WO2016031767A1 - ポンプ装置 - Google Patents

ポンプ装置 Download PDF

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Publication number
WO2016031767A1
WO2016031767A1 PCT/JP2015/073709 JP2015073709W WO2016031767A1 WO 2016031767 A1 WO2016031767 A1 WO 2016031767A1 JP 2015073709 W JP2015073709 W JP 2015073709W WO 2016031767 A1 WO2016031767 A1 WO 2016031767A1
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WO
WIPO (PCT)
Prior art keywords
pressure
pump
fluid pressure
pressure chamber
fluid
Prior art date
Application number
PCT/JP2015/073709
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 CN201580043553.8A priority Critical patent/CN106662103A/zh
Priority to DE112015003982.1T priority patent/DE112015003982T5/de
Priority to US15/502,938 priority patent/US20170227007A1/en
Publication of WO2016031767A1 publication Critical patent/WO2016031767A1/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
    • 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
    • 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
    • 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
    • F04C14/08—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the rotational speed
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/24—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/06—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F04C15/064—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston machines or 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
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C2/34—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
    • F04C2/344—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C2/34—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
    • F04C2/344—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F04C2/3446—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
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2270/00—Control; Monitoring or safety arrangements
    • F04C2270/18—Pressure
    • F04C2270/185—Controlled or regulated

