CN107076142A - Variable displacement vane pump - Google Patents
Variable displacement vane pump Download PDFInfo
- Publication number
- CN107076142A CN107076142A CN201580056627.1A CN201580056627A CN107076142A CN 107076142 A CN107076142 A CN 107076142A CN 201580056627 A CN201580056627 A CN 201580056627A CN 107076142 A CN107076142 A CN 107076142A
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- Prior art keywords
- mentioned
- pressure
- accepting hole
- pump
- valve
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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
- F04C14/18—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber
- F04C14/22—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
- F04C14/18—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber
- F04C14/22—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members
- F04C14/223—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members using a movable cam
- F04C14/226—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 by pivoting the cam around an eccentric axis
-
- 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
-
- 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
- F04C2240/00—Components
- F04C2240/80—Other components
- F04C2240/811—Actuator for control, e.g. pneumatic, hydraulic, electric
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2270/00—Control; Monitoring or safety arrangements
- F04C2270/21—Pressure difference
- F04C2270/215—Controlled or regulated
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
A kind of variable displacement vane pump (1), working oil is supplied to power steering gear, and the variable displacement vane pump (1) possesses：Pump case (2), is made up of the procapsid (5) of bottomed cylindrical and the back casing (6) of closure procapsid；Pumping element (3), is contained in pump case, is connected with suction passage (23) and drain passageway (30) and working oil is sucked and discharged；Flow control valve (33), controls the working oil discharge rate of pumping element；The forced induction valve (50) for the flowing path section area for changing drain passageway is arranged in the bottom wall part (5b) of the midway of drain passageway and procapsid, thus, with the increase of the load pressure of power steering gear, the discharge rate of pumping element increases.Thereby, it is possible to reduce energy loss during for power steering gear, and the maximization of restraining device.
Description
Technical field
The present invention relates to the variable displacement vane pump of the hydraulic power steering apparatus for such as automobile.
Background technology
Generally, variable displacement vane pump possesses：Inside has the pump case of pumping element resettlement section, by engine rotation driving
And by working solution is sucked and is discharged pumping element, drain passageway from the working solution for discharging the pumping element to supply goal directed,
The stream of throttle orifice located at the drain passageway midway, the working solution discharge rate based on the differential pressure control pumping element before and after the throttle orifice
Control valve.
Differential pressure before and after above-mentioned throttle orifice changes according to the discharge rate of above-mentioned pumping element, and the discharge rate is based on above-mentioned engine
Rotating speed determine.That is, rotating speed of the above-mentioned variable displacement vane pump based on above-mentioned engine controls the flow of working solution.
But, in the case where this variable displacement vane pump is used for into the power steering gear of vehicle, hardly
During the vehicle straight trip for the power steering for needing to be produced by hydraulic pressure, also working solution can be discharged to above-mentioned power steering gear, therefore, can
Energy loss can be caused.
Therefore, as the variable displacement vane pump that can reduce energy loss when being installed on above-mentioned power steering gear,
The known vane pump having described in following patent document 1.
Briefly, the variable displacement vane pump that above-mentioned publication is recorded is also equipped with the basis of above-mentioned pump configuration：Will
The by-pass flow path of the upstream side of above-mentioned throttle orifice and downstream connection, located at the by-pass flow path and based on above-mentioned power steering gear
Load press off the forced induction valve closed and state by-pass flow path.
Above-mentioned forced induction valve connects above-mentioned by-pass flow path in the steering that the load pressure of above-mentioned power steering gear rises
It is logical, on the other hand, in the straight ahead that load is forced down, cut off above-mentioned by-pass flow path.Thus, with engine speed independently,
Pump delivery during straight ahead can be reduced, therefore, it is possible to reduce the energy loss of above-mentioned power steering gear.
Prior art literature
Patent document
Patent document 1：(Japan) JP 2003-176791 publications
The content of the invention
But,, therewith, can due to provided with above-mentioned by-pass flow path, causing stream complicated in above-mentioned variable displacement vane pump
It can have to make larger-scale unit.
The present invention be in view of above-mentioned technical problem and research and develop there is provided a kind of variable displacement vane pump, use can be reduced
Energy loss when power steering gear, while the maximization of restraining device.
The present invention provides a kind of variable displacement vane pump, and working solution, its feature are supplied to the power steering gear of vehicle
It is possess：Pump case, it is made up of the first housing and the second housing, and has pumping element resettlement section in the inside of the rwo,
The bottom wall part that first housing is had cylindrical portion and set in the way of the one end open for blocking the cylindrical portion, the second shell
Body in the way of another end opening for blocking the cylindrical portion to set；Drive shaft, it is inserted through in the pump case, by rotatably
E axle supporting；Rotor, it is contained in the pumping element resettlement section, has been circumferentially formed thereon multiple slits, and driven by described
Moving axis rotation driving；Blade, it comes in and goes out is located at the slit freely；The cam ring of ring-type, it is movably disposed in the pump
In component resettlement section, multiple pump chambers are formed together with the rotor and the blade；Suction inlet, it is located at the pump case, to institute
State the inhalation area opening that volume gradually increases with the rotation of the rotor in multiple pump chambers；Outlet, it is located at described
Pump case, the discharging area opening that volume is gradually decreased with the rotation of the rotor into the multiple pump chamber；Suction passage,
It is located at the pump case, and the working solution for being stored in fluid reservoir is supplied to the suction inlet；Drain passageway, it is located at the pump
Shell, working solution being externally supplied to the pump case that will be discharged from the outlet；First fluid balancing gate pit and second fluid pressure
Power room, is respectively arranged on the outer circumferential side of the cam ring, in the cam ring relative to the side that the offset of the rotor increases
In the case of movement, the first fluid balancing gate pit is formed at the side of volume reducing, and the second fluid balancing gate pit is formed
The side increased in volume；First valve accepting hole, its described bottom wall part and the drain passageway located at first housing
Halfway；First valve body, it is movably disposed in the first valve accepting hole, is pressed and from institute based on the suction for acting on a side
The differential pressure discharged between pressure stated drain passageway importing and act on another side moves control, and with mobile change
The flowing path section area of the drain passageway；Second valve accepting hole, it is located at the pump case；Hyperbaric chamber and control pressure chamber, it is described
Hyperbaric chamber is located at a side of the second valve accepting hole, is formed in the way of being connected with the outlet, the control pressure chamber
Located at the another side of the second valve accepting hole, to connect with the further downstream of the first valve accepting hole of the drain passageway
Logical mode is formed；Second valve body, it is movably disposed in the second valve accepting hole, the pressure based on the hyperbaric chamber and
Differential pressure between the pressure of the control pressure chamber controls the pressure of the first fluid balancing gate pit.
In accordance with the invention it is possible to energy loss during for power steering gear be reduced, while the maximization of restraining device.
Brief description of the drawings
Fig. 1 is the stereogram for the variable displacement vane pump for representing embodiment of the present invention.
Fig. 2 is the longitudinal section for representing the variable displacement vane pump.
Fig. 3 is Fig. 2 line A-A sectional view.
Fig. 4 is the longitudinal section for the major part for representing the variable displacement vane pump.
Fig. 5 (A) is to represent to act on Fig. 4 discharged in the case of pressing the differential pressure between suction pressure small of the first valve body
Enlarged view of the main part, (B) be represent differential pressure it is big in the case of Fig. 4 enlarged view of the main part.
Fig. 6 is the stereogram of the state for the first valve body insertion procapsid for representing present embodiment.
Fig. 7 represents the first valve body of present embodiment, and (A) is the stereogram of the first valve body, and (B) is the side view of the first valve body
Figure.
Fig. 8 is Fig. 4 line B-B sectional view.
Fig. 9 is the figure for representing the relation between the revolution speed and delivery flow in the variable displacement vane pump.
Figure 10 is the schematic diagram of the rate of change for the flowing path section area for representing the drain passageway with the movement of the first valve body.
