CN106662103A - Pump device - Google Patents
Pump device Download PDFInfo
- Publication number
- CN106662103A CN106662103A CN201580043553.8A CN201580043553A CN106662103A CN 106662103 A CN106662103 A CN 106662103A CN 201580043553 A CN201580043553 A CN 201580043553A CN 106662103 A CN106662103 A CN 106662103A
- Authority
- CN
- China
- Prior art keywords
- pressure
- fluid
- fluid pressure
- pump
- pressure chamber
- 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.)
- Pending
Links
Classifications
-
- 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
Landscapes
- 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)
Abstract
The invention discloses a pump device (100) which is provided with a flowrate control valve (2) that recirculates, to the intake side, a portion of a working fluid discharged from a pump (1), wherein the flowrate control valve (2) is provided with: a valve body (21); a first fluid pressure chamber (23) provided facing the end surface of one side of the valve body (21) and connected with a discharge channel (82); a second fluid pressure chamber (24) provided facing the end surface of the other side of the valve body (21) and connected with the discharge channel (82); a biasing member (22) that is accommodated in the second fluid pressure chamber (24) and biases the valve body (21) in the valve closure direction; and a pressure regulator (3) that is provided to a connection path (84) connecting the second fluid pressure chamber (24) with the discharge channel (82) and regulates the pressure inside the second fluid pressure chamber (24).
Description
Technical field
The present invention relates to a kind of pump installation.
Background technology
Existed in the past a kind of in order to the flow that sprays of pump is remained into pump installation that is constant and being provided with flow control valve.
A kind of pump installation has been recorded in Japanese JP05-61482U, in the pump installation, the suction of vane pump has been connected to
The midway of the drain passage between path and ejection path is provided with flow control valve.In the pump described in Japanese JP05-61482U
In device, the working oil that ejection path is proportionally ejected into from pump chamber with the rotating speed of pump is fed into hydraulic pressure and drives by throttling element
Dynamic device.Additionally, the pump installation described in Japan JP05-61482U is opened and closed it by controlling flow control valve, by working oil
Constant amount is controlled to from vane pump to the quantity delivered of fluid pressure drive device.
The content of the invention
But, in the pump installation of Japanese JP05-61482U, on the ejection path of pump restriction is provided with.Therefore, because of section
Stream portion and produce the pressure loss, need amount, for transfer tube the moment of torsion corresponding with the amount of the pressure loss.
The present invention puts in view of the above-mentioned problems and completes, and its object is to provide a kind of driving torque of reduction pump simultaneously
And can control the pump installation of flow.
A technical scheme of the invention, a kind of pump installation, it is used for fluid pressure equipment supply working fluid, should
Pump installation is characterised by that the pump installation includes：Pump, it is used to suck working fluid, by working fluid pressurization to discharging jet
Road sprays；And flow control valve, it is used to make a part for the working fluid gushed out from pump to suction side reflux, flow control
Valve processed includes：Valve element；First fluid pressure chamber, its towards valve element an end face arrange, with spray fluid communication；Second fluid
Pressure chamber, its towards valve element another end face arrange, with spray fluid communication；Force application component, it is housed in compressive state
In second fluid pressure chamber, for exerting a force to valve closing direction to valve element；And regulator, it is located at connection and sprays stream and second
The communication paths of fluid pressure chamber, for adjusting the pressure of the second fluid pressure chamber.
Description of the drawings
Fig. 1 is the hydraulic circuit diagram of the pump installation of embodiments of the present invention.
Fig. 2 is the relation between the revolution speed under certain target flow for representing pump installation and the pressure of second fluid pressure chamber
Corresponding diagram.
Fig. 3 is that the pressure and proportional solenoid for representing second fluid pressure chamber applies the corresponding diagram of the relation between electric current.
Fig. 4 is the corresponding diagram for representing the relation between the requirement pressure of pump installation and the pressure of second fluid pressure chamber.
Specific embodiment
Hereinafter, illustrate referring to the drawings the pump installation 100 to embodiments of the present invention.
Fig. 1 is the hydraulic circuit diagram of pump installation 100.
Pump installation 100 includes：Pump 1, it is used to be sucked as working fluid from the suction passage 81 for being connected to fluid tank 4
Working oil, working oil pressurization is sprayed to stream 82 is sprayed；Flow control valve 2, it is used for the working oil for making to be gushed out from pump 1
A part to flowing back in the suction passage 81 of suction side, the stream of the working oil for controlling to press the supply of equipment 50 from pump 1 to fluid
Amount.
Pump 1 is the vane pump of fixed capacity type.Pump 1 includes：Rotor 11, it is driven by driving means such as electromotors (not shown)
Move and rotate；Multiple blades 12, it is set as being moved back and forth freely in radial direction relative to rotor 11；And stator 13, its
Storage rotor 11, and with the rotation of rotor 11, the top ends of blade 12 are slided with the cam surface 13a of the inner circumferential of stator 13 and are connect
Touch.
The slit 14 that there is peristome in outer peripheral face is formed with rotor 11 with radial across predetermined space.Blade
12 sliding freely insert in slit 14.
The ejection pressure for having back pressure chamber 15, pump 1 in the base end side division of slit 14 is imported into the back pressure chamber 15.Adjacent back pressure
Room 15 is connected using the groove 16 of the arc-shaped for being formed at rotor 11.It is imported with pump all the time in the groove 16 and sprays pressure.In back pressure chamber
In the presence of 15 pressure and the centrifugal force that caused by the rotation of rotor 11, blade 12 is pushed to the direction extracted from slit 14,
The top ends of blade 12 are abutted with the cam surface 13a of the inner circumferential of stator 13.Thus, stator 13 inner utilization rotor 11 it is outer
Side face, the cam surface 13a of stator and adjacent pair blade 12 mark off multiple pump chambers 17.
