CN107407275A - Gear pump arrangement - Google Patents

Abstract

The present invention provides a kind of gear pump arrangement, and it makes grinding rib (71f) connect and not connected with as each several part of area of low pressure with periphery high-pressure area.In such a configuration, the periphery high-pressure area for grinding discharge pressure of the rib (71f) with being formed as high pressure is connected, therefore the brake fluid of high pressure is imported into grinding rib (71f).Accordingly, it is capable to access that the brake fluid pressure based on high pressure pushes back gear pump (19,39) pushes back effect.Further, since making grinding rib (71f) connect and not connect with as each several part of area of low pressure with periphery high-pressure area, so high pressure can will be remained in grinding rib (71f), can suppress to push back effect reduction.Therefore, it is possible to prevent from losing the reduction of the minimizing effect of moment of torsion, loss moment of torsion can be made further to reduce.

Description

Gear pump arrangement

Technical field

The present invention relates to the engagement by gear come gear pump arrangements such as the trochoid pumps of force feed fluid.

Background technology

In the past, in gear pump arrangement, formed using together with the axial both ends of the surface used with gear pump by resin etc. Seal member encapsulating method, this turn into cost improve an important factor for, therefore propose by one it is square turn into mechanical seal and The construction of cost of implementation reduction.Specifically, using seal member only to gear pump possessed internal rotor and outer rotor One end surface side is sealed, and other end surface side is formed as each rotor being directly pressed against the sliding surface for the shell for storing each rotor Mechanical seal.

The mechanical seal be the elastic force based on seal member, high-pressure fluid pressure and by metal internal rotor and outer The construction that rotor is strongly pressed against metal shell to be sealed.Therefore, if the cunning of outer rotor, internal rotor and shell The loss moment of torsion in dynamic face is larger, and pump discharge ability, which is given, to be influenceed, and has to make motor dimension become the unfavorable shadow such as big so as to produce Ring.In addition, the sliding surface between outer rotor, internal rotor and shell produces the loss larger part of moment of torsion of rotation and less portion In the case of point, heating is produced in the larger part of loss moment of torsion along with the high speed or prolonged rotation of pump.Also have because The adverse effect of ability is discharged caused by heating part expansion to pump.

Therefore, in patent document 1, proposition has gear pump arrangement corresponding with these problems.Specifically, in shell The sliding surface for undertaking mechanical seal function apply radial grinding rib.Thus, the sliding surface of shell and connecing for two rotors are made Contacting surface product is reduced, and so as to reduce coefficient of friction, therefore promotes supply of the oil to sliding surface.Thereby, it is possible to realize loss moment of torsion Reduce.

Patent document 1:Japanese Unexamined Patent Publication 2003-129964 publications

However, in the gear pump arrangement described in patent document 1, in the sliding surface of shell, from than outer rotor in the outer part Until radial grinding rib is set in entire surface in the inner part than the internal rotor for being configured with axle.Therefore, than outer rotor in the outer part High-pressure area connects with the area of low pressure than internal rotor in the inner part via grinding rib, so as to cause high-pressure fluid from high-pressure area Leaked to area of low pressure side.Thus, relative to the elastic force of seal member, and the high-pressure spray by high-pressure area can not fully be obtained Body pushes back effect from the slip surface side of shell towards what two rotor-sides were pushed back, so as to there is the minimizing effect drop of loss moment of torsion The problem of low.

The content of the invention

The present invention is in view of above-mentioned aspect, there is provided can improve what is pushed back from the slip surface side of shell towards two rotor-sides Effect is pushed back, the gear pump arrangement of the further reduction of loss moment of torsion can be made.

To achieve these goals, in the invention described in technical scheme 1, gear pump arrangement possesses：Gear pump, it has It is standby that there is the outer rotor of interior teeth portion and form multiple space parts and the internal rotor engaged with outer rotor, based in being inserted through turns The rotation of the axle of the centre bore of son makes outer rotor and internal rotor rotate so as to carry out the suction discharging operation of fluid；Shell, its Form the incorporating section of storage gear pump；And sealing mechanism, it is disposed in one of shell and the pump axial end in gear pump Between end face, divide the low-pressure side around the suction side for including suction fluid and axle in gear pump and flowed including discharge The high-pressure side of the part in the gap between the discharge side of body and the periphery of outer rotor and shell, the pressing based on sealing mechanism Power makes another end face of the pump axial end in gear pump be connected to the sliding surface of shell, so as to by the gear pump of the end Low-pressure side and high-pressure side between seal, the gear pump arrangement is characterised by, has fluid lead-in groove in sliding surface, the fluid Lead-in groove by being formed from the center of gear pump with the rib of radiated entends, be imported into periphery as on high-tension side outer rotor with it is outer The fluid in the gap between shell, fluid lead-in groove is away from centre bore and suction side.

