WO2016163302A1 - Varible capacity oil pump - Google Patents
Varible capacity oil pump Download PDFInfo
- Publication number
- WO2016163302A1 WO2016163302A1 PCT/JP2016/060701 JP2016060701W WO2016163302A1 WO 2016163302 A1 WO2016163302 A1 WO 2016163302A1 JP 2016060701 W JP2016060701 W JP 2016060701W WO 2016163302 A1 WO2016163302 A1 WO 2016163302A1
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- WO
- WIPO (PCT)
- Prior art keywords
- oil
- control
- pressure
- oil chamber
- hydraulic oil
- Prior art date
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Classifications
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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
- F04C14/18—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber
- F04C14/22—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members
- F04C14/223—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members using a movable cam
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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
- F04C14/18—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber
- F04C14/22—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members
- F04C14/223—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members using a movable cam
- F04C14/226—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members using a movable cam by pivoting the cam around an eccentric axis
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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
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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
- F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
- F04C15/0057—Driving elements, brakes, couplings, transmission specially adapted for machines or pumps
- F04C15/008—Prime movers
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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
- F04C2/00—Rotary-piston machines or pumps
- F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C2/34—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
- F04C2/344—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2/00—Rotary-piston machines or pumps
- F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C2/34—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
- F04C2/344—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
- F04C2/3441—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2210/00—Fluid
- F04C2210/20—Fluid liquid, i.e. incompressible
- F04C2210/206—Oil
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2270/00—Control; Monitoring or safety arrangements
- F04C2270/18—Pressure
- F04C2270/185—Controlled or regulated
Definitions
- the present invention relates to a variable displacement oil pump that supplies oil serving as a drive source for, for example, lubrication of a sliding portion of an internal combustion engine and auxiliary equipment of the internal combustion engine.
- the first control oil chamber moves the cam ring in a direction in which the amount of eccentricity is reduced by introducing the hydraulic pressure supplied from the first branch passage branched from the main oil gallery.
- the second control oil chamber moves the cam ring in the direction in which the eccentric amount increases by introducing the hydraulic pressure supplied from the second branch passage branched from the main oil gallery.
- the introduction of hydraulic pressure into the second control oil chamber is controlled on and off by switching operation of an electromagnetic switching valve provided in the second branch passage, whereby the pump discharge pressure is reduced and It is controlled to a two-stage characteristic of high pressure.
- a pilot valve for adjusting the amount of hydraulic oil supplied to or discharged from each control oil chamber and stabilizing the two-stage characteristics is disposed.
- a spool valve slidably accommodated inside is controlled based on a differential pressure between the hydraulic pressure supplied from the main oil gallery and the urging force of a valve spring provided therein.
- the hydraulic pressure is appropriately supplied to or discharged from each control oil chamber according to the control position.
- each control oil chamber and the outside of the pump are connected to each other via a spring housing chamber that houses the valve spring and a drain port that is formed through a peripheral wall of the spring housing chamber. To communicate with each other.
- the conventional oil pump discharges the hydraulic oil in each control chamber via the spring accommodating chamber of the pilot valve.
- the pressure in the spring accommodating chamber rises, and as a result, the internal differential pressure of the pilot valve fluctuates, and the behavior of the spool valve becomes unstable, and the pump discharge pressure is set to a preset hydraulic characteristic. There was a risk of loss of control.
- the present invention has been devised in view of the above-described conventional technical problems, and an object thereof is to provide a variable displacement oil pump capable of improving the control accuracy of the pump discharge pressure with respect to the set hydraulic characteristics.
- the volumes of the plurality of pump chambers are changed by being rotationally driven by the internal combustion engine, and the plurality of pump chambers that discharge the hydraulic oil sucked from the suction portion from the discharge portion are moved.
- a movable member that changes the volume change amount of the pump chamber, and a biasing mechanism that is provided with a set load applied thereto and biases the movable member in a direction in which the volume change amount of the plurality of pump chambers increases;
- a first control oil chamber that causes the movable member to act on the movable member in a direction in which the volume change amount of the plurality of pump chambers is reduced by supplying the hydraulic oil, and the plurality of the plurality of the plurality of pump chambers by supplying the hydraulic oil.
- a second control oil chamber that causes the movable member to exert a force in a direction to increase the volume change amount of the pump chamber, a state in which hydraulic oil is discharged from the second control oil chamber, and a second control oil chamber.
- Introducing hydraulic fluid A switching mechanism formed to be switchable, and a state in which the hydraulic oil in the first control oil chamber is discharged when the switching mechanism is in a state of discharging hydraulic oil from the second control oil chamber;
- the hydraulic oil is introduced into the first control oil chamber in a state where the hydraulic oil whose pressure is lower than the discharge pressure from the discharge portion is introduced, and the hydraulic oil is introduced into the first control oil chamber as the discharge pressure increases.
- the switching mechanism When the pressure in the first control oil chamber is adjusted and the switching mechanism is in a state of introducing hydraulic oil into the second control oil chamber, the discharge from the discharge section to the second control oil chamber A state in which the hydraulic oil whose pressure is lower than the pressure is introduced, and a state in which the introduction of the hydraulic oil to the second control oil chamber via the switching mechanism is blocked and the hydraulic oil in the second control oil chamber is discharged.
- the second control oil chamber A control mechanism that discharges the hydraulic oil and adjusts the pressure in the second control oil chamber to be reduced.
- the control mechanism is controlled by the hydraulic pressure of the hydraulic oil and the biasing force of the biasing member, and the biasing member It is characterized in that hydraulic oil is not guided to the portion where is disposed.
- FIG. 1 shows a variable displacement oil pump and a hydraulic circuit according to this embodiment.
- a variable displacement oil pump 10 is rotated by a rotational driving force transmitted from a crankshaft of an internal combustion engine and stored in an oil pan 01. After being sucked from the suction passage 03 via the strainer 02, the oil which is the working oil is discharged from the discharge passage 04 to the main oil gallery 05 formed in the engine.
- the relief passage 06 branched from the discharge passage 04 is provided with a check ball type relief valve 07 for returning oil into the oil pan 01 when the pump discharge pressure is excessively increased.
- a first oil filter 1 for collecting is provided.
- a bypass passage 08 that bypasses the upstream side and the downstream side of the first oil filter 1 is provided at a predetermined portion of the discharge passage 04 sandwiching the first oil filter 1.
- the bypass passage 08 is opened to allow the upstream side and the downstream side of the bypass passage 08 to communicate with each other.
- a check ball type bypass valve 09 is provided.
- the main oil gallery 05 supplies oil to a sliding portion of the engine, for example, an oil jet that injects cooling oil onto a piston, a variable valve device (valve timing control device), and a crankshaft bearing. Yes. That is, the oil flowing through the main oil gallery 05 is not only used as a lubricating oil for lubricating the components included in the engine, but is also cooled by the drive source of the variable valve operating device and the oil jet. It is also used as an oil.
- a first branch passage 3 is formed in the middle of the main oil gallery 05.
- the first branch passage 3 is provided with the second oil filter 2 in the upstream portion, and further, the second and third branch passages 4 and 5 are further branched from the downstream end portion.
- the second oil filter 2 includes a substantially cylindrical main body 2a press-fitted to the inner peripheral surface of the first branch passage 3, and a bottomed body coupled to one end of the main body 2a.
- the cylindrical metal mesh portion 2b is configured to prevent contamination mixed into the oil from flowing into an electromagnetic switching valve 40 described below.
- first and second oil filters 1 and 2 are each a cartridge type in which the mesh portion is detachable, and can be replaced when clogging or the like occurs.
- the first and second oil filters 1 and 2 may perform oil filtration with filter paper attached in a replaceable manner.
- the second branch passage 4 can communicate with a first control oil chamber 31 (to be described later) of the oil pump 10 through a pilot valve 50 and a first supply / discharge passage 7a which are control mechanisms.
- the third branch passage 5 is connected to the oil pump 10 via an electromagnetic switching valve 40 which is a switching mechanism that is electrically controlled and switched, an intermediate passage 70, the pilot valve 50, and the second supply / discharge passage 7b. It is possible to communicate with a second control oil chamber 32 described later.
- the oil pump 10 is provided at the front end of a cylinder block 35 of an internal combustion engine or the like, and as shown in FIGS. 2 to 4, is formed so that one end side is open and has a pump housing chamber 13 inside.
- a pump body 11 having a shape and a cover member 12 that closes one end opening of the pump body 11, and a housing that is rotatably supported by the housing and penetrates substantially the center of the pump housing chamber 13.