Stator 13 is the components of the cam surface 13a for the ring-type of generally elliptical shape of inner circumferential, and it is included with rotor 11
Rotation and inhalation area 13b, 13d of the volume expansion of pump chamber 17 and with rotor 11 rotation and pump chamber 17 volume contraction
Spray region 13c, 13e.
For each pump chamber 17, during rotor 11 rotates a circle, stator 13 inhalation area 13b from suction
Stream 81 is passed through ejection region 13c of the working oil of the suction in stator 13 by suction inlet suction working oil (not shown)
Ejiction opening 18 is ejected into ejection stream 82.Afterwards, inhalation area 13d in stator 13 passes through suction inlet (not from suction passage 81
Diagram) suction working oil, ejection region 13e of the working oil of the suction in stator 13 is ejected into into discharging jet by ejiction opening 18
Road 82.So, each pump chamber 17 is expanded, is shunk with the rotation of rotor 11, suction, spray during rotor 11 rotates a circle
Go out working oil twice.The revolution speed N of pump 1 together changes with the rotating speed of driving means.For pump 1, rise in revolution speed N
When, spray flow and increase in proportion to rotating speed.
As long as the fixed capacity type of the rotary-type form of pump 1, can also be just the pump of the form like that such as gear pump.
Flow control valve 2 includes：Sliding spool 21, it is sliding freely inserted into valve reception hole 25 as valve element；It is first-class
Body pressure chamber 23, its towards sliding spool 21 an end face arrange；Second fluid pressure chamber 24, its towards sliding spool 21 another
End face ground is arranged；And back-moving spring 22, it is housed in second fluid pressure chamber 24 as force application component with compressive state, is used
In exerting a force to sliding spool 21 to valve closing direction.
Sliding spool 21 includes First shoulder 21a and the second shoulders 21b slided along the inner peripheral surface of valve reception hole 25.
The first stopper section 21c is configured with combination with First shoulder 21a in first fluid pressure chamber 23, in sliding spool 21
In the case of moving to the direction of the volume for shrinking first fluid pressure chamber 23, the first stopper section 21c and valve reception hole 25
Bottom abuts and limits the movement more than predetermined extent of sliding spool 21.
It is connected with first fluid pressure chamber 23 from the first communication paths 83 for spraying the branch of stream 82, in second fluid pressure
It is connected with room 24 from the second communication paths 84 for spraying the branch of stream 82.Additionally, being connected with drain passage in flow control valve 2
85, the drain passage 85 and first fluid pressure chamber 23 are connected or blocked using First shoulder 21a.
Sliding spool 21 is by the work for being directed into the first fluid pressure chamber 23 and second fluid pressure chamber 24 being divided at two ends
The position stopping that the load that the pressure of work oil causes is balanced with the force of back-moving spring 22.
The load and back-moving spring 22 caused by the pressure of second fluid pressure chamber 24 force total load be more than by
In the case of the load that the pressure of first fluid pressure chamber 23 causes, back-moving spring 22 extends, and sliding spool 21 becomes the first stopper section
The state that 21c is abutted with the bottom of valve reception hole 25.
In this condition, the First shoulder 21a blocking first fluids pressure chamber 23 of sliding spool 21 and the company of drain passage 85
It is logical.Thus, the whole amount of the working oil for gushing out from pump 1 to fluid pressure equipment 50 is supplied.
In contrast, in the load caused by the pressure of first fluid pressure chamber 23 more than the pressure by second fluid pressure chamber 24
In the case of the load for causing and total load of the force of back-moving spring 22, sliding spool 21 overcome the force of back-moving spring 22 and
It is mobile.
In this condition, the First shoulder 21a of sliding spool 21 makes first fluid pressure chamber 23 connect with drain passage 85.Cause
And, a part for the working oil gushed out from pump 1 is flowed back by first fluid pressure chamber 23 and drain passage 85 to suction passage 81.
Flow control valve 2 also includes regulator 3, and the regulator 3 sprays stream 82 and second fluid pressure located at connection
Second communication paths 84 of room 24, for adjusting the pressure of second fluid pressure chamber 24.Regulator 3 includes logical located at the second connection
The throttling element 40 on road 84, the overflow connected from the branch of the second communication paths 84 and with fluid tank 4 in the downstream of throttling element 40 are led to
Road 86 and the overflow valve 30 located at overflow passage 86.
Overflow valve 30 includes the spring 31 exerted a force to valve closing direction, exerts a force to valve closing direction and can change overflow pressure Pr's
Proportional solenoid 32 and the first guiding path 33 for making the pressure of overflow passage 86 act on to valve opening position.
The pressure in the downstream of throttling element 40 is the pressure P2 of second fluid pressure chamber 24 by overflow passage 86 and first turns on
Road 33 acts on overflow valve 30 to valve opening position force.
Second fluid pressure chamber 24 pressure P2 more than by spring 31 force and proportional solenoid 32 force make a concerted effort
In the case of the overflow pressure Pr of decision, the working oil of second fluid pressure chamber 24 is passed through the second communication paths by the valve opening of overflow valve 30
84 to fluid tank 4 is discharged.And, when the pressure P2 of second fluid pressure chamber 24 is changed into equal with overflow pressure Pr, overflow valve 30 is closed
Valve.So, overflow valve 30 is adjusted so that the pressure P2 of second fluid pressure chamber 24 is equal with overflow pressure Pr.Proportional solenoid
32 and spring 31 force make a concerted effort to valve closing direction force can, or proportional solenoid 32 or spring 31 in appoint
One to valve opening position exerts a force.
