WO2016203811A1 - 可変容量形オイルポンプ - Google Patents
可変容量形オイルポンプ Download PDFInfo
- Publication number
- WO2016203811A1 WO2016203811A1 PCT/JP2016/060702 JP2016060702W WO2016203811A1 WO 2016203811 A1 WO2016203811 A1 WO 2016203811A1 JP 2016060702 W JP2016060702 W JP 2016060702W WO 2016203811 A1 WO2016203811 A1 WO 2016203811A1
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- WIPO (PCT)
- Prior art keywords
- pump
- variable displacement
- oil chamber
- control oil
- 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
- 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
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
- F01M1/00—Pressure lubrication
- F01M1/02—Pressure lubrication using lubricating pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C13/00—Adaptations of machines or pumps for special use, e.g. for extremely high pressures
- F04C13/001—Pumps for particular liquids
-
- 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
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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
- F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
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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
- 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
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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
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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
- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
- F01M1/00—Pressure lubrication
- F01M1/02—Pressure lubrication using lubricating pumps
- F01M2001/0207—Pressure lubrication using lubricating pumps characterised by the type of pump
- F01M2001/0238—Rotary pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
- F01M1/00—Pressure lubrication
- F01M1/02—Pressure lubrication using lubricating pumps
- F01M2001/0207—Pressure lubrication using lubricating pumps characterised by the type of pump
- F01M2001/0246—Adjustable pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
- F01M1/00—Pressure lubrication
- F01M1/02—Pressure lubrication using lubricating pumps
- F01M2001/0253—Pressure lubrication using lubricating pumps characterised by the pump driving means
- F01M2001/0269—Pressure lubrication using lubricating pumps characterised by the pump driving means driven by the crankshaft
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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
- F04C2210/00—Fluid
- F04C2210/20—Fluid liquid, i.e. incompressible
- F04C2210/206—Oil
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16N—LUBRICATING
- F16N13/00—Lubricating-pumps
- F16N13/20—Rotary pumps
Definitions
- the present invention relates to a variable displacement oil pump that supplies oil as a drive source for lubrication of a sliding part such as a crankshaft of an internal combustion engine or auxiliary equipment, for example.
- variable displacement oil pump is suitable for equipment with different required discharge pressures, such as variable sliding devices that control the operating characteristics of engine valves such as intake valves, etc.
- variable sliding devices that control the operating characteristics of engine valves such as intake valves, etc.
- the two-stage characteristics of the low pressure characteristic related to the first rotation region and the high pressure characteristic related to the second rotation region are satisfied.
- the first control oil chamber and the second control oil chamber are separated between the inner peripheral surface of the pump body and the outer peripheral surface of the cam ring, and the pump discharge pressure is supplied to the first control oil chamber,
- the cam ring is biased in the direction of decreasing eccentricity (hereinafter referred to as concentric direction), while the pump discharge pressure is supplied to the second control oil chamber, thereby increasing the eccentric amount of cam ring (hereinafter referred to as eccentricity).
- the spring force of the coil spring urges the cam ring so that the eccentric amount of the cam ring is increased, and the plurality of vanes that protrude in and out from the outer peripheral surface of the rotor in the radial direction and the inner peripheral surface of the cam ring are separated.
- the cam ring is controlled to be eccentric and concentric with the biasing force based on the internal pressure of the pump chamber.
- variable displacement oil pump many bubbles due to aeration, cavitation, etc. are likely to be generated in the oil during inhalation, especially when the pump rotates at high speed (second rotation region).
- a phenomenon such as bubble collapse occurs in the discharge region where the oil is compressed and discharged, and the balance of the internal pressures of the pump chambers is lost.
- the behavior of the cam ring becomes unstable, and the cam ring swings in a concentric direction before reaching the set hydraulic pressure, which may cause unstable control of the high pressure characteristics in the second rotation region.
- the present invention has been devised in view of the above-mentioned conventional technical problems, and even if bubbles are generated in the pump chamber, the destabilization of the behavior of the cam ring is suppressed and the control of the high-pressure characteristics of the pump is stabilized. It is an object of the present invention to provide a variable displacement oil pump capable of achieving the above.
- the present invention provides a pump structure that discharges hydraulic oil sucked from a suction part from a discharge part by changing the volumes of a plurality of pump chambers by being rotationally driven, and the pump structure is accommodated inside,
- a swing member that makes the volume change amount of the plurality of pump chambers opened in the discharge section variable by swinging using a swing support point provided on the side as a fulcrum, and a set load is provided.
- the volume change amount of the plurality of pump chambers is reduced by supplying the urging member for biasing the swinging member in the direction in which the volume change amount of the plurality of pump chambers increases and the hydraulic oil.
- Big second torque A second control oil chamber to act on KiYurado member is characterized by comprising a switching mechanism for switching the supply or discharge of hydraulic oil to the second control oil chamber.
- FIG. 2 is a front view of the variable displacement oil pump shown in FIG. 1.
- FIG. 3 is a cross-sectional view taken along line AA in FIG. 2.
- FIG. 4 is a sectional view taken along line BB in FIG. 3. It is the figure seen from the mating face side with the cover member of the pump body provided to this embodiment. It is a graph showing the hydraulic pressure characteristic of the variable capacity type oil pump concerning the embodiment.
- FIG. 7 is a hydraulic circuit diagram of the variable displacement oil pump according to the embodiment, where (A) shows the state of the pump in the section a of FIG. 6 and (B) shows the pump in the section b of FIG. FIG.
- FIG. 7 is a hydraulic circuit diagram of the variable displacement oil pump according to the embodiment, where (A) shows a section c in FIG. 6 and (B) shows a pump state in a section d in FIG. 6.
- FIG. 7 is a hydraulic circuit diagram of the variable displacement oil pump according to the embodiment, showing a state of the pump at a point CA in FIG. 6. It is a hydraulic circuit diagram which shows 2nd Embodiment of the variable displacement type oil pump in this invention.
- FIG. 5 is a hydraulic circuit diagram showing a third embodiment of a variable displacement oil pump according to the present invention.
- variable displacement oil pump is used to supply engine lubricating oil to a valve timing control device for controlling opening / closing timing of a sliding part of an automotive internal combustion engine or an engine valve.
