, 22, 16) that has an opening (31) formed in the pump chamber, in a region away from the intake opening and discharge opening in order to connect the pump chamber and the intake passage; and a flow rate control valve (70) that controls the flow rate of the fluid in the communication paths. Due to this configuration, by appropriately controlling the flow rate control valve between being completely closed and completely open, it is possible to discharge the fluid at the necessary discharge rate and prevent excessive discharge of fluid, thereby correspondingly suppressing loss of drive power, while achieving a simplified structure, miniaturization, lower cost, and the like.

Description

可変容量型ポンプ及び制御システムVariable displacement pump and control system
　本発明は、流体を吸入、加圧及び吐出すると共に吐出量を変更可能な可変容量型ポンプに関し、特に、インナーロータ及びアウターロータを備えた内接ギヤ式の可変容量型ポンプ及び制御システムに関する。 The present invention relates to a variable displacement pump that can inhale, pressurize, and discharge a fluid and change the discharge amount, and more particularly, to an internal gear type variable displacement pump including an inner rotor and an outer rotor, and a control system.
　従来の固定容量型ポンプとしては、ハウジング、インナーロータ及びアウターロータを備えたトロコイドポンプが知られている（例えば、特許文献１参照）。
　このトロコイドポンプは、例えば車両のエンジンにおいてオイルを供給するために適用される場合、高速回転等の最も吐出量が必要とされる高負荷運転領域に合わせてポンプの吐出（容量）特性が決定されるため、中速回転等の低負荷運転領域ではオイルの吐出量が余剰になり、その分だけ駆動力の損失を招くことになる。 As a conventional fixed displacement pump, a trochoid pump including a housing, an inner rotor, and an outer rotor is known (see, for example, Patent Document 1).
When this trochoid pump is applied, for example, to supply oil in a vehicle engine, the discharge (capacity) characteristics of the pump are determined in accordance with the high load operation region where the most discharge amount is required, such as high-speed rotation. Therefore, in the low load operation region such as medium speed rotation, the oil discharge amount becomes excessive, and the driving force is lost correspondingly.
　一方、従来の可変容量型ポンプとしては、ハウジング、インナーロータ及びアウターロータを含むトロコイドポンプにおいて、ハウジング内に設けられた制御空間（油圧室）、制御空間内の油圧によって回転変位するべくアウターロータの外周に配置された調整リング、ハウジングの外側に配置されたＯＣＶを含む容量可変機構を備えたものが知られている（例えば、特許文献２を参照）。 On the other hand, as a conventional variable displacement pump, in a trochoid pump including a housing, an inner rotor, and an outer rotor, a control space (hydraulic chamber) provided in the housing and an outer rotor to be rotationally displaced by the hydraulic pressure in the control space. There is known one having a variable capacity mechanism including an adjustment ring disposed on the outer periphery and an OCV disposed outside the housing (see, for example, Patent Document 2).
　この容量可変機構では、ＯＣＶにより制御空間内の油圧を適宜制御して、調整リングの回転角度を調整し、ハウジングに対してアウターロータを変位させることにより、エンジンの回転数に応じてポンプ容量を変化させるものである。 In this capacity variable mechanism, the hydraulic pressure in the control space is appropriately controlled by the OCV, the rotation angle of the adjustment ring is adjusted, and the outer rotor is displaced with respect to the housing, so that the pump capacity is increased according to the engine speed. It is something to change.
　しかしながら、上記の容量可変機構は、アウターロータよりも大きい調整リングを必要とするため、構造の複雑化、大型化、高コスト化等を招くものである。 However, since the variable capacity mechanism requires a larger adjustment ring than the outer rotor, the structure becomes complicated, large, and expensive.
特開２００１－１８２６６９号公報JP 2001-182669 A 特開２０１４－１３９４２０号公報JP 2014-139420 A
　本発明は、上記の事情に鑑みて成されたものであり、その目的とするところは、上記従来技術の課題等を解消して吐出量を変更可能な可変容量型ポンプ及び制御システムを提供することにある。 The present invention has been made in view of the above circumstances, and an object thereof is to provide a variable displacement pump and a control system capable of changing the discharge amount by solving the above-described problems of the conventional technology. There is.
　本発明の可変容量型ポンプは、流体を吸入する吸入通路と、吸入通路の下流に位置する吸入口と、吸入口に導かれた流体に対して、吸入、加圧及び吐出のポンプ作用を及ぼすポンプ室と、ポンプ室の下流に位置する吐出口と、ポンプ室と吸入通路とを連通させるべく、吸入口及び吐出口から外れた領域においてポンプ室に開口する開口部を有する連通路と、連通路を流れる流体の流量を制御する流量制御弁とを含む、構成となっている。 The variable displacement pump of the present invention exerts suction, pressurization, and discharge pumping action on the suction passage for sucking fluid, the suction port located downstream of the suction passage, and the fluid guided to the suction port. A pump chamber, a discharge port located downstream of the pump chamber, a communication passage having an opening that opens to the pump chamber in a region away from the suction port and the discharge port, and a communication path; And a flow rate control valve that controls the flow rate of the fluid flowing through the passage.
　上記構成の可変容量型ポンプにおいて、吸入通路及び連通路を有するハウジングと、ポンプ室を画定するべくハウジング内に配置されたインナーロータ及びアウターロータとを備え、流量制御弁は、連通路の途中に介在するようにハウジングに設けられている、構成を採用してもよい。 The variable displacement pump configured as described above includes a housing having a suction passage and a communication passage, and an inner rotor and an outer rotor disposed in the housing so as to define a pump chamber, and the flow control valve is located in the middle of the communication passage. You may employ | adopt the structure provided in the housing so that it may interpose.
　上記構成の可変容量型ポンプにおいて、ハウジングは、インナーロータ及びアウターロータの側面が摺動する壁面において、上記吸入口及び吐出口を含む、構成を採用してもよい。 In the variable displacement pump having the above configuration, the housing may adopt a configuration including the suction port and the discharge port on the wall surface on which the side surfaces of the inner rotor and the outer rotor slide.
　上記構成の可変容量型ポンプにおいて、ハウジングは、インナーロータ及びアウターロータの側面が摺動する壁面において、上記開口部を有する、構成を採用してもよい。 In the variable displacement pump having the above-described configuration, the housing may adopt a configuration in which the opening is provided on the wall surface on which the side surfaces of the inner rotor and the outer rotor slide.
　上記構成の可変容量型ポンプにおいて、開口部は、インナーロータが所定の回転角度領域にあるとき、インナーロータの側面により閉塞される位置に配置されている、構成を採用してもよい。 In the variable displacement pump configured as described above, a configuration may be adopted in which the opening is disposed at a position closed by the side surface of the inner rotor when the inner rotor is in a predetermined rotation angle region.
　上記構成の可変容量型ポンプにおいて、開口部は、ポンプ室による吐出作用の途中からインナーロータの側面により閉塞されて吐出作用中のポンプ室から遮断される位置に配置されている、構成を採用してもよい。 In the variable displacement pump having the above configuration, the opening is disposed at a position where the opening is blocked by the side surface of the inner rotor from the middle of the discharge operation by the pump chamber and blocked from the pump chamber during the discharge operation. May be.
　上記構成の可変容量型ポンプにおいて、開口部は、ポンプ室が吸入作用を完了しかつ吐出作用を開始する直前の状態にある仕切り領域を画定する角度範囲において、略中間の角度位置に配置されている、構成を採用してもよい。 In the variable displacement pump configured as described above, the opening is disposed at an approximately intermediate angular position in an angular range that defines a partition region in a state immediately before the pump chamber completes the suction action and starts the discharge action. A configuration may be adopted.
　上記構成の可変容量型ポンプにおいて、インナーロータ及びアウターロータは、トロコイド式である、構成を採用いてもよい。 In the variable displacement pump configured as described above, the inner rotor and the outer rotor may be configured to be trochoidal.
　本発明の制御システムは、流体としてのオイルを供給するべくエンジンに搭載された上記構成のいずれか一つをなす可変容量型ポンプを制御する制御システムであって、エンジン内のオイル又はエンジンの運転状態に係る情報に基づいて、流量制御弁を駆動制御する制御手段を含む、構成となっている。 A control system of the present invention is a control system for controlling a variable displacement pump having any one of the above-described configurations mounted on an engine to supply oil as a fluid, wherein the oil in the engine or the operation of the engine Based on information relating to the state, it includes a control means for driving and controlling the flow control valve.
　上記構成をなす可変容量型ポンプ及び制御システムによれば、構造の簡略化、小型化、低コスト化等を達成しつつ、流量制御弁を全閉～全開の間で適宜制御することにより、必要に応じた吐出量にて流体を吐出することができる。それ故に、余剰量の吐出を防止でき、その分だけ駆動力の損失を低減できる。 According to the variable displacement pump and control system configured as described above, it is necessary to appropriately control the flow control valve from fully closed to fully open while achieving simplification, miniaturization, cost reduction, etc. The fluid can be discharged with a discharge amount according to the above. Therefore, it is possible to prevent the discharge of an excessive amount, and it is possible to reduce the loss of driving force accordingly.
