CN100425837C - Vane pump - Google Patents

Abstract

The present invention relates to a vane pump which comprises a side plate, a rotor and vanes, wherein the side plate is arranged at the side parts of a stator and discharge ports (21 and 23) are formed on an opening of the side plate; the rotor is arranged in the stator in a free rotating way and is driven to rotate by a drive shaft; the vanes are kept in a plurality of gaps formed on the outer circumferential part of the rotor in a radial direction in the way that the vanes freely comes in and out toward the direction of the inner circumferential face of the stator; whisker-shaped grooves (40 and 40) communicated with the discharge ports are formed on the inner side face forming a sliding contact with the rotor of the side plate, and are formed in the way that the discharge ports gradually form a taper shape along the opposite direction of the rotation direction of the rotor; simultaneously, the front end parts (40b and 40b) of the whisker-shaped grooves points as the inner part by a rotating trajectory X of the base end parts (40a and 40a) of the whisker-shaped grooves of each vane.

Description

Vane pump

Technical field

The present invention relates to be used for the vane pump of oil pressure supply source etc. of the power steering gear of vehicle.

Background technique

This kind is used for vehicle, provided various products in the past as vane pump always, and as one of them, the spy who issues in the Japan special permission Room opens the invention described in the flat 10-89266 communique for well-known.

This vane pump is placed stator respectively and at the side plate of this stator sidepiece in the inside of pump case, simultaneously, the inner rotation of described stator freely be provided with and this stator between form the vane rotor of pressure chamber.

At the peripheral part of this vane rotor, on the almost equally spaced position of circumferencial direction, form a plurality of slits along the radiation direction, blade is supported in the inside in this each slit respectively with freely coming in and going out to the inner peripheral surface direction of stator.

Described side plate forms exhaust port on an end face of vane rotor side, simultaneously, base end part is in must the shape groove being provided with extending with the direction of the direction of rotation of vane rotor of the peritreme upper shed of exhaust port, describedly must form opening area by the curve towards exhaust port and smooth variation by the shape groove.

Described vane rotor links with an end of the live axle that leads in the pump case interpolation.The driven pulley of this live axle by being installed in the other end side transmits rotatory force from the bent axle of motor with synchronous belt.

In addition, as long as vane rotor rotates along with the rotating drive of described live axle, each blade is outstanding from the slit with the pressure of back pressure chamber, and rotate on the inner peripheral surface sliding contact limit of the front end limit of each blade and stator.Therefore, discharge to exhaust port by each blade compresses limit, implement the effect of pump from the workflow cognition limit that the suction port that forms in pump case flows in each interlobate pump chamber.

When described pump chamber is communicated with exhaust port, for the high pressure that prevents exhaust port flows in pump chamber sharp, form so-called must the shape groove, the pressure by this palpus shape groove Control work fluid will rise sleekly and not change the reduction hydro pulse sharp in exhaust port.

Yet as described existing vane pump, each that forms on side plate must form towards exhaust port and by the curve that slyness changes by the shape groove, the radial outside of a side of the blade that front end sensing rotation is moved.

Therefore, when the rotation along with vane rotor, a blade moves in the front end rotation of palpus shape groove, when becoming high pressure in the exhaust port, this pressurized working fluid is adverse current in palpus shape groove, clashes near the outer end radially of a side of the next blade of adjacency from front end.Thereby, effect and the rightabout load of sense of rotation on this blade, the opposing that applies reverse direction on vane rotor is loaded.Pump efficiency might descend as a result.

By with the rightabout load of described blade sense of rotation, the excessive stress that in the slit of described vane rotor, has, this slit might be out of shape.

Summary of the invention

The present invention proposes in view of existing technical task, a kind of vane pump of a first aspect of the present invention, and it comprises: stator, it is taken in and is configured in the pump case; Side plate, it is configured in the sidepiece of this stator, and opening forms exhaust port; Rotor, its rotation freely is placed in this stator, by the drive shaft rotation, the while forms a plurality of in the slit of peripheral part to the extension of radiation direction in a circumferential direction, forms the slit formation portion of the convex of extending to radial outside on two sidepieces of this slit circumferencial direction; Blade, its inner peripheral surface direction to described stator is come in and gone out and is freely remained in the described slit; Palpus shape groove, it forms breach on described side plate and inner side surface described rotor sliding contact, and be communicated with described exhaust port, it is characterized in that, becoming gradually from described exhaust port edge with the direction of the direction of rotation of described rotor, tapered ground forms described palpus shape groove, simultaneously, the front end of this palpus shape groove and the described slit formation portion ground that overlaps is formed.