- a valve timing control device for controlling opening / closing timing of a sliding part of an automotive internal combustion engine or an engine valve. The example applied as is shown.
- This oil pump 10 is provided at the front end of a cylinder block or balancer device of an internal combustion engine (not shown). As shown in FIGS. 1 to 4, the oil pump 10 has a longitudinal section in which one end side is opened and a pump housing chamber 13 is provided. A pump housing 11 having a substantially U-shaped pump body 11 and a cover member 12 that closes the one end opening of the pump body 11, and is rotatably supported by the pump housing. And a drive shaft 14 that is rotationally driven by a crankshaft or a balancer shaft (not shown) and is housed in the pump housing chamber 13 so as to be movable (swingable), and first and second control oil chambers 31 described later.
- a cam ring 15 that is a swinging member that changes the volume change amount of a plurality of pump chambers 24 that are hydraulic oil chambers to be described later.
- the volume of the pump chamber 24 formed between the cam ring 15 and the cam ring 15 is increased / decreased by being accommodated on the inner peripheral side of the cam ring 15 and driven to rotate clockwise in FIG.
- a pilot valve 40 that is a control mechanism that is attached to the cover member 12 and controls the supply and discharge of hydraulic pressure to the second control oil chamber 32, which will be described later.
- Electromagnetic switching which is a switching mechanism which is provided on an oil passage (a second introduction passage 72 which will be described later) formed between the discharge port 22a and which controls the supply of discharged oil to the pilot valve 40 side.
- a valve 60 which is a switching mechanism which is provided on an oil passage (a second introduction passage 72 which will be described later) formed between the discharge port 22a and which controls the supply of discharged oil to the pilot valve 40 side.
- the pump structure is rotatably accommodated on the inner peripheral side of the cam ring 15, and a rotor 16 having a central portion coupled to the outer periphery of the drive shaft 14, and a plurality of radial notches formed in the outer peripheral portion of the rotor 16.
- the vane 17 is housed in the slit 16a so that it can freely enter and exit, and a pair of ring members 18 and 18 are formed on the inner peripheral side of the rotor 16 and have a smaller diameter than the rotor 16. ing.
- the pump body 11 is integrally formed of an aluminum alloy material, and, as shown in FIG. 5, one end portion of the drive shaft 14 is provided at a substantially central position of the end wall 11a constituting the one end wall of the pump housing chamber 13.
- a bearing hole 11b that is rotatably supported is formed.
- a support hole 11c having a substantially semicircular cross section for supporting the cam ring 15 through a rod-like pivot pin 19 so as to be swingable is formed at a predetermined position on the inner peripheral wall of the pump housing chamber 13.
- a straight line (hereinafter referred to as “cam ring reference line”) M connecting the center of the bearing hole 11b and the center of the support hole 11c is located on the upper half side in FIG.
- a first seal slidable contact surface 11d with which the first seal member 20a disposed on the outer periphery of the cam ring 15 is slidably contacted is formed.
- the first seal sliding contact surface 11d is formed in an arcuate surface shape having a predetermined radius R1 from the center of the support hole 11c, and the first seal member 20 can always slide in a range where the cam ring 15 swings eccentrically. It is set to a proper circumferential length.
- R1 predetermined radius
- a second seal slidable contact surface 11e is formed on which the second seal member 20b disposed on the outer periphery of the cam ring 15 is slidably contacted.
- the seal slidable contact surface 11e is formed in an arcuate surface shape having a predetermined radius R2 from the center of the support hole 11c, and the circumferential direction in which the second seal member 20a can always slidably contact within the range in which the cam ring 15 swings eccentrically. It is set to length.
- the discharge port 22 that is a substantially arc-shaped discharge portion is cut out so as to face each other across the bearing hole 11b.
- the suction port 21 is integrally provided with an introduction portion 23 formed so as to bulge toward a spring accommodating chamber 26 described later at a substantially intermediate position in the circumferential direction, and a boundary between the introduction portion 23 and the suction port 21 is provided.
- a suction port 21a that penetrates the end wall 11a of the pump body 11 and opens to the outside is formed in the vicinity of the portion.
- the suction port 21a is configured to communicate with the low pressure chamber 35 formed in the outer peripheral region of the cam ring 15 in the suction region together with the introduction portion 23.
- the low pressure chamber 35 also has a low pressure that is the suction pressure. Oil is guided.
- the discharge port 22 is formed with a discharge port 22a penetrating through the end wall 11a of the pump body 11 and opening to the outside at the start end. Therefore, the oil pressurized and discharged to the discharge port 22 by the pump action by the pump structure passes through the main oil gallery 27 provided in the cylinder block from the discharge port 22a and slides in the engine. It is supplied as a drive source for the lubrication of the parts and the valve timing control device.
- a communication groove 25 that communicates the discharge port 22 and the bearing hole 11b is formed in the inner surface of the end wall 11a, and oil is supplied to the bearing hole 11b through the communication groove 25 and the rotor. By supplying oil also to the side portions of 16 and each vane 17, good lubrication of each sliding portion is ensured.
- the cover member 12 has a substantially plate shape and is attached to the opening end surface of the pump body 11 by a plurality of bolts 29, and faces the bearing hole 11 b of the pump body 11.
- a bearing hole 12a that rotatably supports the other end side of the drive shaft 14 is formed through the position.
- the suction port, the discharge port, and the communication groove corresponding to the pump body 11 are provided on the inner surface of the cover member 12, and the suction port 21, the discharge port 22, and the communication groove on the pump body 11 side. 25.
- the drive shaft 14 is connected to the crankshaft or the like at one end in the axial direction that penetrates the cover member 12 and faces the outside, and the rotor is based on the rotational force transmitted from the crankshaft or the like. 16 is rotated clockwise in FIG.
- a straight line hereinafter referred to as “cam ring eccentric direction line” N passing through the center of the drive shaft 14 and orthogonal to the cam ring reference line M is a boundary line between the suction region and the discharge region. It has become.
- the rotor 16 has a plurality of slits 16a formed radially outward from the center thereof in the radial direction, and inner base ends of the slits 16a.
- back pressure chambers 16b each having a substantially circular cross section for introducing discharged oil, and the vanes 17 are caused by the centrifugal force accompanying the rotation of the rotor 16 and the pressure in the back pressure chambers 16b. It is pushed out to the outside.
