US20180149153A1 - Pump device - Google Patents

Pump device Download PDF

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Publication number
US20180149153A1
US20180149153A1 US15/578,437 US201615578437A US2018149153A1 US 20180149153 A1 US20180149153 A1 US 20180149153A1 US 201615578437 A US201615578437 A US 201615578437A US 2018149153 A1 US2018149153 A1 US 2018149153A1
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United States
Prior art keywords
pump
sub
discharge
rotor
working fluid
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Abandoned
Application number
US15/578,437
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English (en)
Inventor
Koichiro Akatsuka
Tomoyuki Fujita
Tomoyuki Nakagawa
Fumiyasu Katou
Hiroki Gomi
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KYB Corp
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KYB Corp
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Assigned to KYB CORPORATION reassignment KYB CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: AKATSUKA, KOICHIRO, FUJITA, TOMOYUKI, GOMI, Hiroki, KATOU, Fumiyasu, NAKAGAWA, TOMOYUKI
Publication of US20180149153A1 publication Critical patent/US20180149153A1/en
Abandoned legal-status Critical Current

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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
    • 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
    • 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
    • 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 a first vane pump and a second vane pump are connected by a common drive shaft so as to be connected in parallel.
  • a working fluid is supplied to a fluid pressure device by the first vane pump and the second vane pump.
  • the rotation speed of the pump increases and the discharge flow rate of the second vane pump reaches or exceeds a necessary flow rate, the working fluid discharged from the first vane pump is returned to a suction passage, and working fluid is supplied to the fluid pressure device by the second vane pump alone.
  • This kind of vane pump includes a groove-shaped notch which is in communication with a discharge port in order to prevent sudden fluctuations in the pressure of the working fluid that is led to a high-pressure chamber.
  • the notch is formed so as to have a long length and a large cross-section area so that the resistance applied to the flow of working fluid passing therethrough is relatively small.
  • the rate of pressure rise within the pump chamber relative to the rotation angle of the pump increases.
  • the pump chamber communicates with the high-pressure chamber in a state in which the pressure has risen sufficiently such that sudden fluctuations in the pressure of the working fluid are prevented, and the occurrence of vibrations and noise during high rotation of the pump is suppressed.
  • the movement speed of the vanes in the rotation direction of the rotor decreases compared to that during high rotation of the pump, and thus the flow of working fluid from the high-pressure chamber to the pump chamber through the notch is easily promoted. Therefore, during low rotation of the pump, the rate of pressure rise within the pump chamber relative to the rotation angle of the pump is high. Accordingly, if the length of the notch is formed to be relatively long and the cross-section area of the notch is formed to be relatively large, during low rotation of the pump, the rate of pressure rise within the pump chamber relative to the rotation angle of the pump may become too high. Consequently, if the notch is formed to have a long length and a large cross-section area, sudden pressure fluctuations may occur during low rotation of the pump, and this can lead to the occurrence of vibrations and noise.
  • An object of the present invention is to suppress the occurrence of vibrations and noise in a pump device including a main pump and a sub pump.
  • a pump device for supplying working fluid to a fluid pressure device.
  • the pump device includes: a main pump configured to supply the working fluid to the fluid pressure device through a first discharge passage, a sub pump configured to supply the working fluid to the fluid pressure device through a second discharge passage that joins with the first discharge passage, a return passage configured to return the working fluid discharged from the sub pump to a suction side, and a switching valve configured to switch regarding whether or not to return the working fluid discharged from the sub pump to the suction side through the return passage.
  • the main pump and the sub pump each include: a rotor connected to a common drive shaft, a plurality of vanes provided so as to be capable of reciprocating in a radial direction relative to the rotor, a cam ring having an inner peripheral surface. Distal ends of the vanes being configured to be in sliding contact with the inner peripheral surface in accordance with rotation of the rotor.