According to this invention, when rotation along with vane rotor, when a blade pass is crossed the front end of palpus shape groove, from exhaust port must shape in the groove adverse current pressurized working fluid from point to must the shape groove front end, the radial inner end side of a side of the next blade of the front end bump adjacency of side in promptly pointing to.Therefore, to enough little, also descend significantly to the power of the reverse direction of vane rotor with the load (moment) of the direction of rotation direction of relative such blade.The result can suppress the decline of pump efficiency.

The vane pump of a second aspect of the present invention, make described must shape the elongation line of front of the slot portion point to roughly base portion by a side radial length of blade, this blade is along with near the rotation of described rotor rotation must the shape groove is moved.

According to the present invention, as previously mentioned since from exhaust port must shape the working fluid and base portion side collision of adverse current the groove in abutting connection with the inner end of a side of blade, can further reduce the reciprocal load relative with blade.

The vane pump of a third aspect of the present invention, the front end of described palpus shape groove must rotate the direction blade prolongation formation of moving near the shape groove towards the rotation of following described rotor.

Thereby, according to the present invention, by prolong to form must the shape groove front end, to the Directivity grow of the inner end direction radially of a side of adjacency blade, can be more reliably to the inner end direction direct high pressure working fluid of a side.

In addition, must the shape groove by prolonging, for example, particularly keep straight on running when waiting, the variation of the discharge oil pressure in the time of can reducing little amplitude rotating operation steering wheel at vehicle.Promptly when little amplitude rotating operation steering wheel, exhaust port and in its vicinity the differential pressure of the mobile a pair of interlobate pump chamber of rotation can diminish.And along with the rotation of rotor, near the described pump chamber that rotation is moved exhaust port is by must becoming early with the starting point that is communicated with of exhaust port by the shape groove of prolonging, the rotational velocity of relative blade, and the connection time of described pump chamber and exhaust port is elongated.Thereby because the traveling time of the pump chamber of the working fluid in exhaust port is elongated, the pressure (oil pressure) that reduces the working fluid in exhaust port changes.

Even the result when rotating operation steering wheel slightly, also can reduce the hydro pulse in the exhaust port.

Description of drawings

Fig. 1 is the sectional arrangement drawing of the vane pump of expression an embodiment of the present invention;

Fig. 2 is the A-A line sectional drawing of Fig. 1;

Fig. 3 is the vane rotor that provides of present embodiment and the front elevation of stator;

Fig. 4 is the B-B sectional drawing of Fig. 3;

Fig. 5 is the front elevation of the arrow C-side plate that the C direction is seen from Fig. 1;

Fig. 6 is the sectional arrangement drawing of palpus shape groove;

Fig. 7 be expression must shape the D of Fig. 6 of groove to view;

Fig. 8 is the back elevation of described side plate;

Fig. 9 is the E-E line sectional drawing of Fig. 8;

Figure 10 is the sectional arrangement drawing of another routine vane pump of expression;

Figure 11 is the front elevation of the back plate seen from the arrow F-F direction of Figure 10;

Figure 12 is the G-G line sectional drawing of Figure 11;

Figure 13 is the enlarged view of the arrow H portion of Figure 12.

Embodiment

Below, the mode of execution of vane pump of the present invention is described in detail in detail with reference to the accompanying drawings.

This vane pump is the same with existing pump, is the pump that is applicable to as the supply source of the oil pressure mechanical oil-pressures such as power steering gear of supply vehicle.As shown in Figure 1, its mainly by the pump case 1 on the cylinder body that is fixed on internal-combustion engine with screw etc., be configured in pump main body 2 in this pump case 1 and a tip side and insert logical live axle 3 in the inside of pump case 1 and constitute.