- Each vane 17 has its distal end surface in sliding contact with the inner peripheral surface of the cam ring 15 and each proximal end surface in sliding contact with the outer peripheral surface of each of the ring members 18 and 18 when the rotor 16 rotates. Yes. That is, each of the vanes 17 is configured to be pushed up radially outward of the rotor 16 by the ring members 18 and 18, the engine speed is low, and the centrifugal force and the pressure of the back pressure chamber 16b are set. Is small, each tip is in sliding contact with the inner peripheral surface of the cam ring 15 so that each pump chamber 24 is liquid-tightly separated.
- the cam ring 15 is integrally formed of a so-called sintered metal in a substantially cylindrical shape, and a pivot pin 19 whose shaft center forms a swing fulcrum F is fitted into a predetermined position on the outer periphery thereof, thereby forming a circular arc groove shape.
- the pivot portion 15a is notched along the axial direction, and a coil spring 33 serving as an urging member set to a predetermined spring constant is provided at a position opposite to the pivot portion 15a with the center of the cam ring 15 in between.
- the arm portion 15b linked to the projection protrudes along the radial direction.
- the arm portion 15b is provided with a pressing projection (not shown) formed in a substantially arc shape on one side of the moving (turning) direction, and the pressing projection is a coil spring.
- the arm portion 15b and the coil spring 33 are linked together by always abutting against the tip end portion of the 33.
- the pivot pin 19 serving as the swing fulcrum F is a discharge region where the volumes of the plurality of pump chambers 24 are reduced, that is, approximately the center in the circumferential direction of the discharge port 22 on the right side in FIG. Located outside the position.
- a spring housing chamber 26 for housing and holding a coil spring 33 is provided in the pump body 11 at a position facing the support hole 11c, as shown in FIG.
- the coil spring 33 is provided adjacent to the pump housing chamber 13 so as to substantially follow the eccentric direction line N, and the spring housing chamber 26 has a predetermined set load W1 between its one end wall and the lower surface of the arm portion 15b. Is being armored.
- the other end wall of the spring accommodating chamber 26 is configured as a regulating surface 26a that regulates the range of movement of the cam ring 15 in the eccentric direction, and the cam ring is brought into contact with the other side of the arm portion 15b by the regulating surface 26a. Further movement in the 15 eccentric directions is regulated.
- the coil spring 33 is disposed outside the suction region where the volumes of the plurality of pump chambers 24 increase, that is, outside the boundary line N, substantially at the center position in the circumferential direction of the suction port 21 on the left side in FIG. Has been.
- the cam ring 15 is constantly urged in the direction of increasing eccentricity (clockwise in FIG. 4) via the arm portion 15b with the urging force of the coil spring 33, and is inoperative. Then, as shown in FIG. 4, the other side portion of the arm portion 15b is pressed against the restriction surface 26a, and the eccentric amount is restricted to a maximum position.
- first and second seal configurations provided on the outer peripheral portion of the cam ring 15 so as to face the first and second seal sliding contact surfaces 11d and 11e formed by the inner peripheral wall of the pump body 11.
- the portions 15c and 15d are formed so as to protrude, and the seal sliding contact surfaces 11d and 11e are formed in the seal holding grooves respectively formed on the seal surfaces of the seal constituting portions 15c and 15d when the cam ring 15 is eccentrically swung.
- the first and second seal members 20a and 20b that are in sliding contact with each other are accommodated and held.
- each of the first and second seal constituent portions 15c and 15d are formed to have predetermined radii slightly smaller than the radii R1 and R2 constituting the seal sliding contact surfaces 11d and 11e, respectively.
- a predetermined minute clearance is formed between each seal sliding surface 11d, 11e and each seal surface of each seal component 15c, 15d.
- each of the first and second seal members 20a and 20b is formed in an elongated shape linearly along the axial direction of the cam ring 15 with, for example, a fluorine-based resin material having low friction characteristics, and is formed at the bottom of each seal holding groove.
- seal sliding contact surfaces 11d and 11e are pressed against the seal sliding contact surfaces 11d and 11e by the elastic force of the rubber elastic member, and the sealing surfaces of the seal sliding contact surfaces 11d and 11e and the seal constituent portions 15c and 15d are pressed. Is liquid-tightly separated from each other.
- first and second control oil chambers 31 and 32 are separated from each other by the pivot pin 19 and the first and second seal members 20a and 20b in the outer peripheral area of the cam ring 15.
- the engine oil pressure corresponding to the pump discharge pressure is guided to the control oil chambers 31 and 32 through a control pressure introduction passage 70 branched from the main oil gallery 27.
- the pump discharge pressure is supplied to the first control oil chamber 31 through the first introduction passage 71 which is one branch passage branched from the control pressure introduction passage 70 into two branches.
- the second control oil chamber 32 is depressurized via the pilot valve 40 from the second introduction passage 72 which is the other branch passage branched to the control introduction passage 70 via the electromagnetic switching valve 60 which is a switching mechanism.
- Pump discharge pressure (hereinafter referred to as “second discharge pressure”) is supplied.
- the cam ring 15 has a first pressure receiving surface 15e from the first control oil chamber 31 of the cam ring 15 in addition to the biasing force in the direction in which the volume change amount of each pump chamber increases due to the spring force of the coil spring 33.
- the urging force acts in the direction in which the amount of eccentricity is reduced against the spring force of the coil spring 33 by the hydraulic pressure applied to the coil spring 33.
- the cam ring 15 is urged in the direction in which the eccentric amount is increased in cooperation with the spring force of the coil spring 33 by the hydraulic pressure applied from the second control oil chamber 32 to the second pressure receiving surface 15f. ing.
- the second pressure receiving surface 15f is set to have an area larger than that of the first pressure receiving surface 15e, and when the same hydraulic pressure is applied to both, the overall amount of eccentricity is increased (see FIG.
- the cam ring 15 is urged in the clockwise direction (4).
- the difference between the first and second torques (biasing forces) due to the difference in area between the first and second pressure receiving surfaces 15e and 15f can be expressed as a vector, and as shown in FIG.
