CN101033745A

CN101033745A - Variable capacity vane pump und method of controlling the same

Info

Publication number: CN101033745A
Application number: CNA2007100862253A
Authority: CN
Inventors: 山室重明; 小西英男; 仙波总夫
Original assignee: Hitachi Ltd
Current assignee: Hitachi Ltd
Priority date: 2006-03-09
Filing date: 2007-03-09
Publication date: 2007-09-12
Also published as: JP2007239626A; EP1832752A2; US20070212243A1

Abstract

A variable displacement vane pump includes: a cam ring defining first and second fluid pressure chambers on both sides thereof; and a rotor mounted inside the cam ring, the rotor defining an annular chamber outside thereof. Arranged outside of the rotor, vanes divide the annular chamber into a plurality of pump chambers. A suction port is defined in a section of the annular chamber in which each of the pump chambers expands with the rotation of the rotor, while a discharge port is defined in a section of the annular chamber in which each of the pump chambers contracts with the rotation of the rotor. A first fluid passage is connected to one of the first and second fluid pressure chambers. A second fluid passage is connected to one of the suction port and the discharge port. An electromagnetic valve controls fluid communication between the first and second fluid passages.

Description

The method of variable capacity vane pump and this variable capacity vane pump of control

Technical field

Present invention relates in general to variable capacity vane pump, relate more specifically to can be used for the variable capacity vane pump of power steering system.

Background technique

Japanese Patent Application No.2004-218430 illustrates a kind of variable capacity vane pump that comprises rotor and center on the cam ring of this rotor, and wherein, working fluid flows along circumference between rotor and cam ring.Cam ring is installed and is used for oscillating motion.When the cam ring displacement was limited to the shape in the space between rotor and the cam ring with change, the discharge capacity of this pump changed.By the oscillating motion of control valve via two relative fluid pressure chambers control cam rings.Control valve comprises and is used to receive from the guiding chamber of drain passageway with respect to the hydrodynamic pressure of the downstream portion of throttle orifice.The solenoid valve that is provided with in the fluid passage that extends between the second guiding chamber and fluid container is controlled the interior pressure of guiding chamber by the opening of regulated fluid path.This causes the variation of control valve position, and causes the variation of cam ring position thus via fluid pressure chambers.

Summary of the invention

Disclosed variable capacity vane pump faces following problem at least in Japanese Patent Application No.2004-218430.At first, because control valve operates in the interstage, so cam ring one is beginning to move after postponing when solenoid valve receives drive signal.Secondly, because solenoid valve is subjected to along the effect of discharging the travel direction of pressing towards the height of introducing control valve, so solenoid valve need have enough opposing high fluid pressure levels and mobile ability.This trends towards increasing the size and the weight of solenoid valve.

Therefore, the purpose of this invention is to provide a kind of variable capacity vane pump with high responsiveness and compact structure.

According to an aspect of the present invention, a kind of variable capacity vane pump, it comprises: the pump housing; Cam ring, it movably is installed in the pump housing, this cam ring and pump housing between limit first and second fluid pressure chambers, this first fluid pressure chamber has the volume that increases when cam ring when first end position moves, this second fluid pressure chambers has the volume that increases when cam ring when second end position moves; Rotor, it is installed in cam ring inside, is used at least rotating along a direction around axis, and this rotor is in its outside annular chamber that limits; A plurality of blades, it is in the configuration of the outer radial periphery edge of rotor circumference, and to move along with the rotation of rotor, this blade radial extends and annular chamber is divided into a plurality of pump chambers; Suction port is in the first portion that its each pump chambers that is limited to annular chamber enlarges along with the rotation of rotor; Exhaust port, in the second portion that its each pump chambers that is limited to annular chamber is dwindled along with the rotation of rotor, exhaust port limits the third part of sense of rotation from the suction port to the exhaust port along rotor of annular chamber, and the volume of this third part ratio when cam ring is in second end position is big when cam ring is in first end position; The first fluid path, it is connected in first and second fluid pressure chambers one by hydraulic pressure; Second fluid passage, it is connected in suction port and the exhaust port one by hydraulic pressure; And solenoid valve, it is connected to first and second fluid passages by hydraulic pressure, is communicated with control fluid therebetween.

According to a further aspect in the invention, a kind of variable capacity vane pump, it comprises: the pump housing; Cam ring, it movably is installed in the pump housing, this cam ring and pump housing between limit first and second fluid pressure chambers, this first fluid pressure chamber has the volume that increases when cam ring when first end position moves, this second fluid pressure chambers has the volume that increases when cam ring when second end position moves; Rotor, it is installed in cam ring inside, is used at least rotating along a direction around axis, and this rotor is in its outside annular chamber that limits; A plurality of blades, it is in the configuration of the outer radial periphery edge of rotor circumference, and to move along with the rotation of rotor, this blade radial extends and annular chamber is divided into a plurality of pump chambers; Suction port is in the first portion that its each pump chambers that is limited to annular chamber enlarges along with the rotation of rotor; Exhaust port, in the second portion that its each pump chambers that is limited to annular chamber is dwindled along with the rotation of rotor, exhaust port limits the third part of sense of rotation from the suction port to the exhaust port along rotor of annular chamber, and the volume of this third part ratio when cam ring is in second end position is big when cam ring is in first end position; Separator, itself and cam ring are installed in the pump housing contiguously, this separator limits three-fluid pressure chamber and described second fluid pressure chambers in its both sides, this three-fluid pressure chamber has along the interior pressure of directive effect on cam ring that cam ring is moved towards second end position; The three-fluid path, it is connected to three-fluid pressure chamber by hydraulic pressure; And first valve, it is connected to the three-fluid path by hydraulic pressure, is communicated with the fluid of control via the three-fluid path.

In accordance with a further aspect of the present invention, a kind of method of controlling vehicle with variable capacity vane pump, this variable capacity vane pump comprises: the pump housing; Cam ring, it movably is installed in the pump housing, and this cam ring limits pump chambers and first fluid pressure chamber at least, and this first fluid pressure chamber has the interior pressure that acts on the cam ring; Suction port; Exhaust port; Drain passageway, it is positioned at the downstream with respect to exhaust port, and drain passageway has throttle orifice; Control valve is used to control the interior pressure of first fluid pressure chamber, and this control valve response is operated with respect to the pressure of the upstream and downstream portion of throttle orifice from drain passageway; Solenoid valve, its fluid that is used to control between first fluid pressure chamber, suction port and the exhaust port is communicated with, and this method comprises: controlled interior pressure of regulating first fluid pressure chamber according to the running state of vehicle by solenoid valve.

Description of drawings

Fig. 1 is the axial sectional view according to the variable capacity vane pump of the first embodiment of the present invention.

Fig. 2 is first embodiment's the radial cross-section of variable capacity vane pump under cam ring displacement maximum case.

Fig. 3 is the amplification longitudinal sectional view of control valve of first embodiment's variable capacity vane pump.

Fig. 4 is the amplification longitudinal sectional view of solenoid valve of first embodiment's variable capacity vane pump.

Fig. 5 is the radial cross-section according to the variable capacity vane pump of first embodiment's first modification.

Fig. 6 is the radial cross-section according to the variable capacity vane pump of first embodiment's second modification.

Fig. 7 is the radial cross-section of variable capacity vane pump according to a second embodiment of the present invention.

Fig. 8 is the radial cross-section according to the variable capacity vane pump of second embodiment's modification.

Fig. 9 is the radial cross-section of the variable capacity vane pump of a third embodiment in accordance with the invention.

Figure 10 is the radial cross-section according to the variable capacity vane pump of the 3rd embodiment's modification.

Figure 11 is the radial cross-section of the variable capacity vane pump of a fourth embodiment in accordance with the invention.

Figure 12 is the radial cross-section according to the variable capacity vane pump of the 4th embodiment's modification.

Figure 13 is the axial sectional view of variable capacity vane pump according to a fifth embodiment of the invention.

Figure 14 is the 5th embodiment's the radial cross-section of variable capacity vane pump under cam ring displacement maximum case.

Figure 15 is the 5th embodiment's the radial cross-section of variable capacity vane pump under cam ring displacement minimum.

Figure 16 is the axial sectional view according to the variable capacity vane pump of the 5th embodiment's modification.

Figure 17 is the radial cross-section of variable capacity vane pump according to a sixth embodiment of the invention.

Figure 18 is the radial cross-section according to the variable capacity vane pump of the 6th embodiment's first modification.

Figure 19 is the radial cross-section according to the variable capacity vane pump of the 6th embodiment's second modification.