Described pump case 1 is made up of the pump housing 6 with the bulk that sucks path 4 and drain passageway 5 and the pump cover 7 that combines with its pump housing 6 as shown in Figures 1 and 2, is provided with the space portion of placing pump main body 2 between this pump housing 6 and pump cover 7.

Described pump main body 2 is as Fig. 1～shown in Figure 4, comprises accommodating the stator 8 that is configured in described pump cover 7 inside, rotating the pair of side plates 10,11 that freely is arranged on the vane rotor 9 of these stator 8 inboards and is configured in described stator 8 both sides.

Described live axle 3 is being installed the driven pulley 19 that transmits driving usefulness from the pump housing 6 outstanding the other end, by being wrapped in the outer belt of figure on this driven pulley 19, can transmit the power of motor.

Described stator 8 uses the chimeric locating stud of cotter way 8b, 8c 13,13 of putting with a pair of small semicircle shape that forms on the position of 180 ° of the cardinal principles of outer circumferential face to be positioned at circumferencial direction on the pump case 1 as shown in Figure 3, and simultaneously, inner peripheral surface 8a forms ellipticity substantially.

Described vane rotor 9 usefulness sintered alloy unitary mouldings are discoid substantially, are divided into circular substantially pump chamber 14 between the inner peripheral surface 8a of outer circumferential face and stator 8.In addition, in the central authorities of vane rotor 9, the breakthrough form toothing is in conjunction with the zigzag fashion hole 9a of the front end 3a of described live axle 3, and described live axle 3 connects described side plate 10,11.Simultaneously, at peripheral part, on the uniformly-spaced position of circumferencial direction, form 10 slits 15 radially.

This each slit 15 keeps laminal blade 16 in inside to radiation direction free sliding ground respectively, simultaneously, forms in the bottom and to make each blade 16 back pressure chamber 15a that 15 opening end is given prominence to the inner peripheral surface 8a of stator 8 direction from the slit.

In addition, this vane rotor 9 forms circular-arc weight reduction portion 18 as Fig. 1, Fig. 3, shown in Figure 5, and it is the notch part on the position beyond this slit formation portion 17 in described each slit 15 that forms outer circumferential face.

Described each slit formation portion 17 forms convex respectively by the existence of each weight reduction portion 18, simultaneously, forms described slit 15 respectively on the approximate centre position of circumferencial direction.

The side plate 10 of described side's side and the end face crimping of the pump housing 6, in its pressure contact portion, as Fig. 1, Fig. 2 and Fig. 5, shown in Figure 8, with a side of vane rotor 9 sliding contact sides on form the pairing left and right suction port 20,20 that the footpath that is connected with the suction path 4 that has makes progress on the pump housing 6, simultaneously, with the crisscross position of this suction port 20,20 on form a pair of first, second exhaust port 21,34.

On the side plate 11 of described opposite side, at described relatively first exhaust port 21, clip and form the 3rd exhaust port 35 on the symmetrical position of stator 8, described first exhaust port 21 and the 3rd exhaust port 35 and 22 interior connections of pressure chamber described later.In addition, forming the little opening portion 21a of opening area with described first exhaust port 21 of stator 8 opposition sides of side plate 10.

And then, described second exhaust port 34 is as Fig. 1, Fig. 8, shown in Figure 9, the opening portion 34a that the discharge oral area of the zonal and arc of open area ratio stator 8 sides and this discharge oral area on the face of opposition side are also little is roughly fan-shaped to going out interruption-forming from the inlet of fluid, its opening area is set at littler than the opening area of the opening portion 21a of first exhaust port 21 and the 3rd exhaust port 35, and bigger than existing opening portion.

Widen in the maximum of the opening portion 34a of described second exhaust port 34 and to set up bridge 36 on the position, simultaneously, the total length that runs through bridge 36 at the described outlet side of this bridge 36 forms the notch part 37 that the guiding working fluid flows.

Described side plate 10 on same side, with the reciprocal peritreme 21b of sense of rotation, the 34b of the vane rotor 9 of described each exhaust port 21,34 on form a pair of must shape groove 40,40.