  • the main pump and the sub pump each include: pump chambers defined by the rotor, the cam ring, and adjacent pair of the vanes, a discharge port into which the working fluid discharged from the pump chamber is led, and a groove-shaped discharge-side notch formed from an opening edge of the discharge port toward a direction opposite to a rotation direction of the rotor.
  • the switching valve is configured to switch according to a rotation speed of the drive shaft. At least one discharge-side notch of the sub pump is formed so that a resistance applied to the flow of the working fluid passing therethrough is greater than that of the discharge-side notch of the main pump.
  • FIG. 1 is a cross-section view of a pump device according to an embodiment of the present invention.
  • FIG. 2 is a plan view when viewed in the direction of arrow A in FIG. 1 of a pump cartridge in a main pump of the pump device according to the embodiment of the present invention.
  • FIG. 3 is a plan view when viewed in the direction of arrow B in FIG. 1 of a pump cartridge in a sub pump of the pump device according to the embodiment of the present invention.
  • FIG. 4 is a hydraulic circuit diagram of the pump device according to the embodiment of the present invention.
  • FIG. 5 is a graph illustrating the flow rate characteristics of the pump device according to the embodiment of the present invention.
  • FIG. 6A is an enlarged view illustrating the relationship among a pump chamber, a discharge port, and a notch in the main pump of the pump device according to the embodiment of the present invention.
  • FIG. 6B is an enlarged view illustrating the relationship among a pump chamber, a discharge port, and a notch in the sub pump of the pump device according to the embodiment of the present invention.
  • FIG. 7A is a cross-section view illustrating a notch shape of the notch in the main pump of the pump device according to the embodiment of the present invention.
  • FIG. 7B is a cross-section view illustrating a notch shape of the notch in the sub pump of the pump device according to the embodiment of the present invention.
  • FIG. 7C is a view superimposing FIG. 7A and FIG. 7B .
  • FIG. 8A is a cross-section view illustrating an alternative embodiment of the notch shape of the notch in the main pump of the pump device according to the embodiment of the present invention.
  • FIG. 8B is a cross-section view illustrating an alternative embodiment of the notch shape of the notch in the sub pump of the pump device according to the embodiment of the present invention.
  • FIG. 8C is a view superimposing FIG. 8A and FIG. 8B .
  • FIG. 9A is a cross-section view illustrating another alternative embodiment of the notch shape of the notch in the main pump of the pump device according to the embodiment of the present invention.
  • FIG. 9B is a cross-section view illustrating another alternative embodiment of the notch shape of the notch in the sub pump of the pump device according to the embodiment of the present invention.
  • FIG. 9C is a view superimposing FIG. 9A and FIG. 9B .
  • FIG. 10 is a hydraulic circuit diagram illustrating an alternative embodiment of the pump device according to the embodiment of the present invention.
  • FIG. 11 is a plan view of a center plate in an alternative embodiment of the pump device according to the embodiment of the present invention.
  • a pump device 100 according to an embodiment of the present invention will now be explained below referring to the drawings.
  • the pump device 100 is used as a hydraulic supply source of a hydraulic device mounted in a vehicle, such as a power steering device or a transmission.
  • FIGS. 1 to 3 in the pump device 100 , a rotor 2 of a main pump 101 and a rotor 2 of a sub pump 102 are connected to a common drive shaft 1 to which motive power of an engine 24 (refer to FIG. 4 ) is transmitted, and the rotors 2 are rotated by means of the rotation of the drive shaft 1 .
  • FIGS. 2 and 3 respectively illustrate pump cartridges 21 and 22 of the main pump 101 and the sub pump 102
  • FIG. 2 is a plan view when viewed from the direction of arrow A in FIG. 1
  • FIG. 3 is a plan view when viewed from the direction of arrow B in FIG. 1 .
  • the rotor 2 rotates clockwise in FIG. 2 , and rotates counterclockwise in FIG. 3 .
  • the hydraulic oil (working fluid) discharged from the main pump 101 is constantly supplied to a hydraulic device (fluid pressure device) 23 (refer to FIG. 4 ). Meanwhile, the hydraulic oil discharged from the sub pump 102 is supplied to the hydraulic device 23 or returned to the suction side according to the operation of a switching valve 40 (refer to FIG. 4 ).