Figure 20 is the radial cross-section according to the variable capacity vane pump of the 6th embodiment's the 3rd modification.

Figure 21 is the radial cross-section according to the variable capacity vane pump of the 6th embodiment's the 4th modification.

Figure 22 is the axial sectional view according to the variable capacity vane pump of the 6th embodiment's the 5th distortion.

The specific embodiment mode

Fig. 1,2,3 and 4 variable capacity vane pumps that illustrate according to the first embodiment of the present invention.Right hand rectangular coordinate system (xyz) is set in the accompanying drawings.In this variable capacity vane pump, controlled hydrodynamic pressure is introduced into first fluid pressure chamber, is introduced into second fluid pressure chambers and suck to press, and is as described in detail later such.

Variable capacity vane pump 1 totally comprises the solenoid valve 300 of live axle 2, rotor 3, cam ring 4, adapter ring (adapter ring) 5, the pump housing 10, control valve 200 and solenoid valve form.Cam ring 4 movably is installed in the valve body 10, thereby limits first and second fluid pressure chambers A1 and the A2.Rotor 3 is installed in the inside of cam ring 4, rotates along a direction around axis at least, thereby in its outside annular chamber that limits.The axis of rotor 3 extends along the x direction, and the sense of rotation of rotor 3 is counter clockwise directions as shown in Figure 2.As shown in Figure 1, live axle 2 is installed on the pump housing 10, rotating around its longitudinal axis, and extends along the x direction.Live axle 2 is connected to motor drivingly via pulley and Timing Belt, and is mechanically connected to rotor 3, rotates with the rotational synchronization ground with rotor 3.

As shown in Figure 1, the pump housing 10 comprises first housing 11 and second housing 12.First housing 11 of cup-shaped form has the opening axial end in the face of positive x direction.The pressing plate 6 of plate-like form is installed in the bottom 111 of first housing 11.Adapter ring 5, cam ring 4 and rotor 3 are installed in pump parts receiver portion or the space 112, and this pump parts receiver portion or space 112 are limited in the inner periphery of first housing 11 between the pressing plate 6 and second housing 12.First housing 11 is supporting driving shaft 2 rotationally.The axial height of adapter ring 5, cam ring 4 and rotor 3 is the same, forms concordant axial end.Pressing plate 6 does not contact with an axial end of adapter ring 5, cam ring 4 and rotor 3 saturating fluid, and second housing 12 does not contact with another axial end of adapter ring 5, cam ring 4 and rotor 3 saturating fluid.

Second housing 12 is formed with high pressure lead-ingroove 9 in the axial end 120 in the face of negative x direction.High pressure lead-ingroove 9 is arranged in the part with the cam ring 4 constant axial ends that contact 120.High pressure lead-ingroove 9 hydraulically is connected to exhaust port 122.Thus, the contact position that is introduced between the cam ring 4 and second housing 12 is pressed in discharge.Discharge to press basically on whole ring-type contact position, play the effect that balance along the circumferential direction is applied to the pressure of contact position.

Pressing plate 6 is being formed with suction port 62 and exhaust port 63 in the face of in the axial end 61 of positive x direction, and second housing 12 is formed with suction port 121 and exhaust port 122 in axial end 120.

Suction port

62 and 121 hydraulically is connected to and sucks path IN.As shown in Figure 1, suck path IN and have the opening that links to each other with the outside suction pipe 14 that leads to fluid tank 15, this aperture arrangement is at the top of second housing 12.

Exhaust port

63 and 122 hydraulically is connected to drain passageway OUT.As shown in Figure 1, drain passageway OUT has opening at the top of first housing 11.Therefore, working fluid is incorporated in the annular chamber that is limited between rotor 3 and the cam ring 4 via

suction port

62 and 121, and working fluid is discharged via exhaust port 63 and 122.Suck path IN and hydraulically be connected to solenoid valve 300 via fluid communication passageway C2.

Adapter ring 5 is installed in the radial outside of the pump housing 10 reaction rings 4.The adapter ring 5 of elliptical ring shape form has basically along the major axis of y direction with basically along the minor axis of z direction.Adapter ring 5 engages with first housing 11, thereby does not allow adapter ring 5 to rotate with respect to first housing 11.

The cam ring 4 of positive toroidal form has identical with the minor axis of adapter ring 5 basically external diameter diameter.Thus, when cam ring 4 was installed in the adapter ring 5, between limited annular chamber.Cam ring 4 can move along the y direction, that is, move with respect to the direction of the pump housing 10 edges with the axis normal of rotor 3.

As shown in Figure 2, Sealing 50 is installed in the top of the inner peripheral surface 53 of adapter ring 5.As shown in Figure 2, pin 40 is installed in the bottom of inner peripheral surface 53.Cam ring 4 is supported on the pin 40 pivotly, with oscillating motion in adapter ring 5.The annular chamber that pin 40 and Sealing 50 will limit between cam ring 4 and adapter ring 5 is divided into the radially A1 of first fluid pressure chamber in adapter ring 5 and the second fluid pressure chambers A2.The A1 of first fluid pressure chamber is positioned at negative y side with respect to cam ring 4, and the second fluid pressure chambers A2 is positioned at positive y side.The A1 of first fluid pressure chamber has along the interior pressure P1 of directive effect on cam ring 4 towards the first end position wedge cam ring 4, and the second fluid pressure chambers A2 has along the interior pressure P2 of directive effect on cam ring 4 towards the second end position wedge cam ring 4.

The diameter of the outer radial periphery face of rotor 3 is littler than the diameter of the inner peripheral surface of cam ring 4, thereby rotor 3 is installed in cam ring 4 inside.Even when cam ring 4 displacements were maximum, rotor 3 did not contact with cam ring 4 yet.As shown in Figure 2, distance L is defined as the distance between the inner peripheral surface 41 of the outer radial periphery face of rotor 3 and cam ring 4.As shown in Figure 2, in the left side of rotor 3, when cam ring 4 is maximum along positive y direction displacement, the distance L minimum, and when cam ring 4 is maximum along negative y direction displacement, the distance L maximum.

As shown in Figure 2, along the circumferential direction dispose a plurality of blades 32 in the radial outer periphery of rotor 3, be used for moving along with the rotation of rotor 3, these a plurality of blades 32 radially extend and the annular chamber that will limit between rotor 3 and cam ring 4 is divided into a plurality of pump chambers B.In this embodiment, rotor 3 is formed with a plurality of grooves 31 in radial outer periphery.Each groove 31 radially extends.Blade 32 inserts in the respective groove 31, vertically to reciprocatingly slide.Each groove 31 is included in the back pressure chamber 33 of proximal end.Discharge and press each back pressure chamber 33 of introducing to promote each blade 32 with radially outside direction.Pressing plate 6 has the axial end 61 in the face of positive x direction.Be limited with back pressure lead-

ingroove

64 and 124 at the axial end 61 of pressing plate 6 and the axial end 120 of second housing 12 respectively.The discharge that is used for back pressure chamber 33 is pressed via back pressure lead-

ingroove

64 and 124 introducings.

Each blade 32 has bigger than the maximum value of length L at least radial length, thereby is independent of the relative geometrical relation between rotor 3 and the cam ring 4, and blade 32 extends to the inner peripheral surface 41 of cam ring 4 consistently from the groove 31 of rotor 3.Reception is from the back pressure of back pressure chamber 33, and blade 32 is in pressure with the inner peripheral surface 41 of cam ring 4 consistently and does not contact saturating fluid.

Thereby each pump chambers B is not limited between rotor 3 and cam ring 4 by each adjacent two blade 32 saturating fluid.When rotor 3 was located with respect to cam ring 4 off-centre, the volume of each pump chambers B was along with the rotation of rotor 3 changes.

Be limited with the suction port 62,121 that in the pressing plate 6 and second housing 12, limits respectively in the part that each pump chambers B of the annular chamber that limits enlarges along with the rotation of rotor 3 between rotor 3 and cam ring 4.Be limited with the exhaust port 63,122 that in the pressing plate 6 and second housing 12, limits respectively in the part that each pump chambers B of the annular chamber that limits dwindles along with the rotation of rotor 3 between rotor 3 and cam ring 4.Thereby working fluid is introduced via suction port 62,121 and is discharged via exhaust port 63,122.

Pressing plate 6 is formed with to suck in axial end 61 presses lead-ingroove 65.Suck and press lead-ingroove 65 hydraulically to be connected to the second fluid pressure chambers A2, press Pin to introduce the second fluid pressure chambers A2 sucking.