Figure 11 is the load on spring for representing can be used as the variable pitch spring of the helical spring of second embodiment of the invention
The figure of relation between displacement.
Figure 12 is to represent to can be used as between load on spring and the displacement of the volute spring of the helical spring of the embodiment
The figure of relation.
The pressure and section of when Figure 13 is the first valve body for representing to make pressure fluid act on the embodiment, the fluid pressure
The figure of relation between discharge orifice aperture area.
Figure 14 is the longitudinal section of the major part for the variable displacement vane pump for representing third embodiment of the invention.
Embodiment
Hereinafter, each embodiment of the variable displacement vane pump of the present invention is described in detail based on accompanying drawing.In addition, following institute
In each embodiment shown, for example, the variable displacement vane pump is installed on the power steering gear of automobile.
As shown in FIG. 1 to 3, above-mentioned variable displacement vane pump 1 possesses：Pump case 2, inside has columned pumping element
Resettlement section is pumping element reception room 2a；Pumping element 3, is contained in above-mentioned pumping element reception room 2a.Using inserting above-mentioned pumping element
The reception room 2a above-mentioned pumping element 3 of the rotation driving of drive shaft 4, thus, pump work.
As shown in Figures 1 and 2, above-mentioned pump case 2 has：Being formed as the first housing i.e. procapsid 5 of round-ended cylinder shape, closure should
Second housing of the opening portion of procapsid 5 is back casing 6, and the rwo 5,6 is fastened and fixed by multiple bolts 7.
As shown in Figures 2 and 3, above-mentioned pumping element 3 possesses：Setting-in is fixed on the cylindrical portion 5a inner peripheral surfaces of above-mentioned procapsid 5
Substantially circular adaptor ring 8, be movably disposed in the inner space of the formation generally elliptical shape of the adaptor ring 8
Substantially circular cam ring 9, with above-mentioned drive shaft 4 can integrally rotatably be located at the rotor 10 of the inner circumferential side of the cam ring 9, match somebody with somebody
It is placed in the bottom wall part 5b of above-mentioned procapsid 5 and the substantially disk of above-mentioned cam ring 9 and rotor 10 is clamped together with above-mentioned back casing 6
The pressing plate 11 of shape.
As shown in figure 3, above-mentioned adaptor ring 8 has tabular seal member 12 in inner peripheral surface 8a bottom.The tabular sealing
Part 12 has the function of sealing between above-mentioned adaptor ring 8 and cam ring 9, and has as above-mentioned cam ring 9 in above-mentioned mating
The function of rolling surface when being moved in the inner space of ring 8.
In addition, in the inner peripheral surface 8a of above-mentioned adaptor ring 8, the diametrically position relative with above-mentioned tabular seal member 12
Put, in the same manner as the tabular seal member 12, provided with the seal member 13 sealed between above-mentioned adaptor ring 8 and cam ring 9.
Above-mentioned cam ring 9 is being partitioned into first fluid pressure by above-mentioned two seal member 12,13 with above-mentioned adaptor ring 8
Power room 14 and second fluid balancing gate pit 15, based on the pressure differential between these each fluid pressure chamber 14,15, into Fig. 3, left and right directions is moved
It is dynamic, thus, increase and decrease the offset relative to above-mentioned rotor 10.
In addition, above-mentioned cam ring 9 by the return spring 16 with its periphery Elastic Contact always to relative to above-mentioned rotor 10
Offset turns into maximum direction force.
In addition, between above-mentioned adaptor ring 8 and cam ring 9, and the side counterclockwise in Fig. 3 of above-mentioned tabular seal member 12
It is position retaining pin 17 of the position provided with the position for keeping above-mentioned cam ring 9 of the above-mentioned side of second fluid balancing gate pit 15 to side.Should
Position retaining pin 17 is in addition to the function with the position for keeping above-mentioned cam ring 9, also with for limiting above-mentioned cam ring 9
Relative to the rotation stopping function of the inordinate rotation of above-mentioned adaptor ring 8.
When above-mentioned drive shaft 4 is driven in rotation by engine (not shown), above-mentioned rotor 10 is inverse into Fig. 3 therewith
Clockwise (direction of arrow) rotates.In addition, in the peripheral part of above-mentioned rotor 10, being cut along multiple slits 18 that radiation direction extends
Open the substantially position, and via each slit 18, the blade 19 of substantially planar is respectively along upper at equal intervals for being formed at circumferencial direction
The radial direction discrepancy for stating rotor 10 is received freely.
The work that above-mentioned each blade 19 passes through the back pressure chamber 20 for being formed at the inner circumferential side of rotor 10 importing to above-mentioned each slit 18
It is the pressure of working oil as liquid, always to the inner peripheral surface direction stress of above-mentioned cam ring 9.
In addition, above-mentioned each blade 19 is separated between above-mentioned cam ring 9 and rotor 10 using adjacent two blades 19,19
Annulus, forms multiple pump chambers 21.
In addition, in the inner face 6a towards pumping element reception room 2a of above-mentioned back casing 6, equivalent to above-mentioned turn
Sub 10 rotation and the position of inhalation area that the volume of above-mentioned each pump chamber 21 gradually expands, as shown in Figures 2 and 3, are formed with
First suction inlet 22 of arc-shaped.First suction inlet 22 is via the suction passage 23 worn on above-mentioned back casing 6 and storage
The fluid reservoir T connections of working oil.Thus, fluid reservoir T working oil is stored in flow and be oriented in above-mentioned suction passage 23
After above-mentioned first suction inlet 22, effect is entered by the pumping produced in above-mentioned inhalation area and sucked to above-mentioned each pump chamber 21.
In addition, between the bottom surface of above-mentioned procapsid 5 and the end face 11a of pressing plate 11, being formed with as shown in Fig. 2 cutting
With the second suction inlet 24 of the roughly the same shape of the first suction inlet 22.Second suction inlet 24 is through being formed from above-mentioned procapsid
5 low pressure access is current return circuit 25, is connected with as the closure gasket groove 26 of seal member resettlement section.
Above-mentioned closure gasket groove 26 is internally contained in sealing with being circumferentially formed the outer circumferential side of above-mentioned drive shaft 4
State the seal member i.e. sealing ring 27 between procapsid 5 and drive shaft 4.Thus, limit upward from above-mentioned pumping element reception room 2a
The outside for stating working oil to above-mentioned pump case 2 that drive shaft 4 is passed over is spilt, and makes its remaining working oil via above-mentioned time
Logical circulation road 25 flows back to above-mentioned second suction inlet 24.
In addition, in the end face 11a of above-mentioned pressing plate 11, in above-mentioned each pump equivalent to the rotation with above-mentioned rotor 10
The position of the diminishing discharging area of volume of room 21, as shown in Figures 2 and 3, is formed with the outlet 28 of arc-shaped.The row
Outlet 28 is connected with the recessed bottom wall part 5b in above-mentioned procapsid 5 balancing gate pit 29.The balancing gate pit 29 is played by internal pressure
The effect exerted a force to above-mentioned pressing plate 11 to the above-mentioned side of rotor 10.
In addition, as shown in Figures 2 and 3, above-mentioned outlet 28 is through being formed from the bottom wall part 5b of above-mentioned procapsid 5 discharge
Path 30, working oil is supplied to the rotary valve of power steering gear (not shown).
Above-mentioned drain passageway 30 has the metering throttle orifice 32 of cross section circular on the way wherein, utilizes the metering to throttle
Hole 32 makes working oil produce differential pressure.
In addition, as shown in Figures 2 and 3, flow control valve 33 is equipped with the upper end of above-mentioned procapsid 5.The flow control
Valve 33 processed possesses：The the second valve accepting hole for being located at above-mentioned procapsid 5 in the mode orthogonal with above-mentioned drive shaft 4 is that control valve is housed
Hole 34, be sliding freely contained in the control valve accepting hole 34 inside the second valve body i.e. application valve body 35, close above-mentioned control
The axially plug 36 of the opening portion of a side, the valve exerted a force to the side of plug 36 to above-mentioned application valve body 35 of valve accepting hole 34 processed
Spring 37.
