EP3290710A1 - Verstellbare flügelzellenpumpe - Google Patents

Verstellbare flügelzellenpumpe Download PDF

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Publication number
EP3290710A1
EP3290710A1 EP16786367.9A EP16786367A EP3290710A1 EP 3290710 A1 EP3290710 A1 EP 3290710A1 EP 16786367 A EP16786367 A EP 16786367A EP 3290710 A1 EP3290710 A1 EP 3290710A1
Authority
EP
European Patent Office
Prior art keywords
amount
flow
variable
control valve
flow amount
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.)
Withdrawn
Application number
EP16786367.9A
Other languages
English (en)
French (fr)
Other versions
EP3290710A4 (de
Inventor
Koichiro Akatsuka
Tomoyuki Fujita
Tomoyuki Nakagawa
Fumiyasu KATOU
Hiroki GOMI
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
KYB Corp
Original Assignee
KYB Corp
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 Corp filed Critical KYB Corp
Publication of EP3290710A1 publication Critical patent/EP3290710A1/de
Publication of EP3290710A4 publication Critical patent/EP3290710A4/de
Withdrawn legal-status Critical Current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
    • 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
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/18—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber
    • F04C14/22—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/18—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber
    • F04C14/22—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members
    • F04C14/223—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members using a movable cam
    • 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
    • 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
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B2201/00—Pump parameters
    • F04B2201/12—Parameters of driving or driven means
    • F04B2201/1213—Eccentricity of an outer annular cam
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2210/00—Fluid
    • F04C2210/20—Fluid liquid, i.e. incompressible
    • F04C2210/206—Oil
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2270/00—Control; Monitoring or safety arrangements
    • F04C2270/20—Flow
    • 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
    • F04C2270/21—Pressure difference
    • F04C2270/215—Controlled or regulated
    • 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
    • F04C2270/58—Valve parameters
    • F04C2270/585—Controlled or regulated

Definitions

  • the present invention relates to a variable displacement vane pump that is used as a fluid pressure source in a fluid pressure apparatus.
  • variable displacement vane pumps there are pumps in which a discharge capacity is changed by changing an amount of eccentricity of a cam ring with respect to a rotor by making the cam ring swing about a pin as a support point.
  • JP2009-275537A discloses a variable displacement vane pump that includes a control valve that operates in accordance with an upstream-downstream differential pressure of a flow-amount detection orifice and controls an amount of eccentricity of a cam ring with respect to a rotor, a return passage that returns, to a suction passage, a part of working fluid that has been discharged from pump chambers through a discharge passage, and a flow dividing valve that adjusts an opening area of the return passage to the discharge passage.
  • variable displacement vane pump disclosed in JP2009-275537A
  • the amount of eccentricity of the cam ring is reduced by the control valve.
  • the discharge capacity of the pump chambers is reduced, and the flow amount discharged from the variable displacement vane pump is controlled so as to achieve a predetermined flow amount.
  • variable displacement vane pump disclosed in JP2009-275537A when the flow amount of the working fluid discharged from the pump chambers reaches the flow amount at which a predetermined upstream-downstream differential pressure of the flow-amount detection orifice is generated, the flow amount of the working fluid is controlled to a constant flow amount by the control valve so as to maintain the discharge flow amount. Thereby, the working fluid is guided to the return passage at the returning flow amount that is the difference between the discharge flow amount of the variable displacement vane pump controlled by the control valve so as to be constant and the flow amount of the working fluid guided to the discharge passage by being controlled by the flow dividing valve.
  • the variable displacement vane pump disclosed in JP2009-275537A while the discharge flow amount is controlled by the control valve so as to be constant, the returning flow amount is substantially constant.
  • variable displacement vane pump because the discharge flow amount is controlled by the control valve and the returning flow amount becomes substantially constant, there is a risk in that, when the rotating speed of the pump is high, cavitation may be caused due to insufficient suction.
  • An object of the present invention is to provide a variable displacement vane pump that is capable of suppressing occurrence of cavitation.