- a drive shaft 14 that is rotatably supported by the cover member 12 and that is driven by the crankshaft of the engine, and is rotatably accommodated in the pump housing chamber 13, and a central portion is coupled to the drive shaft 14.
- a cam ring 17 that is a movable member separating the chamber 20 and the pump ring 11 are accommodated in the pump body 11, and the cam ring 17 is always attached in a direction in which the amount of eccentricity with respect to the rotor 15 (hereinafter simply referred to as "eccentric amount”) increases.
- a cam spring 18 that is a biasing mechanism that biases, and a pair of ring members 19 and 19 that are slidably disposed at both ends on the inner peripheral side of the rotor 15 and that have a smaller diameter than the rotor 15. It is equipped with.
- the drive shaft 14, the rotor 15, and the vanes 16 are pump components.
- the pump body 11 is integrally formed of an aluminum alloy material, and rotatably supports one end portion of the drive shaft 14 at a substantially central position of the bottom surface 13a of the pump housing chamber 13 as shown in FIGS.
- a bearing hole 11a is formed through.
- a pivot pin 24 which is a swing fulcrum for swingably supporting the cam ring 17 is inserted into a predetermined position on the inner peripheral wall of the pump housing chamber 13 which is the inner surface of the pump body 11.
- the support hole 11b to be fixed is notched.
- a holding groove 11e that holds oil and serves to lubricate the drive shaft 14 is formed on the inner peripheral surface of the bearing hole 11a.
- a straight line (hereinafter referred to as “cam ring reference line”) M connecting the center of the bearing hole 11 a and the center of the support hole 11 b is sandwiched between the inner peripheral walls of the pump housing chamber 13.
- first and second seal slidable contact surfaces 11c and 11d which are slidably contacted with two seal members 30 and 30 (to be described later) disposed on the outer periphery of the cam ring 17, respectively.
- each of the seal sliding contact surfaces 11c and 11d is formed in a circular arc shape with predetermined radii R1 and R2 from the center of the support hole 11b.
- the inner volume of the pump chamber 20 is increased on the bottom surface 13 a of the pump housing chamber 13 in the outer peripheral area of the bearing hole 11 a with the pump action of the pump structure.
- a suction port 21 that is a substantially arc-shaped concave suction portion that opens to a region (suction region) that opens, and a region (discharge region) in which the internal volume of the pump chamber 20 decreases with the pump action of the pump component.
- the discharge port 22 which is a substantially arc-shaped discharge part is cut out so as to be substantially opposed to each other across the bearing hole 11a.
- a suction hole 21a having a substantially circular cross section that passes through the bottom wall of the pump body 11 and opens to the outside is formed at a substantially central position of the suction port 21.
- the suction hole 21a is disposed and formed so as to face an outer peripheral side of the suction side including a spring accommodating chamber 28, which will be described later, of the cam ring 17.
- a discharge hole 22 a having a substantially circular cross section that is open to the outside through the bottom wall of the pump body 11 is formed.
- the oil in each pump chamber 20 in the discharge region pressurized by the pump action of the pump structure is supplied to the main oil gallery 05 through the discharge port 22, the discharge hole 22a, and the discharge passage 04. It is supplied to each sliding part in the engine, a variable valve operating device, and the like.
- the cover member 12 has a substantially plate shape, and a position corresponding to the bearing hole 11 a of the pump body 11 on the outer side is formed in a cylindrical shape, and the substantially axial center of the cylindrical portion is formed.
- a bearing hole 12a that rotatably supports the other end of the drive shaft 14 is formed at a position.
- the cover member 12 is attached to the opening end surface of the pump body 11 by a plurality of bolts 26.
- the drive shaft 14 is configured to rotate the rotor 15 in the clockwise direction in FIG. 2 by a rotational force transmitted from a crankshaft (not shown) via a pulley or the like.
- the rotor 15 has a plurality of slits 15a radially formed from the inner center side to the radially outer side, and the discharge port is provided at the inner base end of each slit 15a.
- a back pressure chamber 15b having a substantially circular cross section for introducing the oil discharged to 22 is formed.
- Each vane 16 is pushed outward by the centrifugal force accompanying the rotation of the rotor 15 and the back pressure of the back pressure chamber 15b.
- the pump chamber 20 is liquid-tightly defined by the side surface.
- each ring member 19 has an outer peripheral surface in sliding contact with the inner end surface of the base end portion of each vane 16, and presses each vane 16 outward by centrifugal force. It has become. As a result, even when the engine speed is low and the centrifugal force or the back pressure in the back pressure chamber 15b is small, the outer end surface of each vane 16 is brought into contact with the inner peripheral surface of the cam ring 17. The liquid tightness of the pump chamber 20 can be secured.
- the cam ring 17 is formed integrally with a sintered metal in an annular shape, and as shown in FIG. 2, the cam ring 17 is fitted in the pivot pin 24 at a predetermined position on the outer peripheral portion to form an eccentric rocking fulcrum.
- a pivot portion 17a protrudes along the axial direction, and an arm portion 17b linked to the cam spring 18 is provided at a position opposite to the pivot portion 17a across the center of the cam ring 17 in the radial direction. Protruding along.
- a spring accommodating chamber 28 that communicates with the pump accommodating chamber 13 via a communication portion 27 is provided at a position opposite to the support hole 11 b of the pump body 11, and the spring accommodating chamber 28 includes the spring accommodating chamber 28.
- a distal end portion of the arm portion 17b and the cam spring 18 are accommodated.
- One end of the cam spring 18 is in elastic contact with the substantially arc-shaped support protrusion 17c protruding from the lower surface of the distal end of the arm portion 17b, and the other end is in elastic contact with the bottom surface of the spring accommodating chamber 28.
- the cam ring 17 is always urged through the arm portion 17b in the direction of increasing the eccentric amount (clockwise in FIG. 2) with a spring force (biasing force).
- the cam ring 17 is pressed against the stopper surface 28 a formed on the lower surface of the upper wall of the spring accommodating chamber 28 by the spring force of the cam spring 18. In this state, the eccentric amount is held at the maximum position.
- first and second seals having a substantially triangular cross section having first and second seal surfaces facing the first and second seal sliding contact surfaces 11c and 11d are provided on the outer peripheral portion of the cam ring 17.
- the component parts 17d and 17e are formed to protrude.
- Each of the seal constituting portions 17d and 17e has first and second seal holding grooves each having a substantially arc concave cross section formed on each of the seal surfaces along the axial direction of the cam ring 17.
- a pair of seal members 30, 30 that are in sliding contact with the seal sliding contact surfaces 11c, 11d when the cam ring 17 is eccentrically swung are accommodated and held in the holding grooves.
- the first and second seal surfaces are separated by a predetermined radius slightly smaller than the radii R1 and R2 from the center of the support hole 11b to the seal sliding contact surfaces 11c and 11d, respectively. It is formed in a circular arc shape, and is in sliding contact with each of the seal sliding contact surfaces 11c and 11d with a small clearance.
- each of the seal members 30 and 30 is formed in a rectangular flat plate shape along the axial direction of the cam ring 17 by using, for example, a fluorine-based resin material having low friction characteristics, and the bottom of each seal holding groove. Are pressed against the seal sliding contact surfaces 11c and 11d by the elastic force of a rubber elastic member disposed on the surface. Thereby, the liquid tightness of each control oil chamber 31 and 32 mentioned later is always ensured.
- first and second control oil chambers 31 and 32 are disposed on the pivot portion 17a side of the cam ring 17, that is, on the outer peripheral area on the pump discharge side, so as to sandwich the pivot portion 17a.
- Each of the control oil chambers 31 and 32 has an inner space having a substantially arc-shaped cross section defined by the inner peripheral surface of the pump body 11, the outer peripheral surface of the cam ring 17, and the seal members 30 and 30. Each part is defined by being further divided into two parts in the vertical direction in FIG.
- the upper first control oil chamber 31 in FIG. 2 is the first supply hole 25 a through the first communication hole 25 a formed through the side of the pump body 11.
- the pump discharge pressure that is connected to the exhaust passage 7a and flows through the main oil gallery 05 is appropriately set via the first and second branch passages 3 and 4, the pilot valve 50, and the first communication hole 25a. It comes to be supplied.
- a first pressure receiving surface 33 for receiving the hydraulic pressure supplied into the first control oil chamber 31 is formed on the outer peripheral surface of the cam ring 17 facing the first control oil chamber 31.