Definitions

  • the present invention relates to a pump device.
  • JP05-61482U describes a pump device provided with a flow control valve in the middle of a drain passage connected between a suction passage and a discharge passage of a vane pump.
  • hydraulic oil discharged from the pump chamber to the discharge passage in proportion to the number of rotations of the pump is supplied to the hydraulic drive device through the orifice.
  • the pump device described in JP05-61482U controls the supply amount of hydraulic oil from the vane pump to the hydraulic drive device by controlling the flow rate control valve to open and close.
  • the present invention has been made in view of the above problems, and an object of the present invention is to provide a pump device capable of controlling the flow rate while reducing the driving torque of the pump.
  • a pump device that supplies a working fluid to a fluid pressure device, the pump that sucks the working fluid, pressurizes the working fluid, and discharges the working fluid to the discharge passage, and the operation discharged from the pump
  • a flow rate control valve that recirculates part of the fluid to the suction side, and the flow rate control valve is provided facing the one end surface of the valve body and the valve body, and communicates with the discharge flow path.
  • a second fluid pressure chamber that is provided facing the other end surface of the valve body and communicates with the discharge passage, and is accommodated in a compressed state in the second fluid pressure chamber, and biases the valve body in the valve closing direction.
  • an urging member, and a pressure regulating device that is provided in a communication passage that communicates the discharge flow path and the second fluid pressure chamber and adjusts the pressure of the second fluid pressure chamber.
  • FIG. 1 is a hydraulic circuit diagram of a pump device according to an embodiment of the present invention.
  • FIG. 2 is a map showing the relationship between the pump speed at a certain target flow rate of the pump device and the pressure in the second fluid pressure chamber.
  • FIG. 3 is a map showing the relationship between the pressure in the second fluid pressure chamber and the proportional solenoid applied current.
  • FIG. 4 is a map showing the relationship between the required pressure of the pump device and the pressure of the second fluid pressure chamber.
  • FIG. 1 is a hydraulic circuit diagram of the pump device 100.
  • the pump device 100 sucks working oil as working fluid from a suction flow path 81 connected to the tank 4, pressurizes the working oil and discharges it to the discharge flow path 82, and working oil discharged from the pump 1. And a flow rate control valve 2 that controls the flow rate of the hydraulic oil supplied from the pump 1 to the fluid pressure device 50.
  • the pump 1 is a fixed capacity type vane pump.
  • the pump 1 houses a rotor 11 that is rotationally driven by a driving device such as an engine (not shown), a plurality of vanes 12 that are provided so as to be capable of reciprocating in the radial direction with respect to the rotor 11, and the rotor 11. Accordingly, the cam ring 13 in which the tip of the vane 12 is slidably contacted with the inner cam surface 13a is provided.
  • slits 14 having openings on the outer peripheral surface are radially formed at predetermined intervals.
  • the vane 12 is slidably inserted into the slit 14.
  • a back pressure chamber 15 into which the discharge pressure of the pump 1 is guided is defined on the proximal end side of the slit 14.
  • Adjacent back pressure chambers 15 communicate with each other through arcuate grooves 16 formed in the rotor 11.
  • a pump discharge pressure is always guided to the groove 16.
  • the vane 12 is pressed in the direction of coming out of the slit 14 by the pressure in the back pressure chamber 15 and the centrifugal force generated by the rotation of the rotor 11, and the tip part comes into contact with the cam surface 13 a on the inner periphery of the cam ring 13.
  • a plurality of pump chambers 17 are defined in the cam ring 13 by the outer peripheral surface of the rotor 11, the cam surface 13 a of the cam ring, and a pair of adjacent vanes 12.
  • the cam ring 13 is an annular member having an inner circumferential cam surface 13a having a substantially elliptical shape, and the suction chambers 13b and 13d in which the volume of the pump chamber 17 expands as the rotor 11 rotates, and the volume of the pump chamber 17 The discharge regions 13c and 13e are contracted.
  • Each pump chamber 17 sucks the working oil from the suction flow path 81 through the suction port 81 (not shown) in the suction region 13 b of the cam ring 13 in the course of one rotation of the rotor 11. It discharges to the discharge flow path 82 through the discharge port 18 in the discharge area
  • each pump chamber 17 expands and contracts with the rotation of the rotor 11, and performs the suction and discharge of hydraulic oil twice in the process of the rotor 11 rotating once.