- the first vector B1 (radius R1) in the direction of the first seal member 20a (end point) and the second vector B2 (radius in the direction of the second seal member 20b (end point)) starting from the pivot point F of the cam ring 15 which is R2).
- the second vector B2 is configured to be larger than the first vector B1.
- the pilot valve 40 is formed integrally with one side portion of the cover member 12 and has a cylindrical valve body having a valve receiving hole 41a formed at the lower end side in the inner axial direction. 41, a plug 42 that closes the lower end opening of the valve body 41, and an axially slidable housing on the inner peripheral side of the valve body 41, with respect to the second control oil chamber 32 according to the sliding position.
- a spool valve body 43 used for hydraulic pressure supply / discharge control is disposed on the inner peripheral side of the lower end portion of the valve body 41, and is spooled between the plug 42 and the spool valve body 43 with a predetermined set load W2.
- a valve spring 44 that constantly urges the valve body 43 toward the upper end side of the valve body 41 is mainly configured.
- the valve accommodating hole 41a accommodates and arranges the spool valve element 43 therein, and the electromagnetic switching valve 60 and the upper end wall via the first branch passage 72a branched on the downstream side of the second introduction passage 72.
- the introduction port 51 to be connected is formed with an opening.
- a plug 42 is press-fitted and fixed in the lower end opening of the valve housing hole 41a.
- the peripheral wall of the valve accommodating portion 41a is connected to the second control oil chamber 32 at one end in the axial direction, and the other end is always connected to a relay chamber 57, which will be described later.
- a supply / discharge port 52 for supplying / discharging hydraulic pressure to / from the control oil chamber 32 is formed as an opening. Further, one end side is connected to the suction side at a position on the lower end side in the axial direction of the valve accommodating hole 41a, and the inside of the second control oil chamber 32 is switched via the relay chamber 57 by switching communication with the relay chamber 57 described later.
- a first drain port 53 through which the hydraulic pressure is discharged is formed.
- valve body 41 is overlapped with a back pressure chamber 58 which will be described later, and a second drain port 54 communicating with the suction side is formed in the same manner as the first drain port 53.
- the supply / discharge port 52 is always in communication with the second control oil chamber 32 via a communication passage 59 formed in the lower portion of the valve body 41.
- the spool valve body 43 is in the upper position (see FIG. 7A) shown in FIG.
- a communication port 55 that connects the second branch passage 72b branched at the downstream end further than the first branch passage 72a and the relay chamber 57 is formed along the radial direction.
- the upper end surface of the first land portion 43a is formed as a pressure receiving surface 56 that receives the discharge pressure guided from the introduction port 51, and the first and second lower end portions in the axial direction Land portions 43a and 43b are provided.
- a small-diameter shaft portion 43c is provided between the land portions 43a and 43b, and the supply / discharge port 52 and the introduction port 51 (communication) are arranged on the outer periphery of the small-diameter shaft portion 43c depending on the axial position of the spool valve body 43.
- a cylindrical relay chamber 57 that relays to the port 55) or the first drain port 53 is formed.
- a back pressure chamber 58 is formed between the second land portion 43b and the plug 42 for discharging oil leaked from the relay chamber 57 through the outer peripheral side (small gap) of the second land portion 43b.
- the pilot valve 40 has a valve spring based on the set load W2 when the discharge pressure acting on the pressure receiving surface 56 from the introduction port 51 is equal to or lower than a predetermined pressure (operating hydraulic pressure of a spool valve 43 described later).
- the spool valve element 43 is positioned in a first area which is a predetermined area on the upper end side of the valve accommodating hole 41a by the urging force of 44 (see FIGS. 4 and 7A).
- the second branch passage 72b and the relay chamber 57 are communicated with each other via the communication port 55, and at the same time, the second land portion 43b and the first drain port 53 are connected.
- the communication between the relay chamber 57 is cut off, and the second control oil chamber 32 and the relay chamber 57 communicate with each other via the supply / discharge port 52.
- the spool valve body 43 moves from the first region to the lower side of the valve accommodating portion 41a against the spring force of the valve spring 44. Therefore, it is located in a second region which is a predetermined region below the valve accommodating portion 41a (see FIG. 8B). That is, when the spool valve body 43 is located in the second region, the second control oil chamber 32 is maintained in communication with the relay chamber 57 via the supply / discharge port 52, and at the same time, by the first land portion 43a. Communication between the communication port 55 and the relay chamber 57 is blocked, and the relay chamber 57 communicates with an oil pan or the like via the first drain port 53.
- the spool valve 43 is moved from the second region by the spring force of the valve spring 44.
- the first land portion 43a of the spool valve 43 closes the communication port 55 to block communication with the relay chamber 57 as shown in FIG.
- the land portion 43 b closes the first drain port 53 and blocks communication with the relay chamber 57.
- the electromagnetic switching valve 60 is interposed between the control pressure introduction passage 70 and the second introduction passage 72, and has a substantially cylindrical shape in which an oil passage 65 is formed so as to penetrate along the internal axis direction.
- the valve body 61 a valve body housing portion 66 formed by expanding the oil passage 65 formed in one end portion of the valve body 61, and press-fitted and fixed to the outer end portion of the valve body housing portion 66,
- a seat member 62 having an introduction port 67 which is an upstream opening connected to the upstream passage of the second introduction passage 72 in the center, and a valve seat 62a formed at the inner end opening edge of the seat member 62
- a solenoid valve 64 provided at the other end of the valve body 61 (the right end in the figure). It is mainly composed.
- the valve body 61 is formed on an inner peripheral portion on one end side of the valve body 61, and also has an inner edge opening edge of the valve body housing portion 66 that houses the ball valve body 63, similar to the valve seat 62 a included in the seat member 62.
- a valve seat 66a is formed.
- the upstream side of the second introduction passage 72 is connected to the outer peripheral portion of the valve body housing portion 66 which is one end side of the peripheral wall of the valve body 61, and is used for supplying and discharging hydraulic pressure to the pilot valve 40.
- a supply / discharge port 68 that is a side opening is formed so as to penetrate along the radial direction, and a drain port 69 connected to a drain side such as an oil pan has a diameter on the outer peripheral portion of the oil passage 65 that is the other end side. A plurality of penetrations are formed along the direction.
