CN107002672A - Variable displacement vane pump - Google Patents
Variable displacement vane pump Download PDFInfo
- Publication number
- CN107002672A CN107002672A CN201580061546.0A CN201580061546A CN107002672A CN 107002672 A CN107002672 A CN 107002672A CN 201580061546 A CN201580061546 A CN 201580061546A CN 107002672 A CN107002672 A CN 107002672A
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- CN
- China
- Prior art keywords
- stator
- pressure chamber
- chamber
- rotor
- pump
- 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
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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
- F04C14/18—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
- 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
- F04C2/3441—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 one line or continuous surface substantially parallel to the axis of rotation
- F04C2/3442—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 one line or continuous surface substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the working space, being surfaces of revolution
-
- 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
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
Variable displacement vane pump (100) includes：Throttle part (37), it is to the flowing application resistance for the working fluid discharged from pump chamber (11)；Control valve (27), its working fluid that will be discharged with the rising of the front and rear pressure difference of throttle part (37) from pump chamber (11) imports the 1st fluid pressure chamber (16), and discharges the working fluid of the 1st fluid pressure chamber (16) with the decline of front and rear pressure difference；Suction passage (22), it is used to guide the working fluid sucked to pump chamber (11), and is connected all the time with the 2nd fluid pressure chamber (17)；And guiding path (36), it connects control valve (27) and the 2nd fluid pressure chamber (17), and the working fluid that control valve (27) is expelled to from the 1st fluid pressure chamber (16) is guided to the 2nd fluid pressure chamber (17).
Description
Technical field
The present invention relates to a kind of variable displacement vane pump as fluid pressure supply source.
Background technology
Recorded in Japanese JP2013-194692A it is a kind of can by make stator relative to rotor offset change
So that the variable displacement vane pump of the discharge rate change of working fluid.
In order that stator is moved, the variable displacement vane pump includes：1st fluid pressure chamber and the 2nd fluid pressure chamber, it is formed
In the outer circumferential side of stator；Metering orifice, it is located at drain passageway；Control valve, it is slided with the front and rear pressure difference according to metering orifice
The movement of guiding valve accordingly imports control pressure to the 1st fluid pressure chamber；And cam spring, it is to stator all the time from the 2nd fluid
Pressure chamber exerts a force towards the 1st fluid pressure chamber side.Stator can make offset turn into maximum most to the movement of the 1st fluid pressure chamber side
Moved between large eccentricity position and the minimum minimum eccentric position of offset.
The content of the invention
In above-mentioned conventional technology, control pressure is imported from control valve to the 1st fluid pressure chamber, in contrast, to the 2nd fluid
Pressure chamber imports suction pressure all the time.Thus, stator is being directed into the 1st fluid pressure in the case of the direction movement reduced to offset
Moved in the presence of the control pressure of room, but in the case of the direction movement increased to offset, stator is in cam spring
Active force in the presence of move.Therefore, in the case of the direction movement for making stator increase to offset, the shifting of stator
Move and postpone and there may be servo-actuated delayed.
The present invention be in view of such technical task and make, its object is to provide a kind of to prevent stator
Servo-actuated delayed variable displacement vane pump.
Using one embodiment of the present invention there is provided a kind of variable displacement vane pump, wherein, the capacity-variable type blade
Pump includes：Rotor, it is linked to drive shaft；Multiple blades, it is located at rotor, and is diametrically moved back and forth certainly relative to rotor
Such as；Stator, the top ends of blade are slided with the rotation for the rotor for being configured at the stator interior with the cam surface of the inner circumferential of stator
Dynamic contact, and the stator can be relative to rotor eccentricity；Pump chamber, it divides formation between rotor and stator, and utilizes many
Individual blade is separated；1st fluid pressure chamber and the 2nd fluid pressure chamber, it is divided to be formed in the receiving space of the outer circumferential side of stator；
Force application component, it exerts a force to the direction that stator increases to offset all the time；Throttle part, it is to the working fluid discharged from pump chamber
Flowing apply resistance；Control valve, its working fluid that will be discharged with the rising of the front and rear pressure difference of throttle part from pump chamber
The 1st fluid pressure chamber is directed into so that the offset of stator reduces, and with front and rear pressure difference decline and by the 1st fluid pressure chamber
Working fluid discharge so that stator offset increase；Suction passage, it is used to guide the working fluid sucked to pump chamber,
And connected all the time with the 2nd fluid pressure chamber；And guiding path, it connects control valve and the 2nd fluid pressure chamber, will be from the 1st fluid
The working fluid that pressure chamber is expelled to control valve is guided to the 2nd fluid pressure chamber.
Brief description of the drawings
Fig. 1 is the section vertical with drive shaft for the variable displacement vane pump for representing the 1st embodiment of the present invention
Sectional view.
Fig. 2 is the section parallel with drive shaft for the variable displacement vane pump for representing the 1st embodiment of the present invention
Sectional view.