  • the pump rotational speed N of the pump 1 varies with the rotational speed of the drive device. In the pump 1, when the pump rotational speed N increases, the discharge flow rate increases in proportion to the rotational speed.
  • the pump 1 may be of a type such as a gear pump as long as it is a fixed displacement type of a rotary type.
  • the flow control valve 2 includes a spool 21 that is slidably inserted into the valve housing hole 25, a first fluid pressure chamber 23 provided facing one end surface of the spool 21, and the other of the spool 21.
  • a second fluid pressure chamber 24 provided facing the end surface of the first fluid pressure chamber 24, a return spring 22 as a biasing member that is housed in a compressed state in the second fluid pressure chamber 24 and biases the spool 21 in the valve closing direction, Is provided.
  • the spool 21 includes a first land portion 21 a and a second land portion 21 b that slide along the inner peripheral surface of the valve housing hole 25.
  • the first fluid pressure chamber 23 when the spool 21 moves in a direction in which the volume of the first fluid pressure chamber 23 contracts, the first fluid pressure chamber 23 abuts against the bottom of the valve housing hole 25 to restrict the movement of the spool 21 beyond a predetermined level.
  • One stopper portion 21c is arranged to be coupled to the first land portion 21a.
  • the first fluid pressure chamber 23 is connected to a first series passage 83 branched from the discharge passage 82, and the second fluid pressure chamber 24 is connected to a second communication passage 84 branched from the discharge passage 82.
  • the flow rate control valve 2 is connected to a drain passage 85 that is communicated with or cut off from the first fluid pressure chamber 23 by the first land portion 21a.
  • the spool 21 stops at a position where the load due to the pressure of the hydraulic oil guided to the first fluid pressure chamber 23 and the second fluid pressure chamber 24 defined at both ends and the urging force of the return spring 22 are balanced.
  • the first land portion 21a of the spool 21 blocks communication between the first fluid pressure chamber 23 and the drain passage 85. As a result, the entire amount of hydraulic fluid discharged from the pump 1 is supplied to the fluid pressure device 50.
  • the first land portion 21a of the spool 21 causes the first fluid pressure chamber 23 and the drain passage 85 to communicate with each other. Thereby, a part of the hydraulic oil discharged from the pump 1 returns to the suction flow path 81 through the first fluid pressure chamber 23 and the drain passage 85.
  • the flow rate control valve 2 further includes a pressure regulating device 3 that is provided in the second communication passage 84 that communicates the discharge flow path 82 and the second fluid pressure chamber 24 to adjust the pressure of the second fluid pressure chamber 24.
  • the pressure regulating device 3 is provided in the orifice 40 provided in the second communication passage 84, a relief passage 86 that branches from the second communication passage 84 downstream of the orifice 40 and communicates with the tank 4, and the relief passage 86.
  • a relief valve 30 is provided in the second communication passage 84 that communicates the discharge flow path 82 and the second fluid pressure chamber 24 to adjust the pressure of the second fluid pressure chamber 24.
  • the pressure regulating device 3 is provided in the orifice 40 provided in the second communication passage 84, a relief passage 86 that branches from the second communication passage 84 downstream of the orifice 40 and communicates with the tank 4, and the relief passage 86.
  • the relief valve 30 urges the valve 31 in the valve closing direction, the proportional solenoid 32 that urges the valve in the valve closing direction to change the relief pressure Pr, and the pressure in the relief passage 86 in the valve opening direction. Pilot passage 33.
  • the relief valve 30 opens, and the second fluid pressure chamber 24 hydraulic fluids are discharged to the tank 4 through the second communication passage 84.
  • the relief valve 30 is closed. In this way, the relief valve 30 adjusts the pressure P2 of the second fluid pressure chamber 24 to be equal to the relief pressure Pr.
  • the proportional solenoid 32 and the spring 31 need only be biased in the valve closing direction, and either the proportional solenoid 32 or the spring 31 may be biased in the valve opening direction.
  • Controller 60 controls applied current I applied to proportional solenoid 32. Further, the controller 60 receives the pump rotational speed N of the pump 1 detected by the pump rotational speed detector 70 and a pressure signal required by the fluid pressure device 50. The pressure signal required by the fluid pressure device 50 will be described later.
  • a map (FIG. 2) showing the relationship between the pump rotation speed N at a certain target flow rate of the pump device 100 and the pressure P2 of the second fluid pressure chamber 24 and the pressure P2 of the second fluid pressure chamber 24 are proportional.
  • a map (FIG. 3) representing the relationship with the solenoid applied current I is stored in advance.