Controller 60 is used to control the applying electric current I of the applying of comparative example solenoid 32.Additionally, turning to the front pump of controller 60
The signal of the pressure required by the revolution speed N of the pump 1 that fast detector 70 is detected and fluid pressure equipment 50.In addition, fluid pressure sets
The signal of the pressure required by standby 50 sees below.
Revolution speed N and second fluid in the case where controller 60 is previously stored with certain target flow for representing pump installation 100
The corresponding diagram (Fig. 2) of the relation between the pressure P2 of pressure chamber 24 and the pressure P2 and proportional solenoid of expression second fluid pressure chamber 24
Apply the corresponding diagram (Fig. 3) of the relation between electric current I.In addition, target flow refer to fluid pressure equipment 50 needed for, set in advance
Flow value, in fig. 2, the target flow is equivalent to the flow that the pump 1 in revolution speed Nm is sprayed.
Pump installation 100 controls, from the flow that stream 82 flows back to suction passage 81 is sprayed, to enter by using flow control valve 2
Row control, so that pressing the flow of the working oil of the supply of equipment 50 to become target flow to fluid from pump 1 by spraying stream 82.
Specifically, with reference to the corresponding diagram of Fig. 2 and Fig. 3, controller 60 adjusts the second of flow control valve 2 by controlling overflow valve 30
The pressure P2 of fluid pressure chamber 24, controls the flow flowed back to suction passage 81 from ejection stream 82.
Illustrate the corresponding diagram shown in Fig. 2.For pump 1, when revolution speed N rises, spray flow and be directly proportional to rotating speed
Ground increases.Thus, the corresponding diagram with reference to shown in Fig. 2, in the case where revolution speed N is more than the rotating speed Nm suitable with target flow,
In order to increase with the increase of revolution speed N from the return flow for spraying stream 82, controller 60 is reducing second fluid pressure
The mode of the setting pressure of the pressure P2 of room 24 is controlled.Additionally, in the case where revolution speed N is below rotating speed Nm, in order to
Do not make from pump 1 to be ejected into the working oil backflow for spraying stream 82 and be controlled to the pressure P2 of second fluid pressure chamber 24 constant.
Then, the corresponding diagram shown in Fig. 3 is illustrated.As shown in figure 3, the pressure P2 of second fluid pressure chamber 24 and overflow valve 30
The applying electric current I direct proportionalities of proportional solenoid 32.Specifically, in order that on the pressure P2 of second fluid pressure chamber 24
Rise, the applying electric current I for making proportional solenoid 32 rises.Thus, the overflow pressure Pr of overflow valve 30 rises, second fluid pressure chamber 24
Pressure P2 rises.In contrast, in order that the pressure P2 declines of second fluid pressure chamber 24, make the applying electric current of proportional solenoid 32
I declines.Thus, the overflow pressure Pr of overflow valve 30 declines, and the pressure P2 of second fluid pressure chamber 24 declines.
Then, the action of pump installation 100 is illustrated.
By using the power of the driving means such as electromotor (not shown), transfer tube 1 rotates, by suction passage 81 from
Fluid tank 4 sucks working oil, and working oil is pressurizeed and ejection stream 82 is ejected into.The working oil for spraying stream 82 is ejected into stream
Body pressure equipment 50 is supplied.
The revolution speed N of pump 1 together changes with the rotating speed of driving means.When revolution speed N rises, the ejection flow of pump 1 with
Rotating speed is increased in proportion to.
When pump 1 drives, working oil is supplied to first fluid pressure chamber 23 by the first communication paths 83 from stream 82 is sprayed.
Thus, with the pressure that sprays in stream 82 equal pressure is acted on first fluid pressure chamber 23.Additionally, passing through from stream 82 is sprayed
Second communication paths 84 to second fluid pressure chamber 24 supplies working oil.The pressure of second fluid pressure chamber 24 is illustrated, it is little in revolution speed N
In the case of rotating speed Nm, due to the ejection flow miss the mark flow of pump 1, therefore, the pressure of second fluid pressure chamber 24 is not
The overflow pressure Pr of overflow valve 30 can be risen to.Thus, working oil will not from the overflow of overflow valve 30, therefore, second fluid pressure chamber 24
Pressure P2 become equal with the pressure of first fluid pressure chamber 23.In contrast, in the situation that revolution speed N is more than rotating speed Nm
Under, because the ejection flow of pump 1 becomes flow more than target flow, therefore, in order that a part for the ejection flow of pump 1 is returned
Flow and utilize overflow valve 30 to control the pressure P2 of second fluid pressure chamber 24.Thus, the pressure P2 of second fluid pressure chamber 24 become with
The overflow pressure Pr of overflow valve 30 is equal.
Additionally, when pump 1 drives, from revolution speed detector 70 to the input speed N of controller 60.Controller 60 is with reference to Fig. 2
Shown corresponding diagram is come the pressure P2 of the corresponding second fluid pressure chamber 24 of the revolution speed N that selects be input into.
Hereinafter, illustrated in case of controlling pump installation 100 under middle pressure characteristic B of Fig. 2.In addition, middle pressure is special
Property B sees below.