- the second control oil chamber 32 is connected to the second supply / discharge passage 7b through a second communication hole 25b formed in a side portion of the pump body 11 in parallel with the first communication hole 25a.
- the pump discharge pressure flowing in the main oil gallery 05 is the first and third branch passages 3 and 5, the electromagnetic switching valve 40, the intermediate passage 70, the pilot valve 50, and the first It is appropriately supplied via the communication hole 25a.
- a second pressure receiving surface 34 is formed on the outer peripheral surface of the cam ring 17 facing the second control oil chamber 32.
- the pressure receiving area of the first pressure receiving surface 33 is set larger than the pressure receiving area of the second pressure receiving surface 34, and is applied based on the internal pressure of the first control oil chamber 31.
- the urging force and the urging force based on the internal pressure of the second control oil chamber 32 and the spring force of the cam spring 18 are balanced with a predetermined force relationship.
- the electromagnetic switching valve 40 is interposed between the third branch passage 5 for supplying hydraulic pressure to the second control oil chamber 32 and the intermediate passage 70.
- the electromagnetic switching valve 40 is a two-port three-position valve, and is transmitted in accordance with the operating state of the engine from a control unit (not shown) that controls the internal combustion engine. Based on the ON / OFF signal, the third branch passage 5 and the intermediate passage 70 are communicated, or the intermediate passage 70 and the drain passage 6 are communicated.
- the electromagnetic switching valve 40 is press-fitted into a valve housing hole 35a drilled from the outside of the cylinder block 35 to the connecting portion between the third branch passage 5 and the intermediate passage 70.
- the valve body 41 is fixed and has an operation hole 41a penetratingly formed along the inner axial direction, and is fitted and fixed to the tip of the valve body 41 (one end portion inside the cylinder block 35) of the operation hole 41a.
- a valve seat 42 formed in the center with a solenoid opening port 42a communicating with the downstream end of the third branch passage 5, and is provided inside and outside the valve seat 42 so as to be separable and openable to open and close the solenoid opening port 42a.
- a solenoid unit 44 coupled to a base end portion (the other end portion) of the valve body 41. That.
- a communication port 45 communicating with the intermediate passage 70 is formed in a radial direction at a side portion position of the ball valve body 43 which is a distal end side of the peripheral wall, while a proximal end portion of the peripheral wall is formed.
- a drain port 46 communicating with the drain passage 6 is formed to penetrate in the radial direction.
- the solenoid unit 44 accommodates and arranges an electromagnetic coil, a fixed plunger, a movable plunger, etc., not shown in the figure, and when a signal is emitted from the control unit to the electromagnetic coil, the movable plunger is moved in the axial direction accordingly. It is designed to move forward and backward.
- a return spring (not shown) is provided for constantly urging the movable plunger in the backward direction.
- one end of a cylindrical rod-shaped push rod 47 accommodated in the operation hole 41 a is coupled to the tip of the movable plunger, and the ball valve body 43 is connected to the valve via the push rod 47. It can be pressed in the direction of the sheet 42.
- a cylindrical passage 48 is formed between the outer peripheral surface of the push rod 47 and the inner peripheral surface of the central portion of the operating hole 41a so as to allow the communication port 45 and the drain port 46 to communicate appropriately.
- the control unit detects the current engine operating state from the oil temperature, water temperature, engine speed, load, etc. of the engine, and particularly when the engine speed is below a predetermined value, an ON signal (energization) is applied to the electromagnetic coil of the solenoid unit 44. When it is higher than a predetermined value, an off signal (non-energized) is output. However, even when the engine speed is below a predetermined value, an off signal is output to the electromagnetic coil when the engine is in a high load range.
- the oil pump 10 selects supply / discharge of the hydraulic pressure in the second control oil chamber 32 in accordance with the switching operation of the electromagnetic switching valve 40 based on the operating state of the engine.
- the pump discharge pressure is controlled based on the hydraulic pressure in the first control oil chamber 31 supplied from the main oil gallery 05 and the biasing force of the cam spring 18.
- there are two types of states a state in which control is performed to a predetermined low pressure P1, and a state in which control is performed to a predetermined high pressure P2 by controlling the amount of eccentricity of the cam ring 17 by adding the hydraulic pressure in the second control oil chamber 32 thereto.
- the discharge pressure characteristic is obtained.
- the set load of the cam spring 18 is set based on these two types of discharge pressure characteristics.
- the cam spring 18 is operated with the hydraulic pressure lower than a predetermined low pressure P1.
- the set load is set so that the operation starts when the pressure becomes equal to or higher than the starting pressure P1 ′.
- the cam spring 18 When the same hydraulic pressure is supplied to the first and second control oil chambers 31 and 32, the cam spring 18 is based on the difference in urging force due to the area difference between the pressure receiving surfaces 33 and 34. In this case, when the hydraulic pressure supplied to the cam springs 31 and 32 becomes equal to or higher than the operation start pressure P2 ′ higher than the predetermined high pressure P2, the cam spring 18 generates a force in a direction against it. Set load is set to start operation.
- the hydraulic pressure at which the cam spring 18 starts operating may fluctuate when the engine speed is high or when bubbles are included in the hydraulic oil, but the operation start pressure P2 ′ is The engine is set so as to be equal to or higher than the desired high pressure P2 in any operating condition of the engine.
- the oil pump 10 is provided with the pilot valve 50.
- the pilot valve 50 includes a cylindrical valve body 51 provided integrally with the outer wall of the pump body 11, and a sliding hole formed in the valve body 51.
- a spool valve 53 slidably accommodated in 52 and a control spring accommodating chamber 54 formed on the other axial end side of the valve body 51 are disposed in the upper direction in the drawing.
- a control spring 55 that is an urging member that urges the valve body 51, and a hook-like press-fit plug 56 that is press-fitted and fixed to the other end opening of the valve body 51 in a state where a spring load of the control spring 55 is applied.
- the sliding hole 52 and the spool valve 53 (first and second land portions 63 and 64 described later) are slightly larger than the outer diameter with reference to the outer diameter of the control spring 55. Each diameter is set.
- an introduction port 57 having a smaller diameter than the sliding hole 52 is formed at an upper end opening located above the sliding hole 52 in FIG.
- the introduction port 57 communicates with the main oil gallery 05 through the first and second branch passages 3 and 4 and the second oil filter 2.
- a stepped taper surface as a seating surface on which the spool valve 53 is seated by being biased upward by the spring force of the control spring 55 at the edge of the sliding hole 52 of the valve body 51 on the introduction port 57 side. 51a is formed.
- a first supply / discharge port 58 which is a first control port communicating with the first control oil chamber 31 via the first supply / discharge passage 7a, is formed on the peripheral wall of the valve body 51 where the sliding hole 52 faces.
- a second supply / discharge port 59 which is a second control port communicating with the second control oil chamber 32 via the second supply / discharge passage 7b, is formed through the radial supply direction.
- a drain port 60 communicating with the atmospheric pressure outside the pump is formed at a position below the port 59 along the radial direction.
- connection port connected to one end of the intermediate passage 70 between the first supply / exhaust port 58 and the second supply / exhaust port 59 on the peripheral wall and at a position opposite to both the ports 58, 59. 61 is formed so as to penetrate along the radial direction, and at the same position in the circumferential direction as the connection port 61 and below the drain port 60, the spool valve communicates with the atmospheric pressure.
- a back pressure port 62 for back pressure relief that ensures good slidability 53 is formed penetrating in the radial direction.
- the drain port 60 and the back pressure port 62 can communicate with the suction port 21 instead of the atmospheric pressure outside the pump.
- the spool valve 53 is integrally formed as a solid body, and has comparatively large-diameter cylindrical first and second land portions 63 and 64 provided on both ends in the axial direction, and the land portions 63 and 64. A comparatively small-diameter columnar small-diameter portion 65 that connects between them.
- the first and second land portions 63 and 64 are formed to have the same outer diameter, and slide on the inner peripheral surface of the sliding hole 52 through a minute gap.
- the first and second land portions 63 and 64 satisfy the conditions for communication or blocking between the ports 58 to 61 in the first to fourth operating states of the oil pump 10 described later.
- the distance between the two 63 and 64 is set.
- the distance L1 between the opposing side surfaces 63a, 64a of the first land portion 63 and the second land portion 64 is equal to the lower end edge 58a of the first supply / discharge port 58 in FIG.
- the distance between the lower end edge 61a of the connection port 61 in the drawing and the upper end edge 60a of the drain port 60 in the drawing is larger than the interval L2 between the upper and lower edges 59a of the two supply / discharge ports 59 in the drawing. It is set to be substantially equal to L3.