Fig. 3 is the hydraulic circuit diagram of the variable displacement vane pump of the 1st embodiment of the present invention.
Fig. 4 be the present invention the 1st embodiment variable displacement vane pump hydraulic circuit diagram, represent stator relative to
The offset of rotor is maximum state.
Fig. 5 be the present invention the 1st embodiment variable displacement vane pump hydraulic circuit diagram, represent stator relative to
The offset of rotor is middle state.
Fig. 6 be the present invention the 1st embodiment variable displacement vane pump hydraulic circuit diagram, represent stator relative to
The offset of rotor is minimum state.
Fig. 7 is the section vertical with drive shaft for the variable displacement vane pump for representing the 2nd embodiment of the present invention
Sectional view.
Fig. 8 is the section parallel with drive shaft for the variable displacement vane pump for representing the 2nd embodiment of the present invention
Sectional view.
Embodiment
Hereinafter, with reference to the accompanying drawings of embodiments of the present invention.
1st embodiment
1~Fig. 3 of reference picture illustrates the variable displacement vane pump 100 of the 1st embodiment of the present invention.
(hreinafter referred to as " the vane pump 100 " of variable displacement vane pump 100.) be used as be equipped on vehicle hydraulic test,
Hydraulic pressure supply source such as power steering gear, buncher.
As shown in figure 1, in vane pump 100, the power of driving source (not shown) being transmitted to drive shaft 1, makes to be linked to drive
The rotor 2 of moving axis 1 rotates.In Fig. 1 and Fig. 3, rotor 2 rotates counterclockwise as shown by the arrows.
Vane pump 100 includes：Multiple blades 3, it is located in the way of diametrically being moved back and forth freely relative to rotor 2
Rotor 2；And stator 4, the top ends of blade 3 can with the rotation for the rotor 2 for being configured inside with the inner circumferential of stator 4
Cam surface 4a sliding contacts, and the stator 4 can be eccentric relative to the center of rotor 2.
As shown in Fig. 2 drive shaft 1 is supported on the pump housing 6 by bushing 5 in the way of rotating freely.Work is formed with the pump housing 6
The pump of recess to accommodate stator 4 accommodates recess 6a.Being provided with the end of the pump housing 6 is used to prevent lubricating oil from the outer of drive shaft 1
The seal 7 leaked between week and the inner circumferential of bushing 5.
The bottom surface 6b for accommodating recess 6a in pump is configured with the side plate 8 abutted against with a sidepiece of rotor 2 and stator 4.Pump holds
Receiving recess 6a opening portion utilizes the pump cover 9 abutted against with the other side of rotor 2 and stator 4 to seal.Pump cover 9 is by bolt 10
(Fig. 1) is anchored on the pump housing 6.
So, pump cover 9 and side plate 8 are configured with the state for clipping the two sides of rotor 2 and stator 4.Thus, rotor 2 with
The pump chamber 11 being separated using each blade 3 is marked off between stator 4.
As shown in figures 1 and 3, stator 4 is the component of ring-type, including：Inhalation area, in the inhalation area, with turn
Son 2 rotation and make the volume enlargement using the pump chamber 11 being separated between each blade 3；And discharging area, in the discharge
In region, the smaller volume using the pump chamber 11 being separated between each blade 3 is made with the rotation of rotor.Pump chamber 11 is being inhaled
Enter region suction as the working oil of working fluid, working oil is discharged in discharging area.In Fig. 1, the top of stator 4 is suction
Region, lower section is discharging area.
The inner peripheral surface for accommodating recess 6a in pump is embedded with the engagement ring 12 of ring-type in the way of surrounding stator 4.With rotor 2 and
In the same manner, the two sides of engagement ring 12 are clipped stator 4 by pump cover 9 and side plate 8.
The support plate 13 extended parallel to drive shaft 1 is supported with the inner peripheral surface of engagement ring 12.Supported in support plate 13
There is stator 4, stator 4 is swung in the inside of engagement ring 12 with support plate 13 for fulcrum.
With the axisymmetric position of support plate 13 it is formed with what is extended parallel to drive shaft 1 in the inner peripheral surface of engagement ring 12
Groove 12a.The outer peripheral face being provided with groove 12a with have compressed the state of elastic component 15 when stator 4 is swung with stator 4 is slided
The containment member 14 of contact.
In this way, the receiving space in the periphery of stator 4 is between inner peripheral surface of the outer peripheral face of stator 4 with engaging ring 12, profit
Being divided with support plate 13 and containment member 14 has the 1st hydraulic pressure chamber 16 as the 1st fluid pressure chamber and the as the 2nd fluid pressure chamber
2 hydraulic pressure chambers 17.