  • the target flow rate is a predetermined flow rate value required by the fluid pressure device 50. In FIG. 2, the target flow rate corresponds to the flow rate discharged by the pump 1 at the pump rotation speed Nm.
  • the pump device 100 controls the flow rate of the hydraulic oil supplied from the pump 1 to the fluid pressure device 50 through the discharge flow channel 82 by controlling the flow rate of the return flow from the discharge flow channel 82 to the suction flow channel 81 by the flow rate control valve 2. Control to achieve the target flow rate. Specifically, the controller 60 adjusts the pressure P2 of the second fluid pressure chamber 24 of the flow control valve 2 by controlling the relief valve 30 with reference to the maps of FIG. 2 and FIG. The flow rate of reflux from 82 to the suction flow path 81 is controlled.
  • the map shown in FIG. 2 will be described.
  • the controller 60 refers to the map shown in FIG. 2 and increases the recirculation flow rate from the discharge passage 82 by increasing the pump rotation speed N when the pump rotation speed N exceeds the rotation speed Nm corresponding to the target flow rate. Therefore, control is performed to lower the set pressure of the pressure P2 in the second fluid pressure chamber 24 in order to increase the pressure.
  • the pressure P2 in the second fluid pressure chamber 24 is controlled to be constant so that the hydraulic oil discharged from the pump 1 to the discharge passage 82 is not recirculated.
  • the pressure P2 of the second fluid pressure chamber 24 and the applied current I of the proportional solenoid 32 of the relief valve 30 are in a proportional relationship. Specifically, in order to increase the pressure P2 in the second fluid pressure chamber 24, the applied current I of the proportional solenoid 32 is increased. As a result, the relief pressure Pr of the relief valve 30 increases and the pressure P2 of the second fluid pressure chamber 24 increases. On the other hand, in order to reduce the pressure P2 of the second fluid pressure chamber 24, the applied current I of the proportional solenoid 32 is reduced. Thereby, the relief pressure Pr of the relief valve 30 decreases, and the pressure P2 of the second fluid pressure chamber 24 decreases.
  • the pump 1 is rotationally driven by the power of a driving device such as an engine (not shown), thereby sucking the hydraulic oil from the tank 4 through the suction flow path 81, pressurizing the hydraulic oil, and discharging it to the discharge flow path 82.
  • the hydraulic oil discharged to the discharge flow channel 82 is supplied to the fluid pressure device 50.
  • the pump rotational speed N of the pump 1 varies with the rotational speed of the driving device.
  • the discharge flow rate of the pump 1 increases in proportion to the rotational speed.
  • the discharge flow rate of the pump 1 becomes a flow rate higher than the target flow rate.
  • the pressure P2 in the pressure chamber 24 is controlled by the relief valve 30. Therefore, the pressure P2 in the second fluid pressure chamber 24 is equal to the relief pressure Pr of the relief valve 30.
  • the pump rotation speed N is input from the pump rotation speed detector 70 to the controller 60.
  • the controller 60 selects the pressure P2 of the second fluid pressure chamber 24 corresponding to the pump rotational speed N input with reference to the map shown in FIG.
  • the controller 60 selects the pressure Pd as the pressure P2 of the second fluid pressure chamber 24 so that the flow rate discharged from the pump 1 is not recirculated as shown in the map of FIG.
  • the controller 60 selects the applied current Id of the proportional solenoid 32 of the relief valve 30 corresponding to the pressure Pd with reference to the map of FIG. In this manner, the controller 60 sets the relief pressure Pr of the relief valve 30 to the pressure Pd by applying the applied current Id to the proportional solenoid 32 of the relief valve 30.
  • the controller 60 selects the pressure Pb as the pressure P2 of the second fluid pressure chamber 24 corresponding to the rotation speed Nb with reference to the map of FIG.
  • the controller 60 refers to the map of FIG. 3 and applies the applied current Id of the proportional solenoid 32 of the relief valve 30 corresponding to the pressure Pd.
  • the applied current I is decreased to the applied current Ib of the proportional solenoid 32 of the relief valve 30 corresponding to the pressure Pb.
  • the urging force of the proportional solenoid 32 decreases, and the relief pressure Pr decreases.
  • the discharge flow rate increases due to the increase in the rotation speed of the pump 1 to the rotation speed Nb, but the spool 21 of the flow control valve 2 opens, and the hydraulic oil (excess flow) in the discharge flow path 82 is first. Since the fluid is returned to the suction flow path 81 through the fluid pressure chamber 23 and the drain passage 85, the flow rate of the hydraulic oil supplied from the pump 1 to the fluid pressure device 50 is maintained constant (target flow rate).
