WO2016194933A1 - ポンプ装置 - Google Patents

ポンプ装置 Download PDF

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Publication number
WO2016194933A1
WO2016194933A1 PCT/JP2016/066137 JP2016066137W WO2016194933A1 WO 2016194933 A1 WO2016194933 A1 WO 2016194933A1 JP 2016066137 W JP2016066137 W JP 2016066137W WO 2016194933 A1 WO2016194933 A1 WO 2016194933A1
Authority
WO
WIPO (PCT)
Prior art keywords
pump
sub
discharge
notch
working fluid
Prior art date
Application number
PCT/JP2016/066137
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
浩一朗 赤塚
藤田　朋之
智行 中川
史恭 加藤
裕希 五味
Original Assignee
Ｋｙｂ株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Ｋｙｂ株式会社 filed Critical Ｋｙｂ株式会社
Priority to CN201680032273.1A priority Critical patent/CN107636309A/zh
Priority to US15/578,437 priority patent/US20180149153A1/en
Priority to EP16803367.8A priority patent/EP3306094A4/en
Publication of WO2016194933A1 publication Critical patent/WO2016194933A1/ja

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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
    • 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
    • F04C14/26—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 using bypass channels
    • 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
    • F04C11/00—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations
    • 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
    • F04C11/00—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations
    • F04C11/001—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations of similar working principle
    • 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
    • F04C14/02—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations specially adapted for several machines or pumps connected in series or in parallel
    • 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
    • F04C15/0042—Systems for the equilibration of forces acting on the machines or pump
    • F04C15/0049—Equalization of pressure pulses
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/06—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C2/34—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
    • F04C2/344—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F04C2/3446—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 more than one line or surface
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/08—Rotary pistons
    • F01C21/0809—Construction of vanes or vane holders
    • F01C21/0818—Vane tracking; control therefor
    • F01C21/0854—Vane tracking; control therefor by fluid means
    • F01C21/0863—Vane tracking; control therefor by fluid means the fluid being the working fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/10—Outer members for co-operation with rotary pistons; Casings
    • F01C21/104—Stators; Members defining the outer boundaries of the working chamber
    • F01C21/108—Stators; Members defining the outer boundaries of the working chamber with an axial surface, e.g. side plates
    • 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
    • F04C2270/12—Vibration
    • 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
    • F04C2270/13—Noise