Adapter ring 5 is formed with radial direction through hole 51 at right-hand member as shown in Figure 2.First housing 11 is formed with connector receiving bore 114 at right-hand member as shown in Figure 2.Cup-shaped connector 70 is inserted in connector receiving bore 114 and the radial direction through hole 51, and bottom surface 73 is in the face of negative y direction.Connector receiving bore 114 is by lid 72 sealings.Connector 70 is pressed P3 as the separator that limits the A3 of three-fluid pressure chamber and the second fluid pressure chambers A2 in its both sides in the A3 of three-fluid pressure chamber has, press in this P3 along make cam ring 4 towards directive effect that second end position moves on cam ring 4.

Spring 71 is maintained in the recess of connector 70, is used for expanding and contraction along the y direction.One end of spring 71 is connected to the bottom of connector 70, and the other end is connected to and covers 72, along negative y direction pushing connector 70.Like this, connector 70 extends through the radial direction through hole 51 of adapter ring 5, feasible bottom 73 and cam ring 4 constant contacts, and along negative y direction pushing cam ring 4.As shown in Figure 2, when cam ring 4 was positioned at the right end position of adapter ring 5, cam ring 4 was with respect to the eccentricity minimum of the axis of rotor 3.As shown in Figure 2, when cam ring 4 was positioned at the left position of adapter ring 5, cam ring 4 was with respect to the eccentricity maximum of the axis of rotor 3.Therefore, connector 70 is along the direction actuating cam ring 4 of cam ring 4 with respect to the displacement increase of rotor 3.The outer circumferential periphery 74 of connector 70 and the not saturating fluid ground sliding contact of connector receiving bore 114 make the not saturating fluid ground, outside of the second fluid pressure chambers A2 and the pump housing 10 separate.

Fig. 3 shows the detailed construction of control valve 200.Control valve 200 is differential pressure actuated valves.Control valve 200 is contained in first housing 11 along in the valve receiving bore 115 of y direction extension.Control valve 200 comprises as the spool 210 of valve element and safety valve 220.The valve element 210 of cup-shaped form has the opening in the face of positive y direction.Valve element bias voltages spring 230 is installed in the bottom of valve receiving bore 115, is used for promoting valve element 210 along negative y direction.Safety valve 220 is installed in the center hole of valve element 210, slides with not saturating fluid ground on the inner periphery 211 of valve element 210.212 places comprise first slide part 213 and second slide part 214 to valve element 210 in the outer periphery.First slide part 213 and second slide part 214 and the not saturating fluid ground sliding contact of valve receiving bore 115.First slide part 213 and second slide part 214 all 212 circumferentially extend and have a diameter bigger than the other parts of outer periphery 212 around the outer periphery.Between first slide part 213 and second slide part 214, define 212 recesses that circumferentially extend 215 like this around the outer periphery.Thereby, the inner space of valve receiving bore 115 is divided into three parts, promptly, as shown in Figure 3, be limited to the left side of first slide part 213 first fluid chamber D1, be limited to second D2 of fluid chamber on recess 215 right sides and be limited to first slide part 213 and second slide part 214 between recess 215 in three-fluid chamber D3.

First fluid chamber D1 is connected to

exhaust port

63 and 122 via fluid passage 21 hydraulic pressure, and second D2 of fluid chamber is connected to

exhaust port

63 and 122 via fluid passage 22 hydraulic pressure.Notice that

fluid passage

21 and 22 is parts of drain passageway OUT.Fluid passage 21 does not comprise throttle orifice, and fluid passage 22 comprises throttle orifice 8.That is to say that first fluid chamber D1 hydraulic pressure is connected to the upstream portion of drain passageway OUT with respect to throttle orifice 8, and second fluid chamber's D2 hydraulic pressure is connected to the downstream portion of drain passageway OUT with respect to throttle orifice 8.Thereby, discharge and press Pout to be introduced into first fluid chamber D1, and the downstream discharge presses Pfb to be introduced into second D2 of fluid chamber.Because the reduction that throttle orifice 8 causes presses Pfb to press Pout little than discharge so be defined as fluid passage 22 with respect to the downstream discharge of the pressure of the downstream portion of throttle orifice 8.Incidentally, reduce under insignificant other situation at the pressure that caused by throttle orifice 8, the downstream is discharged and is pressed Pfb to simplify to be called " discharge and press ".

Three-fluid chamber D3 is connected to via fluid passage 23 hydraulic pressure and sucks path IN, makes to suck and presses Pin to be introduced in wherein.Three-fluid chamber D3 is also via being formed on the inner space that radial hole 216 hydraulic pressure in the recess 215 are connected to valve element 210.Thereby second D2 of fluid chamber and three-fluid chamber D3 are by safety valve 220 hydraulic pressure disconnection each other.

As shown in Figure 3, adapter ring 5 is formed with intercommunicating pore 52 near the top of the negative y side of Sealing 50, and first housing 11 is formed with fluid passage 113.Control valve 200 is connected to the A1 of first fluid pressure chamber via intercommunicating pore 52 and fluid passage 113 hydraulic pressure.Fluid passage 113 also is connected to solenoid valve 300 via fluid communication passageway (or fluid passage) C1 hydraulic pressure.

Fluid passage 113 has opening 113a in the sidewall of valve receiving bore 115.When pump did not turn round, opening 113a made fluid passage 113 hydraulic pressure be connected to three-fluid chamber D3 in the face of the recess 215 of valve element 210.When valve element 210 along positive y direction displacement, thereby when first slide part 213 was moving to the front of opening 113a along positive y direction, fluid passage 113 hydraulic pressure were connected to first fluid chamber D1.

Valve element 210 is subjected to the power Fc1 that interior pressure by first fluid chamber D1 causes power Fv1 along positive y direction, caused the negative y direction in edge that causes along the power Fv2 of negative y direction and by valve element bias voltages spring 230 by the interior pressure of second D2 of fluid chamber.By following The Representation Equation equilibrium conditions.

Fv1＝Fv2+Fc1

Therefore, when equation (a) was set up, valve element 210 moved along negative y direction.

Fv1≤Fv2+Fc1 (a)

Under this condition, opening 113a is positioned at the positive y side of first slide part 213, makes fluid passage 113 hydraulic pressure be connected to three-fluid chamber D3.On the other hand, when equation (b) was set up, valve element 210 moved along positive y direction.

Fv1＞Fv2+Fc1 (b)

Under this condition, opening 113a is positioned at the negative y side of first slide part 213, makes fluid passage 113 hydraulic pressure be connected to first fluid chamber D1.The characteristic of power Fc1 that can be by changing valve element bias voltages spring 230 is come adjusting condition (a) and (b).

Safety valve 220 comprises valve seat 221, ball valve 222, spring retainer 223 and safety valve spring 224.Order according to valve seat 221, ball valve 222, spring retainer 223 and safety valve spring 224 is arranged these parts along negative y direction.Valve seat 221 is installed in the center hole of valve element 210, with the longitudinal sliding motion campaign.Not saturating fluid ground qualifying part second D2 of fluid chamber of valve seat 221.Valve seat 221 comprises the through hole 221a that extends along the y direction.The power Fv2 that is caused by the hydrodynamic pressure from second D2 of fluid chamber acts on the ball valve 222 via through hole 221a.One end of safety valve spring 224 is connected to the bottom 217 of the center hole of valve element 210, promotes ball valve 222 along positive y direction.Thereby ball valve 222 is subjected to the power Fv2 of the negative y direction in edge that the interior pressure by second D2 of fluid chamber causes and the effect of the power Fc2 of the positive y direction in edge that caused by safety valve spring 224.

When satisfying equation (c), ball valve 222 contacts with valve seat 221, to close through hole 221a, second D2 of fluid chamber and three-fluid chamber D3 is cut off each other.

Fv2≤Fc2 (c)

On the other hand, when satisfying equation (d), ball valve 222 shifts out and the contacting of valve seat 221, make second D2 of fluid chamber and three-fluid chamber D3 each other hydraulic pressure be connected.

Fv2＞Fc2 (d)

Thereby, three-fluid chamber D3 hydraulic pressure be connected to suck path IN and second D2 of fluid chamber the two.Can come adjusting condition (c) and (d) by the biasing force Fc2 characteristic that changes safety valve spring 224.