In the case of the fluid lead-in groove of structure as formation, fluid lead-in groove and the discharge pressure as high pressure Periphery high-pressure area connects, therefore in the fluid imported fluid lead-in groove of high pressure.Accordingly, it is capable to access the fluid based on high pressure Push back gear pump pushes back effect.

Even if in addition, making fluid lead-in groove be connected with periphery high-pressure area, do not make fluid lead-in groove yet and turn into low-pressure area The each several part connection in domain.High pressure is remained in groove therefore, it is possible to direct fluid into, can suppress to push back effect reduction.Accordingly, it is capable to Enough prevent from losing the reduction of the minimizing effect of moment of torsion, loss moment of torsion can be made further to reduce.

Brief description of the drawings

Fig. 1 is the braking device for vehicle for representing to apply the gear pump arrangement involved by the first embodiment of the present invention The figure of 1 hydraulic circuit.

Fig. 2 is the sectional view of gear pump arrangement.

Fig. 3 is Fig. 2 III-III' sectional views.

Fig. 4 is the figure for representing the cylinder body 71 when from gear pump 19 or the side of gear pump 39.

Fig. 5 is the pressure distribution for representing to be formed at the grinding rib 71f and sliding surface 71b, 71c of cylinder body 71 etc. of cylinder body 71 Relation figure.

Fig. 6 is to represent the gear pump arrangement possessed gear pump 19 or tooth from involved by second embodiment of the present invention The figure of cylinder body 71 when the side of wheel pump 39 is observed.

Fig. 7 is the pressure distribution for representing to be formed at the grinding rib 71f and sliding surface 71b, 71c of cylinder body 71 etc. of cylinder body 71 Relation figure.

Fig. 8 is discharge pressure region Ra, the suction pressure region Rb and intermediate pressure region Rc for representing gear pump arrangement Figure.

Fig. 9 is to represent gear pump 19,39 and the figure of the pressure distribution between sliding surface 71b, 71c of cylinder body 71.

Figure 10 be represent from the gear pump arrangement possessed gear pump 19 involved by third embodiment of the present invention or The figure of cylinder body 71 when the side of gear pump 39 is observed.

Figure 11 be represent from the present invention the 4th embodiment involved by gear pump arrangement possessed gear pump 19 or The figure of cylinder body 71 when the side of gear pump 39 is observed.

Embodiment

Hereinafter, embodiments of the present invention are illustrated based on accompanying drawing.It is in addition, mutual in following each embodiment In, same reference numerals are marked to mutually identical or equivalent part to illustrate.

(first embodiment)

Reference picture 1 is to applying the braking device for vehicle of the gear pump arrangement involved by an embodiment of the invention 1 hydraulic circuit illustrates.In addition, herein to before and after composition the vehicle application of the hydraulic circuit of pipe arrangement it is of the invention involved And the example of braking device for vehicle 1 illustrate, but can also apply using off-front wheel and left rear wheel as the first pipe arrangement System, using the near front wheel and off hind wheel as in X pipe arrangements of the second piping system etc..

As shown in Figure 1, braking device for vehicle 1 possesses：Brake pedal 11, step-up system 12, M/C13, W/C14, 15th, 34,35 and brake fluid pressure control use actuator 50.In addition, it is assembled with braking in brake fluid pressure control actuator 50 ECU70, brake force caused by braking device for vehicle 1 is controlled by braking ECU70.

Brake pedal 11 is connected with step-up system 12 and M/C13, if driver depresses brake pedal 11, is filled by reinforcement 12 are put by legpower reinforcement, main piston 13a, the 13b for being disposed in M/C13 are pressed.Thus, make to be drawn by main piston 13a, 13b The main chamber 13c and concubine 13d divided produces the M/C pressure with pressure.M/C pressure is by forming hydraulic path caused by the M/C13 Brake fluid pressure control actuator 50 and be transferred to each W/C14,15,34,35.

In addition, it is connected with M/C13 with the main fluid reservoir with main chamber 13c and concubine the 13d path being respectively communicated with 13e.Main fluid reservoir 13e is to supplying brake fluid or stockpiling unnecessary brake fluid in M/C13 in M/C13.