As shown in figure 3, being provided with the inside of above-mentioned control valve accepting hole 34：Hyperbaric chamber 38, located at above-mentioned plug 36 and control
Between valve body 35 processed, the pressure (discharge pressure) of the above-mentioned upstream side of metering throttle orifice 32 is imported；Pressure chamber 39 is controlled, located at axially another
Side, houses above-mentioned valve spring 37, and import the pressure (control pressure) in the above-mentioned downstream of metering throttle orifice 32；Low-pressure chamber 41, shape
Enter pressure from above-mentioned suction passage 23 importing pumping into the outer circumferential side of above-mentioned application valve body 35, and via low-pressure passage 40.These
Each balancing gate pit 38,39 and 41 is divided into respectively using first, second stage portion 35a, 35b of above-mentioned application valve body 35.
In addition, damping orifice 42 is provided between above-mentioned drain passageway 30 and above-mentioned control pressure chamber 39, damping throttling
Hole 42 is used to reduce the fluid pressure of the working oil imported to the control pressure chamber 39, reduces the influence of pulsation.
Moreover, the difference between the pressure of pressure and control pressure chamber 39 of the above-mentioned application valve body 35 based on above-mentioned hyperbaric chamber 38
Pressure, is axially moveable.
Specifically, the pressure differential in above-mentioned hyperbaric chamber 38 and control pressure chamber 39 is smaller, passes through the bullet of above-mentioned valve spring 37
Spring force, in the case that above-mentioned application valve body 35 is located at the above-mentioned side of plug 36, above-mentioned first fluid balancing gate pit 14 and control valve are received
The access 43 for holding the connection of hole 34 is open to above-mentioned low-pressure chamber 41.Thus, from above-mentioned low-pressure chamber 41 to above-mentioned first fluid pressure
Room 14 imports suction pressure.
On the other hand, the pressure differential in above-mentioned hyperbaric chamber 38 and control pressure chamber 39 is larger, on above-mentioned application valve body 35 overcomes
State the pressure of control pressure chamber 39 and the active force of above-mentioned valve spring 37 and in the case that into Fig. 3, right side is mobile, above-mentioned low-pressure chamber
41 are gradually cut off with connecting for first fluid balancing gate pit 15, and above-mentioned hyperbaric chamber 38 is via access 43 and above-mentioned first fluid pressure
Power room 14 is connected.Thus, high pressure is imported from above-mentioned hyperbaric chamber 38 to above-mentioned first fluid balancing gate pit 14.
That is, above-mentioned low-pressure chamber 41 or the hydraulic pressure in hyperbaric chamber 38 are selectively introduced to above-mentioned first fluid balancing gate pit 14.
Moreover, being always introduced into pumping to above-mentioned second fluid balancing gate pit 15 enters pressure, and to above-mentioned first fluid balancing gate pit 14
When importing the suction pressure from above-mentioned low-pressure chamber 41, based on the active force of above-mentioned return spring 16, above-mentioned cam ring 9 to relative to
The offset of above-mentioned rotor 10 turns into maximum position configuration, and pump delivery turns into maximum.
On the other hand, when importing the high pressure in above-mentioned hyperbaric chamber 38 to above-mentioned first fluid balancing gate pit 14, based on the high pressure, on
State cam ring 9 and overcome the active force of above-mentioned return spring 16 to the i.e. above-mentioned side of second fluid balancing gate pit 15 in the direction of offset reduction
Roll, thus, pump delivery is reduced.
In addition, being internally formed safety valve 44 in above-mentioned application valve body 35.The safety valve 44 is in above-mentioned control pressure chamber 39
Pressure valve opening when turning into the regulation above, i.e. valve opening when the load of power steering gear side is pressed to more than regulation becomes pressure
High working oil flows back via above-mentioned low-pressure chamber 41 and low-pressure passage 40 to above-mentioned suction passage 23.
Moreover, as shown in figure 4, being provided with pressure sensitive in the positive upstream position of the metering throttle orifice 32 of above-mentioned drain passageway 30
Valve 50, the forced induction valve 50 senses the load pressure of above-mentioned power steering gear side, changes and reaches above-mentioned metering throttle orifice 32
The flowing path section area in downstream.
Particularly as shown in figure 5, the forced induction valve 50 possesses：There is the columned pressure sensitive valve accepting hole 51 in bottom, be to cut
It is formed at the bottom wall part 5b of above-mentioned procapsid 5 the first valve accepting hole；Cylindric pressure-sensitive valve body 52 (guiding valve), is in the pressure-sensitive
The first valve body that the inside of valve accepting hole 51 is sliding freely housed；Helical spring 53, is to above-mentioned to the pressure-sensitive valve body 52
The spring members of the side of pressing plate 11 force.
As shown in Fig. 4, Fig. 5 and Fig. 8, above-mentioned pressure sensitive valve accepting hole 51 is parallel with above-mentioned drive shaft 4 and forms step diameter shape,
And possess be formed at axial one end open portion side and house the large diameter hole portion 51a of above-mentioned pressure-sensitive valve body 52 and be formed at it is axial
Other end bottom side and the path hole portion 51b for housing above-mentioned helical spring 53.
In addition, the binding site in above-mentioned large diameter hole portion 51a and path hole portion 51b is formed with relative to axially orthogonal circle
The step surface 51c of ring-type.Turn into the feelings of more than setting to the amount of movement of above-mentioned diameter holes portion 51b sides in above-mentioned pressure-sensitive valve body 52
Under condition, above-mentioned step surface 51c plays limitation to the backstop of the above-mentioned side of pressure sensitive valve accepting hole 51 of the movement of path hole portion 51b sides
The effect in portion.
In addition, above-mentioned pressure sensitive valve accepting hole 51 is abreast configured with above-mentioned drive shaft 4, therefore, above-mentioned pressure-sensitive valve body 52 and
Axial movement of the helical spring 53 respectively along above-mentioned drive shaft 4.
In addition, axial substantial middle position and above-mentioned meter of the above-mentioned pressure sensitive valve accepting hole 51 in above-mentioned large diameter hole portion 51a
Amount throttle orifice 32 is connected.
Above-mentioned pressure sensitive valve accepting hole 51 is also formed as：Opening portion and the above-mentioned discharge area represented by the single dotted broken line in Fig. 6
Domain connect, and relative to the discharging area on the circumferencial direction of drive shaft 4 it is overlapping.
As shown in Fig. 7 (A), (B), above-mentioned pressure-sensitive valve body 52 is the so-called guiding valve to form cylindrical shape, is possessed：Located at axially one
End and sliding freely formed with above-mentioned large diameter hole portion 51a inner peripheral surface stage portion 54, located at axial another side and with
Guide portion 55 that above-mentioned stage portion 54 is similarly sliding freely formed with above-mentioned large diameter hole portion 51a inner peripheral surface, it is integrally provided on
The axial outer end portion of the guide portion 55 and constitute for compression chamber 63 described later import working oil stream access structure portion
56。
The spring constant of above-mentioned helical spring 53 has the characteristic of substantial linear.
Above-mentioned stage portion 54 end face 54a formation as stopper section circular tabular surface, by with above-mentioned pressure-sensitive
The stopper section of the side of valve accepting hole 51 is that step surface 51c is abutted, to limit the shifting for the side for stating pressure-sensitive valve body 52 further up
It is dynamic.
Guide sections 55 are slided together with above-mentioned stage portion 54 in the inner peripheral surface of above-mentioned pressure sensitive valve accepting hole 51, in guiding
The movement of pressure-sensitive valve body 52 is stated, suppresses rocking for the pressure-sensitive valve body 52.