Respectively palpus shape groove 40,40 is as Fig. 3 and shown in Figure 5, be arranged to roughly circular-arc from each peritreme 21b, 34b edge of each exhaust port 21,34 with the direction extension of the direction of rotation of vane rotor 9, run through formation front end tapered from base end part 40a to front end 40b, simultaneously, the degree of depth is shown in the longitudinal section of Fig. 6, formation shoals to front end 40b gradually from the darkest base end part 40a, forms at this front end 40b and slightly upwards sharply holds up.In addition, shown in the cross section of Fig. 7, form roughly V word shape, bottom 40c forms acute angle.

Front end 40b ratio more points to interior square one-tenth by the rotary motion trace line (X represents with dot and dash line) of each blade 16 of the approximate centre of described base end part 40a.Promptly this front end 40b forms its elongation line (P line) and also points to close base portion than the substantial middle position of the radial length of blade 16.This blade 16 is along with near the rotation of described vane rotor 9 rotation must shape groove 40 is moved.

In addition, front end 40b prolong to form than described existing must the shape flute length, even below half of the length of the maximum circumferencial direction that also is set at 16,16 in adjacent a pair of blade of its length, simultaneously, further form tapered gradually.

Between the inner peripheral surface of the outer circumferential face of pump main body 2 and pump cover 7, be provided with the pressure chamber 22 that the working oil of discharging from described first～the 3rd exhaust port 21,34,35 flows into.This pressure chamber 22 be located at the pump housing 6 on drain passageway 5 be connected side by side with vent pathway 24 that this path 5 radially forms on the opposition side.

On described drain passageway 5, be provided with variable restrictor device 25, and the upstream extremity of vent pathway 24 be provided with the front and back pressure reduction servo-actuated of variable restrictor device 25 escape cock 26.

Described variable restrictor device 25 comprises: the guiding valve putting hole 27 that forms on the end face of the pressure chamber of the pump housing 6 22 sides; Being advanced and retreat freely is placed in this guiding valve putting hole 27, makes the guiding valve 28 of the opening area increase and decrease of drain passageway 5 according to its advance and retreat position; Make this guiding valve 28 to the pressured spring 29 of pressure chamber's 22 sides.

And this variable restrictor device 25 utilizes the balance advance and retreat action to the elastic force of the oil pressure of the pressure chamber 22 of an end effect of guiding valve 28 and spring 29, and simultaneously, the opening area that is set in drain passageway 5 on the initial position that guiding valve 28 and side plate 10 touch is for maximum.And, the relative position upper shed of the end face with guiding valve 28 of described second exhaust port 34 in side plate 10.

On the other hand, escape cock 26 comprises: the guiding valve putting hole 30 that forms on the end face of the pressure chamber of the pump housing 6 22 sides; Advanced and retreat and freely be placed on guiding valve 31 in this guiding valve putting hole 30; Make the spring 32 of this guiding valve 31 to pressure chamber's 22 side reinforcings; When guiding valve 31 retreats according to 22 upper sheds and constitute the floss hole 33 of the opening end of described vent pathway 24 of its amount of retreating in the pressure chamber.

The pressure in the downstream side of variable restrictor device 25 imports the bottom 30a side that path 23 imports described guiding valve putting hole 30 by pressure.One end face of described guiding valve 31 is to pressure chamber's 22 sides, and therefore, owing to act on the pressure of the front and back of described variable restrictor device 25 in the front and back of guiding valve 31, escape cock 26 will be according to the discharge flow rate of the increase and decrease of the pressure reduction before and after it control from floss hole 33 toward vent pathway 24.

Thereby, according to this mode of execution, when the rotational velocity of live axle 3 (vane rotor 9) is hanged down, because variable restrictor device 25 is under the state of opening drain passageway 5 the biglyyest, the power of escape cock 26 usefulness springs 32 is closed floss hole 33, so can be according to the increase of rotational velocity, the supply flow of drain passageway 5 also increases.

And if the rotational velocity of live axle 3 is increased to a certain degree, the front and back pressure reduction of variable restrictor device 25 surpasses setting value and since with its before and after the pressure reduction servo-actuated, the guiding valve 31 of escape cock 26 is opened floss hole 33, discharge working oil from vent pathway 24, will suppress the increase of the supply flow of drain passageway 5.