It is that in the case that below rotating speed Nm is rotating speed Na, the ejection flow of pump 1 is not up to fluid pressure equipment 50 in revolution speed N
Required target flow.Therefore, as shown in the corresponding diagram of Fig. 2, selection pressure Pd of controller 60 is used as second fluid pressure chamber 24
Pressure P2, with the flow backflow for being sprayed pump 1.Then, controller 60 is selected and pressure Pd phases with reference to the corresponding diagram of Fig. 3
The applying electric current Id of the proportional solenoid 32 of corresponding overflow valve 30.So, controller 60 is by the ratio spiral shell to overflow valve 30
Spool 32 applies electric current Id, and the overflow pressure Pr of overflow valve 30 is set as into pressure Pd.Set in the overflow pressure Pr of overflow valve 30
When being set to pressure Pd, because overflow valve 30 is not opened before the pressure P2 of second fluid pressure chamber 24 becomes pressure Pd, therefore, the
The pressure of one fluid pressure chamber 23 and the pressure of second fluid pressure chamber 24 are equal.Thus, caused by the pressure of first fluid pressure chamber 23
The force of valve opening position and the force in the valve closing direction caused by the pressure of second fluid pressure chamber 24 offset, but due to sliding spool
21 are exerted a force in the presence of the force of back-moving spring 22 to valve closing direction, therefore, the sliding spool 21 of flow control valve 2 is not opened
Valve.Thus, the working oil that pump 1 is sprayed does not flow back.
When revolution speed N rises and becomes the rotating speed Nb more than rotating speed Nm, because the ejection flow of pump 1 presses equipment more than fluid
Flow needed for 50, therefore, produce residual flow.
At this moment, controller 60 with reference to corresponding diagram selection pressure Pb of Fig. 2 as the second fluid pressure corresponding with rotating speed Nb
The pressure P2 of room 24.Controller 60 is in order that the pressure P2 of second fluid pressure chamber 24 drops to pressure Pb, reference Fig. 3 from pressure Pd
Corresponding diagram and applying electric current I is reduced from the applying electric current Id of the proportional solenoid 32 of the overflow valve 30 corresponding with pressure Pd
To the applying electric current Ib of the proportional solenoid 32 of the overflow valve 30 corresponding with pressure Pb.Thus, the force of proportional solenoid 32
Decline, overflow pressure Pr declines.Overflow pressure Pr decline when, in order that the pressure P2 of second fluid pressure chamber 24 be changed into overflow pressure Pr and
Working oil is sprayed from second fluid pressure chamber 24, the pressure P2 of second fluid pressure chamber 24 drops to pressure Pb.So, with second fluid
The amount that the pressure P2 of pressure chamber 24 drops to pressure Pb from pressure Pd correspondingly, to the sliding spool 21 of flow control valve 2 to valve closing side
Decline to the force for applying.
Thus, rotating speed Nb is increased to by the rotating speed of pump 1 and sprays flow increase, but due to the guiding valve of flow control valve 2
The working oil (residual flow) of the valve opening of core 21 and ejection stream 82 is by first fluid pressure chamber 23 and drain passage 85 to suck stream
Road 81 is flowed back, therefore, the flow that the working oil of the supply of equipment 50 is pressed from pump 1 to fluid is maintained constant (target flow).
When revolution speed N further becomes and becomes rotating speed Nc greatly, further increase to the flow for spraying the ejection of stream 82 from pump 1
Plus.At this moment, as shown in Figures 2 and 3, controller 60 is in order that the pressure P2 of second fluid pressure chamber drops to and rotating speed from pressure Pb
Nc corresponding pressure Pe and make applying electric current I drop to applying electric current Ie from electric current Ib is applied.Thus, to flow control valve 2
The force applied to valve closing direction further diminishes.Thus, rotating speed Nc is increased to by the rotating speed of pump 1 and flow increase is sprayed,
But due to also increasing to the working oil that suction passage 81 flows back from ejection stream 82, therefore, press equipment 50 to supply from pump 1 to fluid
The flow of working oil be maintained constant (target flow).
In contrast, in revolution speed more than in the range of predetermined rotating speed Nm, such as revolution speed N is reduced to from rotating speed Nc and turns
During fast Nb, also reduce from pump 1 to the flow reduction that stream 82 sprays, residual flow is sprayed.At this moment, controller 60 with reference to Fig. 2 and
The corresponding diagram of Fig. 3, in order that the pressure P2 of second fluid pressure chamber 24 rises to and rotating speed from the pressure Pe corresponding with rotating speed Nc
Nb corresponding pressure Pb, the applying electric current I for making the proportional solenoid 32 of overflow valve 30 rises to applying electricity from electric current Ie is applied
Stream Ib, so that overflow pressure Pr rises.When overflow pressure Pr rises, the pressure P2 of second fluid pressure chamber 24 rises therewith.Thus,
The amount risen with the pressure P2 of second fluid pressure chamber 24 correspondingly, applies to the sliding spool 21 of flow control valve 2 to valve closing direction
Force rise.
Thus, rotating speed Nb is reduced to by the rotating speed of pump 1 and sprays flow and reduce, but due to by first fluid pressure chamber 23
Working oil to the backflow of suction passage 81 is also reduced, therefore, the flow that the working oil of the supply of equipment 50 is pressed from pump 1 to fluid is maintained
For constant (target flow).
So, even if the revolution speed N of pump 1 changes and the ejection changes in flow rate of pump 1, pump installation 100 also can be by fluid
The flow of the supply of pressure equipment 50 remains constant.Additionally, by the way that using overflow valve 30, simple structural adjustment pressure can be utilized
Power.
When being constant (target flow) by flow-control, for example, if the pressure required by fluid pressure equipment 50 rises,
The pressure for spraying stream 82 rises, and the pressure of first fluid pressure chamber 23 is also increased by the first communication paths 83.Thus, convection current
The sliding spool 21 of control valve 2 to the force that the direction of valve opening applies becomes big, and sliding spool 21 to valve opening position is moved.By guiding valve
The aperture of core 21 becomes big, is increased to the return flow that suction passage 81 flows back by first fluid pressure chamber 23 and drain passage 85,
Cause to spray the changes in flow rate of stream 82.Therefore, pump installation 100 correspondingly selects revolution speed N and second fluid pressure chamber with pressure
The characteristic of the relation between 24 pressure P2, even if so that pressure change also flow is remained it is constant.Hereinafter, specifically enter
Row explanation.