  • a variable displacement vane pump includes: a rotor linked to a driving shaft; a plurality of vanes provided so as to be able to reciprocate in a radial direction relative to the rotor; a cam ring having an inner circumferential surface on which tip ends of the vanes slide by rotation of the rotor; pump chambers defined by the rotor, the cam ring, and pairs of the adjacent vanes; a suction passage configured to guide working fluid to the pump chambers; a first fluid pressure chamber and a second fluid pressure chamber defined in an outer-circumferential accommodating space on outer side of the cam ring, the first fluid pressure chamber and the second fluid pressure chamber being configured to make the cam ring eccentric with respect to the rotor by pressure difference between the first fluid pressure chamber and the second fluid pressure chamber; a control restrictor configured to impart resistance to a flow of the working fluid discharged from the pump chambers; a flow-amount control valve operated in accordance with an upstream-downstream differential pressure of the control restrictor
  • variable displacement vane pump 100 according to an embodiment of the present invention will be described below with reference to the drawings.
  • variable displacement vane pump 100 (hereinafter, simply referred to as "vane pump ”) is used as a hydraulic source for a hydraulic apparatus mounted on a vehicle, such as, for example, a power steering apparatus, a transmission, and the like.
  • the vane pump 100 includes a pump cartridge 101 that discharges working oil (working fluid), a flow-amount control valve 102 that controls the flow amount of the working oil that is discharged from the pump cartridge 101 through a discharge passage 41 and supplied to a hydraulic apparatus 18, and a variable control valve 103 that controls the flow amount of the working oil that is discharged from the pump cartridge 101.
  • working oil working fluid
  • flow-amount control valve 102 that controls the flow amount of the working oil that is discharged from the pump cartridge 101 through a discharge passage 41 and supplied to a hydraulic apparatus 18
  • a variable control valve 103 that controls the flow amount of the working oil that is discharged from the pump cartridge 101.
  • the vane pump 100 further includes a control orifice 104 that is provided in the discharge passage 41 and serves as a control restrictor for imparting resistance to a flow of the working oil discharged from the pump cartridge 101 and a variable orifice 105 that serves as a variable restrictor for imparting resistance to a flow of the working oil that has passed through the control orifice 104.
  • motive power from an engine (not shown) as a motive-power source is transmitted to an end portion of a driving shaft 1, and a rotor 2 linked to the driving shaft 1 is rotated.
  • the rotor 2 is rotated in the clockwise direction in FIG. 1 .
  • the pump cartridge 101 includes a plurality of vanes 3 that are provided so as to be able to reciprocate in the radial direction relative to the rotor 2, a cam ring 4 having an inner circumferential surface on which tip ends of the vanes 3 slide by rotation of the rotor 2, and an annular adapter ring 5 that is provided so as to surround the cam ring 4.
  • a plurality of pump chambers 6 are defined within the cam ring 4 by an outer circumferential surface of the rotor 2, the inner circumferential surface of the cam ring 4, and pairs of adjacent vanes 3.
  • the working oil is sucked into the pump chambers 6 through a suction passage 40 from a tank 17 in a suction region at which the volumes of the pump chambers 6 are expanded, and the working oil is discharged from the pump chambers 6 through the discharge passage 41 in a discharge region at which the volumes of the pump chambers 6 are contracted.
  • a support pin 10 for supporting the cam ring 4 is provided on an inner circumferential surface of the adapter ring 5.
  • the cam ring 4 swings around inside the adapter ring 5 about the support pin 10 as a supporting point, and thereby, the cam ring 4 is made eccentric with respect to the center of the rotor 2.
  • the support pin 10 is the supporting point for the swinging of the cam ring 4.
  • a seal member 11 which is in sliding contact with an outer circumferential surface of the cam ring 4 when the cam ring 4 swings around, is fitted.
  • a first fluid pressure chamber 15 and a second fluid pressure chamber 16 are defined by the support pin 10 and the seal member 11.
  • a first fluid pressure passage 47 of the variable control valve 103 which will be described later, is connected to the first fluid pressure chamber 15, and the working oil is guided through the first fluid pressure passage 47.
  • a second fluid pressure passage 48 of the variable control valve 103 which will be described later, is connected to the second fluid pressure chamber 16.
  • a part of the working oil that has been discharged from the pump chambers 6 is guided to the second fluid pressure chamber 16 through a restricting passage 50 provided with an orifice 106.