Definitions

  • the present invention relates to a pump device.
  • JP2010-14101A discloses a multiple vane pump in which the rotors of the first vane pump and the second vane pump are connected in parallel by being connected by a common drive shaft.
  • This multi-type vane pump supplies the working fluid to the fluid pressure device by the first vane pump and the second vane pump at the time of starting.
  • the working fluid discharged from the first vane pump is returned to the suction passage, and the second vane pump alone is used as a fluid. Supply working fluid to pressure equipment.
  • Such a vane pump has a groove-shaped notch communicating with the discharge port in order to prevent a sudden change in the pressure of the working fluid guided to the high-pressure chamber.
  • the notch in order to prevent sudden pressure fluctuations of the working fluid at the time of high rotation of the pump, the notch has a large length and cross-sectional area, and the resistance given to the flow of the working fluid passing through is compared. May be formed to be smaller.
  • the pressure increase rate in the pump chamber with respect to the rotation angle of the pump is increased by reducing the resistance given by the notch and promoting the flow of the working fluid from the high pressure chamber to the pump chamber through the notch.
  • the pump chamber communicates with the high-pressure chamber in a state where the pressure is sufficiently increased, so that rapid fluctuations in the pressure of the working fluid are prevented, and generation of vibration and noise during high rotation of the pump is suppressed.
  • An object of the present invention is to suppress generation of vibration and noise in a pump device having a main pump and a sub pump.
  • a pump device that supplies a working fluid to a fluid pressure device, the main pump supplying the working fluid to the fluid pressure device through a first discharge passage, and the first discharge passage.
  • a sub-pump for supplying the working fluid to the fluid pressure device through the second discharge passage, a return passage for returning the working fluid discharged from the sub-pump to the suction side, and the working fluid discharged from the sub-pump A switching valve for switching whether or not to circulate to the suction side through a return passage, wherein each of the main pump and the sub pump is reciprocally moved in a radial direction with respect to a rotor connected to a common drive shaft.
  • a plurality of vanes provided freely, a cam ring having an inner peripheral surface on which a tip of the vane slides as the rotor rotates, and the row And a pump chamber defined by the cam ring and a pair of adjacent vanes, a discharge port to which a working fluid discharged from the pump chamber is guided, and the discharge port in a direction opposite to the rotation direction of the rotor
  • a groove-like discharge-side notch formed from the opening edge of the opening, and the switching valve is switched according to the rotational speed of the drive shaft, and is at least one of the discharge-side notches of the sub-pump. Is formed so as to increase the resistance given to the flow of the working fluid that passes therethrough as compared with the discharge-side notch of the main pump.
  • FIG. 1 is a cross-sectional view of a pump device according to an embodiment of the present invention.
  • FIG. 2 is a plan view of a pump cartridge in the main pump of the pump device according to the embodiment of the present invention, and is a view taken in the direction of arrow A in FIG.
  • FIG. 3 is a plan view of a pump cartridge in the sub pump of the pump device according to the embodiment of the present invention, and is a view taken in the direction of arrow B in FIG.
  • FIG. 4 is a hydraulic circuit diagram of the pump device according to the embodiment of the present invention.
  • FIG. 5 is a graph showing the flow characteristics of the pump device according to the embodiment of the present invention.
  • FIG. 6A is an enlarged view showing the relationship between the pump chamber, the discharge port, and the notch of the pump device according to the embodiment of the present invention, and is an enlarged view showing the main pump.
  • FIG. 6B is an enlarged view showing a relationship between a pump chamber, a discharge port, and a notch of the pump device according to the embodiment of the present invention, and is an enlarged view showing a sub pump.
  • FIG. 7A is a cross-sectional view showing a notch shape of the pump device according to the embodiment of the present invention, and is a cross-sectional view showing a notch of the main pump.
  • FIG. 7B is a cross-sectional view showing the notch shape of the pump device according to the embodiment of the present invention, and is a cross-sectional view showing the notch of the sub pump.
  • FIG. 7C is a view obtained by superimposing FIGS. 7A and 7B.