As shown in figure 1, being provided with the cam bullet as force application component on the outer peripheral face by the side of the 2nd hydraulic pressure chamber 17 of stator 4
Spring 18.Cam spring 18 is installed on and the spring connector 19 for being arranged at the pump housing 6 is screwed from side, and through being formed from engagement
The through hole 12b of ring 12 exerts a force to the side of the 1st hydraulic pressure chamber 16 all the time to stator 4.That is, stator 4 by cam spring 18 all the time to bias
The direction force of amount increase.
Stator 4 is with the pressure differential between the working oil of the 1st hydraulic pressure chamber 16 and the working oil of the 2nd hydraulic pressure chamber 17, cam spring
18 active force, the mode of the internal pressure balance of stator 4 are with support plate 13 for branch spot wobble.By stator 4 with support plate 13 for branch
Spot wobble, stator 4 changes relative to the offset of rotor 2.When the offset change of stator 4, the pump that rotor 2 often rotates a circle
Displacement variation.
When the pressure of the 1st hydraulic pressure chamber 16 rises, stator 4 reduces relative to the offset of rotor 2.In this case, rotor 2
The pumpage often rotated a circle reduces.In contrast, when the pressure of the 1st hydraulic pressure chamber 16 declines, stator 4 is relative to rotor 2
Offset increases.In this case, the pumpage increase that rotor 2 often rotates a circle.So, the pumpage of vane pump 100 is according to fixed
Son 4 changes relative to the offset of rotor 2.
The inhalation area with pump chamber 11 is formed with pump cover 9 accordingly in the suction inlet 20 of arc-shaped opening.In addition,
The discharging area with pump chamber 11 is formed with side plate 8 accordingly in the outlet 21 of arc-shaped opening.
As shown in Fig. 2 suction inlet 20 is connected with being formed at the suction passage 22 of pump cover 9 and formed, by suction passage 22
Working oil is guided to the inhalation area of pump chamber 11.Outlet 21 is connected with being formed at the hyperbaric chamber 23 of the pump housing 6 and formed, will be from pump
The working oil of the discharging area discharge of room 11 is guided to hyperbaric chamber 23.
Hyperbaric chamber 23, which is enclosed in pump by using side plate 8 and accommodates recess 6a bottom surface 6b, to be open the groove portion 6c to be formed and divides
Formed.The working oil in hyperbaric chamber 23 is directed to vane pump 100 by being formed at the drain passageway 24 (reference picture 3) of the pump housing 6
Outside hydraulic test.
At the pump housing 6, the position shape corresponding with the inhalation area of pump chamber 11 in the bottom surface 6b that pump accommodates recess 6a
Into the low-pressure chamber 25 having as the 1st guiding path.Low-pressure chamber 25 is enclosed in the inhalation area phase with pump chamber 11 by using side plate 8
The groove portion 6d of corresponding position opening formation and divide to be formed.Low-pressure chamber 25 is formed as parallel with drive shaft 1 linear, and most
In boundary between portion and bushing 5 and seal 7 connect.Low-pressure chamber 25 is constantly coupled to the 2nd hydraulic pressure chamber 17, for reclaiming leakage
To the working oil between the inner circumferential of the periphery of drive shaft 1 and bushing 5 and it is set to be back to the pump chamber of inhalation area 11.
As depicted in figs. 1 and 2, at the pump housing 6, above it is formed with valve in the direction orthogonal with the axis direction of drive shaft 1 and holds
Receive hole 26.The control of the useful pressure in the working oil for controlling the 1st hydraulic pressure chamber 16 and the 2nd hydraulic pressure chamber 17 is accommodated in valve receiving hole 26
Valve 27.Valve receiving hole 26 is sealed using connector 28.
Control valve 27 includes：Guiding valve 29, it is inserted in valve receiving hole 26 in the way of sliding freely；1st pilot chamber 30, its
Towards one end of guiding valve 29；2nd pilot chamber 31, its other end towards guiding valve 29；And back-moving spring 32, it is accommodated in the 2nd
In pilot chamber 31, guiding valve 29 is exerted a force to the direction for the volume for expanding the 2nd pilot chamber 31.
Guiding valve 29 includes：1st back-up ring portion 29a and the 2nd back-up ring portion 29b, its inner peripheral surface along valve receiving hole 26 is slided；Ring-type
Groove 29c, it is formed between the 1st back-up ring portion 29a and the 2nd back-up ring portion 29b；1st bar portion 29d, it is tied with the 1st back-up ring portion 29a phases
Close, and extend in the 1st pilot chamber 30；And the 2nd bar portion 29e, it is combined with the 2nd back-up ring portion 29b, and in the 2nd pilot chamber
Extend in 31.
1st bar portion 29d guiding valve 29 to reduce the 1st pilot chamber 30 volume direction movement in the case of with the phase of connector 28
Abut.2nd bar portion 29e guiding valve 29 to reduce the 2nd pilot chamber 31 volume direction movement in the case of and valve receiving hole 26
Abutted against with the end face of the place side opposite side of connector 28.Back-moving spring 32 is accommodated in the way of surrounding the 2nd bar portion 29e
In 2 pilot chambers 31.
