CN103671092A - Vane pump with variable capacity - Google Patents
Vane pump with variable capacity Download PDFInfo
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- CN103671092A CN103671092A CN201310380464.5A CN201310380464A CN103671092A CN 103671092 A CN103671092 A CN 103671092A CN 201310380464 A CN201310380464 A CN 201310380464A CN 103671092 A CN103671092 A CN 103671092A
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- Prior art keywords
- pressure
- stator
- pump
- housing
- chamber
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
- F04C28/24—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, 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 group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
- F04C18/344—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, 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 group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
- F04C28/18—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by varying the volume of the working chamber
- F04C28/22—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
- F04C29/124—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2210/00—Fluid
- F04C2210/22—Fluid gaseous, i.e. compressible
-
- 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
- F04C2240/30—Casings or housings
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10S415/00—Rotary kinetic fluid motors or pumps
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10S417/00—Pumps
Abstract
The invention provides a vane pump with variable capacity. The vane pump with variable capacity can easily form a pressure introduction channel and a pressure discharge channel which are connected with a pressure switch. In the vane pump with variable capacity, a high pressure introduction channel for introducing high pressure to a control valve and a high pressure introduction channel leading to the pressure switch are partially shared.
Description
Technical field
The present invention relates to a kind of variable displacement vane pump.
Background technique
In the past, in the technology of recording at patent documentation 1, in oil hydraulic circuit, there is pressure switch, in oil hydraulic circuit, become the pressure of regulation when above, for the engine speed of avoiding engine load increase to follow reduces, make to improve the device action of engine speed, prevent thus engine stall.
Patent documentation 1:(Japan) Unexamined Patent 9-180607 communique
At this, in the technology of recording at patent documentation 1, in the situation that the pressure switch that makes the type that piston slides by pressure is set, need to import for detection of the pressure of the pressure of high pressure road and the pressure of the clearance leakage from slide part is discharged to low voltage section return to road.Yet, the in the situation that of variable displacement vane pump, aspect the structure that cam is swung, with respect to core bag (カ ー ト リ ッ ジ) sense of rotation, half is configured to suction side, second half is configured to outlet side, therefore, is difficult to be formed for pressure is imported and discharges with pressure the oil path structure that the two is connected.
Summary of the invention
The object of the present invention is to provide a kind of variable displacement vane pump, this variable displacement vane pump can easily form the pressure being connected with pressure switch and import path and pressure drain passageway.
In order to reach above-mentioned purpose, in the present invention, in variable displacement vane pump, the high pressure importing road that imports high pressure to control valve is partly shared with the high pressure importing road of leading to pressure switch.
Particularly, a kind of variable displacement vane pump of the present invention has: pump case, it consists of the first housing and the second housing, and described the first housing has the bottom of an axial side of cylindrical portion and the described cylindrical portion of sealing, the described axial opposite side of cylindrical portion described in described the second housings close; Live axle, its axle is supported on described pump case; The stator of ring-type, it is located in described cylindrical portion in the mode that can move; Rotor, it is located in described stator, by described drive shaft, is rotated; Slit, its week at described rotor is upwards formed with a plurality of; Blade, it is given prominence to, submerges and is located at freely in described slit, is separated into a plurality of pump chambers together with described stator and described rotor; Platen, it is located between the described bottom and described stator in described cylindrical portion, from the delivery pressure of described pump chamber output, to described stator side, is pushed; First fluid pressure chamber and second fluid pressure chamber, it is the space being formed between the inwall of described cylindrical portion and the outer circumferential face of described stator, described first fluid pressure chamber is located at along with to described stator, the direction with respect to the offset increase of described running shaft moves, one side of volume reducing, described second fluid pressure chamber is located at along with to described stator, the direction with respect to the offset increase of described running shaft moves, the side that volume increases; Suction port, it is located in described pump case, to the rotation along with described rotor, the suction region opening that in described a plurality of pump chambers, volume increases; Delivery outlet, it is located on described platen, to the rotation along with described rotor, the output area opening of volume reducing in described a plurality of pump chambers; Suck path, it is located at described pump case, is connected with described suction port; Hyperbaric chamber, it is located at described the first housing, at the length direction of described live axle, is configured in and the opposed position of described delivery outlet on axially, in the mode being communicated with described delivery outlet, forms; Pressure switch, it is located at the described suction area side of described the first housing, detects delivery pressure; High pressure imports road, and it is located at described the first housing, and a distolateral and described hyperbaric chamber is connected, and another distolateral and described pressure switch is connected; Control valve receiving bore, it is located at described pump case with the radial outside in described stator and with respect to the mode that described live axle is more positioned at described suction area side; Tributary circuit, out, and distolateral and a described high pressure importing road is connected in its Tu Zhong branch that imports road from described high pressure, and another distolateral and described control valve receiving bore is connected; Control valve, it is contained in described control valve receiving bore, comprise guiding valve, the delivery pressure from described delivery outlet based on importing via described tributary circuit is controlled described guiding valve, and in order to control the offset of described stator, controls the pressure of described first fluid pressure chamber or described second fluid pressure chamber.
In addition, another kind of variable displacement vane pump of the present invention comprises: pump case, it consists of the first housing and the second housing, and described the first housing has the bottom of an axial side of cylindrical portion and the described cylindrical portion of sealing, the described axial opposite side of cylindrical portion described in described the second housings close; Live axle, its axle is supported on described pump case; The stator of ring-type, it is located in described cylindrical portion in the mode that can move; Rotor, it is located in described stator, by described drive shaft, is rotated; Slit, its week at described rotor is upwards formed with a plurality of; Blade, it is given prominence to, submerges and is located at freely in described slit, is separated into a plurality of pump chambers together with described stator and described rotor; Platen, it is located between the described bottom and described stator in described cylindrical portion, from the delivery pressure of described pump chamber output, to described stator side, is pushed; First fluid pressure chamber and second fluid pressure chamber, it is the space being formed between the inwall of described cylindrical portion and the outer circumferential face of described stator, described first fluid pressure chamber is located at along with to described stator, the direction with respect to the offset increase of described running shaft moves, one side of volume reducing, described second fluid pressure chamber is located at along with to described stator, the direction with respect to the offset increase of described running shaft moves, the side that volume increases; Suction port, it is located in described pump case, to the rotation along with described rotor, the suction region opening that in described a plurality of pump chambers, volume increases; Delivery outlet, it is located on described platen, to the rotation along with described rotor, the output area opening of volume reducing in described a plurality of pump chambers; Suck path, it is located at described pump case, is connected with described suction port; Hyperbaric chamber, it is located at described the first housing, at the length direction of described live axle, is configured in and the opposed position of described delivery outlet on axially, in the mode being communicated with described delivery outlet, forms; Pressure switch, it is located at the described suction area side of described the first housing, detects delivery pressure; High pressure imports road, and it is located at described the first housing, and a distolateral and described hyperbaric chamber is connected; Control valve receiving bore, it is located at described pump case with the radial outside in described stator and with respect to the mode that described live axle is more positioned at described suction area side; Tributary circuit, out, and distolateral and a described high pressure importing road is connected in its Tu Zhong branch that imports road from described high pressure, and another distolateral and described control valve receiving bore is connected; Control valve, it is contained in described control valve receiving bore, comprise guiding valve, the delivery pressure from described delivery outlet based on importing via described tributary circuit is controlled described guiding valve, and in order to control the offset of described stator, controls the pressure of described first fluid pressure chamber or described second fluid pressure chamber; Recess is installed, and it is formed through to the outside of described the first housing, and described pressure switch is arranged on to its outer openings part; Pressure switch imports road with high pressure, and one is distolateral to be connected with the described control valve receiving bore that is imported into described delivery pressure, and another distolateral bottom opening at described installation recess, is connected with described pressure switch; Drain passageway, it is connected with described suction passage side at the bottom opening of described installation recess.