  • FIG. 8A is a cross-sectional view showing a modification of the notch shape of the pump device according to the embodiment of the present invention, and is a cross-sectional view showing the notch of the main pump.
  • FIG. 8B is a sectional view showing a modification of the notch shape of the pump device according to the embodiment of the present invention, and is a sectional view showing a notch of the sub pump.
  • FIG. 8C is a diagram in which FIG. 8A and FIG. 8B are superimposed.
  • FIG. 9A is a cross-sectional view showing another modification of the notch shape of the pump device according to the embodiment of the present invention, and is a cross-sectional view showing the notch of the main pump.
  • FIG. 9B is a cross-sectional view showing another modification of the notch shape of the pump device according to the embodiment of the present invention, and is a cross-sectional view showing the notch of the sub pump.
  • FIG. 9C is a diagram in which FIG. 9A and FIG. 9B are superimposed.
  • FIG. 10 is a hydraulic circuit diagram showing a modification of the pump device according to the embodiment of the present invention.
  • FIG. 11 is a view showing a modification of the pump device according to the embodiment of the present invention, and is a plan view of the center plate.
  • the pump device 100 is used as a hydraulic supply source for a hydraulic device mounted on a vehicle, for example, a power steering device or a transmission.
  • the pump device 100 is driven by connecting the rotors 2 of the main pump 101 and the sub pump 102 to a common drive shaft 1 to which the power of the engine 24 (see FIG. 4) is transmitted.
  • the rotor 2 is rotated by the rotation of the shaft 1.
  • 2 and 3 are views showing the pump cartridges 21 and 22 of the main pump 101 and the sub pump 102, and are plan views seen from the directions of arrows A and B in FIG. 1, respectively.
  • the rotor 2 rotates clockwise in FIG. 2 and counterclockwise in FIG.
  • the hydraulic oil (working fluid) discharged from the main pump 101 is always supplied to the hydraulic equipment (fluid pressure equipment) 23 (see FIG. 4).
  • the hydraulic oil discharged from the sub pump 102 is supplied to the hydraulic equipment 23 or recirculates to the suction side in accordance with the operation of the switching valve 40 (see FIG. 4).
  • the main pump 101 and the sub-pump 102 contain a plurality of vanes 3 provided so as to be capable of reciprocating in the radial direction with respect to the rotor 2, and accommodate the rotor 2 as the rotor 2 rotates. And a cam ring 4 in which the tip of the vane 3 is in sliding contact with the cam surface 4a on the inner periphery.
  • slits 16 having openings on the outer peripheral surface are radially formed at predetermined intervals, and the vanes 3 are slidably inserted into the slits 16.
  • a back pressure chamber 17 into which pump discharge pressure is guided is defined on the proximal end side of the slit 16.
  • Adjacent back pressure chambers 17 communicate with each other by an arc-shaped groove 2a formed in the rotor 2, and pump discharge pressure is always guided to the groove 2a.
  • the vane 3 is pressed in the direction of coming out of the slit 16 by the pressure of the back pressure chamber 17 and the centrifugal force due to the rotation of the rotor 2, and the tip part comes into contact with the cam surface 4 a on the inner periphery of the cam ring 4.
  • a plurality of pump chambers 7 are defined in the cam ring 4 by the outer peripheral surface of the rotor 2, the cam surface 4 a of the cam ring, and a pair of adjacent vanes 3.
  • the rotor 2, the vane 3, and the cam ring 4 constitute pump cartridges 21 and 22.
  • the cam ring 4 is an annular member having an inner circumferential cam surface 4 a that is substantially elliptical.
  • the suction ring 4 b expands the volume of the pump chamber 7 as the rotor 2 rotates, and the volume of the pump chamber 7 contracts.
  • a discharge region 4c is provided.
  • a center plate 5 is disposed between the pump cartridges 21 and 22 of the main pump 101 and the sub pump 102, and a side plate 6 is disposed on the side of each pump cartridge 21 and 22 (see FIG. 1). As described above, the pump cartridges 21 and 22 are sandwiched between the center plate 5 and the side plate 6, and the pump chamber 7 is sealed by the center plate 5 and the side plate 6.
  • the center plate 5 is formed with a suction port 8 that opens toward the suction region 4 b of the cam ring 4 and guides hydraulic oil to the pump chamber 7.
  • the side plate 6 is formed with two arc-shaped discharge ports 9 that open toward the discharge region 4c of the cam ring 4 and guide the hydraulic oil discharged from the pump chamber 7.
  • groove-shaped notches (discharge side notches) 9a and 9b extending from the opening edge of the discharge port 9 in the direction opposite to the rotation direction of the rotor 2 are formed.