The signal of the pressure being input into needed for fluid pressure equipment 50 to controller 60.
In the signal of the pressure being input into controller 60 required by fluid pressure equipment 50, controller 60 is from prestoring
The pressure of the corresponding pressure required by pressing equipment 50 with fluid, revolution speed N and second fluid pressure chamber 24 is selected in the corresponding diagram of Fig. 2
The characteristic of the relation between power P2.
For example when being controlled with revolution speed Nb under middle pressure characteristic B, if the pressure rise required by fluid pressure equipment 50,
Then controller 60 selects high pressure characteristics A in Fig. 2.That is, the setting pressure of the pressure P2 of second fluid pressure chamber 24 is therefrom
The pressure Pb of pressure characteristic B is changed to the pressure Pa of high pressure characteristics A.Thus, to side from the sliding spool 21 of flow control valve 2 to valve closing
Become big to the force for applying.When fluid presses the pressure rise required by equipment 50, the pressure for spraying stream 82 rises, by the
The pressure of one fluid pressure chamber 23 rises, and the force of the valve opening position of sliding spool 21 becomes big, but the pressure P2 of second fluid pressure chamber 24
Rise cooperating therewithly, big is become to the force that the direction of valve closing applies to the sliding spool 21 of flow control valve 2.So, flow
It is constant that the aperture of the sliding spool 21 of control valve 2 is adjusted to return flow.Thus, it is possible to by pump 1 ejection stream 82 flow
Remain constant (target flow).
Additionally, when being controlled with revolution speed Nb under middle pressure characteristic B, if the pressure drop required by fluid pressure equipment 50
Low, then controller 60 selects the low pressure property C in Fig. 2.That is, the setting pressure of the pressure P2 of second fluid pressure chamber 24 from
The pressure Pb of middle pressure characteristic B is changed to the pressure Pc of low pressure property C.Thus, to the sliding spool 21 of flow control valve 2 to valve closing
The force that direction applies diminishes.When fluid presses the reduced pressure required by equipment 50, the pressure drop of stream 82 is sprayed, passed through
The pressure drop of first fluid pressure chamber 23, the force of the valve opening position of sliding spool 21 diminishes, but the pressure of second fluid pressure chamber 24
P2 declines cooperating therewithly, and sliding spool 21 is diminished to the force that the direction of valve closing applies.So, the cunning of flow control valve 2
It is constant that the aperture of valve element 21 is adjusted to return flow.Thus, it is possible to the flow of the ejection stream 82 of pump 1 be remained constant
(target flow).
So, even if the pressure change required by fluid pressure equipment 50, controller 60 correspondingly selects revolution speed N with pressure
And the characteristic of the relation between the pressure P2 of second fluid pressure chamber 24, the pressure based on the Characteristics Control second fluid pressure chamber 24
P2, thus, it is also possible to the flow of the ejection stream 82 of pump 1 is remained constant (target flow).
In addition, interim characteristic as high pressure characteristics A, middle pressure characteristic B and low pressure property C is illustrated in fig. 2,
But actually, characteristic variations are continuously made between high pressure characteristics A and low pressure property C.It is self-evident, it is also possible to make characteristic rank
The ground change of section property.In addition, middle pressure characteristic B shown in Fig. 2 merely illustrate it is general between high pressure characteristics A and low pressure property C
The characteristic of the property read.
In addition, in the above-described embodiment, it is configured to the pressure required by the input fluid pressure equipment 50 of controller 60
Signal.Replace, or, spray stream 82 in pressure detector is set, to controller 60 be input into the pressure detecting
The signal of device.When from pressure detector to 60 input signal of controller, controller 60 with reference to the corresponding diagram of Fig. 2 suitably select with
The pressure of the ejection stream 82 that pressure detector is detected is corresponding, between revolution speed N and the pressure P2 of second fluid pressure chamber 24
Relation characteristic.Thereby, it is possible to same with the situation of the signal of the pressure being input into controller 60 required by fluid pressure equipment 50
Sample ground control pump installation 100.
In addition it is also possible to be configured to：The mesh being stored with shown in multiple Fig. 2 for different target flows in controller 60
The corresponding diagram of mark flow, according to the instruction that equipment 50 is pressed from fluid the corresponding diagram corresponding with target flow is suitably selected.
In addition, in order to make the corresponding diagram for changing target flow, being by the location change for becoming the rotating speed Nm of the flex point of curve chart only
Become the position of the revolution speed of target flow.
Using the embodiment of the above, effect shown below is produced.
It was in the past to be provided with restriction in the ejection stream of connection pump and fluid pressure equipment, the pressure differential based on its upper and lower sides
Control flow control valve, but in the present embodiment, flow control valve 2 includes regulator 3, and the regulator 3 is located at connection
The second communication paths 84 of stream 82 and second fluid pressure chamber 24 are sprayed, for adjusting the pressure of second fluid pressure chamber 24, therefore,
Even if not arranging restriction in stream 82 is sprayed, it is also possible to by the flow of the working oil for pressing equipment 50 to supply from pump 1 to fluid
It is controlled to constant.Also, due to being not provided with restriction in stream 82 is sprayed, the pressure loss is not produced, therefore, it is possible to reduce use
In the moment of torsion of transfer tube 1.Even if additionally, the pressure change required by fluid pressure equipment 50, it is also possible to remain flow constant.
In addition, pump installation 100 according to fluid press equipment 50 required by pressure come enter to be about to from pump 1 to fluid press equipment 50
The flow-control of the working oil of supply is constant flow-control, if but fluid presses equipment 50 to need the pressure control for making pressure constant
System, then by prestoring the corresponding diagram shown in Fig. 4 in controller 60, can not be carried out flow-control just makes pressure permanent
Fixed Stress control.Hereinafter, specifically illustrate.