Above-mentioned access structure portion 56 forms the diameter cylindrical shape more smaller than guide sections 55, and in circumferencial direction substantially
90 ° of interval locations possess 4 path grooves 57 as groove portion.Above-mentioned each path groove 57 is directed towards the radial direction of above-mentioned pressure-sensitive valve body 52
Formed by incision, cross sectional shape turns into larger rectangle.That is, the one end of above-mentioned pressure-sensitive valve body 52 leaves cross section substantially three
4 protuberances 58 of angular shape, and the major part of circumferencial direction is removed.
In addition, the outer peripheral face at the path position 59 between the above-mentioned stage portion 54 and guide portion 55 of above-mentioned pressure-sensitive valve body 52
It is formed with the endless groove 60 circumferentially cut.The endless groove 60 has in substantially 90 ° of interval locations of circumferencial direction will be upper
4 intercommunicating pore 59a of the inside and outside connection of pressure-sensitive valve body 52 are stated, via in above-mentioned each intercommunicating pore 59a and above-mentioned pressure-sensitive valve body 52
Portion is connected.
In addition, the above-mentioned each intercommunicating pore 59a of ratio inside above-mentioned pressure-sensitive valve body 52 is more integrally formed by the position of a side
There is discoid next door 61.As shown in Fig. 4, Fig. 5 and Fig. 8, the next door 61 by the inner space of above-mentioned pressure sensitive valve accepting hole 51 every
Connect into the suction pressure chamber 62 of the side cut off with above-mentioned drain passageway 30 and via above-mentioned each path groove 57 with drain passageway 30
The compression chamber 63 of another side that is logical and internally importing discharge pressure.
As shown in figs. 5 and 8, above-mentioned suction pressure chamber 62 is through being formed from the low pressure of the bottom surface of above-mentioned pressure sensitive valve accepting hole 51
Road 64 is imported to connect with above-mentioned closure gasket groove 26, from this at import low pressure (suction press).
In addition, in the one end for the pressure-sensitive valve body 52 for constituting above-mentioned suction pressure chamber 62, as shown in Fig. 4, Fig. 5 and Fig. 8, being formed
There is columned spring maintaining part i.e. spring retention groove 65.The spring retention groove 65 is by the end face 61a in above-mentioned next door 61 and upper
The inner peripheral surface for stating stage portion 54 is constituted, and the part for keeping above-mentioned helical spring 53 is housed in its inner circumferential side, and make as groove
The end face 61a in the above-mentioned next door 61 at bottom and above-mentioned helical spring 53 one end Elastic Contact.On the other hand, above-mentioned spiral bullet
The other end of spring 53 and the bottom surface Elastic Contact of above-mentioned pressure sensitive valve accepting hole 51 (path hole portion 51b).Thus, as described above,
Above-mentioned helical spring 53 exerts a force to above-mentioned pressure-sensitive valve body 52 to the above-mentioned side of pressing plate 11.
Above-mentioned compression chamber 63 is formed at the inner circumferential side of above-mentioned pressure-sensitive valve body 52 and more leans on the other end side than above-mentioned next door 61
Position, as indicated by the arrows in fig. 5, make from above-mentioned access structure portion 56 import pressure fluid to the another of above-mentioned next door 61
After end face 61b actuating pressures, exported via above-mentioned each intercommunicating pore 59a and endless groove 60 to the above-mentioned downstream of metering throttle orifice 32.
Moreover, the differential pressure between the pressure of pressure and suction pressure chamber 62 of the above-mentioned pressure-sensitive valve body 52 based on above-mentioned compression chamber 63
It is axially moveable, therewith, blocks a part for above-mentioned metering throttle orifice 32 using the outer peripheral face of above-mentioned stage portion 54, thus, change
Variable-flow-path area of section.
Specifically, above-mentioned compression chamber 63 and suction pressure chamber 62 between pressure differential it is less in the case of, by above-mentioned
Shown in the active force of helical spring 53, such as Fig. 5 (A), above-mentioned pressure-sensitive valve body 52 is configured at above-mentioned each protuberance 58 and pressing plate 11 is supported
The position in left side in the figure connect.In this case, above-mentioned stage portion 54 blocks the substantially half of above-mentioned metering throttle orifice 32, because
This, the flowing path section area of the metering throttle orifice 32 substantially halves.
On the other hand, it is above-mentioned when the pressure differential increase between above-mentioned compression chamber 63 and suction pressure chamber 62 shown in such as Fig. 5 (B)
Pressure-sensitive valve body 52 overcomes the active force of helical spring 53 and when into figure, right side is mobile, above-mentioned metering throttle orifice 32 and stage portion 54
Lap gradually decrease, therewith, flowing path section area becomes larger.Moreover, end face 54a and sense in above-mentioned stage portion 54
In the case that the step surface 51c of pressure valve accepting hole 51 is abutted, lap turns into 0, and flowing path section area turns into maximum.
In addition, in the assembling of above-mentioned variable displacement vane pump 1, relative to the state for having been charged into above-mentioned helical spring 53
Under above-mentioned pressure sensitive valve accepting hole 51, from the opening portion side (above-mentioned large diameter hole portion 51a sides) of the pressure sensitive valve accepting hole 51 to bottom
Side is inserted after above-mentioned pressure-sensitive valve body 52, is blocked, is thus assembled using above-mentioned pressing plate 11.
(action effect of present embodiment)
Therefore, according to the variable displacement vane pump 1, for example, when not needing the straight trip of power steering, not scheming to above-mentioned
The major part of the working oil for the rotary valve supply shown will not be for power steering, but is flowed back to above-mentioned fluid reservoir T, therefore, into
The state forced down for the load of power steering gear side.Moreover, in the drain passageway 30 connected therewith with power steering gear
The fluid pressure of working oil also maintains low state, therefore, envelope of the above-mentioned pressure-sensitive valve body 52 (stage portion 54) to metering throttle orifice 32
Stifled amount is big, and flowing path section area is small.That is, as the situation identical state more than the amount of restriction with variable orifice.
Therefore, the differential pressure between the fluid pressure and the fluid pressure in downstream of metering throttle orifice 32 upstream side becomes big, detects
The situation, above-mentioned flow control valve 33 makes cam ring 9 be rolled to the direction diminished relative to the offset of rotor 10, thus, such as
Shown in Fig. 9 dotted line, pump delivery is reduced.
On the other hand, when needing the steering of power steering, the working oil of supply to above-mentioned rotary valve (not shown) will not
Flow back, but supplied to inside the power cylinder as closing space to above-mentioned fluid reservoir T, therefore, power steering gear side it is negative
Lotus pressure rises.
Then, the fluid pressure of the working oil in drain passageway 30 consequently also rises, above-mentioned pressure-sensitive valve body 52 (stage portion 54)
(reference picture 5 (B)) is moved to axial one end side, therefore, the closure amount of metering throttle orifice 32 diminishes, and flowing path section area becomes big.
That is, as the state for mitigating the throttling in variable orifice.
Therefore, the differential pressure between the fluid pressure and the fluid pressure in downstream of metering throttle orifice 32 upstream side diminishes, and detects
The situation, above-mentioned flow control valve 33 makes cam ring 9 be rolled to the big direction of the eccentric quantitative change relative to rotor 10, thus, such as
Fig. 9's is shown in solid, pump delivery increase.
Therefore, when turning to, such as Fig. 9's is shown in solid, the discharge rate of the working oil supplied to above-mentioned power steering gear
Maintain the state of more amount.
But, present embodiment this variable displacement vane pump 1 inside built with above-mentioned pumping element 3, suction
The various structures of path 23 and drain passageway 30 etc, it is difficult to which new structure is set.