Brake fluid pressure control has the first piping system 50a and the second piping system 50b with actuator 50.First matches somebody with somebody piping System 50a turns into the rear system being controlled to the brake fluid pressure for putting on off hind wheel RR and left rear wheel RL, the second piping system 50b As the preceding system being controlled to the brake fluid pressure for putting on the near front wheel FL and off-front wheel FR.

Hereinafter, first, second piping system 50a, 50b is illustrated, the first piping system 50a and the second piping system 50b is same structure, therefore is illustrated herein for the first piping system 50a, and the second piping system 50b is with reference to the One piping system 50a.

First piping system 50a possesses the pipeline A as main line, and pipeline A is by above-mentioned M/C pressure transmission in left back RL possesseds W/C14 and off hind wheel RR possessed W/C15 is taken turns, produces W/C pressure.Make each W/ by pipeline A C14,15 produce W/C pressure respectively, so as to produce brake force.

Pipeline A possesses and can controlled as connected state and the differential pressure control valve of differential pressure state 16.Producing with driver to system Corresponding to the operation of dynamic pedal 11 during the usual braking of brake force (when being not carried out motion control), the differential pressure control valve 16 adjustment valve Position is with as connected state.If moreover, there are electric current, differential pressure control in the flowing of the possessed solenoid coil of differential pressure control valve 16 Valve 16 processed adjusts valve position with as the more big then bigger differential pressure state of the current value.If the differential pressure control valve 16 turns into differential pressure shape State, then the flowing of brake fluid is limited in a manner of W/C pressure is higher by differential pressure amount compared to M/C pressure.

Pipeline A is branching into two pipelines A1, A2 as than the differential pressure control valve 16 W/C14 farther downstream, 15 sides.Pipe Road A1 possesses the supercharger control valve 17 being controlled to supercharging of the brake fluid pressure to W/C14, pipeline A2 possess to brake fluid pressure to The supercharger control valve 18 that W/C15 supercharging is controlled.

Supercharger control valve 17,18 is by that can control two magnetic valves of connection cut-off state to form.Supercharger control valve 17, 18 be formed as supercharger control valve 17,18 possessed solenoid coils do not flow have control electric current it is non-energized when be controlled as Connected state, there is the open type that cut-off state is controlled as during the energization of control electric current in solenoid coil flowing.

In the work that will link between the supercharger control valve 17,18 in pipeline A and each W/C14,15 with pressure regulation fluid reservoir 20 For the pipeline B of relief line, pressure reduction control valve 21 and pressure reduction control valve 22 are equipped respectively.Above-mentioned pressure reduction control valve 21,22 by Two magnetic valves of connection cut-off state can be controlled to form, and be formed as when non-energized as the normally closed of cut-off state Type.

The pipeline C as return line is equipped between pressure regulation fluid reservoir 20 and pipeline A.Pipeline C be provided with Mode from pressure regulation fluid reservoir 20 towards M/C13 sides or W/C14,15 sides suction discharge brake fluid is driven by motor 60 self-priming Gear pump 19.

In addition, the pipeline D as auxiliary piping is provided between pressure regulation fluid reservoir 20 and M/C13.Utilize gear pump 19 Brake fluid is sucked from M/C13 by pipeline D, and discharged to pipeline A, so as to prevent control, traction control etc. from moving in sideslip During control, brake fluid is supplied to W/C14,15 sides, the W/C pressure of control object wheel is pressurizeed.

On the other hand, as described above, the second piping system 50b is roughly the same with the first piping system 50a structure.Tool For body, differential pressure control valve 16 is corresponding with differential pressure control valve 36.Supercharger control valve 17,18 respectively with 37,38 pairs of supercharger control valve Should, pressure reduction control valve 21,22 is corresponding with pressure reduction control valve 41,42 respectively.Pressure regulation fluid reservoir 20 is corresponding with pressure regulation fluid reservoir 40.Tooth Wheel pump 19 is corresponding with gear pump 39.In addition, pipeline A, pipeline B, pipeline C, pipeline D respectively with pipeline E, pipeline F, pipeline G, pipeline H is corresponding.As described above, form the hydraulic circuit of braking device for vehicle 1, gear pump arrangement make gear pump 19 in them, 39 integrations.To being described after the detailed configuration of gear pump arrangement.