- the first land portion 63 is set so that its axial width is substantially the same as the hole diameter of the first supply / discharge port 58.
- a cylindrical pressure receiving portion 66 having a slightly smaller diameter than the first land portion 63 is formed on the end face of the first land portion 63 on the introduction port 57 side.
- a flat pressure receiving surface 66 a that receives the pump discharge pressure introduced from the introduction port 57 into the sliding hole 52 is formed at the tip of the pressure receiving portion 66.
- a holding projection 67 which is a cylindrical convex portion having a smaller diameter than the second land portion 64, protrudes from the end surface of the second land portion 64 on the press-fit plug 56 side.
- the small-diameter portion 65 allows oil to flow through an annular ring groove 68 formed on the outer periphery between the small-diameter portion 65 and the sliding hole 52.
- the control spring accommodating chamber 54 is cylindrically defined by the inner peripheral surface of the sliding hole 52, the end surface of the second land portion 64 of the spool valve 53 on the press-fit plug 56 side, and the inner end surface of the press-fit plug 56. It is made.
- the control spring 55 is set so that its spring force is smaller than the spring force of the cam spring 18.
- the control spring 55 has one end elastically contacting the end surface of the second land portion 64 on the press-fit plug 56 side, and the other end elastically contacting the inner end surface of the press-fit plug 56.
- the spool valve 53 is always urged toward the introduction port 57 side.
- control spring 55 is held by the outer peripheral surface of the holding projection 67 and substantially the entire outer peripheral portion is held by the inner peripheral surface of the control spring accommodating chamber 54.
- the spool valve 53 is moved downward or upward by the relative pressure between the pump discharge pressure received from the introduction port 57 on the pressure receiving surface 66a and the spring force of the control spring 55, and the ports 57 to 61 are moved. It opens and closes (communicates) as appropriate.
- the opening / closing action of the ports 57 to 61 by the operation of the spool valve 53 will be described in detail in the section of the action of the present embodiment below. [Operation of this embodiment]
- the operation of the variable displacement oil pump according to the present embodiment will be described with reference to FIGS. 2 and 7 to 10.
- the electromagnetic switching valve 40 is energized when the internal electromagnetic coil receives an ON signal from the control unit, and the ball valve body 43 is moved through the movable plunger and the push rod 47.
- the solenoid opening port 42a of the valve seat 42 is closed, while the communication port 45 and the drain port 46 are connected.
- the pilot valve 50 has a low engine speed and low oil pressure, and the pump discharge pressure (pilot pressure) acting on the pressure receiving surface 66a is also small, the spool valve 53 moves toward the press-fit plug 56. In other words, the state where the tip edge of the pressure receiving portion 66 is seated on the stepped tapered surface 51a is maintained.
- the pilot valve 50 is in a state in which the first and second supply / discharge ports 58 and 59 and the connection port 61 are communicated with each other via the annular groove 68 on the outer periphery of the small diameter portion 65.
- the first control oil chamber 31 and the second control oil chamber 32 are both in communication with the drain port 46, so that hydraulic pressure is not introduced into the both 31 and 32.
- the eccentric amount control of the cam ring 17 is performed.
- the cam ring 17 does not depend on the hydraulic pressure in the first and second control oil chambers 31 and 32, and only the spring force of the cam spring 18 is used in the clockwise direction in FIG. The maximum eccentric state in contact with the surface 28a is maintained.
- the pump discharge pressure of the oil pump 10 increases substantially in proportion to the increase in the engine speed, as shown in the rotation region a of FIG.
- the electromagnetic switching valve 40 is maintained in the energized state as in the first operating state.
- the pilot valve 50 communicates the second supply / exhaust port 59 and the connection port 61 through the annular groove 68 in the same manner as in the first operating state, so that the second control oil chamber 32 is The state is communicated with the drain port 46.
- the pilot valve 50 when the pilot valve 50 receives a pump discharge pressure higher than the low pressure P1 on the pressure receiving surface 66a of the spool valve 53, the pilot valve 50 moves backward while resisting the spring force of the control spring 55.
- the introduction port 57 and the first supply / exhaust port 58 are communicated with each other in an orifice state in which the opening area is reduced by the one land portion 63.
- the hydraulic pressure supplied into the first control oil chamber 31 is P1 ′ which is reduced from the pump discharge pressure by passing through the orifice portion, but the set load of the cam spring 18 is also Since the hydraulic pressure is supplied only to the first control oil chamber among the first and second control oil chambers 31 and 32, it is set to operate at the operation start pressure P1 ′.
- the pump discharge pressure can be controlled without being affected by the reduced pressure.
- the first control oil chamber 31 is supplied with a reduced hydraulic pressure through the orifice portion that expands according to the pump discharge pressure, and the cam ring 17 is camped based on the hydraulic pressure. While urging the spring force of the spring 18 to bias the eccentric amount, the pump discharge amount is reduced and the pump discharge pressure is reduced.
- the pilot valve 50 moves the spool valve 53 toward the introduction port 57 by the spring force of the control spring 55.
- the introduction port 57 and the first supply / discharge port 58 are blocked by the first land portion 63 and the first supply / discharge port 58 and the drain port 46 are communicated with each other.
- the pilot valve 50 introduces oil into the first control oil chamber 31 and adjusts the pressure as the pump discharge pressure of the oil pump 10 increases. While the pump discharge pressure is reduced, the pump discharge pressure is improved by adjusting the pressure by deriving oil from the first control oil chamber 31 when the pump discharge pressure is lowered, and the pressure is adjusted to the low pressure P1. Yes.
- the first control The oil supply / discharge of the oil chamber 31 can be switched and controlled only by a minute movement of the spool valve 53. For this reason, since the influence of the spring constant of the control spring 55 hardly affects the discharge pressure control, the pump discharge pressure can be accurately controlled to the low pressure P1.
- the pump discharge pressure of the oil pump 10 is maintained substantially at the low pressure P1 regardless of the increase in the engine speed, as shown in the rotation region b of FIG. It becomes.
- the oil pump 10 performs the third operation shown in FIG. It becomes the operation state.
- the electromagnetic switching valve 40 is in a non-energized state when the internal electromagnetic coil receives an OFF signal from the control unit, and accordingly, the ball valve element 43 moves toward the valve seat 42. Since the urging force is released, the solenoid opening port 42a is opened. When the solenoid opening port 42a is opened, the ball valve body 43 is biased toward the solenoid unit 44 by the pump discharge pressure supplied through the solenoid opening port 42a. Is closed, and the communication between the communication port 45 and the drain port 46 is blocked.
- the pilot valve 50 makes the introduction port 57 and the first supply / discharge port 58 communicate with each other, and makes the second supply / discharge port 59 and the connection port 61 communicate with each other, as in the second operation state. ing.
- the second land portion 64 blocks the second supply / exhaust port 59 and the drain port 60.
- the electromagnetic switching valve 40 is maintained in a non-energized state as in the third operating state.
- the pilot valve 50 allows the introduction port 57 and the first supply / discharge port 58 to communicate with each other as in the third operating state.
- the pilot valve 50 when the pilot valve 50 receives a pump discharge pressure higher than the high pressure P2 on the pressure receiving surface 66a, the pilot valve 50 moves backward against the spring force of the control spring 55, whereby the second supply / discharge port 59 is provided. And the drain port 60 are communicated with each other.
- a hydraulic pressure equivalent to the pump discharge pressure is supplied to the first control oil chamber 31, while the hydraulic pressure introduced from the second control oil chamber 32 to the third operating state is the drain port. It is in a state of being gradually discharged through 60.
- the force in the direction against the cam spring 18 is not only the difference in urging force due to the difference in area between the pressure receiving surfaces 33 and 34 but also in the first and second control oil chambers 31 and 32. Since it is also affected by the hydraulic pressure difference, as a result, the state is the same as when P2 ′ pressurized to the pump discharge pressure is supplied to both 31 and 32.
- the set load of the cam spring 18 is set to operate at the operation start pressure P2 ′ when the hydraulic pressure is supplied to both the first and second control oil chambers 31 and 32. Therefore, the pump discharge pressure can be controlled without being affected by the pressure reduction caused by the discharge of the second control oil chamber 32.
- the second control oil chamber 32 is appropriately depressurized according to the pump discharge pressure, and based on this, the cam ring 17 is moved in the direction of decreasing the eccentric amount, thereby reducing the pump discharge amount. Reduce the pump discharge pressure.
- the pilot valve 50 moves the spool valve 53 toward the introduction port 57 by the spring force of the control spring 55.