Fig. 4 is the corresponding diagram for representing the relation between the requirement pressure Pp of pump 1 and the pressure P2 of second fluid pressure chamber 24.
Equipment 50 is pressed to be input into the signal that fluid presses the requirement pressure Pp required by equipment 50 to controller 60 from fluid.To control
During the signal of the requirement pressure Pp required by the input fluid pressure equipment 50 of device processed 60, the control flow control valve 2 of controller 60, so that
Obtaining to fluid presses the pressure of the working oil of the supply of equipment 50 to become requirement pressure Pp.Specifically, controller 60 is with reference to depositing in advance
Corresponding diagram shown in Fig. 4 and Fig. 3 of storage, by controlling overflow valve 30 the second fluid pressure chamber 24 of flow control valve 2 is adjusted
Pressure P2, the force in the valve closing direction by controlling flow control valve 2, by the pressure of the working oil supplied to fluid pressure equipment 50
Control becomes required requirement pressure Pp.
Then, the Stress control of pump installation 100 is explained.
In the case where pump installation 100 carries out Stress control, flow control valve 2 is used as pressure-control valve function.
It is first-class when the pressure for spraying stream 82 rises and reaches more than the requirement pressure Pp required by fluid pressure equipment 50
The pressure of body pressure chamber 23 also rises, therefore, the force for making the direction of the valve opening of sliding spool 21 becomes big.Due to being controlled using overflow valve 30
The pressure P2 of second fluid pressure chamber 24 processed, therefore, sliding spool 21 overcomes the load caused by the pressure P2 of second fluid pressure chamber 24
Move with the force of back-moving spring 22.When sliding spool 21 is moved, first fluid pressure chamber 23 is connected with drain passage 85.By
This, the working oil for spraying stream 82 is flowed back by first fluid pressure chamber 23 and drain passage 85 to suction passage 81, sprays stream
82 pressure drop.
When the pressure drop for spraying stream 82 presses the requirement pressure Pp required by equipment 50 to fluid, by first fluid pressure
Load that the pressure of room 23 causes with caused by the pressure P2 of second fluid pressure chamber 24 on the direction for making the valve closing of sliding spool 21
The total counterweight balance of the force of load and back-moving spring 22, sliding spool 21 stops in the position of balance.Thereby, it is possible to ejection
It is the flow for requiring pressure Pp that the supply of stream 82 sprays pressure.So, even if spraying the pressure change of stream 82, by using flow
The control adjustment of valve 2 sprays the pressure of stream 82, it is also possible to supply the requirement pressure Pp required by fluid pressure equipment 50.
Additionally, there are the situation of the requirement pressure Pp changes required by fluid pressure equipment 50.For example, equipment is being pressed from fluid
50 are input into when will require that pressure Pp increases to the signal of pressure PH from pressure PM to controller 60, and controller 60 is with reference first to Fig. 4
Shown corresponding diagram selects the pressure Ph of the second fluid pressure chamber 24 corresponding with pressure PH.Then, the correspondence with reference to shown in Fig. 3
Figure, selecting the pressure P2 of second fluid pressure chamber 24 becomes proportional solenoid applying electric current Ih as pressure Ph.By will so
The applying electric current Ih for selecting puts on the proportional solenoid 32 of overflow valve 30, overflow pressure Pr is increased.
In contrast, being for example input into controller 60 and will require that pressure Pp is reduced to from pressure PM from fluid pressure equipment 50
During the signal of pressure PL, controller 60 selects the second fluid pressure corresponding with pressure PL with reference first to the corresponding diagram shown in Fig. 4
The pressure Pl of room 24.Then, with reference to the corresponding diagram shown in Fig. 3, select second fluid pressure chamber 24 pressure P2 become pressure Pl this
The proportional solenoid of sample applies electric current Il.By the ratio helical that the applying so selected electric current Il is put on overflow valve 30
Pipe 32, declines overflow pressure Pr.
So, even if the requirement pressure Pp changes required by fluid pressure equipment 50, by correspondingly controlling with pressure Pp is required
The applying electric current I of the proportional solenoid 32 of overflow valve processed 30 and control overflow pressure Pr, it is also possible to control the valve closing of flow control valve 2
The force in direction, the Stress control for spraying stream 82 can be pressed the requirement pressure Pp required by equipment 50 for fluid.
Hereinafter, structure, effect and the effect of explanation embodiments of the present invention are concluded.
Pump installation 100 is characterised by that the pump installation 100 includes：Pump 1, it is used to suck working oil, working oil is pressurizeed
And spray to stream 82 is sprayed；And flow control valve 2, it is used to make a part for the working oil gushed out from pump 1 to suction
Side (suction passage 81) is flowed back, and flow control valve 2 includes：Valve element (sliding spool 21)；First fluid pressure chamber 23, it is towards valve element
One end face ground of (sliding spool 21) is arranged, and is connected with stream 82 is sprayed；Second fluid pressure chamber 24, it is towards valve element (sliding spool
21) another end face ground is arranged, and is connected with stream 82 is sprayed；Force application component (back-moving spring 22), it is received with compressive state and is filled
In second fluid pressure chamber 24, for exerting a force to valve closing direction to valve element (sliding spool 21)；And regulator 3, its company of being located at
In logical the second communication paths 84 for spraying stream 82 and second fluid pressure chamber 24, for adjusting the pressure of second fluid pressure chamber 24
P2。
Using such structure, the pressure of the second fluid pressure chamber 24 of flow control valve 2 is adjusted using regulator 3
P2.The pressure that first fluid pressure chamber 23 and being imported with according to the pressure for spraying stream 82 is imported with have adjusted by regulator 3
The pressure differential of the second fluid pressure chamber 24 of Pr carrys out open and close controlling flow control valve 2.Thus, even if not arranging in stream 82 is sprayed
Restriction, it is also possible to which the flow-control by the ejection stream of pump 1 is constant.Further, since without throttling in stream 82 is sprayed
Portion, therefore, it is possible to reduce for the moment of torsion of transfer tube 1.