Therefore, can be in the situation that not causing loop structure to complicate setting pressure switch.
Accompanying drawing explanation
Fig. 1 means embodiment 1 the plan view of the variable displacement vane pump of hydraulic power steering apparatus for vehicle that is applicable to.
Fig. 2 means embodiment 1 the rear view of the variable displacement vane pump of hydraulic power steering apparatus for vehicle that is applicable to.
Fig. 3 means embodiment 1 the right elevation of the variable displacement vane pump of hydraulic power steering apparatus for vehicle that is applicable to.
Fig. 4 means embodiment 1 the plan view of the variable displacement vane pump of hydraulic power steering apparatus for vehicle that is applicable to.
Fig. 5 is the X-X sectional view of embodiment 1 variable displacement vane pump.
Fig. 6 is the Y-Y sectional view of embodiment 1 variable displacement vane pump.
Fig. 7 is the A-A sectional view of embodiment 1 variable displacement vane pump.
Fig. 8 is the B-B sectional view of embodiment 1 variable displacement vane pump.
Fig. 9 is the A-A sectional view of embodiment 2 variable displacement vane pump.
Figure 10 is the B-B sectional view of embodiment 2 variable displacement vane pump.
Figure 11 means embodiment 3 the right elevation of the variable displacement vane pump of hydraulic power steering apparatus for vehicle that is applicable to.
Figure 12 means embodiment 3 the plan view of the variable displacement vane pump of hydraulic power steering apparatus for vehicle that is applicable to.
Figure 13 is the B-B sectional view of embodiment 3 variable displacement vane pump.
Figure 14 means embodiment 4 the plan view of the variable displacement vane pump of hydraulic power steering apparatus for vehicle that is applicable to.
Figure 15 means embodiment 4 the rear view of the variable displacement vane pump of hydraulic power steering apparatus for vehicle that is applicable to.
Figure 16 means embodiment 4 the right elevation of the variable displacement vane pump of hydraulic power steering apparatus for vehicle that is applicable to.
Figure 17 means embodiment 4 the plan view of the variable displacement vane pump of hydraulic power steering apparatus for vehicle that is applicable to.
Figure 18 is the A-A sectional view of embodiment 4 variable displacement vane pump.
Figure 19 is the B-B sectional view of embodiment 4 variable displacement vane pump.
Figure 20 means embodiment 5 the plan view of the variable displacement vane pump of hydraulic power steering apparatus for vehicle that is applicable to.
Figure 21 means embodiment 5 the right elevation of the variable displacement vane pump of hydraulic power steering apparatus for vehicle that is applicable to.
Figure 22 means embodiment 5 the plan view of the variable displacement vane pump of hydraulic power steering apparatus for vehicle that is applicable to.
Figure 23 is the A-A sectional view of embodiment 5 variable displacement vane pump.
Description of reference numerals
1 variable displacement vane pump
2 precursors
2a inner bottom surface
2b cylindrical portion
3 rear bodies
4 pump housings
4a holding space
5 pump unit
6 live axles
7 rotors
7a slit
7b back pressure chamber
8 stators
9 adapter rings
10 platens
10a sucks path
14a first fluid pressure chamber
14b second fluid pressure chamber
16 blades
17 pump chambers
18 inlet holes
19c1 switch pin insert port
19d1 sealed member
19a sucks path
19b output channel
19c the first high pressure imports road
19d the second high pressure imports road
19e output channel
20 suction pipes
22 current return circuits
23,25 delivery outlets
24a the first pressure chamber
24b the second pressure chamber
26 control valves
27 connectors
28 control valve receiving bores
28a hyperbaric chamber
Pressure chamber in 28b
28c low pressure chamber
29 guiding valves
30 control valve springs
31 low-pressure passage
32 access
40 pressure switches
41 switch pins
42 terminal components
43 springs
44 switch case
50 variable metering orifices
70 belt wheels
201 install recess
401 drain passageways
401a drain passageway
Embodiment
(embodiment 1)
Fig. 1～Fig. 4 means embodiment 1 the figure of the variable displacement vane pump of hydraulic power steering apparatus for vehicle that is applicable to.Fig. 1 is plan view, and Fig. 2 is rear view, and Fig. 3 is right elevation, and Fig. 4 is plan view.Variable displacement vane pump 1 consists of precursor 2 and 3 two main bodys of rear body, and variable metering orifice 50 described later is arranged on precursor 2 by bolt from main body outside.In addition, at the first high pressure that sucks area side and form to control valve 26 sides from pump unit 5, import the elongation line of road 19c, pressure switch 40 is installed.Below, be elaborated.
Fig. 5, Fig. 6 are the sectional views of embodiment 1 variable displacement vane pump.Fig. 5 is the X-X sectional view of Fig. 4, and Fig. 6 is the Y-Y sectional view of Fig. 4.In holding space 4a in the pump housing 4 that variable displacement vane pump 1 forms in 3 docking of precursor 2 and rear body, hold pump unit 5, by utilizing through live axle 6 driven pump unit 5 rotations of holding space 4a, carry out pump action.Belt wheel 70 is installed on live axle 6, utilizes the band being erected on not shown engine crankshaft to drive live axle 6 rotations.Precursor 2 has the inner bottom surface 2a of cylindrical portion 2b and the conduct bottom of an axial side of sealing cylindrical portion 2b, by forming with the axial opposite side of rear body 3 sealing cylindrical portion 2b the holding space 4a that holds pump unit 5.
Pump unit 5 has rotor 7, roughly circular stator 8, roughly circular adapter ring 9 and discoid platen 10 roughly, rotor 7 links with live axle 6, by this live axle 6, drive rotation, stator 8 is located at the outer circumferential side of this rotor 7, in the direction that the offset of this rotor 7 changes relatively, swing freely, the chimeric periphery barrel surface that is installed on holding space 4a of adapter ring 9, is contained in inner circumferential side by this stator 8, and platen 10 is configured on the inner bottom surface 2a of precursor 2 in accommodation space 4a.