  • the main pump 101 and the sub pump 102 include: a plurality of vanes 3 provided such that they can move reciprocally in the radial direction relative to the rotor 2 , and a cam ring 4 that accommodates the rotor 2 .
  • the distal end of each vane 3 slidingly contacts a cam surface 4 a on the inner periphery of the cam ring 4 in accordance with the rotation of the rotor 2 .
  • slits 16 having an opening on the outer peripheral surface are formed radially at predetermined intervals, and the vanes 3 are slidably inserted into the slits 16 .
  • each slit 16 On the base end side of each slit 16 , a back pressure chamber 17 to which pump discharge pressure is led is defined. Adjacent back pressure chambers 17 communicate with each other by an arc-shaped groove 2 a formed in the rotor 2 , and pump discharge pressure is constantly led to the groove 2 a .
  • Each vane 3 is pressed in the direction in which the vane 3 comes out from the slit 16 by the pressure of the back pressure chamber 17 and the centrifugal force generated by the rotation of the rotor 2 , and the distal end of each vane 3 abuts the cam surface 4 a on the inner periphery of the cam ring 4 .
  • a plurality of pump chambers 7 are defined by the outer peripheral surface of the rotor 2 , the cam surface 4 a of the cam ring, and the adjacent pairs of vanes 3 .
  • Each pump cartridge 21 , 22 is constituted by the rotor 2 , the vanes 3 , and the cam ring 4 .
  • the cam ring 4 is an annular member in which the cam surface 4 a on the inner periphery has an approximately elliptical shape.
  • the cam ring 4 includes a suction region 4 b that expands the capacity of the pump chambers 7 in accordance with the rotation of the rotor 2 , and a discharge region 4 b that contracts the capacity of the pump chambers 7 in accordance with the rotation of the rotor 2 .
  • 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 , 22 (refer to FIG. 1 ).
  • each pump cartridge 21 , 22 is sandwiched between the center plate 5 and the side plate 6 , and the pump chambers 7 are sealed by the center plate 5 and the side plate 6 .
  • suction ports 8 which open toward the suction region 4 b of the cam ring 4 and which lead hydraulic oil to the pump chambers 7 , are formed.
  • each side plate 6 two arc-shaped discharge ports 9 , which open toward the discharge region 4 c of the cam ring 4 and to which hydraulic oil discharged by the pump chambers 7 is led, are formed.
  • Groove-shaped notches (discharge-side notches) 9 a, 9 b which extend from the opening edges of the discharge ports 9 toward the direction opposite of the rotation direction of the rotor 2 , are formed in the side plates 6 of the main pump 101 and the sub pump 102 .
  • these notches 9 a, 9 b By forming these notches 9 a, 9 b , the flow of hydraulic oil from the pump chambers 7 to the discharge ports 9 through the notches 9 a, 9 b is promoted in accordance with the rotation of the rotor 2 , and thus sudden pressure fluctuations in a high-pressure chamber 12 to be explained later are prevented.
  • the pump chambers 7 suction hydraulic oil through the suction port 8 in the suction region 4 b of the cam ring 4 and discharge the suctioned hydraulic oil through the discharge port 9 in the discharge region 4 c of the cam ring 4 , and then suction hydraulic oil through the suction port 8 in the suction region 4 b of the cam ring 4 and discharge the suctioned hydraulic oil through the discharge port 9 in the discharge region 4 c of the cam ring 4 .
  • the pump chambers 7 expand and contract in accordance with the rotation of the rotor 2 , and perform suction/discharge of the hydraulic oil two times over the course of one rotation of the rotor 2 .
  • the drive shaft 1 is rotatably supported via bushes 18 on a first pump body 10 and a second pump body 11 .
  • the side plate 6 and the pump cartridge 21 of the main pump 101 are laminated and accommodated within a pump accommodation recess 10 a formed in the first pump body 10 .
  • the side plate 6 and the pump cartridge 22 of the sub pump 102 as well as the center plate 5 are laminated and accommodated within a pump accommodation recess 11 a formed in the second pump body 11 .
  • 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 surfaces having an opening of the first pump body 10 and the second pump body 11 are abutted to each other to integrally fasten the first pump body 10 and the second pump body 11 together, and thereby the pump accommodation recesses 10 a and 11 a are sealed.