Below how explanation control valve 200 controls the interior pressure of first fluid chamber D1.(i) when first fluid chamber D1 hydraulic pressure is connected to fluid passage 113 (when satisfying equation (b)), the A1 of first fluid pressure chamber is connected to first fluid chamber D1 via fluid passage 113 and intercommunicating pore 52 hydraulic pressure, makes to discharge to press Pout (from the upstream portion of fluid passage 22 with respect to throttle orifice 8) to be introduced into the A1 of first fluid pressure chamber.(ii) when three-fluid chamber D3 hydraulic pressure is connected to fluid passage 113 (when satisfying equation (a)), the A1 of first fluid pressure chamber hydraulic pressure is connected to three-fluid chamber D3.The pressure of introducing depends on the switching of safety valve 220.(ii-1) when safety valve 220 cuts out under condition situation (ii) (when satisfy equation (a) and (c) time), second D2 of fluid chamber and three-fluid chamber D3 cut off each other, make to suck to press Pin to be introduced into the A1 of first fluid pressure chamber.(ii-2) when safety valve 220 is opened under condition situation (ii) (when satisfy equation (a) and (d) time), second D2 of fluid chamber and three-fluid chamber D3 hydraulic pressure each other are connected.At this moment, the interior pressure of three-fluid chamber D3 is based on to suck and presses Pin and downstream to discharge the mixed pressure Pm that presses Pfb to produce.Should mixedly press Pm to be introduced into the A1 of first fluid pressure chamber.Note, satisfy equation (Pin＜Pm＜Pout).Put it briefly, from the pressure of the control valve 200 introducing first fluid A1 of pressure chamber, promptly controlled valve pressure P v equals discharge and presses Pout under condition (i), equals to suck under (ii-1) condition and presses Pin, equals to mix pressure Pm under condition (ii-2).

Replacedly, controlled pressure P v can be introduced into the second fluid pressure chambers A2, rather than the A1 of first fluid pressure chamber.

The annular chamber that between rotor 3 and cam ring 4, limits along the sense of rotation of rotor 3 from suction port 62 and 121 big to the volume of the volume ratio of part when cam ring 4 is in second end position when cam ring 4 is in first end position of exhaust port 63 and 122.Cam ring 4 is subjected to the power F1 of the positive y direction in edge that the interior pressure P1 by the A1 of first fluid pressure chamber causes and the effect of the power F2 of the negative y direction in edge that caused by the interior pressure P2 of the second fluid pressure chambers A2.When power F1＞F2, cam ring 4 is swung clockwise around pin 40 as shown in Figure 2, or moves along positive y direction.This has increased more the pump chambers B near the second fluid pressure chambers A2 _Y+Volume, and reduced more pump chambers B near the second fluid pressure chambers A2 _Y-Volume.Along with pump chambers B _Y-The reducing of volume, working fluid reduces to exhaust port 63 and the amount of flow of 122 unit time from suction port 62 and 121, discharges drops.Then, when preponderating when the interior pressure P1 decline of the A1 of first fluid pressure chamber so that along the composite force F2 that bears the y direction, cam ring 4 is put back as shown in Figure 2 counterclockwise, or retracts along bearing the y direction.

When being in balance along the power F1 of positive y direction and negative y direction and F2, cam ring 4 keeps static.When cam ring 4 and rotor 3 concentric locatings, pump chambers B _Y-Volume and pump chambers B _Y+Volume the same, press the two to be equal to zero thereby suck to press and discharge.So, the also vanishing of interior pressure P1 of the A1 of first fluid pressure chamber, thus spring 71 is along positive y direction actuating cam ring 4.Thereby automatically adjustment cam ring 4 is with respect to the displacement of rotor 3, makes the difference change between pressing with the discharge in downstream side of the upstream side of throttle orifice 8.

Solenoid valve 300 is arranged in the A1 of first fluid pressure chamber hydraulic pressure is connected among the fluid communication passageway C that sucks path IN.Fluid communication passageway C comprises and solenoid valve 300 hydraulic pressure is connected to the fluid communication passageway C1 of the A1 of first fluid pressure chamber and solenoid valve 300 hydraulic pressure is connected to the fluid communication passageway C2 that sucks path IN.Solenoid valve 300 is contained in the valve receiving bore 117 that is limited in first housing 11.Valve receiving bore 117 is limited to the negative y side and the positive z side of the axis of rotor 3, extends along the y direction.Solenoid valve 300 optionally provides the A1 of first fluid pressure chamber and sucks fluid between the path IN and is communicated with or stops the A1 of first fluid pressure chamber to be communicated with fluid between the suction path IN.

Fig. 4 shows the detailed construction of solenoid valve 300.Solenoid valve 300 comprises the valve system that is arranged between distribution channel C1 and the C2 generally and is used to control the electromagnetic actuators of this valve system.Solenoid valve 300 comprises sleeve 310, spool 320, spring 330, bar 340 and coil 360.Bar 340, iron core 350 and coil 360 following integral body are called " solenoid SOL ".Solenoid SOL is as electromagnetic actuators.

The sleeve 310 of cup-shaped form is accommodated in the valve receiving bore 117, and bottom faces is to the bottom of valve receiving bore 117.Spool 320 and spring 330 are contained in the center hole of sleeve 310.An axial end of spring 330 links to each other with the bottom 311 of sleeve 310, promotes spool 320 along negative y direction.

Spool 320 with basically with the inner circumference periphery of sleeve 310 not the mode of saturating fluid ground sliding contact be installed in the center hole of sleeve 310.The 4th D4 of fluid chamber is limited between the bottom 311 of spool 320 and sleeve 310.Two

radial holes

314 and 314 that sleeve 310 is formed with around the outer periphery 312 grooves 313 that extend and leads to fluid communication passageway C2.Sleeve 310 is formed with the longitudinal hole 315 that extends through bottom 311 along the y direction, thereby the 4th fluid chamber's D4 hydraulic pressure is connected to fluid communication passageway C1.

Spool 320 is cylindrical body forms.Spool 320 is formed with recess 321 at an axial end in the face of positive y direction.One end of spring 330 is connected with the recess 321 of spool 320, and the other end links to each other with the bottom 311 of sleeve 310.Spool 320 also is formed with along the through hole 322 of y direction extension and the radial hole 323 that extends along the z direction.Thereby radial hole 323 is connected to recess 321 via through hole 322 hydraulic pressure.

When spool 320 moves along the y direction, when making the radial hole 314 of sleeve 310 be connected with radial hole 323 hydraulic pressure of spool 320, fluid communication passageway C1 is connected to fluid communication passageway C2 via radial hole 314, radial hole 323 and the 4th fluid chamber's D4 hydraulic pressure.

Bar 340 links regularly with iron core 350.By coil 360 excitations, iron core 350 makes bar 340 move along the y direction.Bar 340 has the vertical end 341 that contacts with vertical end 324 of spool 320, so that spool 320 moves along positive y direction.At vertical end 324 of spool 320, the opening of limited hole 322 makes its not overlapping part that contacts with bar 340.This guarantees that bar 340 pushes spool 320 effectively.

When the thrust of iron core 350 was higher than the elastic force of spring 330, spool 320 moved along positive y direction.On the other hand, when iron core 350 was de-energized, spring 330 promoted spool 320 along negative y direction, it is moved along negative y direction, thereby fluid communication passageway C1 and fluid communication passageway C2 hydraulic pressure disconnected.When the thrust of iron core 350 increased, the radial hole 323 of spool 320 was overlapping with the radial hole 314 of sleeve 310, thereby fluid communication passageway C1 is connected with fluid communication passageway C2 hydraulic pressure.

Thrust by regulating solenoid SOL and thus the radial hole 323 overlapping areas of radial hole 314 and the spool 320 of regulating sleeve 310 control flow via the working fluid of fluid communication passageway C.Thereby solenoid valve 300 plays the effect of normally closed linear solenoid valve.During its failure condition, solenoid valve 300 cuts out.Particularly, when solenoid valve SOL broke down or is de-energized, the valve system of solenoid valve 300 was closed.In this case, variable capacity vane pump is only operated based on control valve 200, and can not caused detrimental effects by the fault of solenoid valve 300.

As mentioned above, when solenoid valve 300 was in open mode, fluid communication passageway C opened, and sucked path IN so that the A1 of first fluid pressure chamber hydraulic pressure is connected to.When the interior pressure P1 of the A1 of first fluid pressure chamber was higher than suction pressure Pin, working fluid flowed to via solenoid valve 300 from the A1 of first fluid pressure chamber and sucks path IN.When P1=Pin, working fluid does not flow betwixt.