  • the controller 60 applies the applied current I to the applied current I in order to reduce the pressure P2 of the second fluid pressure chamber from the pressure Pb to the pressure Pe corresponding to the rotational speed Nc. Decrease from Ib to applied current Ie. Thereby, the urging
  • the controller 60 refers to the maps of FIGS. 2 and 3 to increase the pressure P2 of the second fluid pressure chamber 24 from the pressure Pe corresponding to the rotational speed Nc to the pressure Pb corresponding to the rotational speed Nb. Further, the applied pressure I of the proportional solenoid 32 of the relief valve 30 is increased from the applied current Ie to the applied current Ib, thereby increasing the relief pressure Pr.
  • the discharge flow rate decreases due to the decrease in the rotation speed of the pump 1 to the rotation speed Nb, but the hydraulic oil that is returned to the suction flow path 81 via the first fluid pressure chamber 23 also decreases.
  • the flow rate of the hydraulic oil supplied from the pump 1 to the fluid pressure device 50 is maintained constant (target flow rate).
  • the pump device 100 can keep the flow rate supplied to the fluid pressure device 50 constant even if the pump rotation speed N of the pump 1 changes and the discharge flow rate of the pump 1 changes. Moreover, by using the relief valve 30, the pressure can be adjusted with a simple configuration.
  • the flow rate is controlled to be constant (target flow rate), for example, when the pressure required by the fluid pressure device 50 rises, the pressure of the discharge passage 82 rises, and the first fluid pressure chamber passes through the first series passage 83.
  • the pressure at 23 also increases.
  • the urging force that urges the spool 21 of the flow control valve 2 in the opening direction increases, and the spool 21 moves in the opening direction.
  • the opening degree of the spool 21 is increased, the reflux flow rate recirculated to the suction flow path 81 through the first fluid pressure chamber 23 and the drain passage 85 is increased, and the flow rate of the discharge flow path 82 is changed.
  • the pump apparatus 100 selects the characteristic of the relationship between the pump rotation speed N and the pressure P2 of the second fluid pressure chamber 24 according to the pressure so as to keep the flow rate constant even when the pressure changes. This will be specifically described below.
  • the controller 60 receives a pressure signal required by the fluid pressure device 50.
  • the controller 60 selects the pump rotation speed N corresponding to the pressure required by the fluid pressure device 50 and the second value from the map stored in FIG. The characteristic of the relationship with the pressure P2 of the fluid pressure chamber 24 is selected.
  • the controller 60 selects the high pressure characteristic A in FIG. That is, the set pressure of the pressure P2 in the second fluid pressure chamber 24 is changed from the pressure Pb of the intermediate pressure characteristic B to the pressure Pa of the high pressure characteristic A. As a result, the biasing force that biases the spool 21 of the flow control valve 2 in the closing direction is increased.
  • the pressure required by the fluid pressure device 50 is increased, the pressure in the discharge flow path 82 is increased, and the pressure in the first fluid pressure chamber 23 is increased, so that the biasing force in the valve opening direction of the spool 21 is increased.
  • the pressure P2 of the second fluid pressure chamber 24 increases, and the biasing force that biases the spool 21 of the flow rate control valve 2 in the closing direction increases.
  • the opening degree of the spool 21 of the flow control valve 2 is adjusted so that the reflux flow rate does not change. Therefore, the flow rate of the discharge flow path 82 of the pump 1 can be kept constant (target flow rate).
  • the controller 60 selects the low pressure characteristic C in FIG. That is, the set pressure of the pressure P2 in the second fluid pressure chamber 24 is changed from the pressure Pb of the intermediate pressure characteristic B to the pressure Pc of the low pressure characteristic C. As a result, the biasing force that biases the spool 21 of the flow control valve 2 in the closing direction is reduced.
  • the pressure required by the fluid pressure device 50 is lowered, the pressure in the discharge flow path 82 is lowered, and the pressure in the first fluid pressure chamber 23 is lowered, so that the urging force in the valve opening direction of the spool 21 is reduced.
  • the pressure P2 in the second fluid pressure chamber 24 decreases and the urging force that urges the spool 21 in the closing direction becomes smaller.
  • the opening degree of the spool 21 of the flow control valve 2 is adjusted so that the reflux flow rate does not change. Therefore, the flow rate of the discharge flow path 82 of the pump 1 can be kept constant (target flow rate).
  • the controller 60 selects a characteristic of the relationship between the pump rotation speed N and the pressure P2 of the second fluid pressure chamber 24 according to the pressure, Since the pressure P2 of the second fluid pressure chamber 24 is controlled based on the characteristics, the flow rate of the discharge flow path 82 of the pump 1 can be kept constant (target flow rate).