  • the cam rings 4 and the side plates 6 of the main pump 101 and the sub pump 102 are restrained from rotating by two positioning pins 19 (refer to FIGS. 2 and 3 ) that are inserted into the center plate 5 . Relative rotation of the center plate 5 and the side plates 6 relative to the cam ring 4 is restricted by the positioning pins 19 . Thereby, positioning of the suction region 4 b of the cam ring 4 and the suction ports 8 of the center plate 5 is achieved, and positioning of the discharge region 4 c of the cam ring 4 and the discharge ports 9 of the side plates 6 is achieved.
  • a high-pressure chamber 12 into which hydraulic oil discharged from the discharge ports 9 flows is formed.
  • the hydraulic oil of the high-pressure chamber 12 is supplied to the hydraulic device 23 through a first discharge passage 32 and a second discharge passage 34 (refer to FIG. 4 ).
  • the hydraulic oil of the high-pressure chamber 12 is led to the arc-shaped groove 2 a of the rotor 2 through a through-hole 6 a formed in the side plates 6 , and then is led to the back pressure chambers 17 .
  • a suction passage 31 connected to a tank 36 is connected to the suction ports 8 of the main pump 101 and the sub pump 102 .
  • the first discharge passage 32 is connected to the discharge ports of the main pump 101 , and hydraulic oil is constantly supplied from the main pump 101 to the hydraulic device 23 through the first discharge passage 32 .
  • a switching passage 33 is connected to the discharge ports 9 of the sub pump 102 .
  • the switching valve 40 which switches the flow of hydraulic oil discharged from the sub pump 102 , is provided in the switching passage 33 .
  • the following are connected to the switching valve 40 : the second discharge passage 34 that supplies hydraulic oil to the hydraulic device 23 ; and a return passage 35 that returns hydraulic oil to the suction side.
  • the second discharge passage 34 is provided so as to join with the first discharge passage 32 .
  • the switching valve 40 switches regarding whether or not to return the hydraulic oil discharged from the sub pump 102 to the suction side through the return passage 35 .
  • the switching valve 40 selectively switches so as to supply the hydraulic oil discharged from the sub pump 102 to the hydraulic device 23 through the second discharge passage 34 , or to return the hydraulic oil discharged from the sub pump 102 to the suction side through the return passage 35 .
  • the hydraulic oil discharged from the sub pump 102 is selectively led to either the hydraulic device 23 or the suction passage 31 by the switching operation of the switching valve 40 .
  • the switching valve 40 has a first communication position 40 a in which communication is established between the switching passage 33 and the second discharge passage 34 , and a second communication position 40 b in which communication is established between the switching passage 33 and the return passage 35 .
  • the switching valve 40 is an electromagnetic switching valve in which the position is switched by a control current output from a controller 30 .
  • the switching valve 40 is set to the second communication position 40 b by a biasing force of a spring 42 when a solenoid 41 is not energized, and is set to the first communication position 40 a against the biasing force of the spring 42 when the solenoid 41 is energized.
  • the position of the switching valve 40 is switched according to, for example, the rotation speed of the engine 24 that is input into the controller 30 , i.e. a pump rotation speed which is the rotation speed of the drive shaft 1 and the rotor 2 .
  • the switching valve 40 is not limited to an electromagnetic switching valve, and may also be a pilot-type switching valve in which the switching operation is performed by a pilot liquid pressure.
  • the main pump 101 suctions hydraulic oil from the tank 36 through the suction passage 31 , and supplies the hydraulic oil to the hydraulic device 23 through the first discharge passage 32 .
  • the sub pump 102 suctions hydraulic oil from the tank 36 through the suction passage 31 , and supplies the hydraulic oil to the hydraulic device 23 through the second discharge passage 34 or returns the hydraulic oil to the suction side through the return passage 35 .
  • the switching valve 40 is set to the first communication position 40 a.
  • Hydraulic oil discharged from the main pump 101 is supplied to the hydraulic device 23 regardless of which position the switching valve 40 is in.
  • Hydraulic oil discharged from the sub pump 102 is supplied to the hydraulic device 23 through the second discharge passage 34 .
  • hydraulic oil in a flow rate which is the combined total of the discharge flow rates of the main pump 101 and the sub pump 102 is supplied to the hydraulic device 23 .
  • FIG. 5 is a graph illustrating the relationship between the discharge flow rate and the rotation speed of the pump device 100 .