As shown in figure 3, control valve 27 is connected with：1st path 35 and the 2nd path 36 as guiding path, its respectively with
1st hydraulic pressure chamber 16 is connected with the 2nd hydraulic pressure chamber 17；1st impulse passageways 38, its using it is being discharged from hyperbaric chamber 23, positioned at being used as throttling
The working oil of the upstream of the thin-wall hole 37 of part is guided to the 1st pilot chamber 30；And the 2nd impulse passageways 39, it will be from hyperbaric chamber
23 discharges, downstream positioned at thin-wall hole 37 working oil is guided to the 2nd pilot chamber 31.2nd hydraulic pressure chamber 17 is connected with and sucked
The draining path 40 that path 22 is connected all the time.
1st path 35 and the 2nd path 36 are formed as being open to valve receiving hole 26, and insertion engagement ring 12 and respectively to the
1 hydraulic pressure chamber 16 and the 2nd hydraulic pressure chamber 17 are open.
Guiding valve 29 to by between the 1st pilot chamber 30 of both ends of the surface pair and the 2nd pilot chamber 31 pressure differential produce thrust
Slided with the position of the force balance of back-moving spring 32.1st path 35 utilizes the 1st back-up ring portion 29a according to the position of guiding valve 29
Open or close, so as to supply or discharge the working oil of the 1st hydraulic pressure chamber 16.2nd path 36 no matter how begin by the position of guiding valve 29
It is open eventually to endless groove 29c.
What the pressure differential being more than in the active force of back-moving spring 32 between the 1st pilot chamber 30 and the 2nd pilot chamber 31 was produced
In the case of thrust, back-moving spring 32 turns into the state extended.In this condition, as shown in figures 1 and 3, the He of the 1st path 35
2nd path 36 is open to endless groove 29c.Thus, the connection between the 1st hydraulic pressure chamber 16 of cut-out and the 1st pilot chamber 30.
Here, the 1st hydraulic pressure chamber 16, which turns into, passes through the 1st path 35, endless groove 29c, the 2nd path 36 and the 2nd hydraulic pressure chamber 17
And the state connected with draining path 40.Stator 4 is applied by the direction increased to offset all the time in the presence of cam spring 18
Power, therefore stator 4 turns into maximum relative to the offset of rotor 2.
Bullet is resetted in contrast, being more than in the thrust that the pressure differential between the 1st pilot chamber 30 and the 2nd pilot chamber 31 is produced
In the case of the active force of spring 32, guiding valve 29 overcomes the active force of back-moving spring 32 and moved.In this case, the 1st path
35 turn into open mode and are connected with the 1st pilot chamber 30, and are connected by the 1st pilot chamber 30 with the 1st impulse passageways 38.In addition,
2nd path 36 always remains as open mode and connected with endless groove 29c.Thus, the 1st hydraulic pressure chamber 16 is connected with hyperbaric chamber 23.
Rise because the 2nd hydraulic pressure chamber 17 is connected via draining path 40 with suction passage 22, therefore with the pressure of the 1st hydraulic pressure chamber 16,
The offset of stator 4 reduces.That is, when the pressure of the 1st hydraulic pressure chamber 16 rises, it is fixed that the power that stator 4 is born from the 1st hydraulic pressure chamber 16 exceedes
Son 4 from power that cam spring 18 is born and the power sum born due to the internal pressure of stator 4 when, stator 4 is to relative to rotor 2
The direction movement that offset reduces.
As described above, the guiding valve 29 of control valve 27 is produced in the pressure differential between the 1st pilot chamber 30 and the 2nd pilot chamber 31
Thrust be more than back-moving spring 32 active force in the case of, compression reseting spring 32 is simultaneously moved.
It has been directed respectively into be located in the 1st pilot chamber 30 and the 2nd pilot chamber 31 and has been installed on drain passageway 24 and to working oil
Flowing apply resistance the thin-wall hole 37 as throttle part upstream and downstream working oil.That is, hyperbaric chamber 23
Working oil be directly directed to the 1st pilot chamber 30 by the 1st impulse passageways 38 not via thin-wall hole 37, and via thin-walled
Hole 37 is directed to the 2nd pilot chamber 31.Thus, guiding valve 29 is moved according to the front and rear pressure difference of thin-wall hole 37.
Then, 4~Fig. 6 of reference picture illustrates the action of vane pump 100.Fig. 4~Fig. 6 is the hydraulic circuit diagram of vane pump 100,
It is maximum, middle, minimum state relative to the offset of rotor 2 to represent stator 4 respectively.
When to drive shaft 1 transmit driving source power and rotor 2 rotation when, with the rotation of rotor 2 between each blade 3
The pump chamber 11 of expansion sucks working oil by suction inlet 20 from suction passage 22.In addition, the pump chamber 11 shunk between each blade 3 leads to
Cross outlet 21 and discharge working oil to hyperbaric chamber 23.The working oil for being discharged to hyperbaric chamber 23 is supplied to liquid by drain passageway 24
Press equipment.