本発明に係る可変容量型ポンプの一実施形態を示す外観斜視図である。1 is an external perspective view showing an embodiment of a variable displacement pump according to the present invention. 図１に示す可変容量型ポンプの分解斜視図である。It is a disassembled perspective view of the variable displacement pump shown in FIG. 図１に示す可変容量型ポンプの断面図である。It is sectional drawing of the variable displacement pump shown in FIG. 図１に示す可変容量型ポンプのブロック図である。It is a block diagram of the variable displacement pump shown in FIG. 図１に示す可変容量型ポンプの模式図である。It is a schematic diagram of the variable displacement pump shown in FIG. 本発明に係る可変容量型ポンプをエンジンに適用した場合において、流量制御弁を制御する制御システムを示すブロック図である。It is a block diagram which shows the control system which controls a flow control valve, when the variable displacement pump which concerns on this invention is applied to an engine. 図１に示す可変容量型ポンプの動作を説明するものであり、吸入行程の開始側の回転位置における動作図である。FIG. 2 is a view for explaining the operation of the variable displacement pump shown in FIG. 図１に示す可変容量型ポンプの動作を説明するものであり、図７に示す位置からインナーロータが１５度反時計回りに回転した位置における動作図である。FIG. 8 is a view for explaining the operation of the variable displacement pump shown in FIG. 1, and is an operation diagram at a position where the inner rotor is rotated counterclockwise by 15 degrees from the position shown in FIG. 7. 図１に示す可変容量型ポンプの動作を説明するものであり、図８に示す位置からインナーロータが１５度反時計回りに回転した位置における動作図である。FIG. 9 illustrates the operation of the variable displacement pump shown in FIG. 1, and is an operation diagram at a position where the inner rotor rotates 15 degrees counterclockwise from the position shown in FIG. 8. 図１に示す可変容量型ポンプの動作を説明するものであり、図９に示す位置からインナーロータが１５度反時計回りに回転した位置における動作図である。FIG. 10 illustrates the operation of the variable displacement pump shown in FIG. 1, and is an operation diagram at a position where the inner rotor is rotated counterclockwise by 15 degrees from the position shown in FIG. 9. 図１に示す可変容量型ポンプの動作を説明するものであり、図１０に示す位置からインナーロータが１５度反時計回りに回転した位置における動作図である。FIG. 11 is a diagram for explaining the operation of the variable displacement pump shown in FIG. 1, and is an operation diagram at a position where the inner rotor is rotated counterclockwise by 15 degrees from the position shown in FIG. 10. 図１に示す可変容量型ポンプの動作を説明するものであり、図１１に示す位置からインナーロータが１５度反時計回りに回転した位置における動作図である。FIG. 12 is a view for explaining the operation of the variable displacement pump shown in FIG. 1, and is an operation diagram at a position where the inner rotor is rotated 15 degrees counterclockwise from the position shown in FIG. 11. 図１に示す可変容量型ポンプの動作を説明するものであり、図１２に示す位置からインナーロータが１５度反時計回りに回転した位置における動作図である。FIG. 13 is a diagram for explaining the operation of the variable displacement pump shown in FIG. 1, and is an operation diagram at a position where the inner rotor is rotated counterclockwise by 15 degrees from the position shown in FIG. 12. 図１に示す可変容量型ポンプの動作を説明するものであり、図１３に示す位置からインナーロータが１５度反時計回りに回転した位置における動作図である。FIG. 14 illustrates the operation of the variable displacement pump shown in FIG. 1, and is an operation diagram at a position where the inner rotor is rotated counterclockwise by 15 degrees from the position shown in FIG. 図１に示す可変容量型ポンプの動作を説明するものであり、図１４に示す位置からインナーロータが１５度反時計回りに回転した位置における動作図である。FIG. 15 is a view for explaining the operation of the variable displacement pump shown in FIG. 1 and is an operation diagram at a position where the inner rotor is rotated 15 degrees counterclockwise from the position shown in FIG. 14. 図１に示す可変容量型ポンプの動作を説明するものであり、図１５に示す位置からインナーロータが１５度反時計回りに回転した位置における動作図である。FIG. 16 is a view for explaining the operation of the variable displacement pump shown in FIG. 1, and is an operation diagram at a position where the inner rotor is rotated counterclockwise by 15 degrees from the position shown in FIG. 15. 図１に示す可変容量型ポンプの動作を説明するものであり、図１６に示す位置からインナーロータが１５度反時計回りに回転した位置における動作図である。FIG. 17 illustrates the operation of the variable displacement pump shown in FIG. 1, and is an operation diagram at a position where the inner rotor is rotated counterclockwise by 15 degrees from the position shown in FIG. 16. 本発明に係る可変容量型ポンプの一定回転における吐出特性を示すグラフである。It is a graph which shows the discharge characteristic in the fixed rotation of the variable displacement pump which concerns on this invention. 本発明に係る可変容量型ポンプをエンジンに適用した場合において、エンジン回転数に応じて流量制御弁を制御した際の油圧特性を示すグラフである。6 is a graph showing hydraulic characteristics when the flow control valve is controlled in accordance with the engine speed when the variable displacement pump according to the present invention is applied to an engine.
　以下、本発明の実施形態について、添付図面を参照しつつ説明する。
　この実施形態に係る可変容量型ポンプは、エンジン等の適用対象物において、流体としてのオイルを供給するトロコイド式の可変容量型ポンプＶＰである。
　可変容量型ポンプＶＰは、図１ないし図３に示すように、ハウジングＨ、軸線Ｓを中心として矢印Ｒ方向（図５において反時計回り）に回転する駆動軸４０、インナーロータ５０、アウターロータ６０、流量制御弁７０を備えている。
　ここで、ハウジングＨは、ベース１０、ロータケース２０、カバー３０の三分割構造により形成されている。 Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings.
The variable displacement pump according to this embodiment is a trochoidal variable displacement pump VP that supplies oil as a fluid in an application object such as an engine.
As shown in FIGS. 1 to 3, the variable displacement pump VP includes a housing H, a drive shaft 40 that rotates about an axis S in the direction of arrow R (counterclockwise in FIG. 5), an inner rotor 50, and an outer rotor 60. The flow control valve 70 is provided.
Here, the housing H is formed by a three-part structure of the base 10, the rotor case 20, and the cover 30.
　そして、可変容量型ポンプＶＰは、図４及び図５に示すように、適用対象物であるエンジンＥにおいて、エンジンＥ内の潤滑領域等の供給先１に接続された導入通路１ａとオイルパン２に接続された導出通路２ａの間に配置され、導出通路２ａから導かれたオイルを吸入，加圧及び吐出して、導入通路１ａから供給先１に向けて供給する。
　尚、このオイル供給系において、可変容量型ポンプＶＰの吐出口１４から吐出された吐出オイルは、所定レベル以上の過圧状態になると、戻し通路３及び逃し弁４を経てオイルパン２に戻されるようになっている。 As shown in FIGS. 4 and 5, the variable displacement pump VP includes an introduction passage 1 a and an oil pan 2 connected to a supply destination 1 such as a lubrication region in the engine E in the engine E to be applied. The oil is disposed between the outlet passages 2a connected to the outlet, and the oil guided from the outlet passage 2a is sucked, pressurized and discharged, and supplied from the introduction passage 1a to the supply destination 1.
In this oil supply system, the discharge oil discharged from the discharge port 14 of the variable displacement pump VP is returned to the oil pan 2 through the return passage 3 and the relief valve 4 when an overpressure state of a predetermined level or higher is reached. It is like that.
　ベース１０は、鋼、鋳鉄、焼結鋼、アルミニウム合金等の材料を用いて、エンジンＥに接合される接合面１０ａ及びロータケース２０に接合される接合面１０ｂを画定する平板状に形成されている。
　接合面１０ｂは、インナーロータ５０の側面５１及びアウターロータ６０の側面６１が摺動する壁面としても機能する。
　ベース１０は、軸受孔１１、吸入通路１２、吸入口１３、吐出口１４、吐出通路１５、連通路１６、位置決めピンＤを嵌合させる位置決め孔１７、エンジンＥに締結する際の締結ボルト（不図示）を通す円孔１８を備えている。 The base 10 is formed in a flat plate shape that defines a joint surface 10a joined to the engine E and a joint surface 10b joined to the rotor case 20 using a material such as steel, cast iron, sintered steel, and an aluminum alloy. Yes.
The joint surface 10b also functions as a wall surface on which the side surface 51 of the inner rotor 50 and the side surface 61 of the outer rotor 60 slide.
The base 10 includes a bearing hole 11, a suction passage 12, a suction port 13, a discharge port 14, a discharge passage 15, a communication passage 16, a positioning hole 17 for fitting a positioning pin D, and a fastening bolt (not fixed) when fastened to the engine E. It is provided with a circular hole 18 through which it is shown.
　軸受孔１１は、駆動軸４０を軸線Ｓ回りに回動自在に支持するように形成されている。
　吸入通路１２は、図３に示すように、エンジンＥの導出通路２ａと吸入口１３を接続するように、接合面１０ａにおいて溝状に形成されている。
　吸入口１３は、吸入通路１２及び導出通路２ａに臨むと共に図５において二点鎖線で示す略三ケ月状の輪郭をなすように、接合面１０ａから接合面１０ｂまで貫通して形成されている。
　吐出口１４は、吐出通路１５及び導入通路１ａに臨むと共に図５において二点鎖線で示す略三ケ月状の輪郭をなすように、接合面１０ａから接合面１０ｂまで貫通して形成されている。
　吐出通路１５は、エンジンＥの導入通路１ａと吐出口１４を接続するように、接合面１０ａにおいて溝状に形成されている。
　連通路１６は、ポンプ室ＰＣと吸入通路１２とを連通させる連通路の一部をなすものであり、軸線Ｓと平行に伸長する円筒状に形成されて、接合面１０ｂから接合面１０ａ側の吸入通路１２まで貫通して形成されている。 The bearing hole 11 is formed to support the drive shaft 40 so as to be rotatable about the axis S.