Put it briefly, when the A1 of first fluid pressure chamber hydraulic pressure is connected to the three-fluid chamber D3 of control valve 200 and safety valve 220 and closes (when satisfy equation (a) and (c) time), even solenoid valve 300 is opened, the interior pressure P1 of the A1 of first fluid pressure chamber also keeps equaling sucking pressure Pin.On the other hand, in other cases (equation (a) and (c) at least one do not satisfy), the A1 of first fluid pressure chamber hydraulic pressure is connected to the first fluid chamber D1 or second D2 of fluid chamber, makes the interior pressure P1 of the A1 of first fluid pressure chamber equal to discharge pressure Pout or the mixed Pm of pressure.Therefore, pressure P 1 is higher than suction pressure Pin.So when solenoid valve 300 was in open mode, pressure P 1 descended.The reduction that comes pilot pressure P1 by the opening degree of regulating solenoid valve 300.

In this embodiment, mainly also control the interior pressure P1 of the A1 of first fluid pressure chamber extraly by solenoid valve 300 by control valve 200.This causes variable capacity vane pump to have the responsiveness of improvement.Because control valve 200 helps basic pressure control, so the control of the simple pressure of the explanation like this of solenoid valve 300 is enough.

In this embodiment, solenoid valve 300 is only controlled among the interior pressure P2 of the interior pressure P1 of the A1 of first fluid pressure chamber and the second fluid pressure chambers A2 one.Therefore, solenoid valve 300 has simple and compact structure.Sucking the structure of pressing Pin (low pressure) to be introduced the second fluid pressure chambers A2 consistently is favourable for making the working fluid leakage minimum from the second fluid pressure chambers A2 to suction port 62 and 121.Can suitably control discharge capacity according to travel condition of vehicle.

Fig. 5 illustrates the variable capacity vane pump according to first embodiment's first modification.In first embodiment, fluid communication passageway C1 has opening in fluid passage 113.In this modification, fluid communication passageway C1 extends to the A1 of first fluid pressure chamber straight via adapter ring 5.

Fig. 6 illustrates the variable capacity vane pump according to first embodiment's second modification.In this modification, fluid communication passageway C2 is replaced by fluid communication passageway C2 '.Fluid communication passageway C2 ' is connected to drain passageway OUT with solenoid valve 300 hydraulic pressure.Particularly, fluid communication passageway C2 ' has opening in the upstream portion of fluid passage 22 with respect to throttle orifice 8, makes to discharge to press Pout to be introduced into solenoid valve 300.Solenoid valve 300 will be discharged and be pressed Pout to introduce the first fluid A1 of pressure chamber via fluid communication passageway C1.

On the other hand, control valve 200 will be discharged and be pressed Pout (under (i) situation), suction to press one among Pin (under (ii-1) situation) and the mixed Pm of pressure (under (ii-2) situation) to introduce the first fluid A1 of pressure chamber.Therefore, when suction presses Pin or the mixed Pm of pressure to be introduced into the A1 of first fluid pressure chamber, can press Pout to improve the interior pressure P1 of the A1 of first fluid pressure chamber to introduce discharge by opening solenoid valve 300.

Although in the aforementioned embodiment, interior pressure by control valve 200 and the solenoid valve 300 control first fluid A1 of pressure chamber, also can control the interior pressure of the second fluid pressure chambers A2, and will suck the pressure Pin introducing first fluid A1 of pressure chamber by control valve 200 and solenoid valve 300.

Fig. 7 illustrates variable capacity vane pump according to a second embodiment of the present invention.The first modification part that second embodiment is different from first embodiment is, in a second embodiment, the control valve 200 control first fluid A1 of pressure chamber and the second fluid pressure chambers A2 the two.

Particularly, adapter ring 5 is formed with near the intercommunicating pore 54 in top of the positive y side that is arranged in Sealing 50, and first housing 11 is formed with fluid passage 119.The second fluid pressure chambers A2 is connected to control valve 200 via fluid pressure chambers intercommunicating pore 54 and fluid passage 119 hydraulic pressure.Fluid passage 119 has opening 119a in the sidewall of valve receiving bore 115.When pump did not turn round, opening 119a pressed Pfb to introduce the second fluid pressure chambers A2 in the face of second D2 of fluid chamber of control valve 200 so that the downstream is discharged.When valve element 210 is shifted along positive y direction, make that fluid passage 119 hydraulic pressure were connected to three-fluid chamber D3 when second slide part 214 was moving on to the front of opening 119a along positive y direction.As mentioned above, when safety valve 220 cut out, the interior pressure of three-fluid chamber D3 equals to suck pressed Pin, and when safety valve 220 was opened, the interior pressure of three-fluid chamber D3 equaled the mixed Pm of pressure.Thereby control valve 200 is by introducing the interior pressure P2 that the second fluid pressure chambers A2 controls the second fluid pressure chambers A2 with one among pressure P fb, Pin and the Pm.In this embodiment, the A1 of first fluid pressure chamber and the second fluid pressure chambers A2 stand high pressure.This makes the motion stabilization of cam ring 4.

Fig. 8 illustrates the variable capacity vane pump according to second embodiment's modification.In this modification, fluid communication passageway C2 is by replacing as the fluid communication passageway C2 ' in first embodiment's second modification.Fluid communication passageway C2 ' is connected to drain passageway OUT with solenoid valve 300 hydraulic pressure.Particularly, fluid communication passageway C2 ' has opening in the upstream portion of fluid passage 22 with respect to throttle orifice 8, makes to discharge to press Pout to be introduced into solenoid valve 300.Solenoid valve 300 will be discharged and be pressed Pout to introduce the first fluid A1 of pressure chamber via fluid communication passageway C1.

Fig. 9 illustrates the variable capacity vane pump of a third embodiment in accordance with the invention.The 3rd embodiment is identical with first embodiment except following structure.In this modification, as shown in Figure 9, the surface tilt of adapter ring 5 by the bottom that is used for supporting cam wheel ring 4 of " N " expression makes the z coordinate reduce along with the increase of y coordinate.What be called " A3 of three-fluid pressure chamber " is connected to the three-fluid chamber D3 of control valve 200 by connector 70 and lid 72 spaces that limit by hydraulic pressure, makes controlled valve pressure P v be introduced into the A3 of three-fluid pressure chamber.The interior pressure P3 of the A3 of three-fluid pressure chamber is used for oppressing cam ring 4 via the bottom 73 of connector 70 along negative y direction.The A3 of three-fluid pressure chamber is connected to via solenoid valve 300 hydraulic pressure and sucks path IN.Thereby the two controls the interior pressure P3 of the A3 of three-fluid pressure chamber control valve 200 and solenoid valve 300.

Particularly, solenoid valve 300 hydraulic pressure are connected to fluid communication passageway C3 and fluid communication passageway C4.Fluid communication passageway C3 hydraulic pressure is connected to the A3 of three-fluid pressure chamber.Fluid communication passageway C4 hydraulic pressure is connected to and sucks path IN.

As shown in Figure 9, imaginary line K-K is defined as the straight line that connects mid point M1 and mid point M2, wherein, mid point M1 is defined as in the terminal of suction port 62 on the sense of rotation of

rotor

3 and 121 to the mid point between the starting end of

exhaust port

63 and 122, and mid point M2 is defined as terminal in exhaust port 63 on the sense of rotation of

rotor

3 and 122 to the mid point between the starting end of suction port 62 and 121.As shown in Figure 9, the surperficial N of adapter ring 5 tilts with respect to imaginary line K-K, makes distance between surperficial N and the imaginary line K-K along with moving and increase to mid point M2 from mid point M1.

Press Pout to increase along with discharging, because the balance between the pump chambers B, cam ring 4 is gradually toward negative z direction bias voltage.The surperficial N of adapter ring 5 is arranged on cam ring 4 along being effectively for the z position of improving cam ring 4 under the situation of negative y direction displacement big (discharge and press the Pout height), and is disadvantageous for the z position that reduces cam ring 4 under the situation of cam ring 4 little along negative y direction displacement (discharge press Pout low).This because to discharge the mobile of the negative z direction in edge of pressing Pout to cause be effectively, makes vibration and noise minimize on high slewing area hanging down for offsetting cam ring 4 thus.

Cup-shaped connector 70 is installed in the connector receiving bore 114 of first housing 11 in the mode that does not contact between the inner periphery of the outer periphery of keeping connector 70 and plug receiving bore 114 saturating fluid, with along y direction longitudinal sliding motion campaign.The opening of the not saturating fluid ground of lid 72 shut-off plug receiving bore 114.Thereby the A3 of three-fluid pressure chamber is limited between the bottom of lid 72 in the connector receiving bore 114 and connector 70.Spring 71 remains in the recess of connector 70, is used for expanding and contraction along the y direction.One end of spring 71 is connected to the bottom of connector 70, and the other end is connected to and covers 72, thereby promotes connector 70 along negative y direction.Thereby connector 70 extends through the radial direction through hole 51 of adapter ring 5, feasible bottom 73 and cam ring 4 constant contacts, and along negative y direction actuating cam ring 4.The outer circumferential periphery 74 of connector 70 and the not saturating fluid ground sliding contact of connector receiving bore 114 are so that the not saturating fluid ground of the second fluid pressure chambers A2 and the A3 of three-fluid pressure chamber is separated.