  • step-like ones such as a high pressure characteristic A, an intermediate pressure characteristic B, and a low pressure characteristic C are shown. It changes the characteristics. Of course, the characteristics may be changed step by step.
  • the intermediate pressure characteristic B shown in FIG. 2 is merely a conceptual example between the high pressure characteristic A and the low pressure characteristic C.
  • the controller 60 is configured to input a pressure signal required by the fluid pressure device 50.
  • a pressure detector may be provided in the discharge flow path 82 and a signal from the pressure detector may be input to the controller 60.
  • the controller 60 refers to the map of FIG. 2, and the pump rotational speed N and the second fluid pressure chamber 24 according to the pressure of the discharge passage 82 detected by the pressure detector.
  • the characteristic of the relationship with the pressure P2 is appropriately selected. Thereby, the pump apparatus 100 can be controlled similarly to the case where the pressure signal required by the fluid pressure device 50 is input to the controller 60.
  • a map corresponding to the target flow rate may be selected as appropriate in accordance with an instruction from the fluid pressure device 50. Good.
  • a map corresponding to the target flow rate may be selected as appropriate in accordance with an instruction from the fluid pressure device 50. Good.
  • a throttle is provided in the discharge flow path connecting the pump and the fluid pressure device, and the flow control valve is controlled based on the pressure difference between the upper and lower sides.
  • the flow control valve 2 Since the pressure regulating device 3 that adjusts the pressure of the second fluid pressure chamber 24 is provided in the second communication passage 84 that communicates the channel 82 and the second fluid pressure chamber 24, no restriction is provided in the discharge channel 82.
  • the flow rate of the hydraulic oil supplied from the pump 1 to the fluid pressure device 50 can be controlled to be constant.
  • no pressure loss occurs because no restriction is provided in the discharge flow path 82, so that the torque for driving the pump 1 can be reduced.
  • the flow rate can be kept constant.
  • the pump device 100 controls the flow rate of the hydraulic oil supplied from the pump 1 to the fluid pressure device 50 according to the pressure required by the fluid pressure device 50, but the fluid pressure device 50 If pressure control is required to keep the pressure constant, the map shown in FIG. 4 is stored in the controller 60 in advance, so that pressure control is performed to keep the pressure constant without performing flow rate control. Can do. This will be specifically described below.
  • FIG. 4 is a map showing the relationship between the required pressure Pp of the pump 1 and the pressure P2 of the second fluid pressure chamber 24.
  • the controller 60 receives a request pressure Pp signal requested by the fluid pressure device 50 from the fluid pressure device 50.
  • the controller 60 controls the flow control valve 2 so that the pressure of the hydraulic oil supplied to the fluid pressure device 50 becomes the required pressure Pp. .
  • the controller 60 adjusts the pressure P2 of the second fluid pressure chamber 24 of the flow control valve 2 by controlling the relief valve 30 with reference to the maps shown in FIGS. 4 and 3 stored in advance. Then, by controlling the urging force of the flow rate control valve 2 in the valve closing direction, the pressure of the hydraulic oil supplied to the fluid pressure device 50 is controlled to the required pressure Pp.
  • the flow control valve 2 functions as a pressure control valve.
  • the pressure in the discharge channel 82 rises and becomes equal to or higher than the required pressure Pp required by the fluid pressure device 50, the pressure in the first fluid pressure chamber 23 also rises, so the urging force in the direction to open the spool 21 increases. . Since the pressure P 2 in the second fluid pressure chamber 24 is controlled by the relief valve 30, the spool 21 moves against the load due to the pressure P 2 in the second fluid pressure chamber 24 and the biasing force of the return spring 22. When the spool 21 moves, the first fluid pressure chamber 23 and the drain passage 85 communicate with each other. As a result, the hydraulic oil in the discharge passage 82 is returned to the suction passage 81 through the first fluid pressure chamber 23 and the drain passage 85, and the pressure in the discharge passage 82 decreases.
  • the required pressure Pp required by the fluid pressure device 50 may be changed. For example, when a signal for increasing the required pressure Pp from the pressure PM to the pressure PH is input from the fluid pressure device 50 to the controller 60, the controller 60 first corresponds to the pressure PH with reference to the map shown in FIG. The pressure Ph of the second fluid pressure chamber 24 is selected. Next, a proportional solenoid applied current Ih is selected such that the pressure P2 of the second fluid pressure chamber 24 becomes the pressure Ph with reference to the map shown in FIG. By applying the application current Ih selected in this way to the proportional solenoid 32 of the relief valve 30, the relief pressure Pr is increased.