- the second land portion 64 blocks the second supply / exhaust port 59 and the drain port 60.
- the pilot valve 50 allows the oil in the second control oil chamber 32 to be depressurized and adjusted as the pump discharge pressure of the oil pump 10 increases.
- the pump discharge pressure is improved by adjusting the pressure by introducing oil into the second control oil chamber 32 and adjusting the pressure to the high pressure P2. ing.
- the distance L1 between the side surfaces 63a, 64a facing each other in the axial direction of the first and second land portions 63, 64 is substantially equal to the distance L3 between the drain port 60 and the connection port 61. Therefore, the oil supply / discharge of the second control oil chamber 32 can be switched and controlled only by a minute movement of the spool valve 53. For this reason, since the influence of the spring constant of the control spring 55 hardly affects the discharge pressure control, the pump discharge pressure can be accurately controlled to the high pressure P2.
- the pump discharge pressure of the oil pump 10 is maintained substantially at the high pressure P2 regardless of the increase in the engine speed, as shown in the rotation region d of FIG. It becomes.
- the pump discharge pressure can be controlled to the two-stage characteristics of the low pressure P1 and the high pressure P2.
- the pilot valve 50 is configured so that oil does not flow through the control spring accommodating chamber 54 in all of the first to fourth operating states described above.
- a cylinder with a lid having a pressure receiving wall at one end such as the conventional variable displacement oil pump, is generally used.
- the covered cylindrical spool valve must be formed with a valve diameter larger than the outer diameter of the control spring 55 in order to accommodate one end side of the control spring 55 inside. Since the diameter of the sliding hole 52 is increased in accordance with the valve diameter, the pilot valve 50 is increased in size.
- the outer diameter of the control spring 55 inevitably becomes smaller than the diameter of the sliding hole 52, the other end side of the control spring 55 is in an unstable state in which it floats in the air. For this reason, as the plug for sealing the sliding hole 52, a screw plug or the like having a groove for holding the other end of the control spring 55 is used to hold the other end of the control spring 55. However, this may also lead to an increase in the size of the pilot valve 50.
- the spool valve 53 is formed in a solid shape, and oil flows through the annular groove 68 on the outer periphery of the small diameter portion 65, so that the shape is relatively simple. .
- the valve diameter of the spool valve 53 (the outer diameter of each land portion 63, 64). ) Can be set to substantially the same diameter as the outer diameter of the control spring 55, and accordingly, the hole diameter of the sliding hole 52 can be made substantially the same as the outer diameter of the control spring 55.
- the pilot valve 50 can be reduced in size and the control spring 55 is guided by the inner peripheral surface of the sliding hole 52, so that the pump discharge pressure (pilot) acting on the pressure receiving surface 66a can be reduced.
- the spring force can be accurately exhibited with respect to (pressure).
- control spring 55 is held by the inner peripheral surface of the control spring accommodating chamber 54 (the inner peripheral wall of the valve body 51), a simple shape can be used without using a screw plug or the like as described above. It is possible to support the sealing of the sliding hole 52 and the other end of the control spring 55 only by press-fitting the press-fit plug 56.
- the holding projection 67 is formed to project from the end face of the second land portion 64 on the press-fit plug 56 side, one end of the control spring 55 is connected to the inside of the valve body 51. Since it is clamped between the peripheral wall and the outer peripheral surface of the holding projection 67, the holding performance of the control spring 55 is further improved.
- the electromagnetic switching valve 40 is energized when the oil can be discharged from the second control oil chamber 32, that is, in the first and second operating states.
- the oil can be introduced into the second control oil chamber 32, that is, in the third and fourth operating states, the non-energized state is established.
- FIG. 11 shows a second embodiment of the present invention.
- the basic configuration is the same as that of the first embodiment, but the holding structure of the control spring 55 of the pilot valve 50 is changed.
- the second land portion 64 of the spool valve 53 in this embodiment has an axial width longer than that of the first embodiment.
- the holding projection 67 is abolished from the end surface on the control spring 55 side, and a holding groove portion 71, which is a cylindrical recess, is provided in a substantially central position of the end surface.
- the holding groove portion 71 is formed to have a smaller diameter than the outer diameter of the second land portion 64 and slightly larger than the outer diameter of the control spring 55, and the groove bottom is one end portion of the control spring 55. And one end of the control spring 55 is held by the peripheral wall.
- the press-fit plug 56 is abolished on the other end side of the control spring 55 of the valve body 51, and a screw plug 72, which is a cylindrical member with a lid, is screwed and fixed.
- a screw plug 72 which is a cylindrical member with a lid, is screwed and fixed.
- the inner wall of the lid 72a is in elastic contact with the other end of the control spring 55, and the other end of the control spring 55 is held by the inner peripheral wall of the cylindrical portion 72b.
- the oil discharged from the first and second control oil chambers 31 and 32 does not flow through the control spring accommodating chamber 54. It is possible to improve the stability of the position control of the valve 53 and improve the control accuracy of the pump discharge pressure with respect to the set hydraulic characteristics.
- both axial end portions of the control spring 55 can be held in a stable state by the holding groove portion 71 of the second land portion 64 and the inner wall of the screw plug 72, the pump discharge pressure acting on the pressure receiving surface 66a.
- the spring force can be exhibited accurately with respect to (pilot pressure).
- FIG. 12 is a modification of the second embodiment, in which the small-diameter portion 65 of the spool valve 53 is formed to have a larger diameter compared to the second embodiment, and the holding groove portion 71 is The second land portion 64 is recessed from the end surface on the control spring 55 side to the inside of the small diameter portion 65. Therefore, also in this case, it is possible to obtain the same effect as that of the second embodiment.
- the switching times of the respective ports by the first land portion 63 and the second land portion 64 of the spool valve 53 are set at the same time. There may be.
- the characteristics of the opening area may be changed by chamfering or rounding the end edges in the axial direction of the first and second land parts 63 and 64, and these may be adjusted according to the characteristics of the mounted engine. Is done.
- the non-energized state is set in the third and fourth operating states (during high engine speed).
- the energization / non-energization timing of the electromagnetic switching valve 40 can be changed as appropriate according to various configurations. For example, switching to the non-energized state can be performed at a higher engine speed than in the above embodiments. By performing at this point, the oil pump 10 can be directly switched from the second operating state to the fourth operating state.
- variable displacement oil pump based on the embodiment described above, for example, the following modes can be considered.
- variable displacement oil pump is a pump structure that changes the volume of a plurality of pump chambers by being rotationally driven by an internal combustion engine, and discharges hydraulic oil sucked from the suction portion from the discharge portion.
- a movable member that changes the volume change amount of the plurality of pump chambers by moving, and the movable member is provided in a state in which a set load is applied and the volume change amount of the plurality of pump chambers increases.
- a first control oil chamber that applies a force in a direction to reduce the volume change amount of the plurality of pump chambers to the movable member when the hydraulic oil is supplied; Is supplied, the second control oil chamber that causes the movable member to act on the movable member in the direction of increasing the volume change amount of the plurality of pump chambers, and the hydraulic oil is discharged from the second control oil chamber.
- a switching mechanism formed to be switchable between a state and a state in which hydraulic oil is introduced into the second control oil chamber, and a state in which the switching mechanism is in a state of discharging hydraulic oil from the second control oil chamber A state in which the hydraulic oil in the first control oil chamber is discharged, and a state in which the hydraulic oil having a pressure lower than the discharge pressure from the discharge portion is introduced into the first control oil chamber, and the discharge pressure is increased.
- the state in which the hydraulic oil reduced in pressure than the discharge pressure from the discharge unit is introduced into the second control oil chamber, and the introduction of the hydraulic oil into the second control oil chamber via the switching mechanism are shut off, A state in which hydraulic oil in the second control oil chamber is discharged and the discharge pressure A control mechanism that discharges the hydraulic oil in the second control oil chamber as it becomes closer, and adjusts the pressure in the second control oil chamber to a reduced pressure. While being controlled by the urging force, the hydraulic oil is not guided to a portion where the urging member is disposed.
- the control mechanism includes an introduction port for introducing hydraulic pressure of hydraulic oil discharged from the discharge portion, a first control port communicating with the first control oil chamber, A valve body having a second control port communicating with the second control oil chamber; a connection port connected to the switching mechanism; and a drain port communicating with the low pressure portion; and sliding on one end side in the axial direction of the valve body The communication state of the introduction port and the connection port with respect to the first control oil chamber and the communication state of the connection port and the drain port with respect to the second control oil chamber are switched according to the sliding position in the axial direction.