  • the cam ring 4 swings around the support pin 10 by pressure difference of the working oil between the first fluid pressure chamber 15 and the second fluid pressure chamber 16. As the cam ring 4 swings around the support pin 10, the amount of eccentricity of the cam ring 4 with respect to the rotor 2 is changed, and the discharge capacity of the pump chambers 6 is changed. When the pressure in the first fluid pressure chamber 15 is greater than the pressure in the second fluid pressure chamber 16, the amount of eccentricity of the cam ring 4 with respect to the rotor 2 is reduced, and the discharge capacity of the pump chambers 6 is reduced.
  • a return passage 42 that is in communication with the suction passage 40 is connected to the flow-amount control valve 102.
  • a part of the working oil that has been discharged from the pump cartridge 101 is guided to the suction passage 40 through the flow-amount control valve 102 and the return passage 42.
  • the flow-amount control valve 102 has a first spool 20 that moves in response to an upstream-downstream differential pressure between upstream and downstream of the control orifice 104 that imparts resistance to the flow of the working oil that has been discharged from the pump chambers 6.
  • the first spool 20 is inserted into a first-spool accommodating portion 21 in a freely slidable manner.
  • the first spool 20 has a first land portion 20A and a second land portion 20B that are in sliding contact with an inner circumference of the first-spool accommodating portion 21.
  • a first circular groove 20C that opens to an outer circumferential surface of the first spool 20 is formed between the first land portion 20A and the second land portion 20B.
  • a first pressure chamber 22 is defined between the first land portion 20A of the first spool 20 and the one end portion of the first-spool accommodating portion 21.
  • a second pressure chamber 23 is defined between the second land portion 20B of the first spool 20 and the other end portion of the first-spool accommodating portion 21.
  • a first control passage 43 that is in communication with the discharge passage 41 at the upstream side of the control orifice 104 is connected to the first pressure chamber 22, and the working oil is guided to the first pressure chamber 22 from the upstream side of the control orifice 104.
  • a second control passage 44 that is in communication with the discharge passage 41 at the downstream side of the control orifice 104 is connected to the second pressure chamber 23, and the working oil that has passed through the control orifice 104 is guided from the downstream side thereof to the second pressure chamber 23.
  • the working oil that has been discharged from the pump chambers 6 is guided directly to the first pressure chamber 22, the working oil that has been depressurized by passing through the control orifice 104 is guided to the second pressure chamber 23.
  • a first spring 24 serving as a biasing member for biasing the first spool 20 in the direction in which the volume of the second pressure chamber 23 is increased is accommodated. Therefore, the first spool 20 is located at a position where the load based on the upstream-downstream differential pressure of the control orifice 104 and the biasing force exerted by the first spring 24 are balanced.
  • a return port 25 that guides the working oil from the first pressure chamber 22 to the return passage 42 is provided on the first-spool accommodating portion 21.
  • the return port 25 is in a state closed by the first land portion 20A of the first spool 20.
  • the return port 25 is opened.
  • a recessed opposing port 26 is formed at a position opposite to the return port 25, in other words, at a position symmetrical to the return port 25 with respect to the axis of the first-spool accommodating portion 21.
  • the working oil that has flown into the opposing port 26 from the first pressure chamber 22 is guided to the return port 25 through the first circular groove 20C.
  • the upstream-downstream differential pressure of the control orifice 104 reaches a predetermined value at which the first spool 20 of the flow-amount control valve 102 moves against the biasing force exerted by the first spring 24 and the return port 25 is opened.
  • the upstream-downstream differential pressure of the control orifice 104 reaches the predetermined value at which the return port 25 is opened, in accordance with an opening area of the return port 25, a part of the working oil that has been discharged from the pump cartridge 101 is guided to the suction passage 40 through the first pressure chamber 22, the return port 25, and the return passage 42.
  • the variable orifice 105 is provided at the downstream side of the control orifice 104 in the discharge passage 41. More specifically, the variable orifice 105 is provided on the discharge passage 41 at the downstream side of a location at which the second control passage 44 that is connected to the second pressure chamber 23 of the flow-amount control valve 102 communicates with the discharge passage 41.