  • The By forming the notches 9a and 9b, as the rotor 2 rotates, the flow of hydraulic oil through the notches 9a and 9b from the pump chamber 7 to the discharge port 9 is promoted. Pressure fluctuation is prevented.
  • Each pump chamber 7 sucks the working oil through the suction port 8 in the suction region 4 b of the cam ring 4 and makes the sucked hydraulic oil pass through the discharge port 9 in the discharge region 4 c of the cam ring 4 in the process of one rotation of the rotor 2. After that, the hydraulic oil is sucked through the suction port 8 in the suction area 4 b of the cam ring 4, and the sucked hydraulic oil is discharged through the discharge port 9 in the discharge area 4 c of the cam ring 4.
  • each pump chamber 7 expands and contracts with the rotation of the rotor 2, and performs the suction and discharge of the hydraulic oil twice in the process of rotating the rotor 2 once.
  • the drive shaft 1 is rotatably supported by the first pump body 10 and the second pump body 11 via a bush 18.
  • the side plate 6 of the main pump 101 and the pump cartridge 21 are stacked and housed in the pump housing recess 10 a formed in the first pump body 10.
  • the center plate 5 is stacked and housed together with the side plate 6 and the pump cartridge 22 of the sub pump 102.
  • the main pump 101 is accommodated in the first pump body 10 and the sub pump 102 is accommodated in the second pump body 11.
  • the first pump body 10 and the second pump body 11 are fastened together by bringing the surfaces having the openings into contact with each other, and the respective pump housing recesses 10a and 11a are sealed.
  • the cam ring 4 and the side plate 6 of the main pump 101 and the sub pump 102 are prevented from rotating by two positioning pins 19 (see FIGS. 2 and 3) that pass through the center plate 5.
  • the positioning pin 19 restricts the relative rotation of the center plate 5 and the side plate 6 with respect to the cam ring 4. Thereby, the positioning of the suction area 4b of the cam ring 4 and the suction port 8 of the center plate 5 and the positioning of the discharge area 4c of the cam ring 4 and the discharge port 9 of the side plate 6 are performed.
  • a high pressure chamber 12 into which hydraulic oil discharged from the discharge port 9 flows is formed.
  • the hydraulic oil in the high pressure chamber 12 is supplied to the hydraulic equipment 23 through the first discharge passage 32 and the second discharge passage 34 (see FIG. 4).
  • the hydraulic oil in the high pressure chamber 12 is guided to the arc-shaped groove 2 a of the rotor 2 through the through hole 6 a formed in the side plate 6 and is guided to each back pressure chamber 17.
  • the suction passage 31 connected to the tank 36 is connected to the suction port 8 of the main pump 101 and the sub pump 102.
  • the first discharge passage 32 is connected to the discharge port 9 of the main pump 101, and hydraulic oil is always supplied from the main pump 101 to the hydraulic equipment 23 through the first discharge passage 32.
  • the switching passage 33 is connected to the discharge port 9 of the sub pump 102.
  • the switching passage 33 is provided with a switching valve 40 that switches the flow of hydraulic oil discharged from the sub pump 102.
  • the switching valve 40 is connected to a second discharge passage 34 that supplies hydraulic oil to the hydraulic device 23 and a return passage 35 that circulates the hydraulic oil to the suction side.
  • the second discharge passage 34 is provided so as to join the first discharge passage 32.
  • the switching valve 40 switches whether or not the hydraulic oil discharged from the sub pump 102 is circulated to the suction side through the return passage 35. More specifically, the switching valve 40 selectively switches whether the hydraulic oil discharged from the sub pump 102 is supplied to the hydraulic equipment 23 through the second discharge passage 34 or circulated to the suction side through the return passage 35. That is, the hydraulic oil discharged from the sub pump 102 is selectively guided to either the hydraulic equipment 23 or the suction passage 31 by switching the switching valve 40.
  • the switching valve 40 has a first communication position 40 a that communicates the switching passage 33 and the second discharge passage 34, and a second communication position 40 b that communicates the switching passage 33 and the return passage 35.
  • the switching valve 40 is an electromagnetic switching valve whose position is switched by a control current output from the controller 30.
  • the switching valve 40 is set to the second communication position 40b by the biasing force of the spring 42 when the solenoid 41 is not excited, and is set to the first communication position 40a against the biasing force of the spring 42 when the solenoid 41 is excited.
  • the position of the switching valve 40 is switched according to, for example, the rotational speed of the engine 24 input to the controller 30, that is, the pump rotational speed that is the rotational speed of the drive shaft 1 and the rotor 2.