- the solenoid 64 has an armature disposed on the inner peripheral side of the coil and a rod 64b fixed to the coil 64b in FIG. 4 by electromagnetic force generated by energizing a coil (not shown) accommodated in the casing 64a. It is configured to move forward in the left direction.
- the solenoid 64 is energized with an excitation current from an in-vehicle ECU (not shown) based on the engine operating state detected or calculated based on predetermined parameters such as the oil temperature and water temperature of the internal combustion engine, and the engine speed. It becomes.
- the solenoid 64 when the solenoid 64 is energized, the ball valve body 63 disposed at the tip end of the rod 64b is pressed against the valve seat 62a on the seat member 62 side by the advancing movement of the rod 64b. The communication of the supply / discharge port 68 is blocked, and the supply / discharge port 68 and the drain port 69 are connected through the oil passage 65. On the other hand, when the solenoid 64 is not energized, the ball valve body 63 moves backward based on the discharge pressure guided from the introduction port 67, thereby pushing the ball valve body 63 against the valve seat 66 a on the valve body 61 side and introducing it.
- the port 67 and the supply / discharge port 68 are in communication with each other, and the communication between the supply / discharge port 68 and the drain port 69 is blocked.
- P1 is the first required engine oil pressure corresponding to the required oil pressure of the apparatus when, for example, a valve timing control device for improving fuel efficiency is adopted
- P2 in the figure is the bearing of the crankshaft at high engine speed.
- the second engine required oil pressure required for partial lubrication is shown. It is ideal to change the discharge pressure (necessary oil pressure) P according to the engine speed N of the internal combustion engine like these required oil pressures P1 and P2.
- the solid line in FIG. 6 represents the hydraulic characteristic of the oil pump 10 according to the present invention, and the one-dot broken line represents the hydraulic characteristic of the conventional pump from the arrival point CA that has reached the discharge pressure P2. is there.
- the excitation current is supplied to the solenoid 64 in the section a in FIG. 6 corresponding to the rotation range from the engine start to the low rotation range, and as shown in FIG. While the communication between 67 and the supply / discharge port 68 is blocked, the supply / discharge port 68 and the drain port 69 communicate with each other. Accordingly, the discharge pressure P is not introduced to the second control oil chamber 32 (pilot valve 40) side, and the spool valve body 43 of the pilot valve 40 is located in the first region.
- the oil in the second control oil chamber 32 passes through the supply / exhaust port 52, the relay chamber 57, the second branch passage 72b, and the oil passage 65 from the communication passage 59, as indicated by an arrow in the drawing, and the electromagnetic switching valve 60.
- the discharge pressure P is supplied only to the first control oil chamber 31.
- the discharge pressure P is lower than the hydraulic pressure for swinging the cam ring 15 in this engine rotation region, the cam ring 15 is held in the maximum eccentric state, and the discharge pressure P reaches the engine speed N. It becomes a characteristic that increases in an almost proportional manner.
- the biasing force in the eccentric direction with respect to the cam ring 15 is applied in the concentric direction based on the internal pressure of the first control oil chamber 31 by the resultant force of the biasing force W1 of the coil spring 33 and the biasing force based on the internal pressure of the second control oil chamber 32.
- the cam ring 15 is pushed back in an increasing direction, and the amount of increase in the discharge pressure P increases again (section c in FIG. 6).
- the urging force in the concentric direction based on the internal pressure of the first control oil chamber 32 is an urging force in the eccentric direction consisting of the resultant force of the urging force W1 of the coil spring 33 and the urging force based on the internal pressure of the second control oil chamber 32.
- the discharge pressure P decreases as the cam ring 15 moves in the concentric direction.
- the concentric biasing force based on the internal pressure of the first control oil chamber 31 is a resultant force of the biasing force W1 of the coil spring 33 and the biasing force based on the internal pressure of the second control oil chamber 32.
- the discharge pressure P decreases again.
- the spool valve body 43 of the pilot valve 40 allows the communication between the supply / discharge port 52 and the communication port 55 or the first drain port 53 that communicate with the second control oil chamber 32.
- the discharge pressure P is adjusted to be maintained at the operating hydraulic pressure of the spool valve 43.
- such pressure regulation is performed by switching the supply / discharge port 52 by the pilot valve 40, and therefore is not affected by the spring constant of the coil spring 33.
- the pressure adjustment is performed within a very narrow stroke range of the spool valve body 43 related to the switching of the supply / exhaust port 52, there is no possibility of being influenced by the spring constant of the valve spring 44.
- the discharge pressure P of the oil pump 10 does not increase proportionally as the engine speed N increases, but has a substantially flat characteristic.
- the oil pump 10 is required to maintain at least a predetermined pressure (spool valve operating oil pressure) that is at least as high as the second engine required oil pressure P2 based on the pressure regulation control by the pilot valve 40.
- a predetermined pressure spool valve operating oil pressure
- the discharge pressure P can be maintained at the high predetermined pressure P2.
- the discharge pressure P is greater than the operating oil pressure of the spool valve 43 that is greater than the operating oil pressure of the cam ring 15 and less than the operating oil pressure of the spool valve 43.
- the spool valve body 43 moves from the first region to the second region, and the eccentric amount of the cam ring 15 decreases along with this movement, so that the discharge pressure P becomes the spool valve operating hydraulic pressure again.
- the discharge pressure P is maintained at the operating oil pressure of the spool valve 43. And a predetermined high-pressure characteristic P2 can be maintained.
- the sliding position of the spool valve 43 of the pilot valve 40 moves from the first region to the second region, so that the oil is in the second control oil chamber 32.
- the first land portion 43a of the spool valve 43 opens the opening on the side of the valve accommodating hole 41a of the communication port 55 immediately before being discharged to the first drain port 53 from the relay chamber 57.
- the second land portion 43b closes the opening end of the first drain port 53, and the second control oil chamber 32, the communication path 59, and the supply / discharge port 52 are temporarily closed.
- the cam ring 15 since the second control oil chamber 32 is kept filled with oil, the cam ring 15 has the second control oil having a larger area than the first pressure receiving surface 15e on the first control oil chamber 31 side.