At the peripheral part of rotor 7, be circumferentially provided with to equal intervals a plurality of slit 7a that radially cutting forms.The mode that the blade 16 of substantially planar is upwards freely given prominence to, submerged with the footpath at rotor 7 is respectively contained in each slit 7a, by utilize above-mentioned each blade 16 by the annulus between stator 8 and rotor 7 along circumferentially spaced, form a plurality of pump chambers 17.And, by utilizing live axle 6 to drive rotor 7 rotations to the counter clockwise direction in Fig. 2, while each pump chamber 17 makes its volume increase and decrease occur respectively along circumferentially mobile, carry out pump action.In addition, each blade 16 is imported into the pressure of the working oil in back pressure chamber 7b to the inner peripheral surface pushing of stator 8, guarantees the liquid-tight property of pump chamber 17, and back pressure chamber 7b is formed on the inner circumferential side of each slit 7a.
In rear body 3 in the face of on the inner side surface 3a of holding space 4a, the suitable part in suction region expanding gradually along with the rotation of rotor 7 at the volume of each pump chamber 17, cutting is formed with along circumferentially positive apparent time and is roughly meniscate the first inlet hole 18.And this first inlet hole 18 is communicated with the suction path 19a being opened on rear body 3.Thus, the suction pipe 20 being connected via the storage tank with not shown imports to the working oil sucking in path 19a, and the pumping suction effect by above-mentioned suction region is inhaled in each pump chamber 17.
In platen 10 with opposed of rotor 7 on, with the first opposed position of inlet hole 18, cutting is formed with this first inlet hole 18 and is roughly identical shaped the second inlet hole 21.And this second inlet hole 21 is communicated with the current return circuit 22 that is formed on the elliptical shape on precursor 2.This current return circuit 22 is communicated with the recess that sealing precursor 2 is held with sealed member between live axle 6 in precursor 2, by the pumping suction effect by above-mentioned suction region, to each pump chamber 17, supply with the residual oil of above-mentioned sealed member, prevent that above-mentioned residual oil from spilling to outside.
And, in platen 10 with opposed of rotor 7 on, the volume of each pump chamber 17 along with the rotation of rotor 7 the suitable part of diminishing output area, cutting is formed with along circumferentially positive apparent time and is roughly meniscate the first delivery outlet 23.And this first delivery outlet 23 in precursor 2 is communicated with output channel 19b with the first 24a of pressure chamber on the opposed inner bottom surface 2a of platen 10 via recessed being arranged on, and is communicated with the first high pressure importing road 19c via the second 24b of pressure chamber.Thus, by the pumping output action of above-mentioned output area from the working oil of each pump chamber 17 outputs by the first 24a of pressure chamber and output channel 19b and via variable metering orifice 50, via output channel 19e, to the outer output of the pump housing 4, send into the fluid power cylinder of not shown power steering gear.
At this, variable metering orifice 50 is configured to and can, by making guiding valve utilize electromagnetic force to move to change the amount of restriction (throttle diameter) in path, thus, by freely setting with respect to the pressure drop characteristic of flow, seeks controlled raising.In addition, platen 10 is pressed to rotor 7 thrusters by the pressure in the 24a of first and second pressure chamber, 24b.
In addition, in the inner side surface 3a of rear body 3, with the first opposed position of delivery outlet 23, cutting is formed with this first delivery outlet 23 and is roughly identical shaped the second delivery outlet 25.So, by symmetrical vertically mode, first, second inlet hole 18,21 and first, second delivery outlet 23,25 being set across each pump chamber 17, guaranteed the pressure balance of above-mentioned each pump chamber 17 axial both sides.
Fig. 7, Fig. 8 are the sectional views of embodiment 1 variable displacement vane pump.Fig. 7 is the A-A sectional view of Fig. 4, and Fig. 8 is the B-B sectional view of Fig. 4.As shown in Figure 7, Figure 8, the second 24b of pressure chamber imports road 19c with the first high pressure and is connected, and this first high pressure imports road 19c and platen 10 is opened in precursor 2 abreast.And the second 24b of pressure chamber imports road 19d(tributary circuit with the second high pressure) be connected, this second high pressure imports road 19d and live axle 6 is offered substantially in parallel, to control valve 26 described later, supplies with by the high pressure before variable metering orifice 50.The second high pressure imports road 19d and live axle 6 is offered substantially in parallel, with rear body 3 opposed side upper shed, sealed by rear body 3 is arranged on precursor 2.Specifically, the second high pressure imports road 19d and is formed with seal groove in opening periphery, by the liquid-tight property of sealed member, is sealed.In addition, the first high pressure imports road 19c and is formed through to the outside of precursor 2, in its outer openings part, is formed with the installation recess 201 of setting pressure switch 40.In the bottom surface that recess 201 is installed, be formed with switch pin insert port 19c1, this switch pin insert port 19c1 imports road 19c with the first high pressure and is communicated with, and slightly large with the first high pressure importing road 19c phase diameter group.
In recess 201 is installed, be formed with space, the working oil of revealing from the micro-gap between switch pin insert port 19c1 and switch pin 41 flows in this space.In addition, recess 201 is being installed, be connected with the drain passageway 401 being communicated with current return circuit 22, the working oil of leakage is suitably discharged to current return circuit 22 by drain passageway 401, thus the differential pressure maintenance in the installation recess 201 that adaptation is determined by switch pin 41 actions and volume-variation etc.
In addition, form can be by the angle of offering from drill bit that the opening of recess 201 insert is sideling installed for drain passageway 401.In other words, be made as at drain passageway 401 to hull outside overtime the structure of passing through in the open area of recess 201 is installed.Therefore, drain passageway 401 be sealed by pressure switch 40 together with can importing road 19c with the first high pressure, does not need to utilize separately sealing bolt etc. to seal.
So, owing to leading to the first high pressure of control valve 26, import road 19c and import road with the pressure that leads to pressure switch 40 and can partly be shared, therefore, can be in the situation that not causing loop structure to complicate setting pressure switch 40.In addition, because pressure switch 40 is configured in suction area side, therefore, be easily formed for the drain passageway 401 that the pressure that is supplied to pressure switch 40 sides is discharged.In addition, in the situation that there is no the structure of pressure switch, need to utilize drill bit to offer the sealing bolt that the first high pressure imports road 19c in the situation that install the position of pressure switch 40, but owing to utilizing pressure switch 40 just can seal, therefore can save sealing bolt.
The inside of the upper end side in precursor 2, along being provided with the control valve 26 as pressure control mechanism of control pump delivery pressure with the direction (left and right directions of Fig. 6) of live axle 6 quadratures.This control valve 26 comprises control valve receiving bore 28, roughly has guiding valve 29 and the control valve spring 30 of round-ended cylinder shape, control valve receiving bore 28 left side from Fig. 6 on precursor 2 is offered to the right, utilize the opening portion in left side in connector 27 Closed Graph 6, guiding valve 29 is contained in this control valve receiving bore 28 in the mode of sliding in the axial direction freely, and 30 pairs of these guiding valves 29 of control valve spring are to the connector 27 side application of forces.