  • the switching valve 40 is not limited to an electromagnetic switching valve, and may be a pilot switching valve that is switched by a pilot hydraulic pressure.
  • the main pump 101 sucks the hydraulic oil from the tank 36 through the suction passage 31 and supplies the hydraulic oil to the hydraulic equipment 23 through the first discharge passage 32.
  • the sub pump 102 sucks the hydraulic oil from the tank 36 through the suction passage 31, supplies the hydraulic oil to the hydraulic device 23 through the second discharge passage 34, or circulates the hydraulic oil to the suction side through the return passage 35.
  • the switching valve 40 is set to the first communication position 40a.
  • the hydraulic oil discharged from the main pump 101 is supplied to the hydraulic equipment 23 regardless of the position of the switching valve 40.
  • the hydraulic oil discharged from the sub pump 102 is supplied to the hydraulic equipment 23 through the second discharge passage 34.
  • the hydraulic equipment 23 is supplied with hydraulic oil having a flow rate that is the sum of the discharge flow rates of the main pump 101 and the sub pump 102.
  • FIG. 5 is a graph showing the relationship between the discharge flow rate of the pump device 100 and the rotational speed.
  • the solid line is the discharge flow rate of the pump device 100 as a whole
  • the broken line is the total discharge flow rate of the main pump 101 and the sub pump 102 and the discharge flow rate of the main pump 101 alone.
  • the discharge flow rate of the pump device 100 increases as the pump rotational speed increases.
  • the switching valve 40 is switched to the second communication position 40b.
  • the hydraulic oil discharged from the sub pump 102 is returned to the suction side through the return passage 35.
  • the main pump 101 and the sub pump The hydraulic oil discharged from 102 is supplied to the hydraulic device 23.
  • the pump rotation speed is equal to or higher than the pump rotation speed N1 (hereinafter referred to as “at the time of high pump rotation”)
  • the discharge flow rate of the main pump 101 alone is supplied to the hydraulic device 23 and discharged from the sub pump 102.
  • the hydraulic fluid is circulated to the suction side. That is, the sub-pump 102 is used as a pressure source that supplies hydraulic oil to the hydraulic equipment 23 when the pump rotates at a low speed, and is not used as a pressure source when the pump is at a high speed.
  • the notch shapes of the main pump 101 and the sub pump 102 will be specifically described with reference to FIGS.
  • the state where the communication between the pump chamber 7 and the suction port 8 is interrupted with the rotation of the rotor 2 is referred to as “reference state” (broken line in FIG. 6), and the pump chamber 7 and the discharge port 9 are notched 9a, 9b.
  • a state in which communication is performed directly without going through is referred to as a “communication state” (solid line in FIG. 6), and a region between the reference state and the communication state is referred to as a “transition region”.
  • the position in the reference state of the vane 3b on the front side in the rotational direction of the pair of vanes 3a and 3b that divide the pump chamber 7 is a “reference position” (see FIG. 6), and a notch at a position that is separated from the reference position by an angle ⁇ .
  • a cross-sectional area perpendicular to the center line C of 9a and 9b (see FIGS. 2, 3 and 6) is referred to as “notch opening area”.
  • the notches 9a and 9b of the main pump 101 and the sub pump 102 are formed in a substantially triangular shape with a cross-sectional shape perpendicular to the longitudinal direction, that is, a cross-sectional shape perpendicular to the center line C.
  • the notches 9a and 9b of the main pump 101 and the sub pump 102 are formed in a tapered shape in which the cross-sectional area gradually decreases from the opening edge on the rear side in the rotation direction of the discharge port 9 toward the rear in the rotation direction of the rotor 2. Is done.
  • FIGS. 6A and 6B are diagrams showing the relationship among the pump chamber 7, the suction port 8, the discharge port 9, and the notches 9a and 9b.
  • the main pump 101 and the sub pump 102 have the same relationship among the pump chamber 7, the suction port 8, and the discharge port 9, and the shapes of the notches 9a and 9b are different from each other.
  • the notch 9b of the sub-pump 102 passes through the transition region from the reference state indicated by the broken line in FIG. 6B to the communication state indicated by the solid line in FIG. 6B while the vane 3b on the front side in the rotational direction passes.
  • the resistance given to the flow is formed so as to be larger than the notch 9a of the main pump 101.