Here, as not built-in structured position, the region C shown in the double dot dash line in Fig. 4, but the region can be enumerated
Insert has drive shaft 4 in C, accordingly, it would be desirable to avoid the interference with the drive shaft 4.Therefore, for the mechanism with complicated action
Deng actually becoming wasted space, when setting new structure, inevitably result in the external and pump case 2 with mechanism
The overall maximization of the device of maximization etc..
Therefore,, can be at wasted space by using the forced induction valve 50 for carrying out linearly operating in present embodiment
Installed, obtain the discharge rate for being adapted to power steering gear.
Particularly in the present embodiment, by above-mentioned forced induction valve 50 with along the axial movement of above-mentioned drive shaft 4
Mode is set, and can avoid the interference with the drive shaft 4.
In addition, above-mentioned pressure sensitive valve accepting hole 51 is configured on the circumferencial direction of above-mentioned drive shaft 4 and above-mentioned discharge area
Domain is overlapping.Thus, it can shorten for discharge to be pressed into the stream that above-mentioned pressure sensitive valve accepting hole 51 is guided, therefore, it is possible to further
Save space.
In addition, above-mentioned pressure-sensitive valve body 52 is set into guiding valve, the only weight by changing above-mentioned stage portion 54 and metering throttle orifice 32
The control of folded amount just progress flow path area of section, complication and thing followed device therefore, it is possible to dampening mechanism it is big
Type etc..
Therefore, according to the variable displacement vane pump 1 of present embodiment, energy during for power steering gear can be reduced
Amount loss, while the maximization of restraining device.
In addition, by the another side of above-mentioned pressure sensitive valve accepting hole 51 to be connected via each path groove 57 with above-mentioned discharging area
Mode set, can easily carry out discharge pressure importing.
In addition, in present embodiment, flowing through in the case that the fluid of working oil of above-mentioned drain passageway 30 forces down, it is above-mentioned
The substantially half of the closure metering throttle orifice 32 of stage portion 54, and from the state, with the rising of fluid pressure, 54 pairs of stage portion
The region that metering throttle orifice 32 is blocked is gradually decreased.
If that is, investigate with above-mentioned pressure-sensitive valve body 52 movement flowing path section area change, as shown in Figure 10, with
Substantially straight radial line X is basic point and started in the case of being moved to Y-direction (valve opening position) that change is maximum, from the state, with
Tapered into towards arrow Y leading section.In other words, due to the section circle shape of metering throttle orifice 32, flowing path section area
Rate of change with the working oil for flowing through drain passageway 30 pressure rise and gradually decrease.
Thus, after just being turned to from straight ahead, the rate of change of flowing path section area is big, and flow quickly increases therewith
Greatly, so steering response can be improved.In addition, after just recovering to straight trip from steering, the rate of change of flowing path section area
Smaller, flow is slowly reduced, therefore, it is possible to suppress to turn to sense of discomfort.
In addition, by above-mentioned pressure-sensitive valve body 52 from opening portion side (the above-mentioned large diameter hole portion 51a of above-mentioned pressure sensitive valve accepting hole 51
Side) insertion, blocked using above-mentioned pressing plate 11, so as to be assembled, therefore, there is no need to the seal members, energy such as sealing bolt (plug)
The reduction of enough costs of implementation.
In addition, above-mentioned pressure sensitive valve accepting hole 51 is set close to above-mentioned drive shaft 4, therefore, it is possible to easily carry out with connecting
In the connection of the closure gasket groove 26 of above-mentioned inhalation area.As a result, being configured at the suction of the position separated with above-mentioned inhalation area
The importing for sucking pressure can also be carried out by entering in pressure chamber 62.
In addition, each path groove 57 for being radially oriented otch is provided with the access structure portion 56 of above-mentioned pressure-sensitive valve body 52, because
This, can be from each path groove 57 to compression chamber 63 in the case of being abutted even in above-mentioned access structure portion 56 with above-mentioned pressing plate 11
Import working oil.Input open area when particularly each path groove 57 is formed as importing working oil is big, therefore, it is possible to more effectively
Input service oil.
In addition, in present embodiment, as described above, making the end face 54a of above-mentioned stage portion 54 be formed as tabular surface, making this
Tabular surface is abutted with the step surface 51c of above-mentioned pressure sensitive valve accepting hole 51, limits the regulation to a side of above-mentioned pressure sensitive valve body 52
Movement above.Thereby, it is possible to avoid above-mentioned helical spring 53 by excessive condensation, cause the problem of linear characteristic changes.In addition,
To be sealed between the end face 54a of stage portion 54 and the step surface 51c of pressure sensitive valve accepting hole 51, suppress on high-tension side working oil to
Low pressure side reflux, therefore, it is possible to realize the raising of the efficiency of pump.
In addition, in present embodiment, using the above-mentioned spring retention groove 65 for the one end for being formed at above-mentioned pressure-sensitive valve body 52,
Toppling over for above-mentioned helical spring 53 can be suppressed.In addition, the loop length of above-mentioned helical spring 53 is lengthened equivalent to above-mentioned bullet
The amount of the depth of spring retention groove 65, therefore, it is possible to further suppress the spring performance (line of the compression with the helical spring 53
Property characteristic) change.
In addition, in the case of the maximum load in view of applying to above-mentioned pressure-sensitive valve body 52, if comparing above-mentioned metering
Direction (Fig. 5 right direction) and the direction (Fig. 5 left direction) of diminution that the area of throttle orifice 32 expands, due to above-mentioned drain passageway 30
Discharge pressure maximum rise to safe pressure, therefore, will measure throttle hole area expand direction load it is bigger.That is, due to
Foreign matter etc., the sliding of above-mentioned pressure-sensitive valve body 52 deteriorates and in the case of bonding, above-mentioned pressure-sensitive valve body 52 is with above-mentioned stage portion 54
The states that are abutted with the step surface 51c of pressure sensitive valve accepting hole 51 of end face 54a to bond possibility high.In this condition, due to
Flowing path section area turns into maximum, therefore, in the case of being bonded between both 54a, 51c etc., only it is to obtain
Energy-saving effect is obtained, power steering function remains able to maintain.As a result, can ensure that the continuation of safety operation.
In addition, in present embodiment, making the pressure fluid for flowing through above-mentioned drain passageway 30 while to above-mentioned pressure-sensitive valve body 52
Actuating pressure, directly exports to the downstream of metering throttle orifice 32, therefore, pressure fluid is made from via different streams on one side
Structure of position control of the pressure-sensitive valve body 52 etc. is carried out for above-mentioned pressure-sensitive valve body 52 to compare, and can be simplified in above-mentioned pump case 2
The stream of interior formation.As a result, the simplification of device can be realized.
(second embodiment)
Figure 11~Figure 13 represents second embodiment of the present invention, and basic structure is identical with first embodiment, but conduct
Helical spring 53, employs the spring (nonlinear spring) with nonlinear spring constant.
That is, the helical spring 53 of present embodiment is with least one in the design parameters such as coil diameter, pitch and line footpath
More than the modes of Axial changes of the parameter along the helical spring 53 formed, thus, load on spring F with from natural length
The relation of displacement x (hreinafter referred to as " displacement x ") turns into non-linear.
In addition, Figure 11 and Figure 12 be represent for the load on spring F in one of the helical spring 53 of present embodiment with
The figure of relation between displacement x, Figure 11 represents a side so-called 2 section pitch spring different with the pitch of another side, Figure 12
Represent coil diameter from a side towards another side with the expanding so-called volute spring of taper.
(action effect of second embodiment)
In above-mentioned first embodiment, above-mentioned helical spring 53 has linear characteristic, acts on above-mentioned pressure-sensitive valve body 52
The pressure P of pressure fluid and the amount of movement of path hole portion 51b sides to the pressure-sensitive valve body 52 are generally proportionate.Therefore, with upper
The change for stating the aperture area S (hreinafter referred to as " throttle orifice aperture area S ") of the metering throttle orifice 32 of pressure P rising is special
Property is influenceed greatly by the cross sectional shape (toroidal) of above-mentioned metering throttle orifice 32, when throttle orifice aperture area S is from minimum value SminTo
Maximum SmaxDuring change, change maximum in the initial movement of above-mentioned pressure-sensitive valve body 52, on the other hand, with above-mentioned pressure P
Become mode that is big and gradually decreasing to uniquely determine (single dotted broken line of reference picture 13).