As shown in FIG. 3, the suction passage 12 is formed in a groove shape on the joint surface 10 a so as to connect the outlet passage 2 a of the engine E and the suction port 13.
The suction port 13 is formed so as to penetrate from the joint surface 10a to the joint surface 10b so as to face the suction passage 12 and the lead-out passage 2a and to form a substantially crescent-shaped outline indicated by a two-dot chain line in FIG.
The discharge port 14 is formed to penetrate from the joint surface 10a to the joint surface 10b so as to face the discharge passage 15 and the introduction passage 1a and to form a substantially crescent-shaped outline indicated by a two-dot chain line in FIG.
The discharge passage 15 is formed in a groove shape on the joint surface 10 a so as to connect the introduction passage 1 a of the engine E and the discharge port 14.
The communication path 16 forms a part of the communication path that allows the pump chamber PC and the suction path 12 to communicate with each other. The communication path 16 is formed in a cylindrical shape extending in parallel with the axis S, and is connected to the bonding surface 10a side from the bonding surface 10b. It is formed so as to penetrate to the suction passage 12.
　ロータケース２０は、鋼、鋳鉄、焼結鋼、アルミニウム合金等の材料を用いて、ベース１０の接合面１０ｂに接合される接合面２０ａ及びカバー３０に接合される接合面２０ｂを画定する略環状に形成されている。
　ロータケース２０は、内壁面２１、連通路２２、位置決めピンＤを嵌合させる嵌合孔及びネジＢを捩じ込むネジ孔が同軸上に形成されたネジ孔兼位置決め孔２３、締結ボルトを通す円孔２４を備えている。 The rotor case 20 is made of a material such as steel, cast iron, sintered steel, aluminum alloy or the like, and has a substantially annular shape that defines a joining surface 20a joined to the joining surface 10b of the base 10 and a joining surface 20b joined to the cover 30. Is formed.
The rotor case 20 has an inner wall 21, a communication path 22, a fitting hole for fitting the positioning pin D, and a screw hole / positioning hole 23 in which a screw hole for screwing the screw B is formed on the same axis, and a fastening bolt. A circular hole 24 is provided.
　内壁面２１は、インナーロータ５０の中心線Ｌ１から所定量偏倚した中心線Ｌ２を回転中心としてアウターロータ６０の外周面６３を回動自在に支持するべく、中心線Ｌ２を中心とする円筒面として形成されている。
　連通路２２は、ポンプ室ＰＣと吸入通路１２とを連通させる連通路の一部をなすものであり、軸線Ｓと平行に伸長すると共に連通路１６と同軸上において円筒状に形成されて、接合面２０ｂから接合面２０ａまで貫通して形成されている。 The inner wall surface 21 is a cylindrical surface centered on the center line L2 so as to rotatably support the outer peripheral surface 63 of the outer rotor 60 about the center line L2 deviated from the center line L1 of the inner rotor 50 by a predetermined amount. Is formed.
The communication path 22 forms a part of the communication path that allows the pump chamber PC and the suction path 12 to communicate with each other. The communication path 22 extends in parallel with the axis S and is formed in a cylindrical shape coaxially with the communication path 16. It is formed so as to penetrate from the surface 20b to the joint surface 20a.
　カバー３０は、鋼、鋳鉄、焼結鋼、アルミニウム合金等の材料を用いて、ロータケース２０の接合面２０ｂに接合される接合面３０ａ、外側面３０ｂ、外側面３０ｂにおいて畝状に突出する突出部３０ｃを画定する略平板状に形成されている。
　接合面３０ａは、インナーロータ５０の側面５２及びアウターロータ６０の側面６２が摺動する壁面としても機能する。 The cover 30 is made of a material such as steel, cast iron, sintered steel, or aluminum alloy, and protrudes like a bowl on the joint surface 30a, the outer surface 30b, and the outer surface 30b that are joined to the joint surface 20b of the rotor case 20. It is formed in a substantially flat plate shape that defines the portion 30c.
The joint surface 30a also functions as a wall surface on which the side surface 52 of the inner rotor 50 and the side surface 62 of the outer rotor 60 slide.
　カバー３０は、開口部３１、連通路３２（３２ａ，３２ｂ，３２ｃ）、連通路３２の途中に形成された嵌合凹部３３、ネジＢを通す円孔３４、締結ボルトを通す円孔３５を備えている。
　開口部３１は、図３及び図５に示すように、インナーロータ５０及びアウターロータ６０により画定されるポンプ室ＰＣに向けて連通路３２の一部をなす連通路３２ａを開口させるように接合面３０ａに形成されている。 The cover 30 includes an opening 31, a communication path 32 (32 a, 32 b, 32 c), a fitting recess 33 formed in the middle of the communication path 32, a circular hole 34 for passing a screw B, and a circular hole 35 for passing a fastening bolt. ing.
As shown in FIGS. 3 and 5, the opening 31 is a joint surface so as to open a communication path 32 a that forms a part of the communication path 32 toward the pump chamber PC defined by the inner rotor 50 and the outer rotor 60. 30a.
　具体的には、開口部３１は、図７ないし図１７に示すように、回転方向において、吸入口１３及び吐出口１４から外れた接合面３０ａの領域において、ポンプ室ＰＣに開口するように形成されている。
　そして、開口部３１は、図１１ないし図１４に示すように、インナーロータ５０が所定の回転角度領域にあるとき、インナーロータ５０の側面５２から開放される位置に配置されている。
　また、開口部３１は、図１５に示すようにポンプ室ＰＣによる吐出作用の途中からインナーロータ５０の側面５２により閉塞され始め、図１６及び図１７に示すように吐出作用中のポンプ室ＰＣから遮断される位置、すなわち、図１５ないし図１７に示すように、インナーロータ５０が所定の回転角度領域にあるとき、インナーロータ５０の側面５２により閉塞される位置に配置されている。
　尚、開口部３１は、吸入口１３及び吐出口１４から外れた領域でポンプ室ＰＣに開口する領域であれば、要求特性に応じて、吸入口１３側寄りの位置あるいは吐出口１４側よりの位置に配置されてもよい。 Specifically, as shown in FIGS. 7 to 17, the opening 31 is formed so as to open to the pump chamber PC in the region of the joint surface 30 a removed from the suction port 13 and the discharge port 14 in the rotational direction. Has been.
As shown in FIGS. 11 to 14, the opening 31 is disposed at a position that is opened from the side surface 52 of the inner rotor 50 when the inner rotor 50 is in a predetermined rotation angle region.
Further, the opening 31 starts to be blocked by the side surface 52 of the inner rotor 50 in the middle of the discharge action by the pump chamber PC as shown in FIG. 15, and from the pump chamber PC during the discharge action as shown in FIGS. As shown in FIGS. 15 to 17, the position where the inner rotor 50 is located is blocked by the side surface 52 of the inner rotor 50 when the inner rotor 50 is in a predetermined rotation angle region.
In addition, if the opening part 31 is an area | region which opens to the pump chamber PC in the area | region which remove | deviated from the suction inlet 13 and the discharge outlet 14, depending on a required characteristic, the position near the suction inlet 13 side or the discharge outlet 14 side. It may be arranged in a position.
　上記のような位置に開口部３１が配置されることにより、流量制御弁７０を適宜制御することで、ポンプ室ＰＣに吸入されたオイルが吐出される前に、ポンプ室ＰＣ内のオイルを開口部３１及び連通路３２，２２，１６を介して吸入通路１２に効率良く戻すことができる。それ故に、余剰なオイルが吐出されるのを防止でき、無駄な駆動力の損失を低減できる。 By arranging the opening 31 at the position as described above, the oil in the pump chamber PC is opened before the oil sucked into the pump chamber PC is discharged by appropriately controlling the flow rate control valve 70. It is possible to efficiently return to the suction passage 12 via the portion 31 and the communication passages 32, 22, 16. Therefore, it is possible to prevent excessive oil from being discharged, and it is possible to reduce loss of useless driving force.
　特に、開口部３１は、図１３に示すように、ポンプ室ＰＣが吸入作用を完了しかつ吐出作用を開始する直前の状態にある仕切り領域において、ポンプ室ＰＣの仕切り領域を画定する角度領域の略中間の角度位置に配置されてもよい。
　ここで、仕切り領域とは、図１３に示すように、ハウジングＨの接合面１０ｂ，３０ａ及びインナーロータ５０の外周壁面及びアウターロータ６０の内周壁面により、ポンプ室ＰＣが吸入口１３及び吐出口１４から仕切られて遮断された状態にある領域（幾何学的な仕切り区間）を意味するものである。
　上記のような位置に開口部３１が配置されることにより、仮に流量制御弁７０が作動不良になり開弁状態にて停止した場合でも、閉弁状態の吐出量を１００％としたとき、約６０％以上の吐出量を確保することができる。
　尚、開口部３１の形状としては、円形孔を示したが、これに限定されるものではなく、連通路３２をポンプ室ＰＣに開口させる形状であれば、それ以外の形状及び形態を採用することができる。 In particular, as shown in FIG. 13, the opening 31 has an angular region that defines the partition region of the pump chamber PC in the partition region immediately before the pump chamber PC completes the suction action and starts the discharge action. It may be arranged at a substantially intermediate angular position.