  • the notch 9b of the sub-pump 102 has a larger pressure loss of the hydraulic oil guided from the pump chamber 7 through the notch 9b while the vane 3b passes through the transition region, compared to the notch 9a of the main pump 101. It is formed.
  • the opening area S2 see FIG.
  • the notches 9a and 9b of the main pump 101 and the sub pump 102 are formed with the same depth D and opening width W. .
  • the length of the notches 9a and 9b in the rotational direction of the rotor 2 is longer than the length L1 of the notch 9a in the main pump 101.
  • the length L2 is formed to be shorter.
  • the opening area S2 of the notch 9b in the sub pump 102 is smaller than the opening area S1 of the notch 9a in the main pump 101.
  • the notch 9b of the sub pump 102 has a greater resistance to the flow of hydraulic oil passing therethrough than the notch 9a of the main pump 101.
  • Each of the main pump and the sub pump in the pump device according to the comparative example has groove-shaped notches extending from the opening edge of the discharge port toward the rear side in the rotational direction of the rotor and formed in the same shape.
  • the notch is formed such that the resistance given to the hydraulic oil is relatively small by increasing the length and the cross-sectional area.
  • the notch of the pump device according to the comparative example is formed in a shape for suppressing the generation of noise and vibration at the time of high rotation.
  • the notch 9a of the main pump 101 is formed so that the resistance given to the passing hydraulic oil is relatively small, and the notch 9b of the sub pump 102 is compared with the notch 9a of the main pump 101. It is formed so that the resistance given to the passing hydraulic oil is increased.
  • the sub pump 102 it is suppressed that hydraulic fluid is excessively guided from the discharge port 9 to the pump chamber 7 through the notch 9b during the low rotation of the pump. Accordingly, the pressure in the pump chamber 7 of the sub pump 102 at the time of low rotation is prevented from rapidly increasing, and the pressure fluctuation when the pump chamber 7 communicates directly with the discharge port 9 becomes gentle, and noise and vibration are generated. Can be suppressed.
  • the discharge port 9 of the sub pump 102 communicates with the return passage 35, and the hydraulic oil discharged from the sub pump 102 is circulated to the suction side. That is, the pump chamber 7 of the sub pump 102 at the time of high rotation of the pump communicates with the discharge port 9 that communicates with the suction side and has a small pressure.
  • the high pressure chamber is formed at the high rotation. Since the pressure 12 is communicated with the suction side and the pressure is released, the pressure in the high pressure chamber 12 of the sub pump 102 does not fluctuate rapidly. Therefore, generation of vibration and noise of the sub pump 102 at the time of high rotation is suppressed.
  • the notch 9a of the main pump 101 used at the time of low rotation and high rotation of the pump is formed in a shape for suppressing noise and vibration at the time of high rotation
  • the notch 9b of the sub pump 102 not used at the time of high rotation is It is formed in a shape for suppressing noise and vibration during low rotation.
  • the pump device 100 since the sub pump 102 has the notch 9b having a larger resistance to the hydraulic fluid that passes therethrough than the main pump 101, the hydraulic fluid that passes through the notch 9b by the resistance when the pump rotates at low speed. Flow is suppressed. For this reason, sudden fluctuations in the pressure of the hydraulic oil when the pump chamber 7 and the high-pressure chamber 12 communicate with each other can be prevented, and vibration of the sub-pump 102 and generation of noise during the low rotation of the pump can be suppressed. Further, when the rotation speed of the pump device 100 increases, the hydraulic oil discharged from the sub pump 102 by the switching valve 40 is guided to the low-pressure suction side.
  • the main pump 101 and the sub pump 102 do not have a notch communicating with the suction port 8, but as shown in FIG. 11, the rotation direction of the rotor 2 is opposite from the opening edge of the suction port 8.
  • Groove-shaped notches (suction side notches) 8 a and 8 b extending in the direction may be formed in the center plate 5.
  • the suction side notch 8b of the sub pump 102 passes, for example, as shown in FIG. 11, the length of the suction side notch 8b of the sub pump 102 is increased. It is desirable to form so that the resistance given to hydraulic oil becomes large.
  • FIG. 11 is a plan view of the center plate 5 as viewed from the sub-pump 102 side, and the arrows in the figure indicate the rotation direction of the rotor 2.