- the spool valve is accommodated and disposed on the other axial end side of the valve body, and the biasing force that biases the spool valve toward the axial one end side by a biasing force smaller than that of the biasing mechanism. Having a control spring which is member.
- the spool valve has a large-diameter land portion that slides with the valve body at both axial end portions, and each of the land portions.
- a small-diameter portion is formed between the first control oil chamber and the connection port and the drain with respect to the second control oil chamber.
- the port is formed so as to communicate appropriately.
- the introduction port is provided at one axial end of the valve body, and the spool valve is disposed at an axial end on the introduction port side.
- a pressure receiving surface on which hydraulic pressure of the hydraulic oil acts is formed at the portion.
- the first and second control ports and the drain port are respectively formed through the peripheral wall of the valve body.
- the spool valve is formed solid.
- a cylindrical convex portion having a smaller diameter than the land portion is formed to protrude from an end surface of the land portion on the control spring side, One end side of the control spring is held by the convex portion.
- control spring is supported on an inner peripheral wall of the valve body.
- a cylindrical recess having a smaller diameter than the land portion is formed on the end surface on the control spring side of the land portion toward the introduction port side.
- the one end side of the said control spring is hold
- a cylindrical member with a lid is disposed at the control spring side end of the valve body, and the other end of the control spring. The side is held by the inner wall surface of the cylindrical member.
- variable displacement oil pump when the hydraulic oil is discharged from the first and second control oil chambers at the same time, the hydraulic oil is supplied to the small diameter portion. After passing through the outer periphery, it is discharged via the switching mechanism.
- the switching mechanism is an electromagnetic control valve that is electrically switched.
- the electromagnetic control valve in a non-energized state when operating oil is guided to the second control chamber, and the second control oil When operating oil is discharged from the chamber, it is energized.
- the electromagnetic control valve performs switching of supply and discharge of hydraulic oil to and from the second control oil chamber by a ball valve.
- the hydraulic oil discharged from the discharge portion is used as a lubricating oil for lubricating a component member included in the internal combustion engine.
- the hydraulic oil discharged from the discharge unit supplies the hydraulic oil to a drive source of a variable valve operating device and a piston of the internal combustion engine. Used for oil jets.
- variable displacement oil pump includes a rotor that is rotationally driven by an internal combustion engine, a plurality of vanes that are provided in an outer periphery of the rotor, and the rotor and the vanes on an inner peripheral side.
- a plurality of cam chambers that separate the plurality of pump chambers while being housed and change the amount of eccentricity with respect to the axis of the rotor by moving to change the volume change amount of the plurality of pump chambers; and Of these, a suction portion that opens to a suction region that increases in volume as the rotor rotates, a discharge portion that opens to a discharge region whose volume decreases as the rotor rotates among the plurality of pump chambers, and a set load is applied And a biasing mechanism that biases the cam ring in a direction in which the amount of eccentricity increases, and a method in which the amount of eccentricity decreases by supplying hydraulic oil.
- a first control oil chamber that causes the cam ring to act on the cam ring, a second control oil chamber that acts on the cam ring in a direction that increases the amount of eccentricity when the hydraulic oil is supplied, and the second control oil chamber.
- a switching mechanism configured to be able to switch between a state in which the hydraulic oil is discharged from the oil chamber and a state in which the hydraulic oil is introduced into the second control oil chamber, and the switching mechanism discharges the hydraulic oil from the second control oil chamber. When it is in a state of being discharged, it takes a state of discharging the hydraulic oil in the first control oil chamber and a state of introducing hydraulic oil having a pressure lower than the discharge pressure from the discharge portion into the first control oil chamber.
- hydraulic oil is introduced into the first control oil chamber to adjust the pressure in the first control oil chamber, and the switching mechanism moves the hydraulic oil into the second control oil chamber.
- the state where the second control oil chamber is introduced The state in which the hydraulic oil whose pressure is lower than the discharge pressure from the discharge unit is introduced, and the introduction of the hydraulic oil into the second control oil chamber via the switching mechanism is blocked, and the hydraulic oil in the second control oil chamber
- the first and second control oil chambers are provided on an outer peripheral side of the cam ring and defined by a swing fulcrum provided on the outer peripheral side of the cam ring. ing.
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Abstract
Description
〔第1実施形態〕
図1は本実施形態の可変容量形のオイルポンプと油圧回路を示し、可変容量形のオイルポンプ10は、内燃機関のクランクシャフトから伝達された回転駆動力によって回転して、オイルパン01に貯留された作動油であるオイルを、ストレーナ02を介して吸入通路03から吸入した後に、吐出通路04から機関内部に形成されたメインオイルギャラリー05に吐出するようになっている。 Hereinafter, each embodiment of the variable displacement oil pump according to the present invention will be described in detail with reference to the drawings.
[First Embodiment]
FIG. 1 shows a variable displacement oil pump and a hydraulic circuit according to this embodiment. A variable
〔本実施形態の作用〕
以下、本実施形態に係る可変容量形オイルポンプの作動を、図2,図7~図10に基づいて説明する。 The
[Operation of this embodiment]
Hereinafter, the operation of the variable displacement oil pump according to the present embodiment will be described with reference to FIGS. 2 and 7 to 10.
〔第2実施形態〕
図11は本発明の第2実施形態を示し、基本構成は前記第1実施形態と同様であるが、前記パイロット弁50の制御ばね55の保持構造が変更されている。 Thereby, for example, when the electromagnetic coil of the
[Second Embodiment]
FIG. 11 shows a second embodiment of the present invention. The basic configuration is the same as that of the first embodiment, but the holding structure of the
Claims (18)
- 内燃機関によって回転駆動されることにより複数のポンプ室の容積が変化して、吸入部から吸入した作動油を吐出部から吐出するポンプ構成体と、
移動することによって、前記複数のポンプ室の容積変化量を変更させる可動部材と、
セット荷重が付与された状態で設けられ、前記複数のポンプ室の容積変化量が増大する方向へ前記可動部材を付勢する付勢機構と、
作動油が供給されることによって、前記複数のポンプ室の容積変化量を減少させる方向への力を前記可動部材に作用させる第1制御油室と、
作動油が供給されることによって、前記複数のポンプ室の容積変化量を増大させる方向への力を前記可動部材に作用させる第2制御油室と、
前記第2制御油室から作動油を排出する状態と、前記第2制御油室に作動油を導入する状態と、を切換可能に形成された切換機構と、
該切換機構が前記第2制御油室から作動油を排出する状態にある場合に、前記第1制御油室内の作動油を排出する状態と、前記第1制御油室に前記吐出部からの吐出圧よりも減圧された作動油を導入する状態をとると共に、前記吐出圧が大きくなるにしたがって前記第1制御油室内に作動油を導入させて、該第1制御油室内を加圧調整し、かつ
前記切換機構が前記第2制御油室に作動油を導入する状態にある場合に、前記第2制御油室に前記吐出部からの吐出圧よりも減圧された作動油を導入する状態と、前記切換機構を介する前記第2制御油室への作動油の導入を遮断し、前記第2制御油室内の作動油を排出する状態をとると共に、前記吐出圧が大きくなるにしたがって前記第2制御油室内の作動油を排出させて、該第2制御油室内を減圧調整する制御機構と、
を備え、
前記制御機構は、作動油による油圧と付勢部材による付勢力によって制御されると共に、該付勢部材が配置される部位には、作動油が導かれない構成としたことを特徴とする可変容量形オイルポンプ。 A pump structure that discharges hydraulic fluid sucked from the suction portion from the discharge portion, by the volume of the plurality of pump chambers being changed by being rotationally driven by the internal combustion engine;
A movable member that changes a volume change amount of the plurality of pump chambers by moving;
An urging mechanism that is provided in a state in which a set load is applied and urges the movable member in a direction in which a volume change amount of the plurality of pump chambers increases;