  • the controller 60 first refers to the map shown in FIG.
  • the pressure Pl of the second fluid pressure chamber 24 corresponding to the pressure PL is selected.
  • the proportional solenoid applied current Il is selected so that the pressure P2 of the second fluid pressure chamber 24 becomes the pressure Pl.
  • the applied pressure I of the proportional solenoid 32 of the relief valve 30 is controlled according to the required pressure Pp to control the relief pressure Pr.
  • the urging force in the valve closing direction of the flow control valve 2 can be controlled, and the pressure of the discharge flow path 82 can be controlled to the required pressure Pp required by the fluid pressure device 50.
  • the pump device 100 sucks the hydraulic oil, pressurizes the hydraulic oil, and discharges the hydraulic oil to the discharge passage 82, and returns a part of the hydraulic oil discharged from the pump 1 to the suction side (suction passage 81).
  • a flow rate control valve 2 the flow rate control valve 2 facing the one end face of the valve body (spool 21) and the valve body (spool 21), and a first fluid pressure communicating with the discharge flow path 82.
  • a chamber 23 and a second fluid pressure chamber 24 which is provided facing the other end face of the valve body (spool 21) and communicates with the discharge flow path 82; and is accommodated in a compressed state in the second fluid pressure chamber 24;
  • An urging member (return spring 22) that urges the body (spool 21) in the valve closing direction, a second communication passage 84 that communicates the discharge passage 82 and the second fluid pressure chamber 24, and the second fluid
  • a pressure adjusting device 3 that adjusts the pressure P2 of the pressure chamber 24.
  • the pressure P2 in the second fluid pressure chamber 24 of the flow control valve 2 is adjusted by the pressure regulator 3.
  • the flow control valve 2 is controlled to open and close in accordance with the pressure difference between the first fluid pressure chamber 23 to which the pressure of the discharge passage 82 is guided and the second fluid pressure chamber 24 to which the pressure Pr adjusted by the pressure regulator 3 is guided. Is done. Therefore, the flow rate of the discharge flow path of the pump 1 can be controlled to be constant without providing a restriction in the discharge flow path 82. Moreover, since there is no restriction
  • the pressure regulating device 3 is provided in the orifice 40 provided in the second communication passage 84 and the relief passage 86 branched from the second communication passage 84 on the downstream side of the orifice 40, and the relief pressure Pr. And a relief valve 30 that can be changed.
  • the pump device 100 is characterized in that the relief valve 30 includes a proportional solenoid 32 capable of changing the relief pressure Pr.
  • the pressure P2 of the second fluid pressure chamber 24 is adjusted by the relief valve 30. Therefore, the pressure can be adjusted with a simple configuration by using the relief valve 30.
  • the pump device 100 is characterized in that the relief valve 30 adjusts the relief pressure Pr according to the pump rotational speed N of the pump 1.
  • the flow rate of the discharge passage 82 can be made constant by adjusting the relief pressure Pr according to the pump rotation speed N.
  • the pump device 100 is characterized in that the relief pressure 30 of the relief valve 30 is changed according to the pressure required by the fluid pressure device 50.
  • the flow rate of the discharge passage 82 is made constant by controlling the relief pressure Pr according to the pressure required by the fluid pressure device 50. be able to.
  • the pump device 100 includes the flow rate control valve 2 and the pressure regulating device 3 that adjusts the pressure of the second fluid pressure chamber 24 in the second communication passage 84 that communicates the discharge flow path 82 and the second fluid pressure chamber 24.
  • the pressure P2 of the second fluid pressure chamber is changed according to the pump rotational speed N of the pump 1.
  • a flow meter that detects the flow rate discharged by the pump 1 may be provided, and the pressure P2 of the second fluid pressure chamber may be changed according to the detected flow rate.
  • the pressure regulating device 3 includes the relief valve 30 and the orifice 40. Instead, a three-way proportional solenoid control valve that controls the communication between the discharge flow path 82 and the second fluid pressure chamber 24 and the communication between the second fluid pressure chamber 24 and the tank 4 is provided. It is good also as a structure provided in the 2nd communicating path 84. FIG.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Rotary Pumps (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
PCT/JP2015/073709 2014-08-29 2015-08-24 ポンプ装置 WO2016031767A1 (ja)