  • the solid line represents the overall discharge flow rate of the pump device 100
  • the dashed lines represent the combined 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 in accordance with an increase in the pump rotation speed. If the pump rotation speed reaches a predetermined pump rotation speed Ni and the discharge flow rate of the main pump 101 alone reaches or exceeds a required flow rate Q 1 of the hydraulic device 23 , the switching valve 40 is switched to the second communication position 40 b. Thereby, the hydraulic oil discharged from the sub pump 102 is returned to the suction side through the return passage 35 .
  • the pump rotation speed is less than the pump rotation speed Ni at which the discharge flow rate of the main pump 101 reaches the required flow rate Q 1 (hereinafter referred to as “during low rotation of the pump”)
  • hydraulic oil discharged from the main pump 101 and the sub pump 102 is supplied to the hydraulic device 23 .
  • the pump rotation speed is at or above the pump rotation speed N 1 (hereinafter referred to as “during high rotation of the pump”)
  • the discharge flow rate of the main pump 101 alone is supplied to the hydraulic device 23
  • the hydraulic oil discharged from the sub pump 102 is returned to the suction side.
  • the sub pump 102 is used as a pressure source supplying hydraulic oil to the hydraulic device 23 during low rotation of the pump, and is not used as such a pressure source during high rotation of the pump.
  • a state in which communication between the pump chamber 7 and the suction port 8 is blocked in accordance with rotation of the rotor 2 will be referred to as a “reference state” (the dashed lines in FIG. 6 )
  • a state in which there is direct communication between the pump chamber 7 and the discharge port 9 without using the notches 9 a, 9 b will be referred to as a “communication state” (the solid lines in FIG. 6 )
  • a region in the space between the reference state and the communication state will be referred to as a “transition region”.
  • a position in the reference state of a vane 3 b which is on the front side in the rotation direction among the pair of vanes 3 a, 3 b that define the pump chamber 7 will be referred to as a “reference position” (refer to FIG. 6 ), and a cross-section area that intersects a center line C (refer to FIGS. 2, 3, and 6 ) of the notches 9 a, 9 b at a position separated by an angle a from the reference position will be referred to as a “notch opening area”.
  • the notches 9 a, 9 b of the main pump 101 and the sub pump 102 are formed so that the cross-section shape that is perpendicular to the longitudinal direction thereof, i.e. the cross-section shape intersecting the center line C, is an approximately triangular shape. Further, the notches 9 a , 9 b of the main pump 101 and the sub pump 102 are formed in a tapered shape in which the cross-section area of the notch 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 .
  • FIGS. 6A and 6B illustrate the relationship among the pump chamber 7 , the suction port 8 , the discharge port 9 , and the notches 9 a, 9 b.
  • the relationship among the pump chamber 7 , the suction port 8 , and the discharge port 9 is the same in the main pump 101 and the sub pump 102 , but the shapes of the notches 9 a and 9 b are different from each other.
  • the notch 9 b of the sub pump 102 is formed so that the resistance applied to the flow of hydraulic oil passing therethrough is greater than that of the notch 9 a of the main pump 101 in the space where the vane 3 b on the front side in the rotation direction passes through the transition region from the reference state shown by the dashed lines in FIG. 6B to the communication state shown by the solid lines in FIG. 6B .
  • the notch 9 b of the sub pump 102 is formed so that the pressure loss of the hydraulic oil led from the pump chamber 7 through the notch 9 b increases compared to the notch 9 a of the main pump 101 in the space where the vane 3 b passes through the transition region.
  • an opening area S 2 (refer to FIG. 7B ) of the notch 9 b at a position separated from the reference position by an angle a (refer to FIGS. 6A and 6 B) in the sub pump 102 is formed to be smaller than an opening area Si (refer to FIG. 7A ) of the notch 9 a at a position separated from the reference position by an angle a in the main pump 101 .
  • the notches 9 a, 9 b of the main pump 101 and the sub pump 102 are formed so that the depths D and the opening widths W are equivalent to each other.
  • the lengths of the notches 9 a, 9 b toward the rotation direction of the rotor 2 are formed so that a length L 2 of the notch 9 b in the sub pump 102 is shorter than a length L 1 of the notch 9 a in the main pump 101 .