  • the variable orifice 105 is a variable restrictor capable of changing resistance to be imparted to the flow of the working oil passing therethrough by changing its opening area by controlling amount of current flowing to a solenoid (not shown).
  • the variable control valve 103 has a second spool 30 that moves in response to the upstream-downstream differential pressure between upstream and downstream of the variable orifice 105 that is generated by guiding, to the variable orifice 105, the working oil that has passed through the control orifice 104.
  • the second spool 30 has a third land portion 30A and a fourth land portion 30B that are in sliding contact with an inner circumference of a second spool accommodating portion 31.
  • a second circular groove 30C that opens to an outer circumferential surface of the second spool 30 is formed between the third land portion 30A and the fourth land portion 30B.
  • a third pressure chamber 32 is defined between the third land portion 30A of the second spool 30 and the one end portion of the second spool accommodating portion 31.
  • a fourth pressure chamber 33 is defined between the fourth land portion 30B of the second spool 30 and the other end portion of the second spool accommodating portion 31.
  • a third control passage 45 that is in communication with the discharge passage 41 at a location between the control orifice 104 and the variable orifice 105 is connected to the third pressure chamber 32, and the working oil is guided to the third pressure chamber 32 from the upstream side of the variable orifice 105.
  • a fourth control passage 46 that is in communication with the discharge passage 41 at the downstream side of the variable orifice 105 is connected to the fourth pressure chamber 33, and the working oil is guided to the fourth pressure chamber 33 from the downstream side of the variable orifice 105.
  • the working oil that has been discharged from the pump chambers 6 and depressurized by the control orifice 104 is guided to the third pressure chamber 32, the working oil that has been depressurized by passing through the control orifice 104 and the variable orifice 105 is guided to the fourth pressure chamber 33.
  • a second spring 34 serving as a biasing member for biasing the second spool 30 in the direction in which the volume of the fourth pressure chamber 33 is increased is accommodated. Therefore, the second spool 30 is located at a position where the load based on the upstream-downstream differential pressure of the variable orifice 105 and the biasing force exerted by the second spring 34 are balanced.
  • the first fluid pressure passage 47 and the second fluid pressure passage 48 that are in communication with the first fluid pressure chamber 15 and the second fluid pressure chamber 16, respectively, and a drain passage 49 that is in communication with the second circular groove 30C and the suction passage 40 are connected to the second spool accommodating portion 31.
  • the second spool 30 moves against the biasing force exerted by the second spring 34, and thereby the third pressure chamber 32 is communicated with the first fluid pressure passage 47 and the second circular groove 30C is communicated with the second fluid pressure passage 48.
  • the opening area of the first fluid pressure passage 47 to the third pressure chamber 32 is increased, and the opening area of the second fluid pressure passage 48 to the second circular groove 30C is increased.
  • the working oil in the third pressure chamber 32 is supplied to the first fluid pressure chamber 15 through the first fluid pressure passage 47, and the working oil in the second fluid pressure chamber 16 is discharged to the tank 17 through the second fluid pressure passage 48, the second circular groove 30C, and the drain passage 49.
  • the cam ring 4 moves such that the amount of eccentricity with respect to the rotor 2 is reduced in response to the pressure difference between the first fluid pressure chamber 15 and the second fluid pressure chamber 16.
  • the cam ring 4 As the pressure difference between the first fluid pressure chamber 15 and the second fluid pressure chamber 16 is increased in response to the increase in the pump rotation speed, the cam ring 4 is brought into contact with the inner circumferential surface of the adapter ring 5 and the amount of eccentricity of the cam ring 4 is minimized, and thereby, the discharge capacity of the pump chambers 6 becomes a minimum discharge capacity.
  • the variable control valve 103 is operated in accordance with the upstream-downstream differential pressure of the variable orifice 105, even when the pump rotation speed is increased, the discharge flow amount of the pump cartridge 101 is controlled so as to be substantially constant.
  • the upstream-downstream differential pressure of the variable orifice 105 is generated at amount in accordance with the opening area of the variable orifice 105 that is controlled by the amount of current flow to the solenoid and the passing flow amount passing through the variable orifice 105. Therefore, by controlling the opening area of the variable orifice 105 by the solenoid, it is possible to arbitrarily set the passing flow amount of the variable orifice 105 that generates the upstream-downstream differential pressure for operating the variable control valve 103.