Priority Applications (3)

Application Number Priority Date Filing Date Title
CN201580043553.8A CN106662103A (zh) 2014-08-29 2015-08-24 泵装置
DE112015003982.1T DE112015003982T5 (de) 2014-08-29 2015-08-24 Pumpvorrichtung
US15/502,938 US20170227007A1 (en) 2014-08-29 2015-08-24 Pump device

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2014-175449 2014-08-29
JP2014175449A JP6393560B2 (ja) 2014-08-29 2014-08-29 ポンプ装置

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WO2016031767A1 true WO2016031767A1 (ja) 2016-03-03

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JP (1) JP6393560B2 (de)
CN (1) CN106662103A (de)
DE (1) DE112015003982T5 (de)
WO (1) WO2016031767A1 (de)

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Publication number Priority date Publication date Assignee Title
JP6885812B2 (ja) * 2017-07-12 2021-06-16 株式会社山田製作所 油圧制御装置及び油圧制御方法
JP6933132B2 (ja) 2017-12-27 2021-09-08 株式会社ジェイテクト ポンプ装置
CN108825494B (zh) * 2018-06-26 2019-12-06 海南葆润石油化工有限公司 一种石油化工用转子泵
CN108825491B (zh) * 2018-06-26 2019-12-06 苏州理合文科技有限公司 一种节约汽车燃油的方法

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0988533A (ja) * 1995-09-26 1997-03-31 Tokyo Buhin Kogyo Kk エンジン潤滑油供給装置
JP2009293416A (ja) * 2008-06-03 2009-12-17 Hitachi Automotive Systems Ltd バルブ装置
JP2014152721A (ja) * 2013-02-12 2014-08-25 Hitachi Automotive Systems Steering Ltd 可変容量形ポンプ

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4480962A (en) * 1980-08-11 1984-11-06 Vickers, Incorporated Pump with inlet passages downstream and through its flow control valve
JPS60259569A (ja) * 1984-06-06 1985-12-21 Nippon Soken Inc 可変容量制御装置
DE19652420A1 (de) * 1996-12-09 1998-06-10 Luk Fahrzeug Hydraulik Stromregelanordnung für eine hydraulische Fördereinrichtung
ES2218021T3 (es) * 1999-04-30 2004-11-16 Hydraulik-Ring Gmbh Alimentacion con medio a presion para una transmision cvt.
JP2006177230A (ja) * 2004-12-22 2006-07-06 Kayaba Ind Co Ltd ポンプ装置
JP4796026B2 (ja) * 2007-02-13 2011-10-19 株式会社山田製作所 オイルポンプにおける圧力制御装置

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0988533A (ja) * 1995-09-26 1997-03-31 Tokyo Buhin Kogyo Kk エンジン潤滑油供給装置
JP2009293416A (ja) * 2008-06-03 2009-12-17 Hitachi Automotive Systems Ltd バルブ装置
JP2014152721A (ja) * 2013-02-12 2014-08-25 Hitachi Automotive Systems Steering Ltd 可変容量形ポンプ

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DE112015003982T5 (de) 2017-06-08
JP6393560B2 (ja) 2018-09-19
US20170227007A1 (en) 2017-08-10
JP2016050505A (ja) 2016-04-11
CN106662103A (zh) 2017-05-10

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