By contrast, in present embodiment, above-mentioned helical spring 53 have nonlinear characteristic, therefore, above-mentioned pressure P and to
The amount of movement of the path hole portion 51b sides of above-mentioned pressure-sensitive valve body 52 does not form proportionate relationship, in specific pressure span, above-mentioned sense
Pressure valve body 52 is significantly moved, or on the contrary, amount of movement is insignificant.
Then, the throttle orifice aperture area S of adjoint above-mentioned pressure P rising variation characteristic is not only by above-mentioned metering section
The influence of the cross sectional shape (circle) of discharge orifice 32, is also changed by the very big influence of the spring performance of above-mentioned helical spring 53.
Thereby, it is possible to which the variation characteristic with the throttle orifice aperture area S of above-mentioned pressure P rising is set into the shown in solid of Figure 13
Unconventional characteristic.
Moreover, the variation characteristic by above-mentioned helical spring 53 by being altered to the spring with different nonlinear characteristics,
Can freely it adjust to a certain extent.
Therefore, according to present embodiment, because basic structure is identical, so can obtain certainly and above-mentioned first embodiment party
Formula identical action effect, using the helical spring 53 of nonlinear characteristic, can open the throttle orifice of the rising with above-mentioned pressure P
Open area S variation characteristic is easily adjusted into desired value, therefore, it is possible to improve the adjustment free degree.
(the 3rd embodiment)
Figure 14 represents third embodiment of the present invention, and basic structure is identical with first embodiment, but changes pump case 2
Structure.In addition, in the following description, pair mark identical symbol with first embodiment identical structure position and save somewhat
The explanation of body.
I.e., as shown in figure 14, the pump case 2 of present embodiment is by forming flat first housing i.e. procapsid 5 and being formed
It is that back casing 6 is constituted for the second housing of bottomed cylindrical.Also, by by the above-mentioned fore shell in opening portion of above-mentioned back casing 6
The inner face of the side of back casing 6 of body 5 is blocked, and internally forms pumping element reception room 2a.
In addition, being changed with the structure of above-mentioned pump case 2, the adaptor ring 8 and above-mentioned back casing 6 of above-mentioned pumping element 3 are constituted
Cylindrical portion 6b inner peripheral surfaces setting-in is fixed, and above-mentioned pressing plate 11 is configured at the bottom wall part 6c of above-mentioned back casing 6, with above-mentioned procapsid
5 clamp above-mentioned cam ring 9 or rotor 10 together.
In addition, e axle supporting makes the one end 4a of its side of procapsid 5 to outside above-mentioned pump case 2 in the drive shaft 4 of above-mentioned pump case 2
Portion is protruded, and is belt wheel 66 provided with drive shaft transfer part in the protuberance.Above-mentioned belt wheel 66 will be via belt (not shown) etc.
The power of the engine of transmission is transmitted to above-mentioned drive shaft 4, thus the rotation driving drive shaft 4.
In addition, being changed with the structure of above-mentioned pump case 2, the arranging position of the flow control valve 33 of present embodiment is changed to
The cylindrical portion 6b of above-mentioned back casing 6 upper end.
In addition, the forced induction valve 50 of present embodiment changes also with the structure of above-mentioned pump case 2 and changes its disposed portion
Position.That is, the forced induction valve 50 of present embodiment makes its pressure sensitive valve accepting hole 51 be disposed in the midway of above-mentioned drain passageway 30, and
And the above-mentioned rotor 10 of ratio that pressure sensitive valve accepting hole 51 is disposed in the axial direction of the above-mentioned drive shaft 4 of above-mentioned procapsid 5 is more by above-mentioned
The position of the side of belt wheel 66.
In addition, the other structures and annexation and first embodiment of above-mentioned flow control valve 33 and forced induction valve 50
It is identical, therefore, omit specific description.
(action effect of the 3rd embodiment)
The basic structure of the embodiment is also identical with first embodiment, therefore, using above-mentioned forced induction valve 50,
Need that pump delivery can be increased during the steering of larger power steering, or can be reduced when not needing the straight trip of power steering
Pump delivery.Thus, pump delivery is become suitable according to operating condition, the energy loss of pump work can be reduced.
In addition, in present embodiment, from the bearing (not shown) avoided with the above-mentioned drive shaft 4 or e axle supporting drive shaft 4
Deng interference from the viewpoint of, region C (double dot dash line in reference picture 14) near the drive shaft 4 of above-mentioned procapsid 5 for
Mechanism along with compound action etc. turns into actual wasted space, and is carried out directly by turning into above-mentioned forced induction valve 50
The simple structure of line movement, and be disposed in above-mentioned zone C, it can suppress to set caused by above-mentioned forced induction valve 50
Device maximization.
The invention is not restricted to the structure of the respective embodiments described above, it can also change without departing from the spirit and scope of the invention
Structure.
For example, in the respective embodiments described above, entering to the cross sectional shape of above-mentioned metering throttle orifice 32 is set into circular situation
Explanation is gone, but as long as being to rise caused pressure-sensitive valve body 52 with the pressure for the working oil for flowing through above-mentioned drain passageway 30
Mobile, the shape that the rate of change of flowing path section area is gradually decreased can also be formed at section diamond shape etc..
In addition, above-mentioned forced induction valve 50 is formed at into the metering throttle orifice 32 on above-mentioned drain passageway 30 as change
The valve body of flowing path section area is illustrated, but can also abolish the metering throttle orifice 32, directly changes drain passageway 30
Flowing path section area.
In addition, in the respective embodiments described above, illustrating to make the pressure fluid of the flowing in above-mentioned drain passageway 30 right on one side
The above-mentioned actuating pressure of pressure-sensitive valve body 52, is directly exported to the downstream of metering throttle orifice 32 on one side, but also can be by above-mentioned pressure
Inductance valve 50 is set to pilot valve, then sets the pilot flow path from the branch of drain passageway 30, by the pressure for flowing into the pilot flow path
The first pilot of fluid moves pressure-sensitive valve body 52, thus, by the pressure fluid of the flowing in drain passageway 30 indirectly to metering
The downstream export of throttle orifice 32.
In addition, in the respective embodiments described above, the stop portion of movement to a side of above-mentioned pressure sensitive valve body 52 will be limited
Not She Yu the above-mentioned side (end face 54a) of pressure-sensitive valve body 52 and the side (step surface 51c) of pressure sensitive valve accepting hole 51, as long as but stopper section set
In either one of above-mentioned pressure-sensitive valve body 52 and pressure sensitive valve accepting hole 51.
In addition, illustrate by make above-mentioned cam ring 9 above-mentioned tabular seal member 12 upper surface roll, make relative to
The embodiment of the offset increase and decrease of above-mentioned rotor 10, but as long as being movably disposed in above-mentioned pumping element reception room 2a, method
With regard to not limited to this, for example, also above-mentioned position retaining pin 17 can be set into swing pivot, offset is changed by swinging.