Here, as shown in FIG. 13, the partition region means that the pump chamber PC is connected to the suction port 13 and the discharge port by the joint surfaces 10 b and 30 a of the housing H, the outer peripheral wall surface of the inner rotor 50, and the inner peripheral wall surface of the outer rotor 60. 14 is a region (geometric partition section) that is in a state of being partitioned from 14 and blocked.
By arranging the opening 31 at the position as described above, even if the flow rate control valve 70 malfunctions and stops in the open state, when the discharge amount in the closed state is 100%, A discharge amount of 60% or more can be secured.
In addition, although the circular hole was shown as a shape of the opening part 31, as long as it is a shape which opens the communicating path 32 to the pump chamber PC, it is not limited to this, Other shapes and forms are employ | adopted. be able to.
　連通路３２は、ポンプ室ＰＣと吸入通路１２とを連通させる連通路の一部をなすものであり、図３に示すように、連通路３２ａ、連通路３２ｂ、連通路３２ｃにより構成されている。
　連通路３２ａは、接合面３０ａから突出部３０ｃに向けて軸線Ｓに平行に伸長する円筒状に形成されている。
　連通路３２ｂは、突出部３０ｃにおいて、軸線Ｓに垂直に伸長する円筒状に形成されている。
　連通路３２ｃは、突出部３０ｃから接合面３０ａに向けて軸線Ｓに平行に伸長すると共に連通路２２，１６と同軸上において円筒状に形成されている。 The communication path 32 forms part of a communication path that allows the pump chamber PC and the suction path 12 to communicate with each other, and as shown in FIG. 3, the communication path 32 includes a communication path 32a, a communication path 32b, and a communication path 32c. .
The communication path 32a is formed in a cylindrical shape that extends parallel to the axis S from the joint surface 30a toward the protrusion 30c.
The communication path 32b is formed in a cylindrical shape that extends perpendicular to the axis S in the protrusion 30c.
The communication path 32c extends in parallel with the axis S from the protrusion 30c toward the joint surface 30a and is formed in a cylindrical shape coaxially with the communication paths 22 and 16.
　嵌合凹部３３は、流量制御弁７０を嵌合して固定するものであり、突出部３０ｃにおいて、連通路３２ｂと連通路３２ｃの交差領域に形成されている。
　そして、流量制御弁７０の嵌合凸部７２が嵌合凹部３３に嵌合されることにより、連通路３２は、弁体７６の動作に応じて全閉～全開の範囲で、通路面積が調整されるようになっている。 The fitting recess 33 is for fitting and fixing the flow control valve 70, and is formed in the projecting portion 30c at the intersection region of the communication path 32b and the communication path 32c.
Then, by fitting the fitting convex portion 72 of the flow control valve 70 into the fitting concave portion 33, the passage area of the communication passage 32 is adjusted in a range from fully closed to fully open according to the operation of the valve body 76. It has come to be.
　上記のように、ハウジングＨが、ベース１０、ロータケース２０、カバー３０により構成され、ベース１０に対して、吸入通路１２、吸入口１３、吐出口１４、吐出通路１５が設けられるため、ロータケース２０に連通路２２、カバー３０に連通路３２及び流量制御弁７０を取り付ける嵌合凹部３３を設けるような簡単な構造にすることができる。 As described above, the housing H includes the base 10, the rotor case 20, and the cover 30, and the suction passage 12, the suction port 13, the discharge port 14, and the discharge passage 15 are provided to the base 10. A simple structure in which the communication passage 22 is provided in 20 and the fitting recess 33 for attaching the communication passage 32 and the flow control valve 70 to the cover 30 is provided.
　また、上記ハウジングＨにおいては、カバー３０の連通路３２、ロータケース２０の連通路２２、ベース１０の連通路１６により、ポンプ室ＰＣと吸入通路１２とを連通させる連通路が形成されている。
　このように、連通路を別々の部材、すなわち、ベース１０、ロータケース２０、及びカバー３０に分けて形成したことにより、それぞれの連通路１６，２２，３２ａ，３２ｂ，３２ｃのドリル加工等を容易に行うことができる。 In the housing H, a communication path that connects the pump chamber PC and the suction path 12 is formed by the communication path 32 of the cover 30, the communication path 22 of the rotor case 20, and the communication path 16 of the base 10.
As described above, the communication passages are divided into separate members, that is, the base 10, the rotor case 20, and the cover 30, so that drilling of the communication passages 16, 22, 32 a, 32 b, and 32 c is easy. Can be done.
　駆動軸４０は、鋼等を用いて軸線Ｓ方向に伸長して形成され、エンジンＥからの駆動力が伝達される連結部４１、インナーロータ５０の嵌合孔５３に嵌合される嵌合部４２、嵌合部４２に設けられて回り止めピンＦが嵌合される貫通孔４３を備えている。 The drive shaft 40 is formed by extending in the axis S direction using steel or the like, and is a fitting portion that is fitted into the coupling portion 41 to which the driving force from the engine E is transmitted and the fitting hole 53 of the inner rotor 50. 42, a through hole 43 provided in the fitting portion 42 and fitted with the detent pin F is provided.
　インナーロータ５０は、鋼又は焼結鋼等の材料を用いて、ベース１０の接合面１０ｂを摺動する側面５１、カバー３０の接合面３０ａを摺動する側面５２を画定する略星形状に形成されている。
　インナーロータ５０は、嵌合孔５３、ピン溝５４、４つの凸部（山）５５及び４つの凹部（谷）５６を備え、トロコイド曲線による歯形をもつ外歯車として形成されている。 The inner rotor 50 is formed in a substantially star shape that defines a side surface 51 that slides on the joint surface 10b of the base 10 and a side surface 52 that slides on the joint surface 30a of the cover 30 using a material such as steel or sintered steel. Has been.
The inner rotor 50 includes a fitting hole 53, a pin groove 54, four convex portions (ridges) 55, and four concave portions (valleys) 56, and is formed as an external gear having a tooth shape with a trochoidal curve.
　嵌合孔５３は、駆動軸４０の嵌合部４２が嵌合されるように形成されている。
　ピン溝５４は、駆動軸４０の貫通孔４３に挿入された回り止めピンＦの両側部分を嵌め込むように形成されている。
　そして、インナーロータ５０は、軸線Ｓと同軸上の中心線Ｌ１を回転中心として、駆動軸４０と一体的に図５において反時計回りに回転する。 The fitting hole 53 is formed so that the fitting portion 42 of the drive shaft 40 is fitted.
The pin groove 54 is formed so as to fit both side portions of the detent pin F inserted into the through hole 43 of the drive shaft 40.
The inner rotor 50 rotates integrally with the drive shaft 40 in the counterclockwise direction in FIG. 5 with the center line L1 coaxial with the axis S as the center of rotation.
　アウターロータ６０は、鋼又は焼結鋼等の材料を用いて、ベース１０の接合面１０ｂを摺動する側面６１、カバー３０の接合面３０ａを摺動する側面６２を画定する円環状に形成されている。
　アウターロータ６０は、中心線Ｌ２を中心とする円形の外周面６３、５つの凸部６４及び５つの凹部６５を備え、インナーロータ５０に噛合し得る歯形をもつ内歯車として形成されている。 The outer rotor 60 is formed in an annular shape that defines a side surface 61 that slides on the joint surface 10b of the base 10 and a side surface 62 that slides on the joint surface 30a of the cover 30 using a material such as steel or sintered steel. ing.
The outer rotor 60 includes a circular outer peripheral surface 63 centering on the center line L2, five convex portions 64, and five concave portions 65, and is formed as an internal gear having a tooth shape that can mesh with the inner rotor 50.
　外周面６３は、ロータケース２０の内壁面２１に接触して回動自在に支持されるように形成されている。
　５つの凸部６４及び５つの凹部６５は、インナーロータ５０の４つの凸部５５及び４つの凹部５６と部分的に噛み合うように形成されている。 The outer peripheral surface 63 is formed so as to be rotatably supported in contact with the inner wall surface 21 of the rotor case 20.
The five convex portions 64 and the five concave portions 65 are formed so as to partially mesh with the four convex portions 55 and the four concave portions 56 of the inner rotor 50.
　そして、アウターロータ６０は、中心線Ｌ１を回転中心として回転するインナーロータ５０の回転に連動しつつ、インナーロータ５０よりも遅い速度で、中心線Ｌ２を回転中心として、図５において反時計回りに回転する。
　また、インナーロータ５０とアウターロータ６０とが部分的に噛合うことにより、両者の間において、吸入、加圧及び吐出作用を連続的に及ぼすポンプ室ＰＣが画定されるようになっている。 The outer rotor 60 rotates counterclockwise in FIG. 5 with the center line L2 as the rotation center at a slower speed than the inner rotor 50 while interlocking with the rotation of the inner rotor 50 rotating about the center line L1. Rotate.
Further, when the inner rotor 50 and the outer rotor 60 are partially meshed with each other, a pump chamber PC that continuously exerts suction, pressurization, and discharge actions is defined between them.