And then, when the rotational velocity of this state-driven axle 3 increases, the elastic force of the oil pressure antagonistic spring 29 of the working oil of guiding valve 28 usefulness pressure chambers 22 sides of variable restrictor device 25 and retreating, the opening area of drain passageway 5 will dwindle gradually.Therefore, the supply flow of drain passageway 5 reduces gradually, can obtain what is called and blow down (Off ロ one ダ ウ Application) characteristic.

According to this mode of execution, when rotation along with vane rotor 9, when a blade 16 passes through front end 40b, the 40b of palpus shape groove 40,40, from each exhaust port 21,34 must shape the groove pressurized working fluid of adverse current because from front end 40b, 40b that must shape groove 40,40, i.e. front end 40b, the 40b of side in point to more collide by base portion side with the radial inner end 16a side of a side of next blade 16 of adjacency with than this inner end 16a.Therefore, to the load of the direction of rotation direction of relative blade 16, i.e. torque is enough little, and the power of vane rotor 9 to reverse direction is also reduced significantly.The result can suppress the decline of pump efficiency.

By prolong forming front end 40b, the 40b that each must shape groove 40,40, to the Directivity grow of the inner end 16a direction radially of a side of the blade 16 of adjacency, to the inner end 16a direction of side direct high pressure working fluid more reliably.

And, must shape groove 40,40 owing to prolong, for example can make especially at vehicle and keep straight on running when waiting, the variation of the discharge oil pressure when not having rotating operation steering wheel significantly diminishes.Promptly not significantly during the rotating operation steering wheel, exhaust port 21,34 and in its vicinity the pressure reduction of the pump chamber of 16,16 in a pair of blade that moves of rotation diminish.And along with the rotation of vane rotor 9, near the palpus shape groove 40,40 of the described pump chamber that each exhaust port 21,34, moves by the prolongation rotation, become early with the starting point that is communicated with of first, second exhaust port 21,34, the rotational velocity of relative blade 16, the connection time of described pump chamber and first, second exhaust port 21,34 is elongated.Thereby because the working oil in the exhaust port 21,34 is elongated to the traveling time of pump chamber, the oil pressure of the working fluid in exhaust port 21,34 diminishes.

As a result, even also can reduce the pulsation of the oil pressure in the exhaust port 21,34 slightly during the rotating operation steering wheel.

In this embodiment, because the opening portion 34a of second exhaust port 34 formation is bigger, it is big to set the existing product of open area ratio, so can prevent that the off-centre of the top (first exhaust port 21 sides) of vane rotor 9 in Fig. 1 moves at work.

Promptly because relative first exhaust port, 21 sides are big with the whole opening area of the 3rd exhaust port 35 sides, second exhaust port, 34 sides are single openings, so bigger than the operating oil pressure by the first, the 3rd exhaust port 21,35 by the operating oil pressure of this second exhaust port 34.Therefore, vane rotor 9 oil pressure with second exhaust port 34 of high pressure in the work of pump is that upper side is pushed among Fig. 1 to the first, the 3rd exhaust port 21,35 sides, carries out off-centre and moves.Thereby impedance becomes big because near the front end of each blade 16 with the inner peripheral surface sliding contact of powerful and stator 8, rubs, and pump efficiency might descend.

But, as present embodiment because it is big to set the opening area of opening portion 34a of second exhaust port 34, again since with the head pressure of first exhaust port, 21 sides near balance equably roughly, move so can suppress to take place the off-centre of vane rotor 9.The result can reduce each blade 16 local big sliding-frictional resistance of the inner peripheral surface 8a that relative stator 8 takes place.Thereby can prevent the decline of pump efficiency.

Owing to widen in the maximum of the opening portion 34a of described second exhaust port 34 and to set up bridge 36 on the position, certainly guarantee this second exhaust port 34 rigidity on every side, can bring into play restriction effect by this bridge 36, improve the control accuracy of pilot pressure with described variable restrictor device 25.

And then, owing to run through the mobile notch part 37 of total length formation guiding working fluid of bridge 36 at the described outlet side of bridge 36, so can suitably control toward the flow direction (Fig. 1 arrow) of the working fluid of drain passageway 5 with this notch part 37, variable restrictor device 25 can obtain high control accuracy as a result.