  • the notch shapes of the main pump 101 and the sub-pump 102 are not limited to the above shapes, and the hydraulic oil is more hydraulic than the notch 9a of the main pump 101 while the vane 3 on the front side in the rotational direction passes through the transition region. What is necessary is just to form the notch 9b of the subpump 102 so that the resistance to give may become large. A specific example of this will be described with reference to FIGS. 8 and 9 are cross-sectional views showing the opening areas of the notches 9a and 9b of the main pump 101 and the sub pump 102 in the reference state.
  • the notches 9 a and 9 b of the main pump 101 and the sub pump 102 have the same length L and an opening width (not shown), and the depth D 2 of the notch 9 b of the sub pump 102 is the same as that of the main pump 101. You may form so that it may become smaller than the depth D1 of the notch 9a. Thereby, compared with the notch 9a of the main pump 101, the resistance given to the hydraulic fluid which passes by the notch 9b of the sub pump 102 becomes large.
  • the opening area S2 of the notch 9b in the sub pump 102 is larger than the opening area S1 of the notch 9a in the main pump 101.
  • a region R1 and a region R2 in which the opening area S2 of the notch 9b in the sub pump 102 is smaller than the opening area S1 of the notch 9a in the main pump 101 may be formed. Even in this case, while the vane 3b on the front side in the rotational direction moves in the transition region, the resistance given to the entire hydraulic fluid passing through the notch 9b of the sub pump 102 is larger than the notch 9a of the main pump 101.
  • the main pump 101 and the sub pumps 102 have the same number of vanes 3.
  • the numbers of vanes 3 included in the main pump 101 and the sub pump 102 may be different from each other.
  • the volumes of the pump chambers 7 partitioned by the vanes 3 are also different, and the circumferential positions where the suction ports 8 are formed are also different from each other.
  • the vane 3b on the front side in the rotational direction that defines the pump chamber 7 moves in each transition region, the resistance given to the entire hydraulic fluid that passes through is smaller than the notch 9a of the main pump 101 than the sub pump 102.
  • the two notches 9a of the main pump 101 are formed in the same shape.
  • the two notches 9b of the sub pump 102 are also formed in the same shape.
  • the notches 9a of the main pump 101 may be formed in different shapes.
  • the notches 9b of the sub pump 102 may be formed in different shapes.
  • the sub pump 102 One notch 9b may be formed in the same shape as the notch 9a of the main pump 101, and the other notch 9b may be formed so as to increase the resistance applied to the hydraulic oil passing through the notch 9a of the main pump 101.
  • at least one notch 9b among the notches 9b of the sub-pump 102 may be formed so that the resistance given to the passing hydraulic oil is larger than the notch 9a of the main pump 101.
  • the main pump 101 and the sub pump 102 each have two discharge ports 9.
  • the number of discharge ports 9 may be one, or three or more. Also in this case, it is only necessary that at least one notch 9b among the notches 9b of the sub pump 102 has a greater resistance to the passing hydraulic oil than the notch 9a of the main pump 101.
  • the main pump 101 and the sub pump 102 are formed with single notches 9a and 9b so as to communicate with the discharge ports 9, respectively.
  • two or more notches 9a and 9b communicating with one discharge port 9 may be formed.
  • the total resistance given to the hydraulic fluid passing through the plurality of notches 9b communicating with the discharge port 9 of one sub-pump 102 is determined by the notch 9a communicating with any one discharge port 9 of the main pump 101.
  • the notches 9a and 9b of the main pump 101 and the sub pump 102 may be formed so as to be larger than the total resistance given to the hydraulic oil.
  • the switching valve 40 is provided in the switching passage 33, and the second discharge passage 34 and the return passage 35 are connected to the switching valve 40.
  • the second discharge passage 34 may be directly connected to the sub pump 102, and the return passage 35 may be branched from the second discharge passage 34.
  • the second discharge passage 34 is provided with a check valve 37 that allows only the flow of hydraulic oil from the second discharge passage 34 to the first discharge passage 32, and the return passage 35 is provided with the second discharge passage 34.
  • the return passage 35 is provided with a switching valve 140.
  • the switching valve 140 has a blocking position 140 a that blocks the return passage 35 and an opening position 140 b that opens the return passage 35.
  • the pump device 100 may have the above-described configuration, and even in such a case, the same effect as that of the above-described embodiment is achieved.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
PCT/JP2016/066137 2015-06-02 2016-06-01 ポンプ装置 WO2016194933A1 (ja)