　流量制御弁７０は、図３に示すように、ケース７１、ケース７１に連続する嵌合凸部７２、励磁用のコイル７３、鉄芯７４、鉄芯７４に連結されたロッド７５、ロッド７５に連結された弁体７６、弁体７６を閉弁方向に付勢するスプリング７７を備えている。 As shown in FIG. 3, the flow control valve 70 includes a case 71, a fitting convex portion 72 continuous with the case 71, an exciting coil 73, an iron core 74, a rod 75 connected to the iron core 74, and a rod 75. The connected valve body 76 and a spring 77 that biases the valve body 76 in the valve closing direction are provided.
　ケース７１は、磁性金属材料等により全体を覆う円筒状に形成されている。
　嵌合凸部７２は、ケース７１よりも縮径して円筒状に形成され、カバー３０の嵌合凹部３３に堅固に嵌め込まれるようになっている。
　また、嵌合凸部７２は、その内部において弁体７６が着座する弁座７２ａ、外周面において連通路３２ｂと通じる開口部７２ｂ、端面において連通路３２ｃと通じる開口部７２ｃを備えている。 The case 71 is formed in a cylindrical shape covering the whole with a magnetic metal material or the like.
The fitting convex portion 72 is formed in a cylindrical shape with a diameter smaller than that of the case 71, and is firmly fitted into the fitting concave portion 33 of the cover 30.
The fitting projection 72 includes a valve seat 72a in which the valve element 76 is seated, an opening 72b communicating with the communication passage 32b on the outer peripheral surface, and an opening 72c communicating with the communication passage 32c on the end surface.
　上記構成をなす流量制御弁７０は、励磁用のコイル７３の起磁力を駆動源として鉄芯７４を作動させる電磁弁である。
　そして、流量制御弁７０は、コイル７３の通電を適宜制御することにより、以下のように作動する。
　すなわち、コイル７３が非通電の状態においては、スプリング７７の付勢力により、弁体７６が、弁座７２ａに着座して連通路３２ｂ，３２ｃを遮断する。
　一方、コイル７３が適宜通電される状態においては、スプリング７７の付勢力に抗して、弁体７６が、弁座７２ａから離れて連通路３２ｂ，３２ｃを開放する。 The flow control valve 70 configured as described above is an electromagnetic valve that operates the iron core 74 using the magnetomotive force of the exciting coil 73 as a drive source.
The flow control valve 70 operates as follows by appropriately controlling the energization of the coil 73.
That is, when the coil 73 is not energized, the urging force of the spring 77 causes the valve body 76 to be seated on the valve seat 72a and shut off the communication passages 32b and 32c.
On the other hand, in a state where the coil 73 is appropriately energized, the valve element 76 separates from the valve seat 72a and opens the communication passages 32b and 32c against the urging force of the spring 77.
　そして、コイル７３の通電電流の大きさを適宜制御することにより、弁体７６のリフト量が適宜調整されて、連通路３２を流れるオイルの流量が調整されるようになっている。
　流量制御弁７０は、コイル７３の非通電の状態において連通路３２を全閉する閉弁状態に設定されたノーマルクローズの電磁弁であるため、仮に通電不良になっても閉弁状態が維持され、要求される最大吐出量を満たすことができる。
　尚、流量制御弁としては、通電不良の場合に開弁状態が維持されるノーマルオープンの電磁弁を採用してもよい。 Then, by appropriately controlling the magnitude of the energization current of the coil 73, the lift amount of the valve body 76 is appropriately adjusted, and the flow rate of oil flowing through the communication passage 32 is adjusted.
Since the flow control valve 70 is a normally closed electromagnetic valve that is set to a closed state that fully closes the communication path 32 when the coil 73 is not energized, the closed state is maintained even if energization failure occurs. The required maximum discharge amount can be satisfied.
As the flow rate control valve, a normally open solenoid valve that maintains a valve open state in the case of poor energization may be employed.
　流量制御弁７０の取付け手法は、嵌合凸部７２を嵌合凹部３３に堅固に嵌合して固定する手法に限らず、ケース７１に設けられたフランジ等をカバー３０にネジで固定する手法、その他の手法を採用することができる。
　また、流量制御弁７０の取付け方向は、カバー３０から軸線Ｓ方向に突出する方向に限らず、レイアウトの制約を満たすように、連通路３２の経路と一緒に変更することができる。 The attachment method of the flow rate control valve 70 is not limited to the method of firmly fitting and fixing the fitting convex portion 72 to the fitting concave portion 33, and the method of fixing the flange or the like provided in the case 71 to the cover 30 with screws. Other techniques can be employed.
Further, the mounting direction of the flow control valve 70 is not limited to the direction protruding from the cover 30 in the direction of the axis S, but can be changed together with the path of the communication path 32 so as to satisfy the layout constraint.
　上記構成をなす可変容量型ポンプＶＰの組付け作業について説明する。
　先ず、ベース１０、ロータケース２０、カバー３０、駆動軸４０、インナーロータ５０、アウターロータ６０、流量制御弁７０、３つのネジＢ、３つの位置決めピンＤ、一つの回り止めピンＦが準備される。
　続いて、位置決めピンＤを位置決め孔１７及びネジ孔兼位置決め孔２３に圧入しつつ、ベース１０にロータケース２０が接合される。 The assembly work of the variable displacement pump VP having the above configuration will be described.
First, a base 10, a rotor case 20, a cover 30, a drive shaft 40, an inner rotor 50, an outer rotor 60, a flow control valve 70, three screws B, three positioning pins D, and one detent pin F are prepared. .
Subsequently, the rotor case 20 is joined to the base 10 while the positioning pins D are press-fitted into the positioning holes 17 and the screw holes / positioning holes 23.
　続いて、インナーロータ５０及びアウターロータ６０がロータケース２０の内側に嵌め込まれる。
　続いて、駆動軸４０の貫通孔４３に回り止めピンＦが挿入され、駆動軸４０が嵌合孔５３及び軸受孔１１に通されつつ、嵌合部４２が嵌合孔５３に嵌め込まれる共に回り止めピンＦがピン溝５４に嵌め込まれる。
　これにより、駆動軸４０がインナーロータ５０と一体的に回転する状態となる。
　尚、駆動軸４０の連結部４１が軸径よりも大きい場合は、駆動軸４０がベース１０の接合面１０ａ側から挿入され、その後、回り止めピンＦが挿入される手順でもよい。 Subsequently, the inner rotor 50 and the outer rotor 60 are fitted inside the rotor case 20.
Subsequently, the rotation prevention pin F is inserted into the through hole 43 of the drive shaft 40, and the fitting portion 42 is fitted into the fitting hole 53 while the driving shaft 40 is passed through the fitting hole 53 and the bearing hole 11. The stop pin F is fitted into the pin groove 54.
As a result, the drive shaft 40 is rotated integrally with the inner rotor 50.
In addition, when the connection part 41 of the drive shaft 40 is larger than a shaft diameter, the procedure in which the drive shaft 40 is inserted from the joint surface 10a side of the base 10 and then the detent pin F is inserted may be used.
　最後に、カバー３０をロータケース２０の接合面２０ｂに接合して、３つのネジＢを円孔３４に通しつつネジ孔兼位置決め孔２４に捩じ込む。
　そして、カバー３０の嵌合凹部３３に対して、流量制御弁７０が嵌め込まれて固定される。以上により、可変容量型ポンプＶＰの組付けが完了する。
　尚、上記の組付け手順は、一例であって、他の手順を採用することもできる。 Finally, the cover 30 is joined to the joint surface 20 b of the rotor case 20, and the three screws B are screwed into the screw hole / positioning hole 24 while passing through the circular hole 34.
Then, the flow control valve 70 is fitted into the fitting recess 33 of the cover 30 and fixed. Thus, the assembly of the variable displacement pump VP is completed.
The above assembling procedure is an example, and other procedures can be adopted.
　また、可変容量型ポンプＶＰを適用対象物としてのエンジンＥに取り付ける場合は、駆動軸４０の連結部４１をエンジンＥの回転駆動部に連結しつつ、ベース１０の接合面１０ａをエンジンＥの取付け接合面に当接させる。
　その後、締結ボルトを円孔３５，２４，１８に通しつつ、エンジンＥのネジ穴に捩じ込むことにより、その取付け作業が完了する。 Further, when the variable displacement pump VP is attached to the engine E as an application object, the joint surface 10a of the base 10 is attached to the engine E while the connecting portion 41 of the drive shaft 40 is connected to the rotational drive portion of the engine E. Contact the joint surface.
Thereafter, the fastening bolt is passed through the circular holes 35, 24, and 18 and screwed into the screw holes of the engine E, whereby the mounting operation is completed.
　上記構成をなす可変容量型ポンプＶＰは、車両のエンジンＥに搭載された状態において、図６に示すような制御システムにより駆動制御される。
　制御システムは、制御手段としての制御ユニット１００、全体の制御を司るべく車両に搭載されたＥＣＵ１１０、バッテリ１２０、検出回路１３０を備えている。 The variable displacement pump VP having the above configuration is driven and controlled by a control system as shown in FIG.
The control system includes a control unit 100 as control means, an ECU 110 mounted on a vehicle to control the entire system, a battery 120, and a detection circuit 130.