  • the opening area S 2 of the notch 9 b in the sub pump 102 is smaller than the opening area S 1 of the notch 9 a in the main pump 101 .
  • the notch 9 b of the sub pump 102 applies a greater resistance to the flow of hydraulic oil passing therethrough than the notch 9 a of the main pump 101 .
  • the main pump and the sub pump in the pump device according to the comparative embodiment have groove-shaped notches that are formed in the same shape and extend from the opening edge of the discharge port toward the rear side in the rotation direction of the rotor.
  • the notches are formed so that the lengths are long and the cross-section areas are large, and the resistance applied to the hydraulic oil is relatively small.
  • the notches of pump device according to the comparative embodiment are formed so that the resistance applied to the hydraulic oil passing therethrough is relatively small, and thus it becomes easier to lead hydraulic oil from the discharge ports into the pump chambers through the notches.
  • the notches 9 a of the main pump 101 are formed so that the resistance applied to the hydraulic oil passing therethrough is relatively small, and the notches 9 b of the sub pump 102 are formed so that the resistance applied to the hydraulic oil passing therethrough is large compared to the notches 9 a of the main pump 101 .
  • the discharge ports 9 of the sub pump 102 communicate with the return passage 35 , and hydraulic oil discharged from the sub pump 102 is returned to the suction side.
  • the pump chambers 7 of the sub pump 102 during high rotation of the pump communicate with the discharge ports 9 which communicate with the suction side and have low pressure.
  • the high-pressure chamber 12 communicates with the suction side and pressure is released, and thus sudden fluctuations of the pressure in the high-pressure chamber 12 of the sub pump 102 do not occur. Therefore, the occurrence of vibrations and noise in the sub pump 102 during high rotation is suppressed.
  • the notches 9 a of the main pump 101 which is used during low rotation of the pump and during high rotation of the pump, are formed in a shape for suppressing noise and vibrations during high rotation
  • the notches 9 b of the sub pump 102 which is not used during high rotation, are formed in a shape for suppressing noise and vibrations during low rotation.
  • the sub pump 102 has notches 9 b in which the resistance applied to hydraulic oil passing therethrough is greater than that of the main pump 101 , and thus during low rotation of the pump, the flow of hydraulic oil passing through the notches 9 b is suppressed by the resistance. Therefore, sudden fluctuations in the pressure of the hydraulic oil when the pump chambers 7 and the high-pressure chamber 12 are in communication are prevented, and the occurrence of vibrations and noise in the sub pump 102 during low rotation of the pump can be suppressed. Further, if the rotation speed of the pump device 100 increases, hydraulic oil discharged from the sub pump 102 is led to the suction side of the low pressure by the switching valve 40 .
  • the sub pump 102 is provided with the notches 9 b that apply a relatively large resistance to the hydraulic oil, the occurrence of vibrations and noise in the sub pump 102 during high rotation can be suppressed. Accordingly, the occurrence of vibrations and noise can be suppressed in the pump device 100 which includes the main pump 101 and the sub pump 102 .
  • the main pump 101 and the sub pump 102 do not have notches that communicate with the suction ports 8 .
  • groove-shaped notches (suction-side notches) 8 a, 8 b that extend from the opening edge of the suction ports 8 in the direction opposite to the rotation direction of the rotor 2 may be formed in the center plate 5 .
  • the suction-side notches 8 b of the sub pump 102 are preferably formed so that the resistance applied to hydraulic oil passing therethrough becomes greater compared to the suction-side notches 8 a of the main pump 101 , such that, for example, the length of the suction-side notches 8 b of the sub pump 102 is less than that of suction-side notches 8 a of the main pump 101 as shown in FIG. 11 .
  • FIG. 11 is a plan view of the center plate 5 when viewed from the sub pump 102 side, and the arrow in FIG. 11 represents the rotation direction of the rotor 2 .
  • FIGS. 8 and 9 are cross-section views illustrating the opening area of the notches 9 a, 9 b of the main pump 101 and the sub pump 102 in the reference state.
  • the notches 9 a, 9 b of the main pump 101 and the sub pump 102 may be formed so that the lengths L and the opening widths (not illustrated) are equivalent to each other, whereas the depth D 2 of the notch 9 b of the sub pump 102 is smaller than the depth D 1 of the notch 9 a of the main pump 101 .