  • FIG. 2 is a graph showing the relationship between the pump rotation speed and the flow amount of the working oil of the vane pump 100.
  • FIG. 3 is a hydraulic circuit diagram of a vane pump 200 as a comparative example
  • FIG. 4 is a graph showing the relationship between the pump rotation speed and the flow amount of the working oil of the vane pump 200.
  • a flow amount Q shown with a solid line is a supply flow amount of the working oil supplied to the hydraulic apparatus 18, and a flow amount Q1 shown with a broken line is a discharge flow amount of the working oil discharged from the pump cartridge 101.
  • FIGs. 1 is a flow amount of the working oil supplied to the hydraulic apparatus
  • a flow amount Q2 shown with a one-dot chain line is a flow amount of the working oil controlled by the flow-amount control valve 102.
  • a flow amount Q3 is a passing flow amount of the variable orifice 105 required to generate the upstream-downstream differential pressure for operating the variable control valve 103.
  • the passing flow amount of the control orifice 104 required to generate the upstream-downstream differential pressure for operating the flow-amount control valve 102 is referred to as "the cracking flow amount”
  • the flow amount Q2 of the working oil controlled by the flow-amount control valve 102 is referred to as “the control flow amount Q2”
  • the control flow amount of the flow-amount control valve 102 at the pump maximum rotation speed N1 used with the vane pump 100 is referred to as "the maximum control flow amount”.
  • variable-control-setting flow amount Q3 the passing flow amount Q3 of the variable orifice 105 required to generate the upstream-downstream differential pressure for operating the variable control valve 103
  • the constant discharge flow amount the passing flow amount Q3 of the variable orifice 105 required to generate the upstream-downstream differential pressure for operating the variable control valve 103
  • the constant discharge flow amount the discharge flow amount of the pump cartridge 101 that is kept constant by the variable control valve 103
  • the variable-control-setting flow amount Q3 is set by controlling the opening area of the variable orifice 105 by changing the amount of current flow to the solenoid. For example, in a case where the opening area of the variable orifice 105 is set, by flow of the working oil passing through the variable orifice 105 at the flow amount greater than the cracking flow amount, such that the upstream-downstream differential pressure for operating the variable control valve 103 is generated, the variable-control-setting flow amount Q3 becomes greater than the cracking flow amount of the flow-amount control valve 102.
  • variable-control-setting flow amount Q3 becomes smaller than the cracking flow amount of the flow-amount control valve 102.
  • the vane pump 100 the vane pump 200 as a comparative example will be described with reference to FIGs. 3 and 4 .
  • the vane pump 200 includes the variable control valve 103 that is operated by the upstream-downstream differential pressure of the variable orifice 105 provided on the discharge passage 41 and the flow-amount control valve 102 that is operated by the upstream-downstream differential pressure of the control orifice 104 provided on the discharge passage 41 at the downstream side of the variable orifice 105.
  • the flow-amount control valve 102 is provided at the downstream side of the variable control valve 103.
  • FIG. 4(a) is a diagram showing the relationship between the pump rotation speed and the flow amount in a case where the variable-control-setting flow amount Q3 is set so as to be smaller than the cracking flow amount of the flow-amount control valve 102.
  • FIG. 4(b) is a diagram showing the relationship between the pump rotation speed and the flow amount in a case where the variable-control-setting flow amount Q3 is set so as to be greater than the maximum control flow amount of the flow-amount control valve 102.
  • variable-control-setting flow amount Q3 is set so as to be smaller than the cracking flow amount of the flow-amount control valve 102, the discharge flow amount of the working oil from the pump cartridge 101 reaches the variable-control-setting flow amount Q3 in response to the increase in the pump rotation speed, and thereby, the variable control valve 103 is operated.
  • the upstream-downstream differential pressure of the control orifice 104 reaches a predetermined differential pressure at which the flow-amount control valve 102 is operated
  • the upstream-downstream differential pressure of the variable orifice 105 reaches a predetermined differential pressure at which the variable control valve 103 is operated, and thereby, the variable control valve 103 is operated.