When working oil in drain passageway 24 by when, the generation pressure before and after the thin-wall hole 37 of drain passageway 24 is installed on
Power is poor, and the pressure of the upstream and downstream of thin-wall hole 37 is respectively guided to the 1st pilot chamber 30 and the 2nd pilot chamber 31.Control valve 27
Guiding valve 29 between the 1st pilot chamber 30 and the 2nd pilot chamber 31 pressure differential produce thrust and back-moving spring 32 effect
Slide the position of dynamic balance.
Rotor 2 rotating speed for below desired speed when pumping up dynamic, because the rotating speed of rotor 2 is relatively low and pump delivery flow
It is less, therefore the front and rear pressure difference of thin-wall hole 37 is smaller, what the pressure differential between the 1st pilot chamber 30 and the 2nd pilot chamber 31 was produced
Thrust is smaller.Thus, the active force of back-moving spring 32 is more than the pressure differential production between the 1st pilot chamber 30 and the 2nd pilot chamber 31
Raw thrust, back-moving spring 32 turns into the state extended.
In this case, as shown in figure 4, because the 1st path 35 and the 2nd path 36 are open to endless groove 29c, therefore the 1st
Hydraulic pressure chamber 16 is connected by endless groove 29c and the 2nd hydraulic pressure chamber 17 with draining path 40.In this condition, due in the 1st hydraulic pressure
The hydraulic pressure chamber 17 of room 16 and the 2nd do not act on make stator 4 swing hydraulic pressure, therefore stator 4 by cam spring 18 to relative to rotor 2
The direction force of offset increase.Thus, stator 4 turns into maximum relative to the offset of rotor 2.
It is that in the region of below desired speed, stator 4 is maximum relative to the offset of rotor 2, rotor in the rotating speed of rotor 2
2 pumpages often rotated a circle are maximum, and the pump delivery flow of vane pump 100 turns into the stream generally proportionate with the rotating speed of rotor 2
Amount.Thus, in the case of the rotating speed of rotor 2 is less, the working oil of abundant flow can be also supplied to hydraulic test.
When the rotating speed increase of rotor 2, the front and rear pressure difference of thin-wall hole 37 becomes big, and by the 1st pilot chamber 30 and the 2nd pilot chamber
Thrust and the force balance of back-moving spring 32 that pressure differential between 31 is produced, or slightly larger than the active force of back-moving spring 32.
Thus, guiding valve 29 overcomes the active force of back-moving spring 32 to start movement.
Moreover, when the rotating speed of rotor 2 increases and reaches desired speed, as shown in figure 5, with the movement of guiding valve 29, the 1st
Path 35 turns into open mode and connected with the 1st pilot chamber 30 and endless groove 29c, and the 2nd path 36 is always maintained at open mode.By
This, the 1st hydraulic pressure chamber 16 is connected with hyperbaric chamber 23, and the 2nd hydraulic pressure chamber 17 is connected with draining path 40, therefore with the 1st hydraulic pressure chamber 16
Pressure rise, stator 4 to relative to rotor 2 offset reduction direction start movement.
Exceed in the rotating speed of rotor 2 in the region of desired speed, the pump delivery flow constant of vane pump 100.That is, when
1st path 35 and the 2nd path 36 turn into open mode, and stator 4 starts to move to the direction of the offset reduction relative to rotor 2
When dynamic, pump delivery flow reduces and the front and rear pressure difference of thin-wall hole 37 reduces.Thus, back-moving spring 32 extends, and is again switched off the 1st
Path 35.When the 1st path 35 is closed, stator 4 is moved to the direction of the offset increase relative to rotor 2, and pump discharge stream
Amount increase.When pump delivery flow increase, the front and rear pressure difference of thin-wall hole 37 becomes big, and the compression reseting spring 32 of guiding valve 29 is simultaneously moved
It is dynamic, and the 1st path 35 and the 2nd path 36 is turned into open mode again.In this way, the 1st path 35 is opened or closed, and it is so that thin
The mode that the front and rear pressure difference of cinclides 37 is constant is controlled, therefore pump delivery flow constant.
Exceed in the rotating speed of rotor 2 in the region of desired speed, with the increase of the rotating speed of rotor 2, the compression of guiding valve 29 is multiple
Position spring 32 and move amount increase, the 1st path 35 aperture increase, therefore stator 4 relative to rotor 2 offset by
Decrescence small, the pumpage that rotor 2 often rotates a circle is gradually reduced.
When the rotating speed of rotor 2 further increases, as shown in fig. 6, stator 4 turns into minimum relative to the offset of rotor 2,
The pumpage often rotated a circle of rotor 2 turns into minimum.