  • the resistance applied to the hydraulic oil passing through the notch 9 b of the sub pump 102 becomes greater than that of the notch 9 a of the main pump 101 .
  • a region R 1 in which the opening area S 2 of the notch 9 b of the sub pump 102 is larger than the opening area Si of the notch 9 a of the main pump 101 and a region R 2 in which the opening area S 2 of the notch 9 b of the sub pump 102 is smaller than the opening area Si of the notch 9 a of the main pump 101 may be formed.
  • the notches 9 a, 9 b of the main pump 101 and the sub pump 102 are formed so that the notch 9 b of the sub pump 102 applies a greater resistance on the whole to the hydraulic oil passing therethrough compared to the notch 9 a of the main pump 101 in the space where the vane 3 b on the front side in the rotation direction moves through the transition region.
  • the main pump 101 and the sub pump 102 have the same number of vanes 3 .
  • the number of vanes 3 in the main pump 101 may be different from that in the sub pump 102 . If the number of vanes 3 is different between the main pump 101 and the sub pump 102 , the capacity of each pump chamber 7 defined by the vanes 3 will also differ, and thus the positions in the circumferential direction at which the discharge ports 8 are formed will be different.
  • the notch 9 b of the sub pump 102 applies a greater resistance on the whole to the hydraulic oil passing therethrough compared to the notch 9 a of the main pump 101 in the space where the vane 3 b on the front side in the rotation direction that defines the pump chamber 7 moves through the transition region.
  • the two notches 9 a of the main pump 101 are formed in the same shape as each other.
  • the two notches 9 b of the sub pump 102 are also formed in the same shape as each other.
  • the notches 9 a of the main pump 101 may be formed in different shapes from each other.
  • the notches 9 b of the sub pump 102 may also be formed in different shapes from each other.
  • both of the two notches 9 b of the sub pump 102 preferably apply a greater resistance to the hydraulic oil than the notches 9 a of the main pump 101 .
  • one notch 9 b of the sub pump 102 may be formed in the same shape as that of the notches 9 a of the main pump 101 , while the other notch 9 b may be formed so as to apply a greater resistance to hydraulic oil passing therethrough than the notches 9 a of the main pump 101 . In this way, as long as at least one of the notches 9 b of the sub pump 102 is formed so as to apply a greater resistance to hydraulic oil passing therethrough than the notches 9 a of the main pump 101 .
  • the main pump 101 and the sub pump 102 each have two discharge ports 9 .
  • at least one of the notches 9 b of the sub pump 102 is formed so as to apply a greater resistance to hydraulic oil passing therethrough than the notches 9 a of the main pump 101 .
  • a single notch 9 a, 9 b is formed to be in communication with each discharge port 9 in the main pump 101 and the sub pump 102 .
  • two or more notches 9 a, 9 b that communicate with a single discharge port 9 may be formed.
  • the notches 9 a, 9 b of the main pump 101 and the sub pump 102 may be formed so that the total resistance applied to the hydraulic oil passing through the plurality of notches 9 b that communicate with one discharge port 9 of the sub pump 102 is greater than the total resistance applied to the hydraulic oil passing through the notches 9 a that communicate with one of the discharge ports 9 of the main pump 101 .
  • the switching valve 40 is provided to 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 in direct communication with the sub pump 102 and the return passage 35 may be provided so as to branch from the second discharge passage 34 .
  • a check valve 37 that permits only the flow of hydraulic oil from the second discharge passage 34 to the first discharge passage 32 is provided to the second discharge passage 34 , and the return passage 35 is provided so as to branch from the upstream side of the check valve 37 in the second discharge passage 34 .
  • a switching valve 140 is provided to the return passage 35 .
  • the switching valve 140 has a blocked position 140 a in which the return passage 35 is blocked, and an open position 140 b in which the return passage 35 is opened.
  • the position switching operation of the switching valve 140 switches regarding whether or not to return the hydraulic oil discharged from the sub pump 102 to the suction side through the return passage 35 .
  • the pump device 100 may have such a configuration, and even in this case, the pump device 100 achieves effects similar to those of the above-described embodiment.