In control valve receiving bore 28, by guiding valve 29, be separated into hyperbaric chamber 28a respectively, middle pressure chamber 28b and low pressure chamber 28c, hyperbaric chamber 28a is formed between connector 27 and guiding valve 29, be located at the hydraulic pressure of the upstream side of the variable metering orifice 50 in output channel 19b way, namely the hydraulic pressure of the second 24b of pressure chamber is imported into this hyperbaric chamber 28a, middle pressure chamber 28b holds control valve spring 30, the hydraulic pressure in the downstream side of variable metering orifice 50 is imported into pressure chamber 28b in this, low pressure chamber 28c is formed on the outer circumferential side of guiding valve 29, pump intake pressure imports this low pressure chamber 28c from sucking path 19a via low-pressure passage 31.And the pressure difference of guiding valve 29 based on middle pressure chamber 28b and hyperbaric chamber 28a moves vertically.
Specifically, pressure difference at middle pressure chamber 28b and hyperbaric chamber 28a is less, when guiding valve 29 is positioned at connector 27 side, the access 32 that first fluid pressure chamber 14a is communicated with control valve receiving bore 28 is to low pressure chamber 28c opening, and the lower hydraulic pressure of this low pressure chamber 28c is imported in first fluid pressure chamber 14a.On the other hand, pressure difference at middle pressure chamber 28b and hyperbaric chamber 28a increases, the active force of guiding valve 29 opposing control valve springs 30 and while moving vertically, low pressure chamber 28c was cut off gradually with being communicated with of first fluid pressure chamber 14a, hyperbaric chamber 28a is communicated with first fluid pressure chamber 14a via access 32.Thus, the higher hydraulic pressure of hyperbaric chamber 28a is imported in first fluid pressure chamber 14a.That is to say, to the hydraulic pressure that optionally imports low pressure chamber 28c or hyperbaric chamber 28a in first fluid pressure chamber 14a.
And, all the time in second fluid pressure chamber 14b, import pump intake pressure, when importing the hydraulic pressure of low pressure chamber 28c in first fluid pressure chamber 14a, utilize the active force of Returnning spring 15, stator 8 and rotor 7 between the position (leftward position in Fig. 6) of offset maximum, pump delivery is maximum.On the other hand, when importing the hydraulic pressure of hyperbaric chamber 28a in first fluid pressure chamber 14a, utilize the pressure of this first fluid pressure chamber 14a, the active force of stator 8 opposing Returnning springs 15, to reduce the mode of second fluid pressure chamber 14b volume, swing, this stator 8 reduces with the offset of rotor 7, and pump delivery reduces.
As mentioned above, in embodiment 1, can access following effects effect.
(1) variable displacement vane pump of the present embodiment has: pump case, it is by precursor 2(the first housing) and rear body 3(the second housing) form, precursor 2 has the inner bottom surface 2a(bottom of an axial side of cylindrical portion 2b and sealing cylindrical portion 2b), the axial opposite side of rear body 3 sealing cylindrical portion 2b; Live axle 6, its axle is supported on pump case; The stator 8 of ring-type, it is located in cylindrical portion 2b in the mode that can move; Rotor 7, it is located in stator 8, by live axle 6, drives rotation; Slit 7a, its week at rotor 7 is upwards formed with a plurality of; Blade 16, it is given prominence to, submerges and is located at freely in slit 7a, is separated into a plurality of pump chambers 17 together with stator 8 and rotor 7; Platen 10, it is located between the inner bottom surface 2a and stator 8 in cylindrical portion 2b, from the delivery pressure of pump chamber 17 outputs, to stator 8 thrusters, is pressed; First fluid pressure chamber 14a and second fluid pressure chamber 14b, it is the space being formed between cylindrical portion inwall and the outer circumferential face of stator 8, and first fluid pressure chamber 14a is located at the direction increasing along with the offset to stator 8 relative rotation axis and moves, one side of volume reducing, second fluid pressure chamber 14b is located at the direction increasing along with the offset to stator 8 relative rotation axis and moves, the side that volume increases; Inlet hole 18(suction port), it is located in pump case, to the rotation along with rotor 7, and the suction region opening that in a plurality of pump chambers 17, volume increases; Delivery outlet 23, it is located on platen 10, to the rotation along with rotor 7, the output area opening of volume reducing in a plurality of pump chambers 17; Suck path 19a, it is located at pump case, is connected with inlet hole 18; The second hyperbaric chamber 24b, it is located at precursor 2, at the length direction of live axle 6, is configured in and the opposed position of delivery outlet 23 on axially, in the mode being communicated with delivery outlet 23, forms; Pressure switch 40, it is located at the suction area side of precursor 2, detects delivery pressure; The first high pressure imports road 19c, and it is located at precursor 2, and one be distolaterally connected with the second hyperbaric chamber 24b, and another is distolateral is connected with pressure switch 40; Control valve receiving bore 28, it is with the radial outside in stator 8 and with respect to live axle 6, be more positioned at the mode that sucks area side and be located at pump case; The second high pressure imports road 19d(tributary circuit), out, and one be distolaterally connected with the first high pressure importing road 19c in its Tu Zhong branch that imports road 19c from the first high pressure, and another is distolateral is connected with control valve receiving bore 28; Control valve 26, it is contained in control valve receiving bore 28, comprise guiding valve 29, the delivery pressure from delivery outlet 23 based on import road 19d importing via the second high pressure is controlled guiding valve 29, and in order to control the offset of stator 8, controls the pressure of first fluid pressure chamber 14a or second fluid pressure chamber 14b.
So, owing to leading to the first high pressure of control valve 26, import road 19c and import road with the pressure that leads to pressure switch 40 and can partly be shared, therefore, can be in the situation that not causing loop structure to complicate setting pressure switch 40.In addition, because pressure switch 40 is configured in suction area side, therefore, be easily formed for the drain passageway 401 that the pressure that is supplied to pressure switch 40 sides is discharged.In addition, in the situation that there is no the structure of pressure switch, need to utilize drill bit to offer the sealing bolt that the first high pressure imports road 19c in the situation that install the position of pressure switch 40, but owing to utilizing pressure switch 40 just can seal, therefore can save sealing bolt.
(2) second high pressure import road 19d and form and live axle 6 almost parallels.Therefore, the second high pressure import road 19d with rear body 3 opposed side upper shed, therefore can be sealed by rear body 3 is arranged on precursor 2, do not need sealing bolt etc. just can seal.
(3) variable displacement vane pump of the present embodiment comprises: the current return circuit 22 of elliptical shape, and it is communicated with suction path 19a; Recess 201 is installed, and it is formed through to the outside of precursor 2, and pressure switch 40 is arranged on to its outer openings part; Drain passageway 401, it is installing the bottom opening of recess 201, and current return circuit 22 is connected with installation recess 201.
Therefore, the working oil that is leaked to installation recess 201 can turn back to current return circuit 22, can guarantee the suitable action of pressure switch 40.In addition, due to the bottom opening recess 201 is installed, therefore pressure switch 40 can be pressed into and be configured in the position that approaches installation recess 201 bottoms, therefore can seek the miniaturization of device profile.Therefore in addition, because current return circuit 22 forms elliptical shape, can improve the design freedom of offering direction etc. of current return circuit 22.
(4) make drain passageway 401 to hull outside overtime, the path of this prolongation passes through in the open area that recess 201 is installed.