Pump installation 100 is further characterized in that regulator 3 includes：Throttling element 40, it is located at the second communication paths 84；With
And overflow valve 30, it is located in the downstream of throttling element 40 from the overflow passage 86 of the branch of the second communication paths 84, can change
Pr is pressed in overflow.
Pump installation 100 is further characterized in that overflow valve 30 includes that the proportional solenoid 32 that Pr is pressed in overflow can be changed.
Using these structures, using overflow valve 30 the pressure P2 of second fluid pressure chamber 24 is adjusted.Thus, by adopting overflow
Valve 30, can utilize simple structural adjustment pressure.
Pump installation 100 is further characterized in that overflow valve 30 adjusts overflow pressure Pr according to the revolution speed N of pump 1.
Using such structure, even if the revolution speed N changes of pump 1, it is also possible to by adjusting overflow pressure according to revolution speed N
Pr and by spray stream 82 flow remain it is constant.
Pump installation 100 is further characterized in that, pressure of the overflow valve 30 according to required by fluid presses equipment 50 is changing overflow
Pressure Pr.
Using such structure, even if the pressure change required by fluid pressure equipment 50, it is also possible to press equipment according to fluid
Pressure required by 50 come control overflow pressure Pr, and by spray stream 82 flow remain it is constant.
Pump installation 100 is by including flow control valve 2 and connecting the second of ejection stream 82 and second fluid pressure chamber 24
The regulator 3 of the pressure of second fluid pressure chamber 24 is adjusted in communication paths 84, even if the pressure required by fluid pressure equipment 50
Change, it is also possible to remain the flow for spraying stream constant.
Embodiments of the present invention are this concludes the description of, but above-mentioned embodiment show only the application examples of the present invention
A part, is not the meaning of the concrete structure that protection scope of the present invention is defined to above-mentioned embodiment.
In the above-described embodiment, change the pressure P2 of second fluid pressure chamber according to the revolution speed N of pump 1.Replace,
Can also be provided for detecting the effusion meter of the flow that pump 1 is sprayed, second fluid pressure chamber is made according to the flow for detecting
Pressure P2 change.
In the above-described embodiment, regulator 3 includes overflow valve 30 and throttling element 40.Replace, or
The structure of the control valve of the proportional solenoid type of threeway shape is set in the second communication paths 84, and the control valve is used to control discharging jet
Road 82 connects with second fluid pressure chamber 24, and controls connecting for second fluid pressure chamber 24 and fluid tank 4.
This case is excellent based on 2014-No. 175449 opinions of Japanese Patent Application to Japanese Patent Office application on the 29th of August in 2014
First weigh, by the entire disclosure of which by referring to being programmed in this specification.
Claims (5)
1. a kind of pump installation, it is used for fluid pressure equipment supply working fluid, wherein,
The pump installation includes：
Pump, it is used to suck working fluid, and working fluid pressurization is sprayed to stream is sprayed；And
Flow control valve, it is used to make a part for the working fluid sprayed from the pump to suction side reflux,
The flow control valve includes：
Valve element；
First fluid pressure chamber, its towards the valve element an end face arrange, with the ejection fluid communication；
Second fluid pressure chamber, its towards the valve element another end face arrange, with the ejection fluid communication；
Force application component, it is housed in the second fluid pressure chamber with compressive state, for applying to valve closing direction to the valve element
Power；And
Regulator, it is located at the connection communication paths for spraying stream and the second fluid pressure chamber, described for adjusting
The pressure of second fluid pressure chamber.
2. pump installation according to claim 1, wherein,
The regulator includes：
Throttling element, it is located at the communication paths；
Overflow valve, it is located in the downstream of the throttling element from the overflow passage of the communication paths branch, can change excessive
Stream pressure.
3. pump installation according to claim 2, wherein,
The overflow valve includes that the proportional solenoid of the overflow pressure can be changed.
4. pump installation according to claim 2, wherein,
The overflow valve changes the overflow pressure according to the rotating speed of the pump.