First housing 11 is formed with the fluid passage 24 that fluid communication passageway C3 hydraulic pressure is connected to control valve 200.Fluid passage 24 has opening 24a in the part of the sidewall of valve receiving bore 115, and this opening 24a is closed by second slide part 214 of valve element 210 when pump does not turn round.When discharge pressure Pout rose by the operation of pump, the interior pressure reduction between the first fluid chamber D1 and second D2 of fluid chamber was promptly discharged the urgent valve element 200 of differential pressure of pressing Pout and downstream to discharge between the pressure Pfb it is advanced along positive y direction.So, the opening 24a of fluid passage 24 can be shifted relatively to face three-fluid chamber D3, three-fluid chamber D3 hydraulic pressure is connected to the A3 of three-fluid pressure chamber, thereby sets the interior pressure P3 of the A3 of three-fluid pressure chamber for equal three-fluid chamber D3 interior pressure Pv3.As illustrating among first embodiment, when safety valve 220 cuts out, the interior pressure Pv3 of three-fluid chamber D3 equals to suck pressure Pin, and when safety valve 220 was opened, the interior pressure Pv3 of three-fluid chamber D3 equaled to press Pin and downstream to discharge the mixed pressure Pm of pressure Pfb based on sucking.Because being higher than to suck, the mixed Pm of pressure presses Pin, so the A3 of three-fluid pressure chamber is effective for preventing that cam ring 4 from too moving along positive y direction.Thereby solenoid valve 300 is controlled the displacement of cam ring 4 by the interior pressure of controlling the A3 of three-fluid pressure chamber.

In the 3rd embodiment, as shown in Figure 9, solenoid valve 300 is arranged in the positive y side and the positive z side of adapter ring 5 in first housing 11.Solenoid valve 300 is connected to the A3 of three-fluid pressure chamber via fluid communication passageway C3 hydraulic pressure, and is connected to suction path IN via fluid communication passageway C4 hydraulic pressure.Thereby the A3 of three-fluid pressure chamber is connected to via solenoid valve 300 and sucks path IN.Solenoid valve 300 optionally makes the A3 of three-fluid pressure chamber be connected with suction path IN and makes the A3 of three-fluid pressure chamber and suck path IN disconnection.When the interior pressure of the A3 of three-fluid pressure chamber equals the mixed Pm of pressure when (be higher than to suck and press Pin), the opening operation of solenoid valve 300 flows out to the working fluid in the A3 of three-fluid pressure chamber and sucks path IN, reduces the interior pressure P3 of the A3 of three-fluid pressure chamber.

Figure 10 illustrates the variable capacity vane pump according to the 3rd embodiment's modification.In this modification, solenoid valve 300 is connected to drain passageway OUT via fluid communication passageway C4 ' hydraulic pressure.When solenoid valve 300 was in open mode, the A3 of three-fluid pressure chamber hydraulic pressure was connected to drain passageway OUT.Control valve 200 can be selected to suck pressure Pin and mix an introducing three-fluid A3 of pressure chamber who presses among the Pm, and Pin and mixed pressure Pm are pressed in this suction, and the two all presses Pout less than discharge.Thereby, when solenoid valve 300 is in open mode, discharges and press Pout to be introduced into the A3 of three-fluid pressure chamber.This has improved the interior pressure of the A3 of three-fluid pressure chamber, increases the power of the negative y direction in edge that is applied on the cam ring 4.Thereby, can be by the displacement of solenoid valve 300 adjustment cam rings 4.

Figure 11 illustrates the variable capacity vane pump according to fourth embodiment of the invention.The 4th embodiment is identical with the 3rd embodiment except following structure.In the 4th embodiment, the A3 of three-fluid pressure chamber is connected to second D2 of fluid chamber rather than the three-fluid chamber D3 of control valve 200 by hydraulic pressure.

As shown in figure 11, first housing 11 is formed with the fluid passage 25 that fluid communication passageway C3 hydraulic pressure is connected to control valve 200.Fluid passage 25 has opening 25a in the part of the sidewall of valve receiving bore 115.Be independent of the position of the valve element 210 of control valve 200, opening 25a is consistently in the face of second D2 of fluid chamber.Thereby the A3 of three-fluid pressure chamber is connected to second D2 of fluid chamber of control valve 200 consistently, presses the interior pressure of second D2 of fluid chamber of Pfb to be introduced the A3 of three-fluid pressure chamber consistently thereby equal the downstream discharge.In addition, solenoid valve 300 optionally makes the A3 of three-fluid pressure chamber be connected with suction path IN and makes the A3 of three-fluid pressure chamber and suck path IN disconnection, thereby reduces the interior pressure P3 of the A3 of three-fluid pressure chamber.Obtain aforementioned effect by simple and compact solenoid valve is set, this solenoid valve directly interior pressure P3 and the responsiveness of the control three-fluid A3 of pressure chamber is improved.Thereby, can control discharge capacity based on running state.

Figure 12 illustrates the variable capacity vane pump according to the 4th embodiment's modification.In this modification, solenoid valve 300 is connected to drain passageway OUT via fluid communication passageway C4a hydraulic pressure.Solenoid valve 300 optionally makes the A3 of three-fluid pressure chamber be connected with drain passageway OUT and makes the A3 of three-fluid pressure chamber and drain passageway OUT disconnection.Control valve 200 is discharged the downstream consistently and is pressed Pfb to introduce the A3 of three-fluid pressure chamber.When solenoid valve 300 is in open mode, because discharging, the downstream press Pfb to be lower than discharge pressure Pout, so the interior pressure of the A3 of three-fluid pressure chamber improves.

Figure 13,14 and 15 variable capacity vane pumps that illustrate according to a fifth embodiment of the invention.The 5th embodiment is different from first embodiment's part and is solenoid valve 300 near suction path IN layout, and solenoid valve 300 is connected to the A1 of first fluid pressure chamber via the fluid communication passageway C5 hydraulic pressure that the axis along rotor 3 extends.

As shown in figure 13, solenoid valve 300 is configured in first housing 11 with respect to the positive x side of rotor 3 and positive z side, near the opening that sucks path IN.Solenoid valve 300 is connected to the A1 of first fluid pressure chamber via the fluid communication passageway C5 hydraulic pressure that the axis along rotor 3 extends.Fluid communication passageway C6 is connected to solenoid valve 300 hydraulic pressure and sucks path IN.Thereby solenoid valve 300 is disposed among the fluid communication passageway C that comprises fluid communication passageway C5 and fluid communication passageway C6.

Shown in Figure 14 and 15, fluid communication passageway C5 has open C 5a in the part of second housing 12, the feasible position that is independent of cam ring 4, at least a portion of open C 5a is led to the A1 of first fluid pressure chamber consistently, and fluid communication passageway C5 is connected to the A1 of first fluid pressure chamber consistently thus.Replacedly, can promptly in pressing plate 6, limit open C 5a at another axial end of the A1 of first fluid pressure chamber.So the open C 5a of configuration operates solenoid valve 300 consistently with high responsiveness.

According to the 5th embodiment, owing to make the parts of the outside of the pump housing 10 be corrected closer to each otherly, the variable capacity vane pump structure is compact.Can as illustrating among second, third and the 4th embodiment, revise the relation between control valve 200, the A1 of first fluid pressure chamber and the second fluid pressure chambers A2.

Figure 16 illustrates the variable capacity vane pump according to the 5th embodiment's modification.In this modification, solenoid valve 300 has the longitudinal axis perpendicular to the axis of rotor 3 and live axle 2.Solenoid valve 300 is installed in the pump housing 10 outsides, and near opening that sucks path IN and the A1 of first fluid pressure chamber configuration.In the time of on being connected to live axle 2, pulley radially extends from live axle 2.Therefore, the vane pump 1 of band pulley need be on the z direction than the arrangement space of the pump housing 10 longer extensions.Because the arrangement space of pulley can also be used for solenoid valve 300,, there is not unnecessary radial dimension elongation so this embodiment's variable capacity vane pump has compact size in the x direction.

Figure 17 illustrates the variable capacity vane pump according to sixth embodiment of the invention.It is as described below that the 6th embodiment is different from the previous embodiment part.In this embodiment, variable capacity vane pump does not comprise control valve 200.