Therefore, drain passageway 401 be sealed by pressure switch 40 together with can importing road 19c with the first high pressure, does not need to utilize separately sealing bolt etc. to seal.
(embodiment 2)
Then, embodiment 2 is described.Basic structure is identical with embodiment 1, therefore difference is described.Fig. 9, Figure 10 are the sectional views of embodiment 2 variable displacement vane pump.Fig. 9 is the A-A sectional view of Fig. 4, and Figure 10 is the B-B sectional view of Fig. 4.As shown in figure 10, in embodiment 2, with the first high pressure, import component side that road 19c and the second high pressure import road 19d than the mode of the more close live axle 6 of control valve receiving bore 28 side, be formed obliquely the second high pressure and import road 19d.That is, pressure switch 40 need to be guaranteed the length scale of the switch pin insert port 19c1 that inserts for switch pin 41, and the position of control valve 26 is also subject to the restriction of casing rigidity etc.So, by making the second high pressure import road 19d, tilt, and near pump unit 5 side configuration components, can shorten the first high pressure and import road 19c.Therefore, as shown in Figure 9, can dwindle the short transverse size of variable displacement vane pump 1.In addition, in this situation, can not as embodiment 1, utilize rear body 3 sealing the second high pressure to import road 19d, therefore utilize separately sealed member 19d1 to seal.
As mentioned above, in embodiment 2, can access following effects effect.
(5) with the first high pressure, import component side that road 19c and the second high pressure import road 19d than the mode of the more close live axle 6 of control valve receiving bore 28 side, be formed obliquely the second high pressure and import road 19d.Therefore, can seek the miniaturization of device profile.
(embodiment 3)
Then, embodiment 3 is described.Basic structure is identical with embodiment 1, therefore only difference is described.Figure 11, Figure 12 mean embodiment 3 the figure of the variable displacement vane pump of hydraulic power steering apparatus for vehicle that is applicable to.Figure 11 is right elevation, and Figure 12 is plan view.In addition, Figure 13 is the B-B sectional view of embodiment 3 variable displacement vane pump.In embodiment 1, offer substantially in parallel the first high pressure with platen 10 and import road 19c.On the other hand, in embodiment 3, more to approach pressure switch 40 sides, more away from the mode of rear body 3, be formed obliquely the first high pressure importing road 19c ', this point is different.In other words, the first high pressure imports road 19c ' and swings to belt wheel one side configuration.That is, exist with pressure switch 40 and be configured in suction path 10a and the output channel 19e in same side, pipe arrangement etc. are connected with these paths, therefore guarantee that the space on this side has just become problem.Now, by making pressure switch 40 swing to belt wheel one side configuration, can guarantee space, can avoid pipe arrangement etc. to interfere with pressure switch 40.
(6) will suck path 19a, to pump case outside, derive the output channel 19e of delivery pressure and the suction area side that pressure switch 40 is located at precursor 2, more to approach pressure switch 40 sides more away from the mode of rear body 3, be formed obliquely the first high pressure and import road 19c '.
Therefore, can guarantee the space of housing periphery, can avoid pipe arrangement etc. and pressure switch 40 to interfere.
(embodiment 4)
Then, embodiment 4 is described.Basic structure is identical with embodiment 1, therefore difference is described.Figure 14～Figure 19 means embodiment 4 the figure of the variable displacement vane pump of hydraulic power steering apparatus for vehicle that is applicable to.Figure 14 is plan view, and Figure 15 is rear view, and Figure 16 is right elevation, and Figure 17 is plan view.Variable displacement vane pump 1 consists of precursor 2 and 3 two main bodys of rear body, and variable metering orifice 50 described later is arranged on precursor 2 by bolt from main body outside.In addition, sucking area side, from pump unit 5 to radial outside, control valve 26 and pressure switch 40 are installed successively.Below, be elaborated.
Figure 18, Figure 19 are the sectional views of embodiment 4 variable displacement vane pump, and Figure 18 is the A-A sectional view of Figure 17, and Figure 19 is the B-B sectional view of Figure 17.In addition, the X-X section of Figure 19 is identical with Fig. 5, and the basic structure of variable displacement vane pump 1 is identical with embodiment 1, therefore, omits the explanation to common structure.
As shown in figure 19, the second 24b of pressure chamber imports road 19c ' with the first high pressure and is connected, and this first high pressure imports road 19c ' and is opened in abreast in precursor 2 with platen 10.And the second 24b of pressure chamber imports road 19d(tributary circuit with the second high pressure) be connected, this second high pressure imports road 19d and live axle 6 is offered substantially in parallel, to aftermentioned control valve 26, supplies with by the high pressure before variable metering orifice 50.The second high pressure imports road 19d and live axle 6 is offered substantially in parallel, with rear body 3 opposed side upper shed, sealed by rear body 3 is arranged on precursor 2.Specifically, the second high pressure imports road 19d and is formed with seal groove in opening periphery, by the liquid-tight property of sealed member, is sealed.In addition, the first high pressure imports road 19c ' and is formed through to the outside of precursor 2, utilizes sealed member 190 its outer openings parts of sealing.
The inside of the upper end side in precursor 2, along being provided with the control valve 26 as pressure control mechanism of control pump delivery pressure with the direction (left and right directions of Figure 18) of live axle 6 quadratures.This control valve 26 comprises control valve receiving bore 28, roughly has guiding valve 29 and the control valve spring 30 of round-ended cylinder shape, control valve receiving bore 28 left side from Figure 18 on precursor 2 is offered to the right, utilize the opening portion in left side in connector 27 sealing Figure 18, guiding valve 29 is contained in this control valve receiving bore 28 in the mode of sliding in the axial direction freely, and 30 pairs of these guiding valves 29 of control valve spring are to the connector 27 side application of forces.
In control valve receiving bore 28, by guiding valve 29, be separated into hyperbaric chamber 28a respectively, middle pressure chamber 28b and low pressure chamber 28c, hyperbaric chamber 28a is formed between connector 27 and guiding valve 29, be located at the hydraulic pressure of the upstream side of the variable metering orifice 50 in output channel 19b way, namely the hydraulic pressure of the second 24b of pressure chamber is imported into this hyperbaric chamber 28a, middle pressure chamber 28b holds control valve spring 30, the hydraulic pressure in the downstream side of variable metering orifice 50 is imported into pressure chamber 28b in this, low pressure chamber 28c is formed on the outer circumferential side of guiding valve 29, pump intake pressure imports this low pressure chamber 28c from sucking path 19a via low-pressure passage 31.And the pressure difference of guiding valve 29 based on middle pressure chamber 28b and hyperbaric chamber 28a moves vertically.
With control valve receiving bore 28 adjoining positions, be formed with the installation recess 201 of setting pressure switch 40.In the bottom surface that recess 201 is installed, be formed with the pressure switch being communicated with hyperbaric chamber 28a and import road 19f with high pressure, in this pressure switch, with high pressure, import in the opening by installation recess 201 1 sides of road 19f, be formed with the switch pin insert port 19c1 inserting for switch pin 41 described later.