- the hydraulic pressure (second vector B2) acting on the second pressure receiving surface 15f on the chamber 32 side and the resultant force of the coil spring 33 are stably held at a position in the direction in which the amount of eccentricity increases.
- FIG. 10 shows a second embodiment of the variable displacement oil pump, the basic configuration of which is the same as that of the first embodiment, but the difference is between the first control oil chamber 31 and the second control oil chamber 32.
- a third control oil chamber 80 is provided.
- a third control oil chamber 80 is provided between the support hole 11 c that supports the pivot pin 19 of the pump body 11 and the first control oil chamber 31.
- the outer periphery of the cam ring 15 is formed with a third seal constituting portion 15 h that protrudes from the third seal sliding contact surface 11 f that is formed by the inner peripheral wall of the pump body 11.
- the third seal member 20c that is slidably contacted with the third seal slidable contact surface 11f when the cam ring 15 is eccentrically swung is accommodated and held in the seal holding grooves respectively formed on the outer surface of the seal component 15h.
- the third seal member 20c like the first and second seal members 20a and 20b, is formed into a thin and long straight line made of, for example, a fluorine-based resin material having low friction characteristics, and is disposed at the bottom of the seal holding groove. By being pressed against the third seal sliding contact surface 11f by the elastic force of the made elastic member, the third seal sliding contact surface 11f is liquid-tightly separated.
- the third control oil chamber 80 is separated by the pivot pin 19 and the third seal member 20c.
- the third control oil chamber 80 communicates with a low pressure part such as in the oil pan via a drain port 81.
- 1st vector B1 (radius R1) is larger than 1st Embodiment. That is, the second vector B2 that contributes to the swinging force of the cam ring 15 only needs to be larger than the first vector B1, and the first and second control oil chambers 31 and 32 can be appropriately arranged around the outer periphery of the cam ring 15. .
- FIG. 11 shows the third embodiment.
- the formation position of the third control oil chamber 90 is changed, and the first control oil chamber 31 is formed at the same position as in the first embodiment.
- a third control oil chamber 90 is provided between the support hole 11 c that supports the pivot pin 19 of the pump body 11 and the second control oil chamber 32.
- a third seal constituting portion 15i provided to face the third seal sliding contact surface 11g constituted by the inner peripheral wall of the pump body 11 is formed on the outer peripheral portion of the cam ring 15 so as to protrude.
- the third seal member 20d slidably contacting the third seal slidable contact surface 11g when the cam ring 15 is eccentrically swung is accommodated and held in a seal retaining groove formed on the outer surface of the seal component 15i.
- the third seal member 20d is formed in a straight and long shape with, for example, a fluorine resin material having low friction characteristics, and is disposed at the bottom of the seal holding groove.
- the third control oil chamber 90 is liquid-tightly separated between the pivot pin 19 and the third seal sliding contact surface 11g by being pressed against the third seal sliding contact surface 11g with the elastic force of the made elastic member. ing.
- the third control oil chamber 90 communicates with a low pressure portion such as in the oil pan via a drain port 91.
- the cam ring 15 can be stably held at the high pressure characteristic P2.
- oil leaking from the first control oil chamber 31 and the second control oil chamber 32 via the third seal member 20d, the pivot pin 19 and the like is collected in the third control oil chamber 90, from which the drain port is collected. Since the oil amount supplied to the inside of the first control oil chamber 31 and the second control oil chamber 32 can be accurately controlled, the swing position control of the cam ring 15 can be performed. Can be further stabilized.
- the oil pump 10 is mounted for the engine required oil pressures P1 and P2, the operating oil pressure of the cam ring 15 and the operating oil pressure of the spool valve 43. It can be freely changed according to the specifications of the internal combustion engine of the vehicle, the valve timing control device and the like.
- the discharge amount is made variable by swinging the cam ring 15