Stator 4 will not also turn into zero relative to the offset of rotor 2 in the state of the minimum shown in Fig. 6, therefore,
Vane pump 100 is with minimum discharge capacity discharge working oil.
As described above, guiding valve 29 is moved with the change of the rotating speed of rotor 2, the 1st path 35 is with the movement of guiding valve 29
And open or close to adjust pump delivery flow.Specifically, rotor 2 rotating speed for below desired speed when pumping up dynamic,
Guiding valve 29 closes the 1st path 35, therefore, and stator 4 turns into maximum relative to the offset of rotor 2, and pump delivery flow is with rotor 2
Rotating speed increase and increase.In addition, when the rotating speed of rotor 2 exceedes desired speed, being led to using the mobile adjustment the 1st of guiding valve 29
The aperture on road 35, and be controlled in the mode for making the front and rear pressure difference of thin-wall hole 37 constant, therefore pump delivery flow constant.
Here, in the case where the rotating speed of rotor 2 declines from the region for exceeding desired speed, by the 1st pilot chamber 30 and the 2nd
The thrust that pressure differential between pilot chamber 31 is produced declines and guiding valve 29 is slided to the direction that back-moving spring 32 extends.When with cunning
The slip of valve 29 and during inaccessible connection between the 1st path 35 and the 1st pilot chamber 30, guide to the high pressure of the 1st hydraulic pressure chamber 16
Working oil is discharged to endless groove 29c, and then is supplied to the 2nd hydraulic pressure chamber 17 via the 2nd path 36.Then, the 2nd hydraulic pressure chamber 17
Working oil be back to suction passage 22 (Fig. 4, Fig. 5) via draining path 40.
Thus, when the offset of stator 4 increases with the decline of the rotating speed of rotor 2, stator 4 is from the 1st hydraulic pressure chamber
16 are directed to via endless groove 29c in the presence of the operating oil pressure of the 2nd hydraulic pressure chamber 17, are born on the direction that offset increases
Power.
Because the operating oil pressure for being directed to the 2nd hydraulic pressure chamber 17 connects all the time higher than the 2nd hydraulic pressure chamber 17 via draining path 40
The operating oil pressure of logical suction passage 22, therefore compared to the active force merely with cam spring 18 and the internal pressure due to stator 4
And the power born makes the situation that the offset of stator 4 increases, can response make stator 4 eccentric more well.Therefore, it is possible to
Prevent from producing the servo-actuated delayed of stator 4 in the rotating speed decline of rotor 2.
The 1st embodiment more than, plays effect as shown below.
The decline of pressure difference before and after with thin-wall hole 37 and the working oil of the 1st hydraulic pressure chamber 16 is discharged so that stator 4
Offset increase when, be expelled to endless groove 29c working oil via the 2nd path 36 from the 1st hydraulic pressure chamber 16 and be directed to the 2nd liquid
Pressure chamber 17.
Thus, rotor 2 rotating speed decline and the offset of stator 4 increase when, except cam spring 18 on stator 4
Beyond active force, also effect has by the working oil being directed to from the 1st hydraulic pressure chamber 16 via endless groove 29c of the 2nd hydraulic pressure chamber 17
Press the power produced.Thus, it is possible to prevent the servo-actuated delayed of stator 4.
In addition, the 2nd path 36 is open to valve receiving hole 26, also, the insertion engagement ground of ring 12 is in the 2nd hydraulic pressure of engagement ring 12
Inner peripheral surface opening at room 17, therefore, it is possible to shorten be configured at engagement ring 12 radial outside configuration and with the phase of engagement ring 12
The distance between adjacent hydraulic pressure chamber 17 of control valve 27 and the 2nd.
Thus, the rotating speed in rotor 2 declines and in the case of the increase of the offset of stator 4, can shortened from the 1st hydraulic pressure chamber
16 operating oil pressures for being expelled to endless groove 29c supply untill the 2nd hydraulic pressure chamber 17 the required time.Therefore, it is possible to improve to fixed
The rising of the working oil pressure of 2nd hydraulic pressure chamber 17 of the direction force that son 4 increases to offset is so as to be more reliably prevented from stator 4
It is servo-actuated delayed.
2nd embodiment
Reference picture 7 and Fig. 8 illustrate the variable displacement vane pump 200 of the 2nd embodiment of the present invention.
The construction of 2nd path 136 of the variable displacement vane pump 200 of present embodiment is different from the 1st embodiment, its
His aspect is identical with the 1st embodiment.Thus, pair with the 1st embodiment identical structure mark identical reference simultaneously
Omit the description.
In the 1st embodiment, the 2nd path 36 is open to valve receiving hole 26 and insertion engages the ground of ring 12 to the 2nd hydraulic pressure
Room 17 is open and formed, in contrast, in the present embodiment, including the He of low-pressure chamber 25 as the 2nd path 136 of guiding path
The linear passages as the 2nd guiding path linearly to connect the innermost portion of low-pressure chamber 25 and the endless groove 29c of control valve 27
101。
Thus, the working oil that the endless groove 29c of control valve 27 is expelled to from the 1st hydraulic pressure chamber 16 passes through the He of linear passages 101
Low-pressure chamber 25 is fed to the 2nd hydraulic pressure chamber 17.