  • the discharge flow amount from the pump cartridge 101 is controlled to be constant so as to keep the discharge flow amount.
  • variable control valve 103 when the variable control valve 103 is operated, because the discharge flow amount from the pump cartridge 101 is not increased even when the pump rotation speed is increased, the discharge flow amount does not reach the cracking flow amount of the flow-amount control valve 102. In other words, even in a case where the variable-control-setting flow amount Q3 that is set so as to be smaller than the cracking flow amount of the flow-amount control valve 102 passes through the control orifice 104, the upstream-downstream differential pressure for operating the flow-amount control valve 102 is not generated at the control orifice 104. Thus, as shown in FIG.
  • the flow amount of the working oil that has passed through the variable orifice 105 is not controlled by the flow-amount control valve 102, and the working oil whose flow amount is controlled by the variable control valve 103 so as to achieve the variable-control-setting flow amount Q3 is guided to the hydraulic apparatus 18.
  • the variable-control-setting flow amount Q3 is set so as to be smaller than the cracking flow amount of the flow-amount control valve 102, because the flow-amount control valve 102 is not operated, the working oil is not guided to the suction passage 40 through the return passage 42.
  • variable-control-setting flow amount Q3 is set so as to be higher than the maximum control flow amount of the flow-amount control valve 102
  • the discharge flow amount from the pump cartridge 101 is increased in response to the increase in the pump rotation speed and reaches the cracking flow amount of the flow-amount control valve 102.
  • the upstream-downstream differential pressure of the control orifice 104 reaches a predetermined value and the flow-amount control valve 102 is operated, and thereby, the return port 25 is opened.
  • the flow amount of the working oil that has been discharged from the pump cartridge 101 is controlled by the flow-amount control valve 102 so as to achieve the control flow amount Q2 and the working oil is guided to the hydraulic apparatus 18.
  • variable control valve 103 because the variable control valve 103 is in a non-operating state, the cam ring 4 is in the maximum eccentric state and the discharge capacity of the pump chambers 6 is maintained in the maximum state. Therefore, as the pump rotation speed is further increased, the discharge flow amount from the pump cartridge 101 is increased in a manner proportional to the increase in the pump rotation speed.
  • the discharge flow amount from the pump cartridge 101 is increased and reaches the variable-control-setting flow amount Q3
  • the upstream-downstream differential pressure of the variable orifice 105 reaches a predetermined value.
  • the variable control valve 103 is operated, and as shown in FIG. 4(b) , the discharge flow amount from the pump cartridge 101 is controlled so as to achieve the variable-control-setting flow amount Q3 as the constant discharge flow amount.
  • the vane pump 200 because the variable control valve 103 is provided at the upstream side of the flow-amount control valve 102, as the pump rotation speed is increased, the discharge flow amount from the pump cartridge 101 is controlled by the variable control valve 103 so as to achieve the variable-control-setting flow amount Q3, and so, the discharge flow amount does not exceeds the variable-control-setting flow amount Q3. Therefore, a part of the working oil guided to the flow-amount control valve 102 at the variable-control-setting flow amount Q3 is guided to the suction passage 40 as the returning flow amount. In other words, in the vane pump 200, as shown in FIG. 4(b) , the returning flow amount guided to the return passage 42 is a difference between the control flow amount Q2 and the variable-control-setting flow amount Q3 as the constant discharge flow amount.
  • variable-control-setting flow amount Q3 is set so as to be smaller than the cracking flow amount of the flow-amount control valve 102 by controlling the amount of current flow to the solenoid, similarly to the vane pump 200, the flow-amount control valve 102 is not operated and the working oil is not guided to the suction passage 40 through the return passage 42. In this case, all of the working oil discharged from the pump cartridge 101 is guided to the hydraulic apparatus 18.
  • variable-control-setting flow amount Q3 is set so as to be greater than the maximum control flow amount of the flow-amount control valve 102, similarly to the vane pump 200, the discharge flow amount from the pump cartridge 101 of the vane pump 100 is increased in response to the increase in the pump rotation speed and reaches the cracking flow amount of the flow-amount control valve 102.
  • the working oil whose flow amount is controlled by the flow-amount control valve 102 so as to achieve the control flow amount Q2 is guide to the hydraulic apparatus 18.