Figure 10～Figure 13 represents another mode of execution, and structure of pump case etc. is different with foregoing product in the blade pump structure, and other basic structure is identical.

Be open rearward end back plate 51 obturations of pump case 50, it is that screw is fixed on the plate member on the pump case 50.In the inside of pump case 50, take in the described stator of configuration 52 respectively and rotate freely be located at these stator 52 inside, by the vane rotor 53 that sintered alloy material is formed, simultaneously, on a side of stator 52, dispose the side plate 54 of side's side.In addition, the front end 55a axle of the live axle 55 of described perforation pump case 50 is supported on the bearing hole 51b of the substantial middle formation of back plate 51, simultaneously, position near this front end 55a combines with the zigzag fashion hole 53a zigzag fashion of the central authorities of described vane rotor 53, and the opposing party's terminal side rotates with ball bearing 56 and freely supporting.

In a plurality of slits that on vane rotor 53, have, the outer blade of figure is set radially, simultaneously, the pump chamber that forms between this blade is because the rotation of vane rotor 53, its volume changes, form between suction area in the part that causes volume to increase by this variation, and form between discharge zone in the part of volume reducing.

Described pump chamber is communicated with the hyperbaric chamber 58 that forms in the inner recesses of pump case 50 by the intercommunicating pore 57 of side plate.In addition, the suction port 59 that is provided with in pump case 50 is communicated with pump chamber by pairing left and right suction port 60,60 and the inner low-pressure passage 61 that forms on the plate 51 of back as shown in figure 11.

In addition, with figure that hyperbaric chamber 58 is communicated with outside high-pressure passage and described low-pressure passage between be provided with flow control valve 62, remainder in the discharge oil in guiding hyperbaric chamber 58 is refluxed to low-pressure passage 61, will be controlled at certain amount to the exhaust port from scheming outside to the working fluid of actuator discharge.

Described back plate 51 aluminum alloy material unitary moulding, as Figure 10～shown in Figure 12, interior edge face 51a is along with the rotation of described vane rotor 53 and a side 53b sliding contact of this vane rotor 53, simultaneously, this interior edge face 51a at least with the position of a side 53b sliding contact of described vane rotor 53 on, as shown in figure 13, form numerous small oil collection part 63.

This oil collection part 63 is by so-called abrasive machining, is formed by the cross recesses of the numerous wire breach 64 that forms at the surperficial upper edge of described interior edge face 51a any direction.

Thereby, between a side 53b of described interior edge face 51a and vane rotor 53, form oil film because be used in the lubricant oil of concentrating in this numerous oil collection part 63, so the greasy property between both 51a, the 53b uprises, can prevent fully that the interior edge face 51a of the back plate 51 lower than vane rotor 53 hardness from wearing and tearing.

In addition, because oil collection part 63 forms by abrasive machining, it is simple that it forms operation, can carry out small processing simultaneously.

And then oil collection part 63 is because its size is minimum as previously mentioned, so also can not reduce and the sealing of 50 of pump cases even form on whole of interior edge face 51a.

In addition, also can only on a side 53b of vane rotor 53, form described small oil collection part 63, and then, also can form the interior edge face 51a both sides of this side 53b and back plate 51.

Be described as follows for the technological thought beyond the claim that can comprise by described mode of execution.

(1) vane pump comprises: take in the stator that is configured in the pump case; Be configured in the side plate of this stator sidepiece; The a pair of exhaust port that forms in roughly radially the object's position upper shed of described side plate; Rotation freely is placed in this stator, uses the drive shaft rotor rotated; Inner peripheral surface direction discrepancy to described stator freely remains on the peripheral part of this rotor along the blade in a plurality of slits that the radiation direction forms.

This vane pump one side forms the 3rd exhaust port at the opposition side of the stator of first exhaust port that clips a described side, two systems that formation makes this first, the 3rd exhaust port be communicated with the pressure chamber that forms between described pump case and stator, on the other hand, make the opening area of second exhaust port form greatlyyer, make its opening area near described the first, the 3rd exhaust port integral body.