Braking ECU70 administers the control system of braking device for vehicle 1, as known in possessing CPU, ROM, RAM, I/O etc. Microcomputer form.Braking ECU70 performs the processing such as various computings according to the program for being stored in ROM etc., performs sideslip Prevent the vehicle motion controls such as control.Specifically, it is various come computing to brake detections of the ECU70 based on sensor class (not shown) Physical quantity, and based on the operation result to whether performing vehicle motion control and judging.Moreover, braking ECU70 is performing car Obtained during motion control relative to the controlled quentity controlled variable of control object wheel W/C pressure i.e. caused by the W/C of control object wheel.It is based on The result, braking ECU70 is to for driving each control valve 16~18,21,22,36~38,41,42 and gear pump 19,39 Motor 60 is controlled, and so as to be controlled to the W/C pressure of control object wheel, carries out vehicle motion control.

For example, when not producing pressure in M/C13 preventing control such as traction control, sideslip, driving gear pump 19, 39, and differential pressure control valve 16,36 is formed as differential pressure state.Thus, brake fluid is supplied to differential pressure by pipeline D, H and controlled The downstream of valve 16,36, the in other words side of W/C14,15,34,35.Moreover, by suitably control supercharger control valve 17,18, 37th, 38, pressure reduction control valve 21,22,41,42 is controlled come the increase and decrease pressure of the W/C pressure to control object wheel, and W/C is pressed Power control turns into desired controlled quentity controlled variable.

In addition, when anti-skidding (ABS) is controlled, by suitably controlling supercharger control valve 17,18,37,38, pressure reduction control valve 21st, 22,41,42, and driving gear pump 19,39, to control the increase and decrease pressure of W/C pressure, W/C Stress controls are turned into and wished The controlled quentity controlled variable of prestige.

Next, 2~Fig. 5 of reference picture is to the detailed of the gear pump arrangement of braking device for vehicle 1 that forms as described above Thin construction illustrates.In addition, Fig. 2 is the housing 101 for representing pump main body 100 being assembled in brake fluid pressure control actuator 50 When situation, such as by make Fig. 2 and Fig. 3 paper above-below direction turn into vehicle above-below direction in a manner of assemble.

As described above, braking device for vehicle 1 is by the first piping system 50a and the second piping system 50b two systems Form.Therefore, pump main body 100 possesses the first piping system 50a piping system 50b of gear pump 19 and second gear 39 two gear pumps of pump.

Make to be rotated by the rotary shaft 54 that clutch shaft bearing 51 and second bearing 52 support by motor 60, it is built-in so as to drive In the gear pump 19,39 of pump main body 100.The profile of pump main body 100 is made up of the cylinder body 71 and connector 72 of aluminum.Clutch shaft bearing 51 are configured at cylinder body 71, and second bearing 52 is configured at connector 72.

In the state of cylinder body 71 and the arranged coaxial of connector 72 side of cylinder body 71 relative to connector 72 be pressed into so as to Cylinder body 71 is integrated with connector 72, forms the profile of pump main body 100.Moreover, possesses gear pump together with cylinder body 71, connector 72 19th, 39, thus various seal members etc. form pump main body 100.

So it is integrally formed the pump main body 100 of construction.From paper right, insertion is formed at the pump main body 100 of the Construction integration In the recess 101a of the substantially cylindrical shape of the housing 101 of aluminum.Moreover, in the recess 101a internal thread groove that digs out of entrance 101b screw threads for fastening has the externally threaded item (screw) 102 of ring-type, so as to which pump main body 100 is fixed on into housing 101.By this The screw threads for fastening of externally threaded item 102 and be formed as the construction that pump main body 100 will not come off from housing 101.

Like this by the way that pump main body 100 is fixed on into housing 101 to form gear pump arrangement.Moreover, by cylinder body 71, insert Plug 72 and housing 101 form the shell of gear pump arrangement, and gear pump 19,39 is accommodated with the inside of the shell.

In addition, in this manual, the pump main body 100 is referred to as inserted to the recess 101a of housing 101 direction of insertion Enter direction.It is in addition, pump main body 100, the axial direction of each gear pump 19,39 and circumference is in other words axial, all with rotary shaft 54 Circumferentially be referred to as to consistent pump shaft to, pump shaft axially, it is circumferential.