The 2nd embodiment more than, plays effect as shown below.
Because the 2nd path 136 accommodates the inhalation area of the recess 6a bottom surface 6b volume enlargement positioned at pump chamber 11 in pump
Interior outs open, therefore through hole need not be set in the engagement ring 12 for dividing receiving space in the outer circumferential side of stator 4.
Therefore, except need not engagement ring 12 set through hole in addition to, it is not necessary to dock cyclization 12 through hole and with control
The hole that the mode of the endless groove 29c connections of valve 27 is formed at the pump housing 6 is alignd, therefore, it is possible to reduce manufacturing cost and prevent
Stator 4 it is servo-actuated delayed.
Further, since the 2nd path 136 includes being formed as the linear low-pressure chamber 25 parallel with drive shaft 1 and with straight line
The linear passages 101 of the innermost portion of shape connection low-pressure chamber 25 and the endless groove 29c of control valve 27, therefore only by setting two directly
The path of wire, it becomes possible in the 2nd path 136 of formation of the pump housing 6.Therefore, it is possible to improve the processing for setting the 2nd path 136
Easiness and manufacturing cost can be reduced.
Further, since a part for the 2nd path 136 is made up of low-pressure chamber 25, therefore, it is possible to by only setting linear passages
101 just form the 2nd path 136.Therefore, it is possible to further improve for set the 2nd path 136 processing easiness and can
Further reduce manufacturing cost.
Embodiments of the present invention are this concludes the description of, but the embodiment illustrate only the application examples of the present invention,
Its objective does not simultaneously lie in the concrete structure that protection scope of the present invention is defined in the embodiment.
For example, in said embodiment, exemplified with situation of the working oil as working fluid is used, it is also possible to use
The fluids such as water, water-soluble replacement liquid beyond working oil.
In addition, in said embodiment, linear feelings are all formed as exemplified with low-pressure chamber 25 and linear passages 101
Condition, but this is not limited to, it can also be that at least one is formed as curve-like, the shape in midway bending.
The application is advocated based on November 26th, 2014 to the Japanese Patent Application 2014-239200 of Japanese Patent Office application
Priority, the entire disclosure of which is by referring to being programmed into this specification.
Claims (4)
1. a kind of variable displacement vane pump, wherein,
The variable displacement vane pump includes：
Rotor, it is linked to drive shaft；
Multiple blades, it is located at the rotor, and is diametrically moved back and forth freely relative to the rotor；
Stator, the top ends of the blade with the rotation for the rotor for being configured at the stator interior with the inner circumferential of the stator
Cam surface sliding contact, and the stator can be relative to the rotor eccentricity；
Pump chamber, it is divided to be formed between the rotor and the stator, and is separated using the multiple blade；
1st fluid pressure chamber and the 2nd fluid pressure chamber, it is divided to be formed in the receiving space of the outer circumferential side of the stator；
Force application component, it exerts a force to the direction that the stator increases to offset all the time；
Throttle part, it is to the flowing application resistance for the working fluid discharged from the pump chamber；
Control valve, it imports the working fluid discharged from the pump chamber with the rising of the front and rear pressure difference of the throttle part
To the 1st fluid pressure chamber so that the offset of the stator reduces, and with the front and rear pressure difference decline and by institute
The working fluid discharge of the 1st fluid pressure chamber is stated so that the offset increase of the stator；
Suction passage, it is used to guide the working fluid sucked to the pump chamber, and connects all the time with the 2nd fluid pressure chamber
It is logical；And
Guiding path, it connects the control valve and the 2nd fluid pressure chamber, will be expelled to from the 1st fluid pressure chamber described
The working fluid of control valve is guided to the 2nd fluid pressure chamber.
2. variable displacement vane pump according to claim 1, wherein,
The variable displacement vane pump also includes：
Ring is engaged, it is annularly set in the way of surrounding the stator；And
The pump housing, it has the recess for accommodating the engagement ring,
The control valve is configured at the radial outside of the engagement ring, and adjacent with the engagement ring,
Inner peripheral surface opening of the guiding path at the 2nd fluid pressure chamber of the engagement ring.
3. variable displacement vane pump according to claim 1, wherein,
The variable displacement vane pump also includes the pump housing, and the pump housing has the recess for being used for accommodating the stator and formed
State guiding path,
Portion of the guiding path in the inhalation area of the volume enlargement positioned at the pump chamber of the bottom surface of the recess is separated
Mouthful.