5. pump installation according to claim 2, wherein,
Pressure of the overflow valve according to required by the fluid pressure equipment is changing the overflow pressure.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2014175449A JP6393560B2 (en) | 2014-08-29 | 2014-08-29 | Pump device |
| JP2014-175449 | 2014-08-29 | ||
| PCT/JP2015/073709 WO2016031767A1 (en) | 2014-08-29 | 2015-08-24 | Pump device |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN106662103A true CN106662103A (en) | 2017-05-10 |
Family
ID=55399657
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201580043553.8A Pending CN106662103A (en) | 2014-08-29 | 2015-08-24 | Pump device |
Country Status (5)
| Country | Link |
|---|---|
| US (1) | US20170227007A1 (en) |
| JP (1) | JP6393560B2 (en) |
| CN (1) | CN106662103A (en) |
| DE (1) | DE112015003982T5 (en) |
| WO (1) | WO2016031767A1 (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108825491A (en) * | 2018-06-26 | 2018-11-16 | 闫羽 | A method of saving vehicle fuel |
| CN108825494A (en) * | 2018-06-26 | 2018-11-16 | 闫羽 | A kind of petrochemical industry impeller pump |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP6885812B2 (en) * | 2017-07-12 | 2021-06-16 | 株式会社山田製作所 | Flood control device and flood control method |
| JP6933132B2 (en) | 2017-12-27 | 2021-09-08 | 株式会社ジェイテクト | Pump device |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4597718A (en) * | 1984-06-06 | 1986-07-01 | Nippon Soken, Inc. | Hydraulic fluid supply system with variable pump-displacement arrangement |
| JPH0988533A (en) * | 1995-09-26 | 1997-03-31 | Tokyo Buhin Kogyo Kk | Engine lubricant oil feeder |
| US6012907A (en) * | 1996-12-09 | 2000-01-11 | Luk Fahrzeug-Hydraulik Gmbh & Co. Kg | Flow-regulating arrangement for a hydraulic transporting device |
| US6387000B1 (en) * | 1999-04-30 | 2002-05-14 | Hydraulik-Ring Gmbh | Pressure medium supply arrangement for a continuous variable transmission |
| US20060222519A1 (en) * | 2004-12-22 | 2006-10-05 | Tomoyuki Fujita | Pump device |
| JP2009293416A (en) * | 2008-06-03 | 2009-12-17 | Hitachi Automotive Systems Ltd | Valve device |
Family Cites Families (3)
| 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 |
| JP4796026B2 (en) * | 2007-02-13 | 2011-10-19 | 株式会社山田製作所 | Pressure control device in oil pump |
| JP2014152721A (en) * | 2013-02-12 | 2014-08-25 | Hitachi Automotive Systems Steering Ltd | Variable displacement pump |
-
2014
- 2014-08-29 JP JP2014175449A patent/JP6393560B2/en active Active
-
2015
- 2015-08-24 DE DE112015003982.1T patent/DE112015003982T5/en not_active Withdrawn
- 2015-08-24 WO PCT/JP2015/073709 patent/WO2016031767A1/en active Application Filing
- 2015-08-24 US US15/502,938 patent/US20170227007A1/en not_active Abandoned
- 2015-08-24 CN CN201580043553.8A patent/CN106662103A/en active Pending
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4597718A (en) * | 1984-06-06 | 1986-07-01 | Nippon Soken, Inc. | Hydraulic fluid supply system with variable pump-displacement arrangement |
| JPH0988533A (en) * | 1995-09-26 | 1997-03-31 | Tokyo Buhin Kogyo Kk | Engine lubricant oil feeder |
| US6012907A (en) * | 1996-12-09 | 2000-01-11 | Luk Fahrzeug-Hydraulik Gmbh & Co. Kg | Flow-regulating arrangement for a hydraulic transporting device |
| US6387000B1 (en) * | 1999-04-30 | 2002-05-14 | Hydraulik-Ring Gmbh | Pressure medium supply arrangement for a continuous variable transmission |
| US20060222519A1 (en) * | 2004-12-22 | 2006-10-05 | Tomoyuki Fujita | Pump device |
| JP2009293416A (en) * | 2008-06-03 | 2009-12-17 | Hitachi Automotive Systems Ltd | Valve device |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108825491A (en) * | 2018-06-26 | 2018-11-16 | 闫羽 | A method of saving vehicle fuel |
| CN108825494A (en) * | 2018-06-26 | 2018-11-16 | 闫羽 | A kind of petrochemical industry impeller pump |
| CN108825494B (en) * | 2018-06-26 | 2019-12-06 | 海南葆润石油化工有限公司 | Rotor pump for petrochemical |
| CN108825491B (en) * | 2018-06-26 | 2019-12-06 | 苏州理合文科技有限公司 | Method for saving automobile fuel |
Also Published As
| Publication number | Publication date |
|---|---|
| DE112015003982T5 (en) | 2017-06-08 |
| WO2016031767A1 (en) | 2016-03-03 |
| US20170227007A1 (en) | 2017-08-10 |
| JP2016050505A (en) | 2016-04-11 |
| JP6393560B2 (en) | 2018-09-19 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN106662103A (en) | Pump device | |
| EP2063087B1 (en) | Fuel staging system | |
| EP2668379B1 (en) | Oil pump with selectable outlet pressure | |
| CN102459921B (en) | Two position three way valve | |
| CN103109095A (en) | Hydraulic valve with pressure limiter | |
| JP5452993B2 (en) | Electromagnetic proportional directional flow control valve with pressure compensation | |
| CN104159807A (en) | Hydraulic steering device | |
| EP2541023A2 (en) | Ecology valve for draining a manifold of a gas turbine engine, fuel system and method for draining fuel | |
| CN102459920B (en) | Hydraulic system | |
| US20150107699A1 (en) | Valve for valve assembly | |
| WO2012173815A3 (en) | Hydrostatic circuits with variable charge and variable flushing systems | |
| CN106103999B (en) | Pump installation | |
| ITUB20159571A1 (en) | HYDRAULIC VALVE SYSTEM WITH MORE WORKING SECTIONS WITH PUMP CONTROL SYSTEM WITH BY-PASS LINE | |
| CN105351188B (en) | A kind of two grades of variable displacement vane pump control systems of combination valve type | |
| CN205533479U (en) | Defeated material actuating system and paver | |
| CN102803747A (en) | Valve device | |
| CN105351028B (en) | A kind of one-level variable displacement vane pump | |
| CN107636309A (en) | Pump installation | |
| CN104564875A (en) | Valve assembly | |
| CN104141765B (en) | A kind of converter coupling control valve | |
| CN102434517A (en) | Speed adjusting valve | |
| JP6265008B2 (en) | Triple gear pump and fluid supply device | |
| CN102400970B (en) | Overflow throttling valve | |
| JP5869391B2 (en) | Flow control valve | |
| KR20180085936A (en) | Hydraulic pressure control device for a variable oil pump |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| WD01 | Invention patent application deemed withdrawn after publication | ||
| WD01 | Invention patent application deemed withdrawn after publication |
Application publication date: 20170510 |