In recess 201 is installed, be formed with space, the working oil of revealing from the micro-gap between switch pin insert port 19c1 and switch pin 41 flows in this space.In addition, recess 201 is being installed, be connected with the drain passageway 401a being communicated with low pressure chamber 28c, the working oil of leakage is suitably discharged to low pressure chamber 28c by drain passageway 401a, thus the differential pressure maintenance in the installation recess 201 that adaptation is determined by switch pin 41 actions and volume-variation etc.
In addition, form can be by the angle of offering from drill bit that the opening of recess 201 insert is sideling installed for drain passageway 401a.In other words, be made as at drain passageway 401a to hull outside overtime the structure of passing through in the open area of recess 201 is installed.Therefore, drain passageway 401a can import together with the 19f of road and be sealed by pressure switch 40 with high pressure with pressure switch, does not need to utilize separately sealing bolt etc. to seal.
So, by utilizing pressure switch to import road 19f with high pressure, the hyperbaric chamber 28a of control valve 26 is connected with pressure switch 40, can be in the situation that not causing loop structure to complicate setting pressure switch 40.In addition, because pressure switch 40 and the control valve receiving bore 28 with low pressure chamber 28c configure adjacently, be therefore easily formed for the drain passageway 401a that the pressure that is supplied to pressure switch 40 sides is discharged.
As mentioned above, in embodiment 4, can access following effects effect.
(7) variable displacement vane pump of the present embodiment comprises: pump case, it is by precursor 2(the first housing) and rear body 3(the second housing) form, precursor 2 has the inner bottom surface 2a(bottom of an axial side of cylindrical portion 2b and sealing cylindrical portion 2b), the axial opposite side of rear body 3 sealing cylindrical portion 2b; Live axle 6, its axle is supported on pump case; The stator 8 of ring-type, it is located in cylindrical portion 2b in the mode that can move; Rotor 7, it is located in stator 8, by live axle 6, drives rotation; Slit 7a, its week at rotor 7 is upwards formed with a plurality of; Blade 16, it is given prominence to, submerges and is located at freely in slit 7a, is separated into a plurality of pump chambers 17 together with stator 8 and rotor 7; Platen 10, it is located between the inner bottom surface 2a and stator 8 in cylindrical portion 2b, from the delivery pressure of pump chamber 17 outputs, to stator 8 thrusters, is pressed; First fluid pressure chamber 14a and second fluid pressure chamber 14b, it is the space being formed between cylindrical portion inwall and the outer circumferential face of stator 8, and first fluid pressure chamber 14a is located at the direction increasing along with the offset to stator 8 relative rotation axis and moves, one side of volume reducing, second fluid pressure chamber 14b is located at the direction increasing along with the offset to stator 8 relative rotation axis and moves, the side that volume increases; Inlet hole 18(suction port), it is located in pump case, to the rotation along with rotor 7, and the suction region opening that in a plurality of pump chambers 17, volume increases; Delivery outlet 23, it is located on platen 10, to the rotation along with rotor 7, the output area opening of volume reducing in a plurality of pump chambers 17; Suck path 19a, it is located at pump case, is connected with inlet hole 18; The second hyperbaric chamber 24b, it is located at precursor 2, at the length direction of live axle 6, is configured in and the opposed position of delivery outlet 23 on axially, in the mode being communicated with delivery outlet 23, forms; Pressure switch 40, it is located at the suction area side of precursor 2, detects delivery pressure; The first high pressure imports road 19c ', and it is located at precursor 2, and one is distolaterally connected with hyperbaric chamber 28a; Control valve receiving bore 28, it is with the radial outside in stator 8 and with respect to live axle 6, be more positioned at the mode that sucks area side and be located at pump case; The second high pressure imports road 19d(tributary circuit), it imports road 19c ' Tu Zhong branch out from the first high pressure, and one be distolaterally connected with the first high pressure importing road 19c ', and another is distolateral is connected with control valve receiving bore 28; Control valve 26, it is contained in control valve receiving bore 28, comprise guiding valve 29, the delivery pressure from delivery outlet 23 based on import road 19d importing via the second high pressure is controlled guiding valve 29, and in order to control the offset of stator 8, controls the pressure of first fluid pressure chamber 14a or second fluid pressure chamber 14b; Recess 201 is installed, and it is formed through to the outside of precursor 2, and pressure switch 40 is arranged on to its outer openings part; Pressure switch imports road 19f with high pressure, and one is distolateral to be connected with the control valve receiving bore 28 that is imported into delivery pressure, and another distolateral bottom opening recess 201 is installed, is connected with pressure switch 40; Drain passageway 401a, it is installing the bottom opening of recess 201, is connected with suction passage side.
So, owing to utilizing pressure switch to import road 19f with high pressure, control valve 26 is connected with pressure switch 40, therefore, can be in the situation that not causing loop structure to complicate setting pressure switch 40.In addition, because pressure switch 40 is configured in suction area side, therefore, be easily formed for the drain passageway 401a that the pressure that is supplied to pressure switch 40 sides is discharged.In addition, in the situation that there is no the structure of pressure switch, need to offer the sealing bolt that the first high pressure imports road 19c ' in the situation that drill bit utilization is installed in the position of pressure switch 40, but owing to utilizing pressure switch 40 just can seal, therefore can save sealing bolt.In addition, because control valve 26 is compared the position in more approaching installation recess 201 with current return circuit 22, therefore can seek to shorten drain passageway 401a.
(8) make drain passageway 401a to hull outside overtime, the path of this prolongation passes through in the open area that recess 201 is installed.
Therefore, drain passageway 401a be sealed by pressure switch 40 together with can importing road 19c ' with the first high pressure, does not need to utilize separately sealing bolt etc. to seal.
(9) second high pressure import road 19d and form and live axle 6 almost parallels.Therefore, the second high pressure import road 19d with rear body 3 opposed side upper shed, therefore can be sealed by rear body 3 is arranged on precursor 2, do not need sealing bolt etc. just can seal.
(10) in addition, also can suck path 19a, to pump case outside, derive the output channel 19e of delivery pressure and the suction area side that pressure switch 40 is located at precursor 2, more to approach pressure switch 40 sides, more away from the mode of rear body 3, be formed obliquely the first high pressure importing road 19c '.In this situation, can guarantee the space of housing periphery, can avoid pipe arrangement etc. and pressure switch 40 to interfere.
(embodiment 5)
Then, embodiment 5 is described.Basic structure is identical with embodiment 4, therefore difference is described.Figure 20～Figure 23 means embodiment 5 the figure of the variable displacement vane pump of hydraulic power steering apparatus for vehicle that is applicable to.Figure 20 is plan view, and Figure 21 is right elevation, and Figure 22 is plan view.Figure 23 is the sectional view of embodiment 5 variable displacement vane pump.Figure 23 is the A-A sectional view of Figure 22.In embodiment 4, as drain passageway 401a, form the structure being connected with the low pressure chamber 28c of control valve 26.On the other hand, in embodiment 5, form the drain passageway 401a that the bottom that recess 201 is installed is connected with current return circuit 22.As illustrated in embodiment 1, this current return circuit 22 is communicated with the recess that sealing precursor 2 is held with sealed member between live axle 6 in precursor 2, by the pumping suction effect by above-mentioned suction region, to each pump chamber 17, supply with the residual oil of above-mentioned sealed member, prevent that above-mentioned residual oil from spilling to outside.