- means for making the discharge amount variable only the means related to the swing is described.
- the cam ring 15 may be moved linearly in the radial direction.
- the mode of movement of the cam ring 15 is not limited as long as the discharge amount can be changed (the volume change amount of the pump chamber 24 can be changed).
- variable displacement vane pump has been described as an example.
- present invention can also be applied to, for example, a trochoid pump.
- an outer rotor that constitutes an external gear is attached to the swing member.
- the variable mechanism is configured by disposing the outer rotor so as to be eccentrically movable like the cam ring 15 and disposing the control oil chamber and the spring on the outer peripheral side thereof.
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Abstract
Description
〔オイルポンプの作用〕
以下、本実施形態に係るオイルポンプ10の作用を、図7~図9に基づいて説明する。
〔第2実施形態〕
図10は可変容量形オイルポンプの第2実施形態を示し、基本構成は第1実施形態と同様であるが、異なるところは、第1制御油室31と第2制御油室32との間に第3制御油室80が設けられている。
〔第3実施形態〕
図11は第3実施形態を示し、この実施形態では、第3制御油室90の形成位置を変更したもので、第1制御油室31が第1実施形態と同じ位置に形成されているが、前記ポンプボディ11のピボットピン19を支持する支持穴11cと第2制御油室32との間に第3制御油室90が設けられている。
Claims (16)
- 回転駆動されることにより複数のポンプ室の容積を変化させて吸入部から吸入された作動油を吐出部から吐出するポンプ構成体と、
該ポンプ構成体を内側に収容し、外周側に設けられた揺動支点を支点として揺動することによって、前記吐出部に開口した前記複数のポンプ室の容積変化量を可変にする揺動部材と、
セット荷重が付与された状態で設けられ、前記揺動部材を前記複数のポンプ室の容積変化量が増大する方向へ付勢する付勢部材と、
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が小さくなる方向の第1トルクを前記揺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が大きくなる方向でかつ前記第1トルクよりも大きな第2トルクを前記揺動部材に作用させる第2制御油室と、
該第2制御油室に対する作動油の供給あるいは排出を切り換える切換機構と、
を備えたことを特徴とする可変容量形オイルポンプ。 - 請求項1に記載の可変容量形オイルポンプにおいて、
前記第2トルクに供される前記揺動支点を始点とする第2ベクトルは、前記第1トルクに供される前記揺動支点を始点とする第1ベクトルよりも大きいことを特徴とする可変容量形オイルポンプ。 - 請求項2に記載の可変容量形オイルポンプにおいて、
前記揺動支点は、前記吐出部が形成された前記複数のポンプ室の容積が減少する吐出領域に設けられていると共に、
前記付勢部材は、前記吸入部が形成された前記複数のポンプ室の容積が増加する吸入領域に設けられていることを特徴とする可変容量形オイルポンプ。 - 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ベクトルの終点は、前記吐出領域に設けられている一方、
前記第2ベクトルの終点は、前記吸入領域に設けられていることを特徴とする可変容量形オイルポンプ。 - 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ベクトルの終点は、前記吸入領域に設けられていることを特徴とする可変容量形オイルポンプ。 - 請求項1に記載の可変容量形オイルポンプにおいて、
前記第2トルクに供される前記揺動部材の第2受圧面の面積は、前記第1トルクに供される前記揺動部材の第1受圧面よりも大きいことを特徴とする可変容量形オイルポンプ。 - 請求項1に記載の可変容量形オイルポンプにおいて、
前記第2制御油室と切換機構との間に設けられ、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く状態と、前記第2制御油室内の作動油が排出される状態とすると共に、前記第1制御油室に作動油が導入されている状態において、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を設けたことを特徴とする可変容量形オイルポンプ。 - 請求項7に記載の可変容量形オイルポンプにおいて、
前記制御機構は、前記第2制御油室に対して作動油が導入される状態から排出される状態に切り換える際に、一旦、前記第2制御油室に対する作動油の導入及び排出が遮断される状態にすることを特徴とする可変容量形オイルポンプ。 - 請求項1に記載の可変容量形オイルポンプにおいて、
前記揺動支点を挟んだ周方向の前記第1制御油室と第2制御油室との間でかつ前記揺動支点と第1制御油室に隣接した位置に、低圧側と連通する第3制御油室を有することを特徴とする可変容量形オイルポンプ。 - 請求項1に記載の可変容量形オイルポンプにおいて、
前記揺動支点を挟んだ周方向の前記第1制御油室と第2制御油室との間でかつ前記揺動支点と第2制御油室に隣接した位置に、低圧側と連通する第3制御油室を有することを特徴とする可変容量形オイルポンプ。 - 請求項10に記載の可変容量形オイルポンプにおいて、
前記第2トルクに供される前記揺動部材の外周面に形成された第2受圧面の面積は、前記第1トルクに供される前記揺動部材の外周面の第1受圧面の面積よりも大きく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。 - ポンプハウジング内に収容され、回転駆動されることにより複数のポンプ室の容積を変化させて吸入部から吸入された作動油を吐出部から吐出するポンプ構成体と、
該ポンプ構成体を内側に収容し、外周側に設けられた揺動支点を支点として揺動することによって、前記吐出部に開口した前記複数のポンプ室の容積変化量を可変にする揺動部材と、
セット荷重が付与された状態で設けられ、前記揺動部材を前記複数のポンプ室の容積変化量が増大する方向へ付勢する付勢部材と、
前記ポンプハウジングの内周面と前記揺動部材の外周面との間に隔成されると共に、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が小さくなる方向の力を前記揺動部材の第1受圧面に作用させる第1制御油室と、
前記ポンプハウジングの内周面と前記揺動部材の外周面との間に隔成されると共に、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が大きくなる方向の力を前記揺動部材の第2受圧面に作用させる第2制御油室と、
前記ポンプハウジングの内周面に形成され、前記揺動支点と協働して前記第1制御油室を隔成しつつ前記揺動部材の外周部に有する第1シール部材が摺接すると共に、前記揺動支点から第1シール摺接面までの第1半径長さを有する円弧状の第1シール摺接面と、
前記ポンプハウジングの内周面に形成され、前記揺動支点と協働して前記第2制御油室を隔成しつつ前記揺動部材の外周部に有する第2シール部材が摺接すると共に、前記揺動支点から第2シール摺接面までの第2半径長さが前記第1半径長さよりも大きく形成された円弧状の第2シール摺接面と、
を備えたことを特徴とする可変容量形オイルポンプ。 - 請求項12に記載の可変容量形オイルポンプにおいて、
前記第2受圧面の面積は、前記第1受圧面の面積よりも大きく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。 - 請求項13に記載の可変容量形オイルポンプにおいて、
前記揺動支点は、前記吐出部を有する前記複数のポンプ室の容積が減少する吐出領域に設けられている一方、
前記付勢部材は、前記吸入部を有する前記複数のポンプ室の容積が増加する吸入領域に設けられ、
前記第1、第2半径長さは、前記吸入領域に設けられていることを特徴とする可変容量形オイルポンプ。 - 請求項14に記載の可変容量形オイルポンプにおいて、
前記ポンプハウジングの内側に設けられた前記揺動部材の外周が摺接する第3シール摺接部と前記揺動部材の外周及び前記揺動支点とによって隔成されて、低圧側と連通する第3制御油室を前記吐出領域に配置したことを特徴とする可変容量形オイルポンプ。 - 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、
前記ロータとベーンが内側に収容され、内径中心が前記ロータの回転中心と偏心して配置され、内部に複数のポンプ室を隔成すると共に、外周側に設けられた揺動支点を支点として揺動することによって偏心量が変化して前記複数のポンプ室の容積変化量を可変にするカムリングと、
前記ロータの回転によってポンプ容積が増大する前記複数のポンプ室に開口した吸入部と、
前記ロータの回転によってポンプ容積が減少する前記複数のポンプ室に開口した吐出部と、
セット荷重が付与された状態で設けられ、前記カムリングを前記複数のポンプ室の容積変化量が増大する方向へ付勢する付勢部材と、