Solenoid valve 300 ' is connected to suction

port

62 and 121 via fluid communication passageway C8 hydraulic pressure.Solenoid valve 300 ' also is connected to the A1 of first fluid pressure chamber via being formed on intercommunicating pore 52 in the adapter ring 5 and the fluid communication passageway C7 hydraulic pressure that is formed in first housing 11.In addition, solenoid valve 300 ' is connected to drain passageway OUT via the fluid communication passageway C9 hydraulic pressure that is formed in first housing 11.Thereby solenoid valve 300 ' is arranged in the path that comprises fluid communication passageway C7, C8 and C9.

The second fluid pressure chambers A2 is connected to drain passageway OUT via fluid passage 26 and fluid pressure chambers intercommunicating pore 54 hydraulic pressure.Therefore, discharge pressure Pout and introduced the second fluid pressure chambers A2 consistently.Drain passageway OUT is included in the throttle orifice 7 between fluid communication passageway C9 and the fluid passage 26.

Solenoid valve 300 ' comprises spool 320 ', spring 330 ', bar 340, iron core 350 and coil 360.Sleeve 310 is not set in this embodiment.

Spool 320 ' is the general cylindrical form.Spool 320 ' is accommodated in the valve receiving bore 117 ', with the saturating fluid ground sliding contact of valve receiving bore 117 '.Valve receiving bore 117 ' has vertical end 117a ' in positive y side, has another vertically end 117b ' in negative y side.Between vertical end 117a ' of spool 320 ' and valve receiving bore 117 ', limit the 5th D5 ' of fluid chamber.One end of spring 330 ' is connected to vertical end 117a ', to promote spool 320 ' along negative y direction.

On the other hand, at one of spool 320 ' vertical qualification the 4th D4 ' of fluid chamber between vertical end 117b ' of end 321 ' and valve receiving bore 117 '.Fluid communication passageway C8 has open C 8a in the sidewall of the 4th D4 ' of fluid chamber.Be independent of the position of spool 320 ', fluid communication passageway C8 is connected to the 4th D4 ' of fluid chamber consistently.Fluid communication passageway C7 has open C 7a in the sidewall with respect to the positive y side of open C 8a of valve receiving bore 117 '.In addition, fluid communication passageway C9 has in the sidewall of valve receiving bore 117 ' and open C 7a opening opposing C9a.Spool 320 ' is radially comprising groove 323 ' in the outer peripheral surface 322 ', and groove 323 ' extends around whole circumference.

When spool 320 ' was shifted along negative y direction, the open C 7a of fluid communication passageway C7 was connected to the open C 8a of fluid communication passageway C8 via groove 323 ' hydraulic pressure.On the other hand, when spool 320 ' was shifted along positive y direction, the open C 7a of fluid communication passageway C7 was connected to the open C 9a of fluid communication passageway C9 via groove 323 ' hydraulic pressure.No matter where spool 320 ' is positioned at, and the open C 9a hydraulic pressure of the open C 8a of fluid communication passageway C8 and fluid communication passageway C9 is separated.

Thereby, solenoid valve 300 ' with fluid communication passageway C7 optionally hydraulic pressure be connected among fluid communication passageway C8 and the C9 one so that the A1 of first fluid pressure chamber selects shape ground hydraulic pressure to be connected to suction

port

62 and 121 or drain passageway OUT.

Spool 320 ' is formed with the through hole 324 ' that extends along the y direction, makes the 5th fluid chamber's D5 ' hydraulic pressure be connected to the 4th D4 ' of fluid chamber.Thereby, suck and press Pin to introduce the 5th D5 ' of fluid chamber from the 4th D4 ' of fluid chamber.Therefore, spool 320 ' is subjected to pressing along the two the suction of positive y direction and negative y direction the effect of Pin.On the other hand, discharge pressure Pout and only be applied to groove 323 '.Put it briefly, suck and press Pin and discharge to press Pout in spool 320 ', to offset.Solenoid SOL can produce the enough thrust of antagonistic spring 330 '.Therefore, solenoid SOL forms simple and compactly.

The bar 340 of solenoid valve 300 ' contacts with the axial end 321 ' of spool 320.Solenoid valve 300 ' makes spool 320 slide along the y direction, the A1 of first fluid pressure chamber optionally is connected to suction

port

62 and 121 or drain passageway OUT.

As mentioned above, discharge and press Pout to be introduced the second fluid pressure chambers A2 consistently, and solenoid valve 300 ' optionally will be discharged pressure Pout and suction presses one among the Pin to introduce the first fluid A1 of pressure chamber.Thereby, by the position of solenoid valve 300 ' control cam ring 4.

Figure 18 illustrates the variable capacity vane pump according to the 6th embodiment's first modification.In this modification, suck the position that path IN and drain passageway OUT are arranged in modification.

Figure 19 illustrates the variable capacity vane pump according to the 6th embodiment's second modification.This modification is different from the first modification part and is that the second fluid pressure chambers A2 is connected to suction path IN by hydraulic pressure, rather than drain passageway OUT.In this modification, first housing 11 is formed with the second fluid pressure chambers A2 hydraulic pressure is connected to the fluid passage 26 ' that sucks path IN.

Figure 20 illustrates the variable capacity vane pump according to the 6th embodiment's the 3rd modification.This modification is different from the first modification part and is that solenoid valve 300 ' is connected to the second fluid pressure chambers A2 by hydraulic pressure, rather than the A1 of first fluid pressure chamber.In this modification, the A1 of first fluid pressure chamber is connected to drain passageway OUT via fluid communication passageway C8 ' hydraulic pressure, and the second fluid pressure chambers A2 is connected to solenoid valve 300 ' via fluid communication passageway C7 ' and fluid pressure chambers intercommunicating pore 54.In addition, first housing 11 is formed with the fluid passage 21 ' that comprises throttle orifice 8.Thereby, suck and press Pin and discharge to press one among the Pout optionally to be introduced into the second fluid pressure chambers A2.Solenoid valve 300 ' is arranged in the positive y side with respect to live axle 2, and in first modification, solenoid valve 300 ' is arranged in negative y side.

Figure 21 illustrates the variable capacity vane pump according to the 6th embodiment's the 4th modification.This modification is different from the 3rd modification part and is that the A1 of first fluid pressure chamber is connected to suction consistently and presses Pin.In this modification, first housing 11 is formed with the A1 of first fluid pressure chamber hydraulic pressure is connected to the fluid communication passageway C8 ' that sucks path IN.

Figure 22 illustrates the variable capacity vane pump according to the 6th embodiment's the 5th modification.Provide this modification based on the 3rd embodiment, cancelled control valve 200.Particularly, first housing 11 is formed with the fluid communication passageway C3 ' that solenoid valve 300 ' hydraulic pressure is connected to the A3 of three-fluid pressure chamber, and the A3 of this three-fluid pressure chamber is limited between connector 70 and the lid 72.First housing 11 is formed with the fluid communication passageway C9 ' that solenoid valve 300 ' hydraulic pressure is connected to drain passageway OUT.In addition, first housing 11 is formed with solenoid valve 300 ' hydraulic pressure is connected to the fluid communication passageway C8 that sucks path IN ".Solenoid valve 300 ' optionally will suck presses Pin and discharges an introducing three-fluid A3 of pressure chamber who presses among the Pout.

The No.2006-63851 of Japanese patent application formerly that the application submitted to based on March 9th, 2006.The full content of this Japanese patent application No.2006-63851 is introduced in this as a reference.

Although the present invention has been described above, the invention is not restricted to the embodiment of above-mentioned explanation with reference to some embodiments of the present invention.To those skilled in the art, under above-mentioned teaching, can make amendment and change the foregoing description.Limit scope of the present invention with reference to claims.

Claims

1. variable capacity vane pump, it comprises:

The pump housing;

Cam ring, it movably is installed in the pump housing, this cam ring and pump housing between limit first and second fluid pressure chambers, this first fluid pressure chamber has the volume that increases when cam ring when first end position moves, this second fluid pressure chambers has the volume that increases when cam ring when second end position moves;

Rotor, it is installed in cam ring inside, is used at least rotating along a direction around axis, and this rotor is in its outside annular chamber that limits;

A plurality of blades, it is used for moving along with the rotation of rotor in the outer radial periphery edge of rotor circumference, and this blade radial extends and annular chamber is divided into a plurality of pump chambers;

Suction port, its be limited to annular chamber first portion in, in this first portion, each pump chambers enlarges along with the rotation of rotor;

Exhaust port, its be limited to annular chamber second portion in, in this second portion, each pump chambers is dwindled along with the rotation of rotor, described exhaust port limits the third part of sense of rotation from the suction port to the exhaust port along rotor of annular chamber, and the volume of this third part ratio when cam ring is in second end position is big when cam ring is in first end position;

First fluid path, its hydraulic pressure are connected in first and second fluid pressure chambers;

Second fluid passage, its hydraulic pressure are connected in suction port and the exhaust port; And

Solenoid valve, its hydraulic pressure is connected to first and second fluid passages, and the fluid that is used to control between the two is communicated with.