In recess 201 is installed, be formed with space, from being formed on, pressure switch imports the switch pin insert port 19c1 of 19f end, road with high pressure and the working oil of the leakage of the micro-gap between switch pin 41 flows in this space.In addition, recess 201 is being installed, be connected with the drain passageway 401a being communicated with current return circuit 22, the working oil of leakage is suitably discharged to current return circuit 22 by drain passageway 401a, thus the differential pressure maintenance in the installation recess 201 that adaptation is determined by switch pin 41 actions and volume-variation etc.
In addition, form can be by the angle of offering from drill bit that the opening of recess 201 insert is sideling installed for drain passageway 401a.In other words, be made as at drain passageway 401a to hull outside overtime the structure of passing through in the open area of recess 201 is installed.Therefore, drain passageway 401a can import together with the 19f of road and be sealed by pressure switch 40 with high pressure with pressure switch, does not need to utilize separately sealing bolt etc. to seal.
So, by utilizing pressure switch to import road 19f with high pressure, the hyperbaric chamber 28a of control valve 26 is connected with pressure switch 40, can be in the situation that not causing loop structure to complicate setting pressure switch 40.In addition, because pressure switch 40 and the control valve receiving bore 28 with low pressure chamber 28c configure adjacently, be therefore easily formed for the drain passageway 401a that the pressure that is supplied to pressure switch 40 sides is discharged.
As mentioned above, in embodiment 5, can access following effects effect.
(11) variable displacement vane pump of the present embodiment has the current return circuit 22 of the elliptical shape being communicated with suction path 19a, and drain passageway 401a is connected with the current return circuit 22 that sucks passage side.
Therefore, the working oil that is leaked to installation recess 201 can turn back to current return circuit 22, can guarantee the suitable action of pressure switch 40.In addition, due to the bottom opening recess 201 is installed, therefore pressure switch 40 can be pressed into and be configured in the position that approaches installation recess 201 bottoms, therefore can seek the miniaturization of device profile.Therefore in addition, because current return circuit 22 forms elliptical shape, can improve the design freedom of offering direction etc. of current return circuit 22.
Based on embodiment, the present invention has been described above, but has the invention is not restricted to above-described embodiment, also can adopt other structures.For example, in an embodiment, form the structure that drain passageway 401 is connected with current return circuit 22, but be not limited to situation about being connected with current return circuit 22, also can form the structure of discharging to other low-pressure sections.For example, in the situation that drain passageway 401 is connected with the low pressure chamber 28c of control valve 26, preferably form as follows, that is, the drain passage and the drain passageway 401 that are formed in control valve 26 are in a straight line.In this situation, can offer simultaneously drain passage and drain passageway the two, can seek the simplification of manufacturing process.
Claims (11)
1. a variable displacement vane pump, is characterized in that, has:
Pump case, it consists of the first housing and the second housing, and described the first housing has the bottom of an axial side of cylindrical portion and the described cylindrical portion of sealing, the described axial opposite side of cylindrical portion described in described the second housings close;
Live axle, its axle is supported on described pump case;
The stator of ring-type, it is located in described cylindrical portion in the mode that can move;
Rotor, it is located in described stator, by described drive shaft, is rotated;
Slit, its week at described rotor is upwards formed with a plurality of;
Blade, it is given prominence to, submerges and is located at freely in described slit, is separated into a plurality of pump chambers together with described stator and described rotor;
Platen, it is located between the described bottom and described stator in described cylindrical portion, from the delivery pressure of described pump chamber output, to described stator side, is pushed;
First fluid pressure chamber and second fluid pressure chamber, it is the space being formed between the inwall of described cylindrical portion and the outer circumferential face of described stator, described first fluid pressure chamber is located at along with to described stator, the direction relative to the offset increase of described running shaft moves, one side of volume reducing, described second fluid pressure chamber is located at along with to described stator, the direction relative to the offset increase of described running shaft moves, the side that volume increases;
Suction port, it is located in described pump case, to the rotation along with described rotor, the suction region opening that in described a plurality of pump chambers, volume increases;
Delivery outlet, it is located on described platen, to the rotation along with described rotor, the output area opening of volume reducing in described a plurality of pump chambers;
Suck path, it is located at described pump case, is connected with described suction port;
Hyperbaric chamber, it is located at described the first housing, at the length direction of described live axle, is configured in and the opposed position of described delivery outlet on axially, in the mode being communicated with described delivery outlet, forms;
Pressure switch, it is located at the described suction area side of described the first housing, detects delivery pressure;
High pressure imports road, and it is located at described the first housing, and a distolateral and described hyperbaric chamber is connected, and another distolateral and described pressure switch is connected;
Control valve receiving bore, it is located at described pump case with the radial outside in described stator and with respect to the mode that described live axle is more positioned at described suction area side;
Tributary circuit, out, and distolateral and a described high pressure importing road is connected in its Tu Zhong branch that imports road from described high pressure, and another distolateral and described control valve receiving bore is connected;
Control valve, it is contained in described control valve receiving bore, comprise guiding valve, the delivery pressure from described delivery outlet based on importing via described tributary circuit is controlled described guiding valve, and in order to control the offset of described stator, controls the pressure of described first fluid pressure chamber or described second fluid pressure chamber.
2. variable displacement vane pump according to claim 1, is characterized in that,
With component side, than the mode of the more close described live axle of control valve receiving bore side, be formed obliquely described tributary circuit.
3. variable displacement vane pump according to claim 1, is characterized in that,
Described tributary circuit forms and described live axle almost parallel.
4. according to the variable displacement vane pump described in any one in claims 1 to 3, it is characterized in that, comprising:
The current return circuit of elliptical shape, it is communicated with described suction path;
Recess is installed, and it is formed through to the outside of described the first housing, and described pressure switch is arranged on to its outer openings part;
Drain passageway, it is connected described current return circuit at the bottom opening of described installation recess with described installation recess.
5. variable displacement vane pump according to claim 4, is characterized in that,
Make described drain passageway to hull outside overtime, the path of this prolongation passes through in the open area that recess is installed.
6. according to the variable displacement vane pump described in any one in claim 1 to 5, it is characterized in that,
By described suction path, to the output channel of the described delivery pressure of described pump case outside derivation and the suction area side that described pressure switch is located at described the first housing,
To approach described pressure switch side more away from the mode of described the second housing, be formed obliquely described high pressure and import road.