4. variable displacement vane pump according to claim 3, wherein,
The guiding path has：1st guiding path, it and is formed as and the drive shaft in the bottom surface opening of the recess
Parallel is linear；And the 2nd guiding path, it is linearly to connect the 1st guiding path and the control valve.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2014239200A JP6375212B2 (en) | 2014-11-26 | 2014-11-26 | Variable displacement vane pump |
| JP2014-239200 | 2014-11-26 | ||
| PCT/JP2015/082937 WO2016084804A1 (en) | 2014-11-26 | 2015-11-24 | Variable capacity vane pump |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN107002672A true CN107002672A (en) | 2017-08-01 |
Family
ID=56074359
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201580061546.0A Pending CN107002672A (en) | 2014-11-26 | 2015-11-24 | Variable displacement vane pump |
Country Status (5)
| Country | Link |
|---|---|
| US (1) | US20170321696A1 (en) |
| EP (1) | EP3225847A4 (en) |
| JP (1) | JP6375212B2 (en) |
| CN (1) | CN107002672A (en) |
| WO (1) | WO2016084804A1 (en) |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107532593B (en) * | 2015-04-09 | 2019-05-31 | 日立汽车系统株式会社 | Capacity-variable type oil pump |
| JP7042099B2 (en) | 2018-02-06 | 2022-03-25 | 日立Astemo株式会社 | Pump device |
| WO2020234765A1 (en) | 2019-05-20 | 2020-11-26 | Stackpole International Engineered Products, Ltd. | Spool valve used in a variable vane pump |
| JP7289372B2 (en) * | 2019-05-29 | 2023-06-09 | ピアーブルグ パンプ テクノロジー ゲゼルシャフト ミット ベシュレンクテル ハフツング | Variable displacement lubricating oil pump |
| WO2022037792A1 (en) * | 2020-08-21 | 2022-02-24 | Pierburg Pump Technology Gmbh | Variable displacement lubricant pump |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101560975A (en) * | 2008-04-15 | 2009-10-21 | 萱场工业株式会社 | Variable displacement vane pump |
| JP2010255551A (en) * | 2009-04-27 | 2010-11-11 | Kayaba Ind Co Ltd | Variable displacement vane pump |
| WO2013141129A1 (en) * | 2012-03-21 | 2013-09-26 | カヤバ工業株式会社 | Variable-capacity vane pump |
| US20130251584A1 (en) * | 2012-03-22 | 2013-09-26 | Hitachi Automotive Systems Steering, Ltd. | Variable displacement pump |
| CN103573618A (en) * | 2013-10-26 | 2014-02-12 | 奇瑞汽车股份有限公司 | Variable-displacement power steering pump for cars |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2007087704A1 (en) * | 2006-01-31 | 2007-08-09 | Magna Powertrain Inc. | Variable displacement variable pressure vane pump system |
| JP5116546B2 (en) * | 2008-04-23 | 2013-01-09 | カヤバ工業株式会社 | Variable displacement vane pump |
| JP2010255552A (en) * | 2009-04-27 | 2010-11-11 | Kayaba Ind Co Ltd | Variable displacement vane pump |
-
2014
- 2014-11-26 JP JP2014239200A patent/JP6375212B2/en not_active Expired - Fee Related
-
2015
- 2015-11-24 WO PCT/JP2015/082937 patent/WO2016084804A1/en active Application Filing
- 2015-11-24 EP EP15863924.5A patent/EP3225847A4/en not_active Withdrawn
- 2015-11-24 CN CN201580061546.0A patent/CN107002672A/en active Pending
- 2015-11-24 US US15/525,385 patent/US20170321696A1/en not_active Abandoned
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101560975A (en) * | 2008-04-15 | 2009-10-21 | 萱场工业株式会社 | Variable displacement vane pump |
| JP2010255551A (en) * | 2009-04-27 | 2010-11-11 | Kayaba Ind Co Ltd | Variable displacement vane pump |
| WO2013141129A1 (en) * | 2012-03-21 | 2013-09-26 | カヤバ工業株式会社 | Variable-capacity vane pump |
| US20150044083A1 (en) * | 2012-03-21 | 2015-02-12 | Kayaba Industry Co., Ltd. | Variable capacity type vane pump |
| US20130251584A1 (en) * | 2012-03-22 | 2013-09-26 | Hitachi Automotive Systems Steering, Ltd. | Variable displacement pump |
| CN103573618A (en) * | 2013-10-26 | 2014-02-12 | 奇瑞汽车股份有限公司 | Variable-displacement power steering pump for cars |
Also Published As
| Publication number | Publication date |
|---|---|
| WO2016084804A1 (en) | 2016-06-02 |
| US20170321696A1 (en) | 2017-11-09 |
| EP3225847A4 (en) | 2018-07-18 |
| EP3225847A1 (en) | 2017-10-04 |
| JP6375212B2 (en) | 2018-08-15 |
| JP2016098802A (en) | 2016-05-30 |
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| AD01 | Patent right deemed abandoned |
Effective date of abandoning: 20191108 |