A first control oil chamber that applies a force to the movable member in a direction to reduce a volume change amount of the plurality of pump chambers by supplying hydraulic oil;
A second control oil chamber that applies a force to the movable member in a direction to increase a volume change amount of the plurality of pump chambers by supplying hydraulic oil;
A switching mechanism formed to be switchable between a state in which the hydraulic oil is discharged from the second control oil chamber and a state in which the hydraulic oil is introduced into the second control oil chamber;
When the switching mechanism is in a state of discharging the hydraulic oil from the second control oil chamber, the state of discharging the hydraulic oil in the first control oil chamber and the discharge from the discharge unit to the first control oil chamber Taking a state of introducing hydraulic oil whose pressure is lower than the pressure, introducing hydraulic oil into the first control oil chamber as the discharge pressure increases, and adjusting the pressure in the first control oil chamber; And when the switching mechanism is in a state of introducing hydraulic oil into the second control oil chamber, a state of introducing hydraulic oil having a pressure lower than the discharge pressure from the discharge portion into the second control oil chamber; The introduction of hydraulic oil into the second control oil chamber via the switching mechanism is shut off, the hydraulic oil in the second control oil chamber is discharged, and the second control is increased as the discharge pressure increases. The hydraulic oil in the oil chamber is discharged and the pressure in the second control oil chamber is reduced. A control mechanism to adjust;
With
The control mechanism is controlled by a hydraulic pressure by hydraulic oil and a biasing force by a biasing member, and has a configuration in which the hydraulic oil is not guided to a portion where the biasing member is disposed. Shape oil pump. - 請求項1に記載の可変容量形オイルポンプにおいて、
前記制御機構は、
前記吐出部から吐出された作動油の油圧を導入する導入ポートと、前記第1制御油室に連通する第1制御ポートと、前記第2制御油室と連通する第2制御ポートと、前記切換機構と接続される接続ポート及び低圧部に連通するドレンポートと、を有するバルブボディと、
該バルブボディの軸方向一端側に摺動自在に収容され、軸方向の摺動位置に応じて前記第1制御油室に対する前記導入ポート及び接続ポートの連通状態と、前記第2制御油室に対する前記接続ポート及びドレンポートの連通状態を切り替えるスプール弁と、
前記バルブボディの軸方向他端側に収容配置され、前記付勢機構より小さな付勢力によって前記スプール弁を軸方向一端側へ付勢する前記付勢部材である制御ばねと、
を有することを特徴とする可変容量形オイルポンプ。 The variable displacement oil pump according to claim 1, wherein
The control mechanism is
An introduction port for introducing hydraulic pressure of hydraulic oil discharged from the discharge section, a first control port communicating with the first control oil chamber, a second control port communicating with the second control oil chamber, and the switching A valve body having a connection port connected to the mechanism and a drain port communicating with the low pressure portion;
The valve body is slidably accommodated at one axial end of the valve body, and the communication state of the introduction port and the connection port with respect to the first control oil chamber according to the axial sliding position, and the second control oil chamber A spool valve that switches the communication state of the connection port and the drain port;
A control spring that is an urging member that is accommodated and disposed on the other axial end side of the valve body, and that urges the spool valve toward one axial end side by an urging force smaller than the urging mechanism;
A variable displacement oil pump characterized by comprising: - 請求項2に記載の可変容量形オイルポンプにおいて、
前記スプール弁は、軸方向両端部に前記バルブボディと摺動する大径なランド部をそれぞれ有すると共に、該各ランド部の間に小径部が形成され、
該小径部の外周を介して、前記第1制御油室に対して前記接続ポートを適宜連通させると共に、前記第2制御油室に対して前記接続ポート及びドレンポートを適宜連通させることを特徴とする可変容量形オイルポンプ。 The variable displacement oil pump according to claim 2,
The spool valve has a large-diameter land portion that slides with the valve body at both axial ends, and a small-diameter portion is formed between the land portions,
The connection port is appropriately communicated with the first control oil chamber through the outer periphery of the small diameter portion, and the connection port and the drain port are appropriately communicated with the second control oil chamber. Variable displacement oil pump. - 請求項3に記載の可変容量形オイルポンプにおいて、
前記導入ポートは、前記バルブボディの軸方向一端部に設けられ、
前記スプール弁は、前記導入ポート側の軸方向端部に、作動油の油圧が作用する受圧面が形成されていることを特徴とする可変容量形オイルポンプ。 In the variable displacement oil pump according to claim 3,
The introduction port is provided at one axial end of the valve body,
The variable displacement oil pump according to claim 1, wherein the spool valve has a pressure receiving surface on which an oil pressure of hydraulic oil acts at an axial end on the introduction port side. - 請求項4に記載の可変容量形オイルポンプにおいて、
前記第1、第2制御ポート及びドレンポートは、前記バルブボディの周壁にそれぞれ貫通形成されていることを特徴とする可変容量形オイルポンプ。 The variable displacement oil pump according to claim 4,
The variable displacement oil pump according to claim 1, wherein the first and second control ports and the drain port are respectively formed through the peripheral wall of the valve body. - 請求項5に記載の可変容量形オイルポンプにおいて、
前記スプール弁は中実に形成されていることを特徴とする可変容量形オイルポンプ。 In the variable displacement oil pump according to claim 5,
2. The variable displacement oil pump according to claim 1, wherein the spool valve is solid. - 請求項6に記載の可変容量形オイルポンプにおいて、
前記ランド部の前記制御ばね側の端面には、前記ランド部よりも小径な円柱状の凸部が突出形成され、
該凸部によって前記制御ばねの一端側が保持されていることを特徴とする可変容量形オイルポンプ。 The variable displacement oil pump according to claim 6,
On the end surface of the land portion on the control spring side, a cylindrical convex portion having a smaller diameter than the land portion is formed to protrude,
One end side of the control spring is held by the convex portion. - 請求項7に記載の可変容量形オイルポンプにおいて、
前記制御ばねは、前記バルブボディの内周壁に支持されていることを特徴とする可変容量形オイルポンプ。 The variable displacement oil pump according to claim 7,
The variable displacement oil pump, wherein the control spring is supported on an inner peripheral wall of the valve body. - 請求項5に記載の可変容量形オイルポンプにおいて、
前記ランド部の前記制御ばね側の端面には、前記ランド部よりも小径な円柱状の凹部が前記導入ポート側へ向かって凹設され、
該凹部によって前記制御ばねの一端側が保持されていることを特徴とする可変容量形オイルポンプ。 In the variable displacement oil pump according to claim 5,
On the end face of the land portion on the control spring side, a cylindrical concave portion having a smaller diameter than the land portion is provided in the direction toward the introduction port,
One end side of the control spring is held by the concave portion. - 請求項9に記載の可変容量形オイルポンプにおいて、
前記バルブボディの前記制御ばね側端部には、有蓋円筒状の筒状部材が配置され、
前記制御ばねの他端側は、前記筒状部材の内壁面に保持されていることを特徴とする可変容量形オイルポンプ。 The variable displacement oil pump according to claim 9,
At the control spring side end of the valve body, a covered cylindrical tubular member is disposed,
2. The variable displacement oil pump according to claim 1, wherein the other end side of the control spring is held by an inner wall surface of the cylindrical member. - 請求項3に記載の可変容量形オイルポンプにおいて、
前記第1、第2制御油室から作動油が同時に排出される状態の場合、該作動油は、前記小径部の外周を介した後に、前記切換機構を経由して排出されることを特徴とする可変容量形オイルポンプ。 In the variable displacement oil pump according to claim 3,
When hydraulic oil is discharged from the first and second control oil chambers at the same time, the hydraulic oil is discharged via the switching mechanism after passing through the outer periphery of the small diameter portion. Variable displacement oil pump. - 請求項1に記載の可変容量形オイルポンプにおいて、
前記切換機構は、電気的に切り換え制御される電磁制御弁であることを特徴とする可変容量形オイルポンプ。 The variable displacement oil pump according to claim 1, wherein
The variable displacement oil pump according to claim 1, wherein the switching mechanism is an electromagnetic control valve that is electrically controlled to be switched. - 請求項12に記載の可変容量形オイルポンプにおいて、
前記電磁制御弁は、前記第2制御室に作動油を導いている時には非通電状態をとり、前記第2制御油室から作動油を排出している時には通電状態をとることを特徴とする可変容量形オイルポンプ。 The variable displacement oil pump according to claim 12,
The electromagnetic control valve is in a non-energized state when hydraulic oil is introduced into the second control chamber, and is in an energized state when hydraulic oil is discharged from the second control oil chamber. Capacity type oil pump. - 請求項13に記載の可変容量形オイルポンプにおいて、