2. variable capacity vane pump as claimed in claim 1 also comprises:

Drain passageway, it is positioned at the downstream with respect to exhaust port, and this drain passageway comprises throttle orifice; And

Control valve, its hydraulic pressure are connected to upstream portion and the downstream portion of drain passageway with respect to throttle orifice, and hydraulic pressure is connected to one in first and second fluid pressure chambers, are used for controlling described one the interior pressure of first and second fluid pressure chambers.

3. variable capacity vane pump as claimed in claim 2 is characterized in that,

The second fluid pressure chambers hydraulic pressure is connected to suction port;

Control valve hydraulic pressure is connected to suction port; And

Control valve with first fluid pressure chamber optionally hydraulic pressure be connected in suction port and the exhaust port one.

4. variable capacity vane pump as claimed in claim 2 is characterized in that,

Control valve is connected to the upstream portion of drain passageway with first fluid pressure chamber hydraulic pressure, and the second fluid pressure chambers hydraulic pressure is connected to the downstream portion of drain passageway.

5. variable capacity vane pump as claimed in claim 4 is characterized in that,

First fluid path hydraulic pressure is connected to first fluid pressure chamber;

The second fluid passage hydraulic pressure is connected to exhaust port; And

Electromagnetic valve first fluid pressure chamber is communicated with fluid between the exhaust port.

6. variable capacity vane pump as claimed in claim 4 is characterized in that,

The second fluid passage hydraulic pressure is connected to suction port; And

Fluid flow between electromagnetic valve first fluid pressure chamber and the suction port.

7. variable capacity vane pump as claimed in claim 2 is characterized in that,

Control valve hydraulic pressure is connected to suction port; And

Control valve with second fluid pressure chambers optionally hydraulic pressure be connected in suction port and the exhaust port one.

8. variable capacity vane pump as claimed in claim 7 is characterized in that,

First fluid path hydraulic pressure is connected to second fluid pressure chambers;

The second fluid passage hydraulic pressure is connected to exhaust port; And

Electromagnetic valve second fluid pressure chambers is communicated with fluid between the exhaust port.

9. variable capacity vane pump as claimed in claim 2 also comprises:

Separator, itself and cam ring are installed in the pump housing in contact, this separator limits three-fluid pressure chamber and described second fluid pressure chambers in its both sides, this three-fluid pressure chamber has along the interior pressure of directive effect on cam ring that cam ring is moved towards second end position; And

The three-fluid path, its hydraulic pressure is connected to three-fluid pressure chamber,

Wherein, described solenoid valve hydraulic pressure is connected to the three-fluid path, and the fluid that is used to control by the three-fluid path is communicated with.

10. variable capacity vane pump as claimed in claim 1 is characterized in that,

The first fluid path has one opening of one the axial end that is arranged in first and second fluid pressure chambers.

11. variable capacity vane pump as claimed in claim 10 is characterized in that,

The position of the opening of described first fluid path is defined as and makes that at least a portion of this opening is led in first and second fluid pressure chambers consistently when arbitrary position of cam ring between first and second end positions.

12. variable capacity vane pump as claimed in claim 1 also comprises:

The 4th fluid passage, it is connected to exhaust port with solenoid valve hydraulic pressure, and wherein, described one in suction port and the exhaust port is suction port; Solenoid valve optionally is connected in the second and the 4th fluid passage one with the first fluid path.

13. variable capacity vane pump as claimed in claim 12 is characterized in that,

Described one in first and second fluid pressure chambers is first fluid pressure chamber.

14. variable capacity vane pump as claimed in claim 12 is characterized in that,

Described one in first and second fluid pressure chambers is second fluid pressure chambers.

15. variable capacity vane pump as claimed in claim 12 also comprises:

The three-fluid path, it is connected to three-fluid pressure chamber with solenoid valve hydraulic pressure,

Wherein, solenoid valve with the three-fluid path optionally hydraulic pressure be connected in the second and the 4th fluid passage one.

16. variable capacity vane pump as claimed in claim 1 is characterized in that,

Solenoid valve comprises the valve system that is arranged between first and second fluid passage and is used to control the electromagnetic actuators of this valve system.

17. variable capacity vane pump as claimed in claim 16 also comprises:

Suck path, it is limited in the pump housing, and hydraulic pressure is connected to suction port and outside suction pipe, and wherein, electromagnetic actuators is near the aperture arrangement that sucks path.

18. variable capacity vane pump as claimed in claim 17 is characterized in that,

Electromagnetic actuators has the longitudinal axis perpendicular to the axis of rotor.

19. variable capacity vane pump as claimed in claim 16 is characterized in that,

The valve system of solenoid valve is closed when electromagnetic actuators breaks down.

20. variable capacity vane pump as claimed in claim 19 is characterized in that,

The valve system of solenoid valve is closed when electromagnetic actuators is de-energized.

21. variable capacity vane pump as claimed in claim 1 also comprises:

Live axle, it is supported on the pump housing rotationally and is mechanically connected to rotor, to rotate along with the rotation of rotor;

Sealing, its outer radial at cam ring arranges that the sealing part limits described first and second fluid pressure chambers in its both sides;

First member, it is installed in the pump housing and is arranged in an axial end place of cam ring; And

Second member, it is installed in the pump housing and is arranged in another axial end place of cam ring,

Wherein, rotor is included in a plurality of grooves that the radially outer circumferential periphery of rotor is arranged, each groove radially extends and holds in the blade corresponding one, to allow the longitudinal movement of blade;

Suction port is limited among in first and second members one;

Exhaust port is limited among in first and second members one; And

Electromagnetic valve first fluid pressure chamber be communicated with fluid between the exhaust port and second fluid pressure chambers and suction port and exhaust port in one between fluid be communicated with.

22. a variable capacity vane pump, it comprises:

The pump housing;

A plurality of blades, it is used for moving along with the rotation of rotor in the configuration of the outer radial periphery edge of rotor circumference, and this blade radial extends and described annular chamber is divided into a plurality of pump chambers;

Separator, itself and cam ring are installed in the pump housing in contact, this separator limits three-fluid pressure chamber and described second fluid pressure chambers in its both sides, this three-fluid pressure chamber has along the interior pressure of directive effect on cam ring that cam ring is moved towards second end position;

The three-fluid path, its hydraulic pressure is connected to three-fluid pressure chamber; And

First valve, its hydraulic pressure is connected to the three-fluid path, is communicated with the fluid of control via the three-fluid path.

23. variable capacity vane pump as claimed in claim 22 also comprises:

Second fluid passage, its hydraulic pressure is connected to suction port; And

The 5th fluid passage, it is connected to exhaust port with three-fluid pressure chamber hydraulic pressure,

Wherein, the first valve hydraulic pressure is connected to second fluid passage, with control second and the three-fluid path between fluid flow.

24. variable capacity vane pump as claimed in claim 22 also comprises:

The 4th fluid passage, its hydraulic pressure is connected to exhaust port,

Wherein, the first valve hydraulic pressure is connected to the 4th fluid passage, with control the 3rd with the 4th fluid passage between fluid be communicated with.

25. a method of controlling vehicle with variable capacity vane pump, this variable capacity vane pump comprises: the pump housing; Cam ring, it movably is installed in the pump housing, and this cam ring limits at least one pump chambers and first fluid pressure chamber, and this first fluid pressure chamber has the interior pressure that acts on the cam ring; Suction port; Exhaust port; Drain passageway, it is positioned at the downstream with respect to exhaust port, and drain passageway comprises throttle orifice; Control valve, it is used to control the interior pressure of first fluid pressure chamber, and this control valve response is from the pressure operation of drain passageway with respect to the upstream and downstream portion of throttle orifice; Solenoid valve, the fluid that is used to control between first fluid pressure chamber, suction port and the exhaust port is communicated with, and this method comprises;

Regulate controlled interior pressure of first fluid pressure chamber by solenoid valve according to the running state of vehicle.

26. method as claimed in claim 25 also is included in during the fault state of solenoid valve, closes this solenoid valve.