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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)
US15/578,437 2015-06-02 2016-06-01 Pump device Abandoned US20180149153A1 (en)

Applications Claiming Priority (3)

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JP2015-112566 2015-06-02
JP2015112566A JP6522430B2 (ja) 2015-06-02 2015-06-02 ポンプ装置
PCT/JP2016/066137 WO2016194933A1 (ja) 2015-06-02 2016-06-01 ポンプ装置

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US20180149153A1 true US20180149153A1 (en) 2018-05-31

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US15/578,437 Abandoned US20180149153A1 (en) 2015-06-02 2016-06-01 Pump device

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US (1) US20180149153A1 (ja)
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JP (1) JP6522430B2 (ja)
CN (1) CN107636309A (ja)
WO (1) WO2016194933A1 (ja)

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CN114109810A (zh) * 2020-08-28 2022-03-01 日本电产东测株式会社 电动泵
US11549508B2 (en) * 2018-01-12 2023-01-10 Nidec Gpm Gmbh Flow-optimised vane pump

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DE102020105173A1 (de) * 2020-02-27 2021-09-02 Fte Automotive Gmbh Pumpenaggregat für einen Antriebsstrang eines Kraftfahrzeugs

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US20020192080A1 (en) * 2000-01-21 2002-12-19 Rytlewski Thomas C. Dual discharge hydraulic pump and system therefor
US20080289338A1 (en) * 2004-11-19 2008-11-27 Goodrich Pump & Engine Control Systems, Inc. High Efficiency 2-Stage Fuel Pump and Control Scheme for Gas Turbines

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JP3866410B2 (ja) * 1998-04-23 2007-01-10 ユニシア ジェーケーシー ステアリングシステム株式会社 可変容量形ポンプ
JP3884280B2 (ja) * 2001-12-14 2007-02-21 ユニシア ジェーケーシー ステアリングシステム株式会社 ベーンポンプ
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
JP2010014101A (ja) * 2008-06-05 2010-01-21 Kayaba Ind Co Ltd 多連式ベーンポンプ
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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US20020192080A1 (en) * 2000-01-21 2002-12-19 Rytlewski Thomas C. Dual discharge hydraulic pump and system therefor
US20080289338A1 (en) * 2004-11-19 2008-11-27 Goodrich Pump & Engine Control Systems, Inc. High Efficiency 2-Stage Fuel Pump and Control Scheme for Gas Turbines

Cited By (2)

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Publication number Priority date Publication date Assignee Title
US11549508B2 (en) * 2018-01-12 2023-01-10 Nidec Gpm Gmbh Flow-optimised vane pump
CN114109810A (zh) * 2020-08-28 2022-03-01 日本电产东测株式会社 电动泵

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JP6522430B2 (ja) 2019-05-29
EP3306094A4 (en) 2019-01-16
CN107636309A (zh) 2018-01-26
WO2016194933A1 (ja) 2016-12-08
EP3306094A1 (en) 2018-04-11
JP2016223393A (ja) 2016-12-28

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