  • a part of the working oil discharged from the pump cartridge 101 through the return passage 42 is guided to the suction passage 40.
  • variable-control-setting flow amount Q3 is set so as to be greater than the maximum control flow amount of the flow-amount control valve 102, because the control flow amount Q2 does not reach the variable-control-setting flow amount Q3 even when the pump rotation speed is increased, the variable control valve 103 is not operated and the cam ring 4 of the pump cartridge 101 is maintained in the maximum eccentric state. Therefore, the discharge capacity of the pump chambers 6 is maintained in the maximum state, and the discharge flow amount from the pump cartridge 101 is increased in a manner proportional to the increase in the pump rotation speed. Therefore, as shown in FIG.
  • the difference between the discharge flow amount Q 1 of the pump cartridge 101, in which the discharge capacity of the pump chambers 6 is in the maximum state (the cam ring 4 is in the maximum eccentric state), and the control flow amount Q2 can be used as the returning flow amount.
  • FIG. 2(c) is a diagram showing a case in which the variable-control-setting flow amount Q3 is set between the cracking flow amount of the flow-amount control valve 102 and the maximum control flow amount. In this case, until the control flow amount Q2 reaches the variable-control-setting flow amount Q3, the difference between the discharge flow amount Q1 of the pump cartridge 101, in which the discharge capacity of the pump chambers 6 is in the maximum state, and the control flow amount Q2 is guided to the suction passage 40 as the returning flow amount.
  • the variable control valve 103 As the pump rotation speed is increased, the control flow amount Q2 reaches the variable-control-setting flow amount Q3, and the upstream-downstream differential pressure of the variable orifice 105 reaches a predetermined value, the variable control valve 103 is operated. Thereby, as shown in FIG. 2(c) , even when the pump rotation speed is increased, the discharge flow amount from the pump cartridge 101 is controlled so as to achieve the constant discharge flow amount at which the discharge flow amount becomes constant. Therefore, the working oil is guided to the hydraulic apparatus 18 at the variable-control-setting flow amount Q3, and the difference between the discharge flow amount Q1 as the constant discharge flow amount and the variable-control-setting flow amount Q3 is guided to the return passage 42 as the returning flow amount.
  • variable control valve 103 is operated by the working oil whose flow amount is controlled by the flow-amount control valve 102 so as to achieve the control flow amount Q2
  • the variable control valve 103 is not operated until the control flow amount Q2 reaches the variable-control-setting flow amount Q3, and the amount of eccentricity of the cam ring 4 is maintained in the maximum state.
  • the discharge capacity of the pump chambers 6 is maintained at the maximum discharge capacity.
  • the vane pump 100 the working oil can be discharged from the pump cartridge 101 at the flow amount equal to or greater than the variable-control-setting flow amount Q3 in response to the increase in the pump rotation speed, and the difference between the discharge flow amount Q1 and the control flow amount Q2 can be guided to the suction passage 40 as the returning flow amount. Therefore, with the vane pump 100, it is possible to secure greater returning flow amount.
  • variable-control-setting flow amount Q3 is set on the basis of, for example, the pump rotation speed.
  • variable-control-setting flow amount Q3 is set so as to be smaller than the cracking flow amount of the flow-amount control valve 102, is used when the pump rotation speed is low, for example.
  • variable-control-setting flow amount Q3 is set so as to be greater than the maximum control flow amount of the flow-amount control valve 102, is used when the pump rotation speed is high, for example.
  • variable-control-setting flow amount Q3 may be set between the maximum control flow amount of the flow-amount control valve 102 and the cracking flow amount.
  • the settings of the variable-control-setting flow amount Q3 are not limited to those based on the pump rotation speed, and the setting may be performed on the basis of a driving state of a vehicle, an operating state of the hydraulic apparatus 18, and so forth. For example, even when the pump rotation speed is low, when a gear of a vehicle is shifted, the vane pump 100 may be operated so as to output large torque by setting the variable-control-setting flow amount Q3 so as to be equal to or greater than the maximum control flow amount of the flow-amount control valve 102 and by maintaining the cam ring 4 in the maximum eccentric state.