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へ第1トルク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でかつ前記第1トルクよりも大きな第2トルク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制御油室に対して作動油を供給あるいは排出を切り換える切換機構と、
を備えたことを特徴とする可変容量形オイルポンプ。
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CN201910659886.3A CN110360100B (zh) | 2015-06-19 | 2016-03-31 | 可变容量型油泵 |
DE112016002759.1T DE112016002759T5 (de) | 2015-06-19 | 2016-03-31 | Verstellbare Ölpumpe |
US15/737,595 US11905948B2 (en) | 2015-06-19 | 2016-03-31 | Variable displacement oil pump including swing member |
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Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP6491305B1 (ja) * | 2017-10-20 | 2019-03-27 | ミョンファ インダストリー カンパニー,リミテッド | 2段可変オイルポンプ |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP7077638B2 (ja) * | 2018-01-31 | 2022-05-31 | 株式会社アイシン | 可変オイルポンプ |
FR3136807B1 (fr) * | 2022-06-17 | 2024-06-21 | Safran Trans Systems | Module de lubrification d’un poste de lubrification d’une turbomachine |
Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5970891A (ja) * | 1982-10-16 | 1984-04-21 | Toyota Central Res & Dev Lab Inc | 可変容量形ベ−ンポンプ |
JP2000104671A (ja) * | 1998-09-28 | 2000-04-11 | Kayaba Ind Co Ltd | 可変容量型ベーンポンプ |
JP2002147373A (ja) * | 2000-11-13 | 2002-05-22 | Unisia Jecs Corp | 可変容量型ベーンポンプ |
JP2013130089A (ja) * | 2011-12-21 | 2013-07-04 | Hitachi Automotive Systems Ltd | 可変容量形ポンプ |
WO2014038302A1 (ja) * | 2012-09-07 | 2014-03-13 | 日立オートモティブシステムズ株式会社 | 可変容量形オイルポンプ及びこれを用いたオイル供給システム |
Family Cites Families (18)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US7794217B2 (en) | 2004-12-22 | 2010-09-14 | Magna Powertrain Inc. | Variable capacity vane pump with dual control chambers |
JP5174720B2 (ja) * | 2009-03-09 | 2013-04-03 | 日立オートモティブシステムズ株式会社 | 可変容量形ポンプ |
JP5145271B2 (ja) * | 2009-03-11 | 2013-02-13 | 日立オートモティブシステムズ株式会社 | 可変容量オイルポンプ |
JP2011163194A (ja) * | 2010-02-09 | 2011-08-25 | Hitachi Automotive Systems Ltd | 可変容量形ポンプと、該可変容量形ポンプを用いた潤滑システム及びオイルジェット |
JP5550784B2 (ja) | 2010-05-28 | 2014-07-16 | ピールブルグ パンプ テクノロジー ゲゼルシャフト ミット ベシュレンクテル ハフツング | 可変容積形潤滑剤ポンプ |
JP5564450B2 (ja) * | 2011-02-17 | 2014-07-30 | 日立オートモティブシステムズ株式会社 | オイルポンプ |
JP5620882B2 (ja) * | 2011-05-23 | 2014-11-05 | 日立オートモティブシステムズ株式会社 | 可変容量形ポンプ |
JP5688003B2 (ja) * | 2011-12-21 | 2015-03-25 | 日立オートモティブシステムズ株式会社 | 可変容量形オイルポンプ |
JP5970891B2 (ja) * | 2012-03-21 | 2016-08-17 | 株式会社リコー | 電子写真感光体、電子写真感光体の製造方法、画像形成装置用プロセスカートリッジおよび画像形成装置 |
JP6050640B2 (ja) * | 2012-09-07 | 2016-12-21 | 日立オートモティブシステムズ株式会社 | 可変容量形オイルポンプ |
JP6082548B2 (ja) * | 2012-09-07 | 2017-02-15 | 日立オートモティブシステムズ株式会社 | 可変容量形ポンプ |
US20140105620A1 (en) * | 2012-10-17 | 2014-04-17 | Lexmark International, Inc. | Methods for Providing an Estimated Replacement Date for a Replaceable Unit of an Image Forming Device |
JP5993291B2 (ja) * | 2012-11-27 | 2016-09-14 | 日立オートモティブシステムズ株式会社 | 可変容量形ポンプ |
JP6006098B2 (ja) | 2012-11-27 | 2016-10-12 | 日立オートモティブシステムズ株式会社 | 可変容量形ポンプ |
JP6004919B2 (ja) * | 2012-11-27 | 2016-10-12 | 日立オートモティブシステムズ株式会社 | 可変容量形オイルポンプ |
US20140182541A1 (en) * | 2012-12-28 | 2014-07-03 | Kia Motors Corporation | Oil pump for vehicle |
JP6289943B2 (ja) * | 2014-03-10 | 2018-03-07 | 日立オートモティブシステムズ株式会社 | 可変容量形ポンプ |
JP2016104967A (ja) * | 2014-12-01 | 2016-06-09 | 日立オートモティブシステムズ株式会社 | 可変容量形オイルポンプ |
-
2016
- 2016-03-31 MX MX2017016286A patent/MX2017016286A/es unknown
- 2016-03-31 CN CN201910659886.3A patent/CN110360100B/zh active Active
- 2016-03-31 JP JP2017524681A patent/JP6635437B2/ja active Active
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- 2016-03-31 CN CN201680035897.9A patent/CN107709780B/zh active Active
- 2016-03-31 US US15/737,595 patent/US11905948B2/en active Active
- 2016-03-31 WO PCT/JP2016/060702 patent/WO2016203811A1/ja active Application Filing
-
2019
- 2019-12-09 JP JP2019221936A patent/JP6838772B2/ja active Active
Patent Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5970891A (ja) * | 1982-10-16 | 1984-04-21 | Toyota Central Res & Dev Lab Inc | 可変容量形ベ−ンポンプ |
JP2000104671A (ja) * | 1998-09-28 | 2000-04-11 | Kayaba Ind Co Ltd | 可変容量型ベーンポンプ |
JP2002147373A (ja) * | 2000-11-13 | 2002-05-22 | Unisia Jecs Corp | 可変容量型ベーンポンプ |
JP2013130089A (ja) * | 2011-12-21 | 2013-07-04 | Hitachi Automotive Systems Ltd | 可変容量形ポンプ |
WO2014038302A1 (ja) * | 2012-09-07 | 2014-03-13 | 日立オートモティブシステムズ株式会社 | 可変容量形オイルポンプ及びこれを用いたオイル供給システム |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP6491305B1 (ja) * | 2017-10-20 | 2019-03-27 | ミョンファ インダストリー カンパニー,リミテッド | 2段可変オイルポンプ |
JP2019078258A (ja) * | 2017-10-20 | 2019-05-23 | ミョンファ インダストリー カンパニー,リミテッド | 2段可変オイルポンプ |
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