　制御ユニット１００は、制御を司るマイコン１０１、マイコン１０１の制御信号に基づいて流量制御弁７０を駆動する駆動回路１０２、マイコン１０１とＥＣＵ１１０との間で通信により信号の送受信を行うＩ／Ｆ（インターフェース）回路１０３、マイコン１０１に電源を導く電源回路１０４を備えている。 The control unit 100 includes a microcomputer 101 that performs control, a drive circuit 102 that drives a flow control valve 70 based on a control signal of the microcomputer 101, and an I / F (interface) that transmits and receives signals between the microcomputer 101 and the ECU 110 by communication. ) A circuit 103 and a power supply circuit 104 for guiding the power supply to the microcomputer 101 are provided.
　マイコン１０１は、検出回路１３０の検出情報、例えば、油圧、油温、エンジン回転数等に基づいて、流量制御弁７０の開閉動作を制御するべく、コイル７３の通電電流の大きさ等を適宜算出するようになっている。 The microcomputer 101 appropriately calculates the magnitude of the energization current of the coil 73 in order to control the opening / closing operation of the flow control valve 70 based on detection information of the detection circuit 130, for example, oil pressure, oil temperature, engine speed, and the like. It is supposed to be.
　検出回路１３０は、油圧センサＥ１、油温センサＥ２、エンジン回転センサＥ３等の出力信号に基づいて、潤滑領域等のオイルの圧力及び温度、エンジンＥの回転数等を検出するものである。
　そして、検出回路１３０により、種々の情報が検出されると、ＥＣＵ１１０を介して、制御ユニット１００により、流量制御弁７０が適宜駆動制御されるようになっている。
　すなわち、制御ユニット１００は、エンジンＥ内のオイル又はエンジンＥの運転状態に係る情報に基づいて、流量制御弁７０を駆動制御するようになっている。 The detection circuit 130 detects the pressure and temperature of oil in the lubrication region, the rotation speed of the engine E, and the like based on output signals from the hydraulic sensor E1, the oil temperature sensor E2, the engine rotation sensor E3, and the like.
When various information is detected by the detection circuit 130, the flow control valve 70 is appropriately driven and controlled by the control unit 100 via the ECU 110.
That is, the control unit 100 controls the drive of the flow control valve 70 based on the oil in the engine E or information related to the operating state of the engine E.
　ここでは、オイルに係る情報として、油圧、油温を示したが、これに限定されるものではなく、オイルの粘度、オイルの汚れ状態等も情報として適用することができる。
　また、エンジンＥの運転状態に係る情報として、エンジン回転数を示したが、これに限定されるものではなく、スロットル開度、冷却水温度、その他の運転状態を特定する情報を適用することができる。 Here, the oil pressure and the oil temperature are shown as the information related to the oil, but the present invention is not limited to this, and the viscosity of the oil, the dirt state of the oil, and the like can be applied as the information.
Moreover, although the engine speed is shown as information related to the operating state of the engine E, the present invention is not limited to this, and it is possible to apply information specifying the throttle opening, the coolant temperature, and other operating states. it can.
　次に、可変容量型ポンプＶＰの動作について、図７ないし図１７を参照しつつ説明する。尚、図７～図１７は、駆動軸４０が反時計回りに１５度毎に回転した時の時系列ごとの動作状態を示す。
　ここでは、インナーロータ５０の一つの凸部５５（黒丸印を付したもの）の回転方向Ｒにおける前側に着目して説明する。 Next, the operation of the variable displacement pump VP will be described with reference to FIGS. FIGS. 7 to 17 show time-series operation states when the drive shaft 40 rotates counterclockwise every 15 degrees.
Here, a description will be given focusing on the front side in the rotation direction R of one convex portion 55 (with a black circle mark) of the inner rotor 50.
　駆動軸４０が、図７に示す位置まで回転したとき、凸部５５の前側では、吸入口１３からポンプ室ＰＣにオイルが吸入される途中状態にある（吸入行程）。
　続いて、駆動軸４０が、図８ないし図１０に示す吸入行程の状態を経て、４５度反時計回りに回転すると、図１１に示す位置において、凸部５５の前側では、吸入口１３からポンプ室ＰＣへのオイルの吸入作用（吸入行程）が維持されると共に、開口部３１がインナーロータ５０の側面５２から開放された状態になる。
　この状態において、流量制御弁７０が開弁駆動されると、開口部３１及び連通路３２，２２，１６を介して、ポンプ室ＰＣと吸入通路１２を連通させることができる。 When the drive shaft 40 is rotated to the position shown in FIG. 7, the front side of the convex portion 55 is in a state where oil is sucked into the pump chamber PC from the suction port 13 (suction stroke).
Subsequently, when the drive shaft 40 rotates 45 degrees counterclockwise through the state of the suction stroke shown in FIGS. 8 to 10, the pump shaft 40 extends from the suction port 13 to the front side of the convex portion 55 at the position shown in FIG. 11. The oil suction action (suction stroke) to the chamber PC is maintained, and the opening 31 is opened from the side surface 52 of the inner rotor 50.
In this state, when the flow control valve 70 is driven to open, the pump chamber PC and the suction passage 12 can be communicated with each other via the opening 31 and the communication passages 32, 22, and 16.
　続いて、駆動軸４０が、１５度反時計回りに回転すると、図１２に示す位置において、凸部５５の前側では、吸入口１３からポンプ室ＰＣへのオイルの吸入作用が完了する直前の状態になり、又、開口部３１が側面５２から開放された状態が維持されている。
　この状態でも同様に、流量制御弁７０が開弁駆動されると、開口部３１及び連通路３２，２２，１６を介して、ポンプ室ＰＣと吸入通路１２とを連通させることができる。 Subsequently, when the drive shaft 40 rotates counterclockwise by 15 degrees, the state immediately before the oil suction operation from the suction port 13 to the pump chamber PC is completed at the position shown in FIG. In addition, the state where the opening 31 is opened from the side surface 52 is maintained.
Similarly, in this state, when the flow control valve 70 is driven to open, the pump chamber PC and the suction passage 12 can be communicated with each other via the opening 31 and the communication passages 32, 22, and 16.
　続いて、駆動軸４０が、１５度反時計回りに回転すると、図１３に示す位置において、凸部５５の前側では、吸入口１３からポンプ室ＰＣ内へのオイルの吸入作用が完了した状態になり、開口部３１が側面５２から開放された状態が維持されており、又、ポンプ室ＰＣから吐出口１４へ向けてオイルの加圧及び吐出作用、すなわち、加圧及び吐出行程が開始される直前の状態になる。
　このとき、開口部３１は、ポンプ室ＰＣの回転方向Ｒにおける略中間位置に位置した状態となる。
　この状態でも同様に、流量制御弁７０が開弁駆動されると、開口部３１及び連通路３２，２２，１６を介して、ポンプ室ＰＣと吸入通路１２とを連通させることができる。 Subsequently, when the drive shaft 40 rotates counterclockwise by 15 degrees, at the position shown in FIG. 13, the suction of oil from the suction port 13 into the pump chamber PC is completed on the front side of the convex portion 55. Thus, the state in which the opening 31 is opened from the side surface 52 is maintained, and the pressurization and discharge action of oil from the pump chamber PC toward the discharge port 14, that is, the pressurization and discharge stroke, is started. It will be in the previous state.
At this time, the opening 31 is located at a substantially intermediate position in the rotation direction R of the pump chamber PC.
Similarly, in this state, when the flow control valve 70 is driven to open, the pump chamber PC and the suction passage 12 can be communicated with each other via the opening 31 and the communication passages 32, 22, and 16.
　続いて、駆動軸４０が、１５度反時計回りに回転すると、図１４に示す位置において、凸部５５の前側では、ポンプ室ＰＣから吐出口１４に向けてオイルの加圧及び吐出作用が開始され始めた状態になり、又、開口部３１が側面５２から開放された状態が維持されている。
　この状態でも同様に、流量制御弁７０が開弁駆動されると、開口部３１及び連通路３２，２２，１６を介して、ポンプ室ＰＣと吸入通路１２とを連通させることができる。 Subsequently, when the drive shaft 40 rotates counterclockwise by 15 degrees, at the position shown in FIG. 14, on the front side of the convex portion 55, the pressurization and discharge action of oil from the pump chamber PC toward the discharge port 14 starts. In this state, the state where the opening 31 is opened from the side surface 52 is maintained.
Similarly, in this state, when the flow control valve 70 is driven to open, the pump chamber PC and the suction passage 12 can be communicated with each other via the opening 31 and the communication passages 32, 22, and 16.
　続いて、駆動軸４０が、１５度反時計回りに回転すると、図１５に示す位置において、凸部５５の前側では、ポンプ室ＰＣから吐出口１４に向けてオイルの加圧及び吐出作用が維持され、又、開口部３１が側面５２により閉塞され始めた状態になる。
　この状態でも同様に、流量制御弁７０が開弁駆動されると、開口部３１及び連通路３２，２２，１６を介して、ポンプ室ＰＣと吸入通路１２とを連通させることができる。 Subsequently, when the drive shaft 40 rotates counterclockwise by 15 degrees, at the position shown in FIG. 15, the pressurization and discharge action of oil from the pump chamber PC toward the discharge port 14 is maintained on the front side of the convex portion 55. In addition, the opening 31 starts to be blocked by the side surface 52.
Similarly, in this state, when the flow control valve 70 is driven to open, the pump chamber PC and the suction passage 12 can be communicated with each other via the opening 31 and the communication passages 32, 22, and 16.