  • the vane pump 100 a part of the working oil discharged from the pump chambers 6 of the pump cartridge 101 is guided to the return passage 42 by the flow-amount control valve 102, and the flow amount of the working oil is controlled so as to achieve the control flow amount Q2.
  • the variable control valve 103 is operated by the working oil whose control flow amount is controlled by the flow-amount control valve 102.
  • the variable control valve 103 is not operated and the discharge capacity of the pump chambers 6 is maintained in the maximum state.
  • variable control valve 103 is operated by the working fluid whose flow amount is controlled by the control flow amount Q2, it is possible to discharge the working fluid from the pump chambers 6 of the pump cartridge 101 at the flow amount equal to or greater than the variable-control-setting flow amount Q3. Therefore, the difference between the discharge flow amount from the pump chambers 6 that is increased to the variable-control-setting flow amount Q3 or more in response to the increase in the pump rotation speed and the control flow amount Q2 is guided to the return passage 42. Therefore, it is possible to circulate greater amount of the working oil through the return passage 42 and to suppress occurrence of the cavitation.
  • the amount of eccentricity of the cam ring 4 with respect to the rotor 2 is controlled by the pressure difference between the pressure of the working oil guided to the first fluid pressure chamber 15 and the pressure of the working oil guided to the second fluid pressure chamber 16.
  • a biasing member for example, a coil spring
  • the amount of eccentricity of the cam ring 4 is controlled by the biasing force exerted by the biasing member and the pressure difference between the first fluid pressure chamber 15 and the second fluid pressure chamber 16.

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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)
EP16786367.9A 2015-04-27 2016-04-19 Verstellbare flügelzellenpumpe Withdrawn EP3290710A4 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2015090303A JP6577227B2 (ja) 2015-04-27 2015-04-27 可変容量型ベーンポンプ
PCT/JP2016/062416 WO2016175090A1 (ja) 2015-04-27 2016-04-19 可変容量型ベーンポンプ

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EP3290710A1 true EP3290710A1 (de) 2018-03-07
EP3290710A4 EP3290710A4 (de) 2018-10-03

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US (1) US20180112661A1 (de)
EP (1) EP3290710A4 (de)
JP (1) JP6577227B2 (de)
CN (1) CN107532594A (de)
WO (1) WO2016175090A1 (de)

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS56148693A (en) * 1980-04-17 1981-11-18 Mitsubishi Motors Corp Rated displacement oil pump
JPS59131989U (ja) * 1983-02-24 1984-09-04 アイシン精機株式会社 流量調整弁付きベ−ンポンプ
JP4673493B2 (ja) * 2001-03-21 2011-04-20 株式会社ショーワ 可変容量型ポンプ
JP2003097454A (ja) * 2001-09-26 2003-04-03 Hitachi Unisia Automotive Ltd ベーンポンプ
JP2005042674A (ja) * 2003-07-25 2005-02-17 Unisia Jkc Steering System Co Ltd 可変容量形ポンプ
US20050100447A1 (en) * 2003-11-11 2005-05-12 Desai Mihir C. Flow control system for a gas turbine engine
JP5216397B2 (ja) * 2008-04-15 2013-06-19 カヤバ工業株式会社 可変容量型ベーンポンプ
JP5116546B2 (ja) * 2008-04-23 2013-01-09 カヤバ工業株式会社 可変容量型ベーンポンプ
JP2009275537A (ja) * 2008-05-13 2009-11-26 Kayaba Ind Co Ltd 可変容量型ベーンポンプ
JP2010255551A (ja) * 2009-04-27 2010-11-11 Kayaba Ind Co Ltd 可変容量型ベーンポンプ
JP5993291B2 (ja) * 2012-11-27 2016-09-14 日立オートモティブシステムズ株式会社 可変容量形ポンプ
JP5998044B2 (ja) * 2012-12-26 2016-09-28 Ｋｙｂ株式会社 可変ポンプ

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WO2016175090A1 (ja) 2016-11-03
JP6577227B2 (ja) 2019-09-18
JP2016205310A (ja) 2016-12-08
US20180112661A1 (en) 2018-04-26
CN107532594A (zh) 2018-01-02
EP3290710A4 (de) 2018-10-03

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