前記電磁制御弁は、前記第2制御油室に対する作動油の給排の切り換えをボール弁によって行うことを特徴とする可変容量形オイルポンプ。 The variable displacement oil pump according to claim 13,
A variable displacement oil pump, wherein the electromagnetic control valve performs switching of supply and discharge of hydraulic oil to and from the second control oil chamber by a ball valve. - 請求項1に記載の可変容量形オイルポンプにおいて、
前記吐出部から吐出された作動油は、前記内燃機関の内部に有する構成部材を潤滑する潤滑油として用いられることを特徴とする可変容量形オイルポンプ。 The variable displacement oil pump according to claim 1, wherein
The variable displacement oil pump according to claim 1, wherein the hydraulic oil discharged from the discharge portion is used as a lubricating oil for lubricating a constituent member included in the internal combustion engine. - 請求項15に記載の可変容量形オイルポンプにおいて、
前記吐出部から吐出された作動油は、可変動弁装置の駆動源及び前記内燃機関のピストンに作動油を供給するオイルジェットにも用いられることを特徴とする可変容量形オイルポンプ。 The variable displacement oil pump according to claim 15,
The variable displacement oil pump is characterized in that the hydraulic oil discharged from the discharge unit is also used for an oil jet that supplies hydraulic oil to a drive source of a variable valve device and a piston of the internal combustion engine. - 内燃機関によって回転駆動されるロータと、
該ロータの外周に出没自在に設けられた複数のベーンと、
内周側に前記ロータ及び前記ベーンを収容しつつ複数のポンプ室を隔成すると共に、移動することによって前記ロータの軸心に対する偏心量が変化して前記複数のポンプ室の容積変化量を変化させるカムリングと、
前記複数のポンプ室のうち前記ロータの回転に伴い容積が増大する吸入領域に開口する吸入部と、
前記複数のポンプ室のうち前記ロータの回転に伴い容積が減少する吐出領域に開口する吐出部と、
セット荷重が付与された状態で設けられ、前記偏心量が大きくなる方向へ前記カムリングを付勢する付勢機構と、
作動油が供給されることによって、前記偏心量が小さくなる方向の力を前記カムリングに作用させる第1制御油室と、
作動油が供給されることによって、前記偏心量が大きくなる方向の力を前記カムリングに作用させる第2制御油室と、
前記第2制御油室から作動油を排出する状態と、前記第2制御油室に作動油を導入する状態とを切換可能に形成された切換機構と、
該切換機構が前記第2制御油室から作動油を排出する状態にある場合に、前記第1制御油室内の作動油を排出する状態と、前記第1制御油室に前記吐出部からの吐出圧よりも減圧された作動油を導入する状態をとると共に、前記吐出圧が大きくなるにしたがって前記第1制御油室内に作動油を導入させて、該第1制御油室内を加圧調整し、かつ
前記切換機構が前記第2制御油室に作動油を導入する状態にある場合に、前記第2制御油室に前記吐出部からの吐出圧よりも減圧された作動油を導入する状態と、前記切換機構を介する前記第2制御油室への作動油の導入を遮断し、前記第2制御油室内の作動油を排出する状態をとると共に、前記吐出圧が大きくなるにしたがって前記第2制御油室内の作動油を排出させて、該第2制御油室内を減圧調整する制御機構と、
を備え、
前記制御機構は、作動油による油圧と付勢部材による付勢力によって制御されると共に、該付勢部材が配置される部位には、作動油が導かれない構成としたことを特徴とする可変容量形オイルポンプ。 A rotor driven to rotate by an internal combustion engine;
A plurality of vanes provided on the outer periphery of the rotor so as to be freely movable; and
A plurality of pump chambers are separated while accommodating the rotor and the vanes on the inner peripheral side, and the amount of eccentricity with respect to the shaft center of the rotor is changed by moving to change the volume change amount of the plurality of pump chambers. Cam ring to make,
A suction portion that opens to a suction region whose volume increases with rotation of the rotor among the plurality of pump chambers;
A discharge portion that opens to a discharge region whose volume decreases with rotation of the rotor among the plurality of pump chambers;
An urging mechanism that is provided in a state where a set load is applied and urges the cam ring in a direction in which the amount of eccentricity increases;
A first control oil chamber that applies a force in a direction in which the amount of eccentricity is reduced to the cam ring by supplying hydraulic oil;
A second control oil chamber that applies a force in a direction in which the amount of eccentricity increases to the cam ring by supplying hydraulic oil;
A switching mechanism formed so as to be switchable between a state in which the hydraulic oil is discharged from the second control oil chamber and a state in which the hydraulic oil is introduced into the second control oil chamber;
When the switching mechanism is in a state of discharging the hydraulic oil from the second control oil chamber, the state of discharging the hydraulic oil in the first control oil chamber and the discharge from the discharge unit to the first control oil chamber Taking a state of introducing hydraulic oil whose pressure is lower than the pressure, introducing hydraulic oil into the first control oil chamber as the discharge pressure increases, and adjusting the pressure in the first control oil chamber; And when the switching mechanism is in a state of introducing hydraulic oil into the second control oil chamber, a state of introducing hydraulic oil having a pressure lower than the discharge pressure from the discharge portion into the second control oil chamber; The introduction of hydraulic oil into the second control oil chamber via the switching mechanism is shut off, the hydraulic oil in the second control oil chamber is discharged, and the second control is increased as the discharge pressure increases. The hydraulic oil in the oil chamber is discharged and the pressure in the second control oil chamber is reduced. A control mechanism to adjust;
With
The control mechanism is controlled by a hydraulic pressure by hydraulic oil and a biasing force by a biasing member, and has a configuration in which the hydraulic oil is not guided to a portion where the biasing member is disposed. Shape oil pump. - 請求項17に記載の可変容量形オイルポンプにおいて、
前記第1、第2制御油室は、前記カムリングの外周側に設けられていると共に、該カムリングの外周側に設けられた揺動支点によって画成されていることを特徴とする可変容量形オイルポンプ。 The variable displacement oil pump according to claim 17,
The first and second control oil chambers are provided on the outer peripheral side of the cam ring and are defined by a swing fulcrum provided on the outer peripheral side of the cam ring. pump.
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JP2017510955A JP6622792B2 (en) | 2015-04-09 | 2016-03-31 | Variable displacement oil pump |
CN201680020383.6A CN107532593B (en) | 2015-04-09 | 2016-03-31 | Capacity-variable type oil pump |
US15/563,991 US20180135625A1 (en) | 2015-04-09 | 2016-03-31 | Variable capacity oil pump |
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JP (1) | JP6622792B2 (en) |
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US7988433B2 (en) | 2009-04-07 | 2011-08-02 | Emerson Climate Technologies, Inc. | Compressor having capacity modulation assembly |
US9249802B2 (en) | 2012-11-15 | 2016-02-02 | Emerson Climate Technologies, Inc. | Compressor |
JP6411228B2 (en) * | 2015-01-19 | 2018-10-24 | アイシン・エィ・ダブリュ株式会社 | Transmission device |
JP6567678B2 (en) * | 2015-09-18 | 2019-08-28 | 日立オートモティブシステムズ株式会社 | Variable displacement oil pump |
US10995753B2 (en) | 2018-05-17 | 2021-05-04 | Emerson Climate Technologies, Inc. | Compressor having capacity modulation assembly |
US11655813B2 (en) | 2021-07-29 | 2023-05-23 | Emerson Climate Technologies, Inc. | Compressor modulation system with multi-way valve |
US11846287B1 (en) | 2022-08-11 | 2023-12-19 | Copeland Lp | Scroll compressor with center hub |
US11965507B1 (en) | 2022-12-15 | 2024-04-23 | Copeland Lp | Compressor and valve assembly |
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JP6375212B2 (en) * | 2014-11-26 | 2018-08-15 | Kyb株式会社 | Variable displacement vane pump |
-
2016
- 2016-03-31 CN CN201680020383.6A patent/CN107532593B/en not_active Expired - Fee Related
- 2016-03-31 WO PCT/JP2016/060701 patent/WO2016163302A1/en active Application Filing
- 2016-03-31 JP JP2017510955A patent/JP6622792B2/en not_active Expired - Fee Related
- 2016-03-31 US US15/563,991 patent/US20180135625A1/en not_active Abandoned
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JPS5442537A (en) * | 1977-09-09 | 1979-04-04 | Toyota Motor Corp | Throttle device for two-barrel carburetor |
JPH0333420A (en) * | 1989-06-29 | 1991-02-13 | Mazda Motor Corp | Cooling device of engine |
JPH10184958A (en) * | 1996-12-20 | 1998-07-14 | Kubota Corp | Emergency valve for earthquake-proof water storage tank |
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JP2015021400A (en) * | 2013-07-17 | 2015-02-02 | 日立オートモティブシステムズ株式会社 | Variable capacity type pump |
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JP6622792B2 (en) | 2019-12-18 |
CN107532593A (en) | 2018-01-02 |
JPWO2016163302A1 (en) | 2017-10-19 |
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