According to this invention, because the opening area of second exhaust port is set greatlyyer, balance can suppress that rotor eccentricity takes place and move owing to be bordering on roughly homogeneous with first head pressure of discharging oral-lateral again.The result can lower each blade of generation to the sliding friction impedance part, big of stator inner peripheral surface.Thereby, can prevent the decline of pump efficiency.

(2) in the described vane pump of first aspect present invention, roughly be expanded into the opening portion that fan forms described second exhaust port to outlet from the inlet of fluid.

According to this invention, because the opening shape of the opening portion of second exhaust port roughly enlarges the formation fan-shaped, can obtain good flowability to the working fluid of variable restrictor device direction, simultaneously, can lower head pressure effectively.

(3) in first aspect present invention or the described vane pump of second aspect, widen on the position in the maximum of the opening portion of described second exhaust port and to build bridge, simultaneously, the total length that runs through bridge at the described outlet side of this bridge forms the notch part that the guiding working fluid flows.

According to this invention, owing to widen on the position in the maximum of the opening portion of described second exhaust port and to build bridge, certainly guarantee this second exhaust port rigidity on every side, can bring into play restriction effect, improve control accuracy with described variable restrictor device pilot pressure by this bridge.

And then, form the notch part that the guiding working fluid flows owing to run through the total length of bridge, suitably the Control work fluid is to the mobile flow direction of drain passageway by this notch part, and the variable restrictor device can obtain high control accuracy as a result.

(4) vane pump comprises: take in the stator that is configured in the pump case; One end opening of inaccessible described pump case and with the plate member of a contacts side surfaces of described stator; Rotation freely is placed in this stator, when using drive shaft turns, and the rotor of the interior edge face sliding contact of a side and described plate member; Inner peripheral surface direction discrepancy to described stator freely remains on the peripheral part of this rotor along the blade in a plurality of slits that the radiation direction forms.This vane pump is at the small oil collection part of at least one square one-tenth of a side of the interior edge face of described plate member or rotor.

According to the present invention,,, can fully prevent between rotor and back plate sliding friction to take place so greasy property between the two improves owing between a side of described interior edge face and rotor, often form oil film with the lubricant oil that concentrates on small oil collection part.

(5) as the described vane pump of fourth aspect present invention, it forms described oil collection part by the intersection point groove of going up the wire breach that forms in any direction.

(6) as the described vane pump of fifth aspect present invention, it is formed on the intersection point groove of the wire breach that forms on any direction by abrasive machining.

According to this invention, owing to form oil collection part by abrasive machining, it is simple that it forms operation, can smallly process simultaneously.

The invention is not restricted to the structure of described each mode of execution, as also can with as described in oil collection part be used for first mode of execution, promptly with opposite that two side slip of vane rotor contact on form or on two sides of vane rotor formation described oil collection part on the opposite of two side plates 10,11 this moment.

Claims (4)

1. vane pump, it comprises: stator, it is taken in and is configured in the pump case; Side plate, it is configured in the sidepiece of this stator, and opening forms exhaust port; Rotor, its rotation freely is placed in this stator, by the drive shaft rotation, the while forms a plurality of in the slit of peripheral part to the extension of radiation direction in a circumferential direction, forms the slit formation portion of the convex of extending to radial outside on two sidepieces of this slit circumferencial direction; Blade, its inner peripheral surface direction to described stator is come in and gone out and is freely remained in the described slit; Palpus shape groove, it forms breach on described side plate and inner side surface described rotor sliding contact, and be communicated with described exhaust port, becoming gradually from described exhaust port edge with the direction of the direction of rotation of described rotor, tapered ground forms described palpus shape groove, it is characterized in that, simultaneously, the front end of this palpus shape groove and the described slit formation portion ground that overlaps is formed.

2. vane pump as claimed in claim 1 is characterized in that, make the front end of this palpus shape groove form cross base end part that must the shape groove than described each blade pass the rotary motion trace line more point to interior side.

3. vane pump as claimed in claim 1 is characterized in that, make described must shape the elongation line of front of the slot portion point to the more close base portion in substantial middle position than the radial length of blade, this blade along with the rotation of described rotor near must the shape groove rotation move.

4. vane pump as claimed in claim 1 is characterized in that, makes the front end of described palpus shape groove must rotate the direction blade prolongation formation of moving near the shape groove towards the rotation of following described rotor.

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