Priority Applications (3)

Application Number Priority Date Filing Date Title
CN201680032273.1A CN107636309A (zh) 2015-06-02 2016-06-01 泵装置
US15/578,437 US20180149153A1 (en) 2015-06-02 2016-06-01 Pump device
EP16803367.8A EP3306094A4 (en) 2015-06-02 2016-06-01 PUMP DEVICE

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2015-112566 2015-06-02
JP2015112566A JP6522430B2 (ja) 2015-06-02 2015-06-02 ポンプ装置

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WO2016194933A1 true WO2016194933A1 (ja) 2016-12-08

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EP (1) EP3306094A4 (zh)
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DE102018100614B4 (de) * 2018-01-12 2021-07-22 Nidec Gpm Gmbh Strömungsoptimierte Flügelzellenpumpe
DE102020105173A1 (de) * 2020-02-27 2021-09-02 Fte Automotive Gmbh Pumpenaggregat für einen Antriebsstrang eines Kraftfahrzeugs
JP2022039456A (ja) * 2020-08-28 2022-03-10 日本電産トーソク株式会社 電動ポンプ

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JPH11303773A (ja) * 1998-04-23 1999-11-02 Jidosha Kiki Co Ltd 可変容量形ポンプ
JP2003184759A (ja) * 2001-12-14 2003-07-03 Unisia Jkc Steering System Co Ltd ベーンポンプ
JP2010014101A (ja) * 2008-06-05 2010-01-21 Kayaba Ind Co Ltd 多連式ベーンポンプ

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US6641372B2 (en) * 2000-01-21 2003-11-04 Delphi Technologies, Inc. Dual discharge hydraulic pump and system therefor
JP3874694B2 (ja) * 2002-04-26 2007-01-31 株式会社ジェイテクト オイルポンプ装置
US7770388B2 (en) * 2004-11-19 2010-08-10 Goodrich Pump & Engine Control Systems, Inc. High efficiency 2-stage fuel pump and control scheme for gas turbines
JP2011149334A (ja) * 2010-01-21 2011-08-04 Showa Corp 車両の油圧制御装置
JP5877976B2 (ja) * 2011-08-31 2016-03-08 株式会社ショーワ ベーンポンプ

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Publication number Priority date Publication date Assignee Title
JPH11303773A (ja) * 1998-04-23 1999-11-02 Jidosha Kiki Co Ltd 可変容量形ポンプ
JP2003184759A (ja) * 2001-12-14 2003-07-03 Unisia Jkc Steering System Co Ltd ベーンポンプ
JP2010014101A (ja) * 2008-06-05 2010-01-21 Kayaba Ind Co Ltd 多連式ベーンポンプ

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Title
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US20180149153A1 (en) 2018-05-31
JP6522430B2 (ja) 2019-05-29
EP3306094A4 (en) 2019-01-16
JP2016223393A (ja) 2016-12-28
CN107636309A (zh) 2018-01-26
EP3306094A1 (en) 2018-04-11

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