Claims (20)
1. a kind of variable displacement vane pump, supplies working solution, it is characterised in that possess to the power steering gear of vehicle：
Pump case, it is made up of the first housing and the second housing, and has in the inside of the rwo pumping element resettlement section, described
The bottom wall part that one housing is had cylindrical portion and set in the way of the one end open for blocking the cylindrical portion, second housing is to seal
The mode for blocking up another end opening of the cylindrical portion is set；
Drive shaft, it is inserted through in the pump case, is rotated freely ground axle suspension；
Rotor, it is contained in the pumping element resettlement section, has been circumferentially formed thereon multiple slits, and by the drive shaft
Rotation driving；
Blade, it comes in and goes out is located at the slit freely；
The cam ring of ring-type, it is movably disposed in the pumping element resettlement section, the shape together with the rotor and the blade
Into multiple pump chambers；
Suction inlet, its be located at the pump case, into the multiple pump chamber with the rotation of the rotor what volume gradually increased
Inhalation area opening；
Outlet, its be located at the pump case, into the multiple pump chamber with the rotation of the rotor what volume was gradually decreased
Discharging area opening；
Suction passage, it is located at the pump case, the working solution for being stored in fluid reservoir is supplied to the suction inlet；
Drain passageway, it is located at the pump case, working solution being externally supplied to the pump case that will be discharged from the outlet；
First fluid balancing gate pit and second fluid balancing gate pit, are respectively arranged on the outer circumferential side of the cam ring, in the cam ring
In the case of the direction movement increased relative to the offset of the rotor, the first fluid balancing gate pit is formed at volume reducing
Side, the second fluid balancing gate pit be formed at volume increase side；
First valve accepting hole, it is located at the bottom wall part of first housing and the midway of the drain passageway；
First valve body, it is movably disposed in the first valve accepting hole, is pressed and from institute based on the suction for acting on a side
The differential pressure discharged between pressure stated drain passageway importing and act on another side moves control, and with mobile change
The flowing path section area of the drain passageway；
Second valve accepting hole, it is located at the pump case；
Hyperbaric chamber and control pressure chamber, the hyperbaric chamber are located at a side of the second valve accepting hole, to connect with the outlet
Logical mode is formed, and the control pressure chamber is located at the another side of the second valve accepting hole, with the institute with the drain passageway
The mode for stating the further downstream connection of the first valve accepting hole is formed；
Second valve body, it is movably disposed in the second valve accepting hole, pressure and the control based on the hyperbaric chamber
Differential pressure between the pressure of pressure chamber controls the pressure of the first fluid balancing gate pit.
2. variable displacement vane pump as claimed in claim 1, it is characterised in that
First valve body is arranged along the axial movement of the drive shaft.
3. variable displacement vane pump as claimed in claim 1, it is characterised in that
The first valve accepting hole is configured to opening portion side and connected with the discharging area.
4. variable displacement vane pump as claimed in claim 3, it is characterised in that
The first valve accepting hole is provided in overlapping with the discharging area on the circumferencial direction of the drive shaft.
5. variable displacement vane pump as claimed in claim 4, it is characterised in that
First valve body is inserted from the opening portion side of the first valve accepting hole.
6. variable displacement vane pump as claimed in claim 4, it is characterised in that
The pump case has：
Seal member resettlement section, it houses to be circumferentially formed the outer circumferential side of the drive shaft and seals the pump case and the drive
Seal member between moving axis；
Low pressure access, it connects the seal member resettlement section with the inhalation area；
Low pressure imports road, and it connects a side of the first valve accepting hole with the seal member resettlement section.
7. variable displacement vane pump as claimed in claim 1, it is characterised in that
First valve body is guiding valve, with step, is changed by changing the lap between the step and the drain passageway
Become the flowing path section area of the drain passageway.
8. variable displacement vane pump as claimed in claim 7, it is characterised in that
The groove portion for being radially oriented and cutting and being formed is formed with the another side of first valve body.
9. variable displacement vane pump as claimed in claim 7, it is characterised in that
With the spring members exerted a force to first valve body to another side,
First valve body at one end portion have limitation to one end side to movement stopper section.
10. variable displacement vane pump as claimed in claim 9, it is characterised in that
The spring members are helical spring,
Side has the spring maintaining part for housing the part for keeping the spring members to first valve body at one end.
11. variable displacement vane pump as claimed in claim 9, it is characterised in that
First valve body is formed as, and when limiting mobile using the stopper section, the flowing path section area turns into maximum.
12. variable displacement vane pump as claimed in claim 7, it is characterised in that
The drain passageway is formed as, and the pressure with the discharge pressure for the another side for acting on first valve body rises, institute
The rate of change for stating flowing path section area is gradually decreased.
13. variable displacement vane pump as claimed in claim 1, it is characterised in that
Possess spring members, the spring members exert a force in the first valve accepting hole to first valve body,
The spring members have nonlinear spring constant.
14. variable displacement vane pump as claimed in claim 1, it is characterised in that
The working solution that first valve body will act on another side swims side export directly down.
15. variable displacement vane pump as claimed in claim 1, it is characterised in that
The first valve accepting hole is configured to its bottom side and connected with the suction passage.
16. a kind of variable displacement vane pump, supplies working solution, it is characterised in that possess to the power steering gear of vehicle：
Pump case, it is made up of the first housing and the second housing, and has in the inside of the rwo pumping element resettlement section, described
One housing formation tabular, second housing is had a cylindrical portion and set in the way of the one end open for blocking the cylindrical portion
Bottom wall part, another end opening of the cylindrical portion is blocked using first housing；
Drive shaft, it is inserted through in the pump case, is rotated freely ground axle suspension；
Drive shaft transfer part, it is located in the drive shaft to the outside prominent part of the pump case, by the power of outside to
The drive shaft transmission；
Rotor, it is contained in the pumping element resettlement section, has been circumferentially formed thereon multiple slits, and by the drive shaft
Rotation driving；
Blade, it comes in and goes out is located at the slit freely；
The cam ring of ring-type, it is movably disposed in the pumping element resettlement section, the shape together with the rotor and the blade
Into multiple pump chambers；
Suction inlet, its be located at the pump case, into the multiple pump chamber with the rotation of the rotor what volume gradually increased
Inhalation area opening；
Outlet, its be located at the pump case, into the multiple pump chamber with the rotation of the rotor what volume was gradually decreased
Discharging area opening；
Suction passage, it is located at the pump case, the working solution for being stored in fluid reservoir is supplied to the suction inlet；
Drain passageway, it is located at the pump case, working solution being externally supplied to the pump case that will be discharged from the outlet；
First fluid balancing gate pit and second fluid balancing gate pit, are respectively arranged on the outer circumferential side of the cam ring, in the cam ring
In the case of the direction movement increased relative to the offset of the rotor, the first fluid balancing gate pit is formed at volume reducing
Side, the second fluid balancing gate pit be formed at volume increase side；
First valve accepting hole, its be located in first housing in the axial direction of the drive shaft than the rotor more by described
The position of drive shaft transfer part side and the midway of the drain passageway；
First valve body, it is movably disposed in the first valve accepting hole, is pressed and from institute based on the suction for acting on a side
The differential pressure discharged between pressure stated drain passageway importing and act on another side moves control, and with mobile change
The flowing path section area of the drain passageway；
Second valve accepting hole, it is located at the pump case；
Hyperbaric chamber and control pressure chamber, the hyperbaric chamber are located at a side of the second valve accepting hole, to connect with the outlet
Logical mode is formed, and the control pressure chamber is located at the another side of the second valve accepting hole, with the institute with the drain passageway
The mode for stating the further downstream connection of the first valve accepting hole is formed；
Second valve body, it is movably disposed in the second valve accepting hole, pressure and the control based on the hyperbaric chamber
Differential pressure between the pressure of pressure chamber controls the pressure of the first fluid balancing gate pit.
17. variable displacement vane pump as claimed in claim 16, it is characterised in that
First valve body is arranged along the axial movement of the drive shaft.
18. variable displacement vane pump as claimed in claim 16, it is characterised in that
The first valve accepting hole is configured to opening portion side and connected with the discharging area.
19. variable displacement vane pump as claimed in claim 18, it is characterised in that
The first valve accepting hole is provided in overlapping with the discharging area on the circumferencial direction of the drive shaft.