　続いて、駆動軸４０が、１５度反時計回りに回転すると、図１６に示す位置において、凸部５５の前側では、ポンプ室ＰＣから吐出口１４に向けてオイルの加圧及び吐出作用が維持され、又、開口部３１が側面５２により完全に閉塞された状態になる。
　すなわち、図１５に示す状態から図１６に示す状態に至る過程において、開口部３１は、ポンプ室ＰＣによる加圧及び吐出作用の途中からインナーロータ５０の側面５２により閉塞されて加圧及び吐出作用中のポンプ室ＰＣから遮断された状態となる。
　したがって、開口部３１が完全に閉塞された後は、流量制御弁７０が開弁状態にあっても、ポンプ室ＰＣから吐出口１４に向けてオイルの吐出動作のみが行われる。 Subsequently, when the drive shaft 40 rotates counterclockwise by 15 degrees, the pressurization and discharge action of oil from the pump chamber PC toward the discharge port 14 is maintained on the front side of the convex portion 55 at the position shown in FIG. In addition, the opening 31 is completely closed by the side surface 52.
That is, in the process from the state shown in FIG. 15 to the state shown in FIG. 16, the opening 31 is closed by the side surface 52 of the inner rotor 50 in the middle of the pressurizing and discharging action by the pump chamber PC, and the pressurizing and discharging action. It will be in the state where it was cut off from inside pump room PC.
Therefore, after the opening 31 is completely closed, only the oil discharge operation from the pump chamber PC toward the discharge port 14 is performed even if the flow control valve 70 is in the open state.
　続いて、駆動軸４０が、１５度反時計回りに回転すると、図１７に示す位置において、凸部５５の前側では、ポンプ室ＰＣから吐出口１４に向けてオイルの加圧及び吐出作用が維持され、又、開口部３１が加圧及び吐出作用中のポンプ室ＰＣから遮断された状態が維持されている。
　その後、駆動軸４０が、反時計回りに回転すると、凸部５５の前側では、加圧及び吐出作用が終了して、図７に示す状態に戻る。 Subsequently, when the drive shaft 40 rotates counterclockwise by 15 degrees, at the position shown in FIG. 17, the oil pressurization and discharge action from the pump chamber PC toward the discharge port 14 is maintained on the front side of the convex portion 55. In addition, the state in which the opening 31 is blocked from the pump chamber PC during pressurizing and discharging is maintained.
Thereafter, when the drive shaft 40 rotates counterclockwise, the pressurizing and discharging action is finished on the front side of the convex portion 55, and the state returns to the state shown in FIG.
　ここでは、一つの凸部５５に着目して説明したが、実際には、４つの凸部５５がそれぞれ同様の動作（ポンプ作用）を行う。したがって、駆動軸４０が一回転する間に、４回の吐出動作が行われることになる。 Here, the description has been made by paying attention to one convex portion 55, but actually, the four convex portions 55 each perform the same operation (pump action). Therefore, four discharge operations are performed while the drive shaft 40 makes one rotation.
　上記一連のポンプ作用が行われる過程において、図１１ないし図１５に示すような回転角度領域にあるとき、開口部３１はインナーロータ５２の側面５２から開放された状態にあり、図１６に示す状態の回転角度領域にあるとき、開口部３１はインナーロータ５２の側面５２により閉塞された状態にある。 In the process of performing the series of pump actions, the opening 31 is open from the side surface 52 of the inner rotor 52 when it is in the rotation angle region as shown in FIGS. 11 to 15, and the state shown in FIG. The opening 31 is in a state of being closed by the side surface 52 of the inner rotor 52 when it is in the rotation angle region.
　すなわち、開口部３１が、上記のような配置関係をなす位置に配置されることにより、開口部３１が開放された状態でかつ吸入作用～加圧及び吐出作用の回転角度領域において、流量制御弁７０を適宜開弁制御することにより、ポンプ室ＰＣに充填された吐出される前のオイルを効率良く吸入通路１２に戻すことができる。これにより、余剰のオイルを吐出させるための駆動力の損失を低減できる。
　また、ポンプ室ＰＣ内の圧力が所定レベル以下に低下する運転状態のときは、流量制御弁７０を適宜開弁制御することにより、吸入通路１２から直接的にポンプ室ＰＣにオイルを吸入することができる。これにより、キャビテーションの発生等を抑制ないし防止することができる。 That is, by arranging the opening 31 at a position having the above-described arrangement relationship, the flow rate control valve is in a state where the opening 31 is opened and in the rotation angle region of suction action to pressurization and discharge action. By appropriately opening the valve 70, it is possible to efficiently return the unfilled oil filled in the pump chamber PC to the suction passage 12. Thereby, the loss of the driving force for discharging excess oil can be reduced.
Further, when the pressure in the pump chamber PC is reduced to a predetermined level or less, the flow control valve 70 is appropriately controlled to open the oil, and the oil is directly sucked into the pump chamber PC from the suction passage 12. Can do. Thereby, generation | occurrence | production of a cavitation etc. can be suppressed thru | or prevented.
　すなわち、上記構成をなす可変容量型ポンプＶＰによれば、固定型の吐出性能として設定された吐出量を必要としない使用領域において、流量制御弁７０を適宜開閉制御することにより、吐出前のポンプ室ＰＣに吸入された流体（オイル）を、連通路３２，２２，１６を介して吸入通路１２に戻すことにより、図１８に示すように、吐出圧を下げて駆動負荷を低減することができる。 That is, according to the variable displacement pump VP having the above-described configuration, the flow control valve 70 is appropriately controlled to be opened and closed in a use region where the discharge amount set as the fixed discharge performance is not required, so that the pump before discharge By returning the fluid (oil) sucked into the chamber PC to the suction passage 12 through the communication passages 32, 22, and 16, the discharge pressure can be lowered and the driving load can be reduced as shown in FIG. .
　特に、上記構成をなす可変容量型ポンプＶＰがエンジンＥに適用された場合において、制御ユニット１００により、図１９に示すように、エンジンＥが中速回転の領域にあるとき、流量制御弁７０を所定開度の開弁状態とするべく駆動制御することができる。
　これにより、中速回転領域での余剰量のオイルの吐出を防止でき、その分だけ駆動力の損失を低減できる。
　また、ポンプ室ＰＣ内の圧力が所定レベル以下に低下するような運転状態のときは、制御ユニット１００により、流量制御弁７０を所定開度の開弁状態とする駆動制御を行うことで、ポンプ室ＰＣの負圧を抑制してキャビテーションの発生を抑制ないし防止できる。 In particular, when the variable displacement pump VP having the above configuration is applied to the engine E, the flow rate control valve 70 is set by the control unit 100 when the engine E is in the medium speed rotation region as shown in FIG. The drive can be controlled so that the valve is opened at a predetermined opening.
As a result, discharge of an excessive amount of oil in the medium speed rotation region can be prevented, and loss of driving force can be reduced accordingly.
Further, in an operation state in which the pressure in the pump chamber PC drops below a predetermined level, the control unit 100 performs drive control to open the flow rate control valve 70 with a predetermined opening, thereby It is possible to suppress or prevent the occurrence of cavitation by suppressing the negative pressure of the chamber PC.
　以上述べたように、上記構成をなす可変容量型ポンプＶＰによれば、構造の簡略化、小型化、低コスト化等を達成しつつ、流量制御弁７０を全閉～全開の間で適宜制御することにより、必要に応じた吐出量にて流体を吐出することができる。
　それ故に、余剰量の吐出を防止でき、その分だけ駆動力の損失を低減でき、又、ポンプ室ＰＣの負圧を抑制してキャビテーションの発生を抑制ないし防止できる。 As described above, according to the variable displacement pump VP having the above configuration, the flow control valve 70 is appropriately controlled between fully closed and fully opened while achieving simplification of structure, size reduction, cost reduction, and the like. By doing so, the fluid can be discharged with a discharge amount as required.
Therefore, an excessive amount of discharge can be prevented, and the loss of driving force can be reduced accordingly, and the negative pressure in the pump chamber PC can be suppressed to suppress or prevent the occurrence of cavitation.
　上記実施形態においては、ポンプ室ＰＣを画定するポンプ作用部材として、トロコイド歯形をなすインナーロータ５０及びアウターロータ６０を含むトロコイドポンプを示したが、これに限定されるものではない。
　例えば、インボリュート歯形のインナーロータ及びアウターロータ、あるいはその他の歯形をなすインナーロータ及びアウターロータ等を備えた構成において、本発明を適用してもよい。 In the said embodiment, although the trochoid pump containing the inner rotor 50 and the outer rotor 60 which make a trochoid tooth profile was shown as a pump action member which demarcates the pump chamber PC, it is not limited to this.
For example, the present invention may be applied to a configuration including an inner rotor and an outer rotor having involute teeth, or an inner rotor and an outer rotor having other tooth shapes.
　上記実施形態においては、インナーロータ５０及びアウターロータ６０がトロコイド式の４葉５節からなる構成を示したが、これに限定されるものではなく、その他の個数からなる構成を採用してもよい。 In the above-described embodiment, the inner rotor 50 and the outer rotor 60 are configured with the trochoidal four-leaf five-node, but the present invention is not limited to this, and a configuration with other numbers may be adopted. .
　上記実施形態においては、ポンプとして、トロコイドポンプを示したが、これに限定されるものではなく、吸入、加圧及び吐出作用を及ぼすポンプ室を画定するものであれば、ベーンポンプ、その他の容積型ポンプにおいて、本発明を採用してもよい。 In the above embodiment, a trochoid pump is shown as a pump. However, the present invention is not limited to this, and a vane pump or other positive displacement type may be used as long as it defines a pump chamber that exerts suction, pressurization, and discharge. You may employ | adopt this invention in a pump.