7. a variable displacement vane pump, is characterized in that, comprising:
Pump case, it consists of the first housing and the second housing, and described the first housing has the bottom of an axial side of cylindrical portion and the described cylindrical portion of sealing, the described axial opposite side of cylindrical portion described in described the second housings close;
Live axle, its axle is supported on described pump case;
The stator of ring-type, it is located in described cylindrical portion in the mode that can move;
Rotor, it is located in described stator, by described drive shaft, is rotated;
Slit, its week at described rotor is upwards formed with a plurality of;
Blade, it is given prominence to, submerges and is located at freely in described slit, is separated into a plurality of pump chambers together with described stator and described rotor;
Platen, it is located between the described bottom and described stator in described cylindrical portion, from the delivery pressure of described pump chamber output, to described stator side, is pushed;
First fluid pressure chamber and second fluid pressure chamber, it is the space being formed between the inwall of described cylindrical portion and the outer circumferential face of described stator, described first fluid pressure chamber is located at along with to described stator, the direction relative to the offset increase of described running shaft moves, one side of volume reducing, described second fluid pressure chamber is located at along with to described stator, the direction relative to the offset increase of described running shaft moves, the side that volume increases;
Suction port, it is located in described pump case, to the rotation along with described rotor, the suction region opening that in described a plurality of pump chambers, volume increases;
Delivery outlet, it is located on described platen, to the rotation along with described rotor, the output area opening of volume reducing in described a plurality of pump chambers;
Suck path, it is located at described pump case, is connected with described suction port;
Hyperbaric chamber, it is located at described the first housing, at the length direction of described live axle, is configured in and the opposed position of described delivery outlet on axially, in the mode being communicated with described delivery outlet, forms;
Pressure switch, it is located at the described suction area side of described the first housing, detects delivery pressure;
High pressure imports road, and it is located at described the first housing, and a distolateral and described hyperbaric chamber is connected;
Control valve receiving bore, it is located at described pump case with the radial outside in described stator and with respect to the mode that described live axle is more positioned at described suction area side;
Tributary circuit, out, and distolateral and a described high pressure importing road is connected in its Tu Zhong branch that imports road from described high pressure, and another distolateral and described control valve receiving bore is connected;
Control valve, it is contained in described control valve receiving bore, comprise guiding valve, the delivery pressure from described delivery outlet based on importing via described tributary circuit is controlled described guiding valve, and in order to control the offset of described stator, controls the pressure of described first fluid pressure chamber or described second fluid pressure chamber;
Recess is installed, and it is formed through to the outside of described the first housing, and described pressure switch is arranged on to its outer openings part;
Pressure switch imports road with high pressure, and one is distolateral to be connected with the described control valve receiving bore that is imported into described delivery pressure, and another distolateral bottom opening at described installation recess, is connected with described pressure switch;
Drain passageway, it is connected with described suction passage side at the bottom opening of described installation recess.
8. variable displacement vane pump according to claim 7, is characterized in that,
The current return circuit with the elliptical shape being communicated with described suction path,
Described drain passageway is connected with the described current return circuit of described suction passage side.
9. variable displacement vane pump according to claim 8, is characterized in that,
Make described drain passageway to hull outside overtime, the path of this prolongation passes through in the open area that recess is installed.
10. according to the variable displacement vane pump described in any one in claim 7 to 9, it is characterized in that,
By described suction path, to the output channel of the described delivery pressure of described pump case outside derivation and the suction area side that described pressure switch is located at described the first housing,
To approach described pressure switch side more away from the mode of described the second housing, be formed obliquely described high pressure and import road.
11. variable displacement vane pumps according to claim 7, is characterized in that,
Described tributary circuit forms and described live axle almost parallel.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JPJP2012-203812 | 2012-09-18 | ||
| JP2012203812A JP5997556B2 (en) | 2012-09-18 | 2012-09-18 | Variable displacement vane pump |
| JP2012-203812 | 2012-09-18 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN103671092A true CN103671092A (en) | 2014-03-26 |
| CN103671092B CN103671092B (en) | 2017-03-01 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201310380464.5A Expired - Fee Related CN103671092B (en) | 2012-09-18 | 2013-08-28 | Variable displacement vane pump |
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| Country | Link |
|---|---|
| JP (1) | JP5997556B2 (en) |
| KR (1) | KR20140036964A (en) |
| CN (1) | CN103671092B (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107743550A (en) * | 2015-06-24 | 2018-02-27 | 皮尔伯格泵技术有限责任公司 | Mechanical automobile vavuum pump |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH03134283A (en) * | 1989-10-20 | 1991-06-07 | Mitsubishi Motors Corp | Oil pump for vehicle |
| JPH09151862A (en) * | 1995-11-28 | 1997-06-10 | Kayaba Ind Co Ltd | Flow rate control valve for vane pump |
| JPH109150A (en) * | 1996-06-20 | 1998-01-13 | Unisia Jecs Corp | Liquid pump |
| US6280150B1 (en) * | 1997-09-18 | 2001-08-28 | Jidosha Kiki Co., Ltd. | Variable displacement pump |
| JP2002147374A (en) * | 2000-11-13 | 2002-05-22 | Unisia Jecs Corp | Variable displacement vane pump |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2526632Y2 (en) * | 1990-10-15 | 1997-02-19 | 自動車機器株式会社 | Rotary pump with pressure switch |
| JPH0599163A (en) * | 1991-10-04 | 1993-04-20 | Nissan Motor Co Ltd | Oil pressure control device for variable capacity vane pump |
| US7628596B2 (en) * | 2006-09-22 | 2009-12-08 | Ford Global Technologies, Llc | Power steering pump |
| JP5133647B2 (en) * | 2007-10-05 | 2013-01-30 | カヤバ工業株式会社 | Vane pump |
-
2012
- 2012-09-18 JP JP2012203812A patent/JP5997556B2/en not_active Expired - Fee Related
-
2013
- 2013-08-28 CN CN201310380464.5A patent/CN103671092B/en not_active Expired - Fee Related
- 2013-09-09 KR KR1020130107830A patent/KR20140036964A/en not_active Application Discontinuation
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH03134283A (en) * | 1989-10-20 | 1991-06-07 | Mitsubishi Motors Corp | Oil pump for vehicle |
| JPH09151862A (en) * | 1995-11-28 | 1997-06-10 | Kayaba Ind Co Ltd | Flow rate control valve for vane pump |
| JPH109150A (en) * | 1996-06-20 | 1998-01-13 | Unisia Jecs Corp | Liquid pump |
| US6280150B1 (en) * | 1997-09-18 | 2001-08-28 | Jidosha Kiki Co., Ltd. | Variable displacement pump |
| JP2002147374A (en) * | 2000-11-13 | 2002-05-22 | Unisia Jecs Corp | Variable displacement vane pump |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107743550A (en) * | 2015-06-24 | 2018-02-27 | 皮尔伯格泵技术有限责任公司 | Mechanical automobile vavuum pump |
| US10619638B2 (en) | 2015-06-24 | 2020-04-14 | Pierburg Pump Technology Gmbh | Mechanical automotive vacuum pump with cantilevered rotor |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2014058892A (en) | 2014-04-03 |
| JP5997556B2 (en) | 2016-09-28 |
| KR20140036964A (en) | 2014-03-26 |
| CN103671092B (en) | 2017-03-01 |
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Granted publication date: 20170301 Termination date: 20180828 |