20. a kind of variable displacement vane pump, supplies working solution, it is characterised in that possess to the power steering gear of vehicle：
Pump case, it is made up of the first housing and the second housing, and has in the inside of the rwo pumping element resettlement section, described
The bottom wall part that one housing is had cylindrical portion and set in the way of the one end open for blocking the cylindrical portion, second housing is to seal
The mode for blocking up another end opening of the cylindrical portion is set；
Drive shaft, it is inserted through in the pump case, is rotated freely ground axle suspension；
Rotor, it is contained in the pumping element resettlement section, has been circumferentially formed thereon multiple slits, and by the drive shaft
Rotation driving；
Blade, it comes in and goes out is located at the slit freely；
The cam ring of ring-type, it is movably disposed in the pumping element resettlement section, the shape together with the rotor and the blade
Into multiple pump chambers；
Suction inlet, its be located at the pump case, into the multiple pump chamber with the rotation of the rotor what volume gradually increased
Inhalation area opening；
Outlet, its be located at the pump case, into the multiple pump chamber with the rotation of the rotor what volume was gradually decreased
Discharging area opening；
Suction passage, it is located at the pump case, the working solution for being stored in fluid reservoir is supplied to the suction inlet；
Drain passageway, it is located at the pump case, working solution being externally supplied to the pump case that will be discharged from the outlet；
First fluid balancing gate pit and second fluid balancing gate pit, are respectively arranged on the outer circumferential side of the cam ring, in the cam ring
In the case of the direction movement increased relative to the offset of the rotor, the first fluid balancing gate pit is formed at volume reducing
Side, the second fluid balancing gate pit be formed at volume increase side；
First valve accepting hole, it is located at the bottom wall part of first housing and the midway of the drain passageway；
First valve body, it is movably disposed in the first valve accepting hole, is pressed and from institute based on the suction for acting on a side
The differential pressure discharged between pressure stated drain passageway importing and act on another side moves control, and while with movement
Change the flowing path section area of the drain passageway, while exporting the working solution acted on to another side；
Second valve accepting hole, it is located at the pump case；
Hyperbaric chamber and control pressure chamber, the hyperbaric chamber are located at a side of the second valve accepting hole, to connect with the outlet
Logical mode is formed, and the control pressure chamber is located at the another side of the second valve accepting hole, with the institute with the drain passageway
The mode for stating the further downstream connection of the first valve accepting hole is formed；
Second valve body, it is movably disposed in the second valve accepting hole, pressure and the control based on the hyperbaric chamber
Differential pressure between the pressure of pressure chamber controls the pressure of the first fluid balancing gate pit.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2014-236059 | 2014-11-21 | ||
| JP2014236059 | 2014-11-21 | ||
| PCT/JP2015/079106 WO2016080113A1 (en) | 2014-11-21 | 2015-10-15 | Variable capacity vane pump |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN107076142A true CN107076142A (en) | 2017-08-18 |
Family
ID=56013671
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201580056627.1A Pending CN107076142A (en) | 2014-11-21 | 2015-10-15 | Variable displacement vane pump |
Country Status (5)
| Country | Link |
|---|---|
| US (1) | US20170314555A1 (en) |
| JP (1) | JP6251822B2 (en) |
| CN (1) | CN107076142A (en) |
| DE (1) | DE112015005251T5 (en) |
| WO (1) | WO2016080113A1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108843562A (en) * | 2018-06-25 | 2018-11-20 | 东台帕瓦环保节能科技有限公司 | A kind of energy-saving anti-return hydraulic pump |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102015111344A1 (en) * | 2015-07-14 | 2017-01-19 | Robert Bosch Automotive Steering Gmbh | PULSATION CONTROLLED BEAD MOTOR STEERING |
| WO2020157618A1 (en) | 2019-01-31 | 2020-08-06 | Stackpole International Engineered Products, Ltd. | Panic valve integrated in pivot pin of pump |
| US11421685B2 (en) | 2019-04-23 | 2022-08-23 | Stackpole International Engineered Products, Ltd. | Vane pump with improved seal assembly for control chamber |
| GB2583542B (en) * | 2019-05-03 | 2021-10-13 | Leybold France S A S | Pump with exhaust valve |
| CA3140286A1 (en) | 2019-05-20 | 2020-11-26 | Stackpole International Engineered Products, Ltd. | Spool valve used in a variable vane pump |
Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1392345A (en) * | 2001-06-18 | 2003-01-22 | 尤尼西亚Jkc控制系统株式会社 | Variable pump controller for power turning device |
| JP2003176791A (en) * | 2001-12-11 | 2003-06-27 | Kayaba Ind Co Ltd | Variable displacement vane pump |
| CN1464197A (en) * | 2002-06-13 | 2003-12-31 | 尤尼西亚Jkc控制系统株式会社 | Variable delivery pump |
| JP2004293414A (en) * | 2003-03-27 | 2004-10-21 | Kayaba Ind Co Ltd | Variable capacity vane-pump and pressure supply device |
| US20090081052A1 (en) * | 2007-09-21 | 2009-03-26 | Hitachi, Ltd. | Variable displacement pump |
| JP2012145095A (en) * | 2010-12-21 | 2012-08-02 | Aisin Seiki Co Ltd | Oil pump |
| CN104295490A (en) * | 2013-07-17 | 2015-01-21 | 日立汽车系统株式会社 | Variable displacement pump |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE19846815B4 (en) * | 1997-10-16 | 2014-08-07 | Ixetic Bad Homburg Gmbh | Valve assembly and pump for a transmission |
| JP5065919B2 (en) * | 2008-01-15 | 2012-11-07 | 日立オートモティブシステムズ株式会社 | Pump device |
| JP5154469B2 (en) * | 2009-02-17 | 2013-02-27 | 日立オートモティブシステムズ株式会社 | Variable displacement pump and power steering device using the same |
-
2015
- 2015-10-15 US US15/520,195 patent/US20170314555A1/en not_active Abandoned
- 2015-10-15 WO PCT/JP2015/079106 patent/WO2016080113A1/en active Application Filing
- 2015-10-15 CN CN201580056627.1A patent/CN107076142A/en active Pending
- 2015-10-15 JP JP2016560114A patent/JP6251822B2/en active Active
- 2015-10-15 DE DE112015005251.8T patent/DE112015005251T5/en not_active Withdrawn
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1392345A (en) * | 2001-06-18 | 2003-01-22 | 尤尼西亚Jkc控制系统株式会社 | Variable pump controller for power turning device |
| JP2003176791A (en) * | 2001-12-11 | 2003-06-27 | Kayaba Ind Co Ltd | Variable displacement vane pump |
| CN1464197A (en) * | 2002-06-13 | 2003-12-31 | 尤尼西亚Jkc控制系统株式会社 | Variable delivery pump |
| JP2004293414A (en) * | 2003-03-27 | 2004-10-21 | Kayaba Ind Co Ltd | Variable capacity vane-pump and pressure supply device |
| US20090081052A1 (en) * | 2007-09-21 | 2009-03-26 | Hitachi, Ltd. | Variable displacement pump |
| JP2012145095A (en) * | 2010-12-21 | 2012-08-02 | Aisin Seiki Co Ltd | Oil pump |
| CN104295490A (en) * | 2013-07-17 | 2015-01-21 | 日立汽车系统株式会社 | Variable displacement pump |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108843562A (en) * | 2018-06-25 | 2018-11-20 | 东台帕瓦环保节能科技有限公司 | A kind of energy-saving anti-return hydraulic pump |
Also Published As
| Publication number | Publication date |
|---|---|
| JPWO2016080113A1 (en) | 2017-05-25 |
| US20170314555A1 (en) | 2017-11-02 |
| WO2016080113A1 (en) | 2016-05-26 |
| DE112015005251T5 (en) | 2017-08-10 |
| JP6251822B2 (en) | 2017-12-20 |
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Legal Events
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|---|---|---|---|
| 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: 20170818 |