　上記実施形態においては、流量制御弁として、軸線方向に往復動する弁体７６を含む流量制御弁７０を示したが、これに限定されるものではなく、ロータリ式の流量制御弁、あるいはその他の形態をなす流量制御弁を採用してもよい。 In the above embodiment, the flow control valve 70 including the valve body 76 that reciprocates in the axial direction is shown as the flow control valve. However, the flow control valve 70 is not limited to this, and is not limited to this. You may employ | adopt the flow control valve which makes a form.
　上記実施形態においては、ハウジングＨをベース１０及びロータケース２０並びにカバー３０に分離した構成において、本発明を採用した場合を示したが、これに限定されるものではなく、ベースとロータケースを一体型とした構成を採用し、この部分において、ポンプ室と吸入通路とを連通させる連通路、及びポンプ室に連通路を開口させる開口部を設けてもよい。 In the above embodiment, the case where the present invention is adopted in the configuration in which the housing H is separated into the base 10, the rotor case 20, and the cover 30 is shown. However, the present invention is not limited to this. A configuration having a body shape may be adopted, and in this portion, a communication path that allows the pump chamber and the suction path to communicate with each other, and an opening that opens the communication path in the pump chamber may be provided.
　上記実施形態においては、インナーロータ５０の側面５２が開口部３１を閉塞する構成を示したが、これに限定されるものではなく、開口部３１の配置位置によっては、アウターロータ６０の側面６２が開口部３１を閉塞する構成を採用してもよい。 In the above embodiment, the configuration in which the side surface 52 of the inner rotor 50 closes the opening 31 is shown, but the present invention is not limited to this, and the side surface 62 of the outer rotor 60 may vary depending on the position of the opening 31. You may employ | adopt the structure which obstruct | occludes the opening part 31. FIG.
　上記実施形態においては、本発明に係る可変容量型ポンプＶＰを、自動車等に搭載されるエンジンに適用する場合を示したが、これに限定されるものではなく、トランスミッション、その他の潤滑系に適用してもよく、又、オイル以外の流体を用いる装置に適用してもよい。 In the above embodiment, the variable displacement pump VP according to the present invention is applied to an engine mounted on an automobile or the like. However, the present invention is not limited to this and is applied to a transmission and other lubrication systems. Alternatively, the present invention may be applied to an apparatus using a fluid other than oil.
ＶＰ　可変容量型ポンプ
Ｅ　エンジン
Ｈ　ハウジング
１０　ベース（ハウジング）
１０ａ，１０ｂ　接合面（壁面）
１２　吸入通路
１３　吸入口
１４　吐出口
１６　連通路
２２　連通路
３０　カバー（ハウジング）
３０ａ　接合面（壁面）
３１　開口部
３２（３２ａ，３２ｂ，３２ｃ）　連通路
４０　駆動軸
ＰＣ　ポンプ室
５０　インナーロータ
５２　側面
６０　アウターロータ
７０　流量制御弁
１００　制御ユニット（制御手段）
  VP Variable displacement pump E Engine H Housing 10 Base (housing)
10a, 10b Joint surface (wall surface)
12 suction passage 13 suction port 14 discharge port 16 communication path 22 communication path 30 cover (housing)
30a Joint surface (wall surface)
31 Opening 32 (32a, 32b, 32c) Communication passage 40 Drive shaft PC Pump chamber 50 Inner rotor 52 Side surface 60 Outer rotor 70 Flow rate control valve 100 Control unit (control means)

Claims (9)

  1. 　流体を吸入する吸入通路と、
    　前記吸入通路の下流に位置する吸入口と、
    　前記吸入口に導かれた流体に対して、吸入、加圧及び吐出のポンプ作用を及ぼすポンプ室と、
    　前記ポンプ室の下流に位置する吐出口と、
    　前記ポンプ室と前記吸入通路とを連通させるべく、前記吸入口及び吐出口から外れた領域において前記ポンプ室に開口する開口部を有する連通路と、
    　前記連通路を流れる流体の流量を制御する流量制御弁と、
    を含む、可変容量型ポンプ。     A suction passage for sucking fluid;
    A suction port located downstream of the suction passage;
    A pump chamber that exerts suction, pressurization, and discharge pumping action on the fluid guided to the suction port;
    A discharge port located downstream of the pump chamber;
    A communication path having an opening that opens to the pump chamber in a region away from the suction port and the discharge port in order to communicate the pump chamber and the suction passage;
    A flow rate control valve for controlling the flow rate of the fluid flowing through the communication path;
    Including variable displacement pump.
  2. 　前記吸入通路及び連通路を有するハウジングと、
    　前記ポンプ室を画定するべく前記ハウジング内に配置されたインナーロータ及びアウターロータと、を備え、
    　前記流量制御弁は、前記連通路の途中に介在するように前記ハウジングに設けられている、
    ことを特徴とする請求項１に記載の可変容量型ポンプ。     A housing having the suction passage and the communication passage;
    An inner rotor and an outer rotor disposed in the housing to define the pump chamber,
    The flow control valve is provided in the housing so as to be interposed in the middle of the communication path.
    The variable displacement pump according to claim 1.
  3. 　前記ハウジングは、前記インナーロータ及びアウターロータの側面が摺動する壁面において、前記吸入口と、前記吐出口を含む、
    ことを特徴とする請求項２に記載の可変容量型ポンプ。     The housing includes the suction port and the discharge port on a wall surface on which side surfaces of the inner rotor and the outer rotor slide.
    The variable displacement pump according to claim 2, wherein:
  4. 　前記ハウジングは、前記インナーロータ及びアウターロータの側面が摺動する壁面において、前記開口部を有する、
    ことを特徴とする請求項２又は３に記載の可変容量型ポンプ。     The housing has the opening on a wall surface on which side surfaces of the inner rotor and outer rotor slide.
    The variable displacement pump according to claim 2 or 3, wherein
  5. 　前記開口部は、前記インナーロータが所定の回転角度領域にあるとき、前記インナーロータの側面により閉塞される位置に配置されている、
    ことを特徴とする請求項４に記載の可変容量型ポンプ。     The opening is disposed at a position closed by a side surface of the inner rotor when the inner rotor is in a predetermined rotation angle region.
    The variable displacement pump according to claim 4, wherein:
  6. 　前記開口部は、前記ポンプ室による吐出作用の途中から前記インナーロータの側面により閉塞されて前記吐出作用中のポンプ室から遮断される位置に配置されている、
    ことを特徴とする請求項５に記載の可変容量型ポンプ。     The opening is disposed at a position that is blocked by the side surface of the inner rotor from the middle of the discharge operation by the pump chamber and is blocked from the pump chamber during the discharge operation.
    The variable displacement pump according to claim 5.
  7. 　前記開口部は、前記ポンプ室が吸入作用を完了しかつ吐出作用を開始する直前の状態にある仕切り領域を画定する角度範囲において、略中間の角度位置に配置されている、
    ことを特徴とする請求項４又は５に記載の可変容量型ポンプ。     The opening is disposed at a substantially intermediate angular position in an angular range that defines a partition region in a state immediately before the pump chamber completes the suction action and starts the discharge action.
    6. The variable displacement pump according to claim 4 or 5, wherein:
  8. 　前記インナーロータ及びアウターロータは、トロコイド式である、
    ことを特徴とする請求項１ないし７いずれか一つに記載の可変容量型ポンプ。     The inner rotor and outer rotor are trochoidal.
    The variable displacement pump according to any one of claims 1 to 7, wherein the variable displacement pump is provided.
  9. 　流体としてのオイルを供給するべくエンジンに搭載された請求項１ないし８いずれか一つに記載の可変容量型ポンプを制御する制御システムであって、
    　前記エンジン内のオイル又は前記エンジンの運転状態に係る情報に基づいて、前記流量制御弁を駆動制御する制御手段を含む、
    ことを特徴とする制御システム。
          A control system for controlling a variable displacement pump according to any one of claims 1 to 8, wherein the control system is mounted on an engine to supply oil as fluid.
    Control means for driving and controlling the flow rate control valve based on the oil in the engine or information on the operating state of the engine;
    A control system characterized by that.
PCT/JP2018/002133 2017-04-28 2018-01-24 Variable capacity pump and control system WO2018198451A1 (en)

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JP2017-090198 2017-04-28

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20220341419A1 (en) * 2021-04-26 2022-10-27 Mikuni Corporation Pump device

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6123483U (en) * 1984-07-17 1986-02-12 株式会社 山田製作所 Trochoid pump for engine lubrication
JPH08114186A (en) * 1994-08-25 1996-05-07 Aisin Seiki Co Ltd Oil pump device

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6123483U (en) * 1984-07-17 1986-02-12 株式会社 山田製作所 Trochoid pump for engine lubrication
JPH08114186A (en) * 1994-08-25 1996-05-07 Aisin Seiki Co Ltd Oil pump device

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20220341419A1 (en) * 2021-04-26 2022-10-27 Mikuni Corporation Pump device
US11795945B2 (en) * 2021-04-26 2023-10-24 Mikuni Corporation Pump device with air introduction hole that opens into pump chamber at predetermined opening time immediately before suction stroke

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