The front position in front of direction of insertion in recess 101a in other words in recess 101a bottom with rotation Position corresponding to the front end (Fig. 2 left end) of axle 54, the second recess 101c formed with toroidal.Second recess 101c Diameter be more than the diameter of rotary shaft 54, the front end of rotary shaft 54 is located in second recess 101c, rotary shaft 54 not with housing 101 contacts.

Cylinder body 71 and connector 72 possess centre bore 71a, 72a respectively.Rotary shaft is inserted into above-mentioned centre bore 71a, 72a 54, the rotary shaft 54 is fixed in the clutch shaft bearing 51 of the centre bore 71a of cylinder body 71 inner circumferential and is fixed on the center of connector 72 The second bearing 52 of hole 72a inner circumferential supports.

In the both sides of clutch shaft bearing 51 in other words than clutch shaft bearing 51 more by the region in front of direction of insertion and first, the Region folded by two bearings 51,52 possesses gear pump 19,39 respectively.

As shown in figure 3, gear pump 19 is configured at turn that the recess being recessed by making the end face of cylinder body 71 with toroidal is formed In seed cell (incorporating section) 100a.The internal gear pump that gear pump 19 is driven by the rotary shaft 54 being inserted through in rotor chamber 100a (trochoid pump：Trochoid pump) form.

Specifically, gear pump 19 possesses by outer rotor 19a of the inner circumferential formed with interior teeth portion and being formed on the outer periphery outer The rotating part that the internal rotor 19b of teeth portion is formed, turns into structures of the internal rotor 19b centre bore 19ba inserted with rotary shaft 54. Moreover, being embedded in key 54b in the hole 54a for being formed at rotary shaft 54, the moment of torsion transmission to internal rotor 19b is carried out by key 54b.

Outer rotor 19a is engaged to form multiple space parts with internal rotor 19b by the interior teeth portion formed respectively with outer toothed portion 19c.Moreover, space part 19c size variations are made by the rotation of rotary shaft 54, so as to carry out the suction of brake fluid discharge.

On the other hand, as shown in Fig. 2 gear pump 39 is configured at what is be recessed by making another end face of cylinder body 71 with toroidal In rotor chamber (incorporating section) 100b that recess is formed, and the rotary shaft 54 by being inserted through in rotor chamber 100b drives.Gear pump 39 Also outer rotor 39a and internal rotor 39b is likewise supplied with gear pump 19, turns into and is inserted in internal rotor 39b centre bore 39ba There is the structure of rotary shaft 54.Moreover, by engaged by each rotor 39a, 39b two teeth portion multiple space part 39c for being formed come The internal gear pump for carrying out the suction discharge of brake fluid is formed.The gear pump 39 turns into makes gear centered on rotary shaft 54 Pump 19 almost have rotated 180 ° of configuration.By being configured so that, gear pump 19, space part 19c, 39c of 39 respective suction sides Turn into symmetric position centered on rotary shaft 54 with space part 19c, 39c of discharge side, can be by the system of the high pressure of discharge side The power that hydrodynamic pressure gives clutch shaft bearing 51 is offset.

Said gear pump 19,39 essentially becomes identical construction.Moreover, in the present embodiment, relative to conventional Change what is formed on sliding surface 71b, 71c in the cylinder body 71 of a part for the shell of gear pump as composition 19,39 Grind rib (Japanese：Grind rib) 71f (reference picture 4, Fig. 5) structure.Hereby it is achieved that the reduction of loss moment of torsion.This is ground afterwards The details of mill rib 71f construction illustrates.

In addition, in one end surface side of cylinder body 71, and across gear pump 19 and the opposite side of cylinder body 71, in other words in cylinder Between body 71 and gear pump 19 and housing 101, possesses the sealing mechanism 111 for pressing gear pump 19 to the side of cylinder body 71.Also, In another end face side of cylinder body 71, and across gear pump 39 and the opposite side of cylinder body 71, in other words in cylinder body 71 and Between gear pump 39 and connector 72, possesses the sealing mechanism 115 for pressing gear pump 39 to the side of cylinder body 71.

Sealing mechanism 111 is made up of the endless member with the hollow bulb inserted for rotary shaft 54.Utilize the sealing mechanism 111 press outer rotor 19a and internal rotor 19b to the side of cylinder body 71, thus relatively low to the ratio of one end surface side in gear pump 19 The position of pressure is sealed with the position than higher pressure.Specifically, sealing mechanism 111 by with the gabarit as housing 101 Recess 101a bottom surface and outer rotor 19a, internal rotor 19b desired position abut and play sealing function.

In this case, sealing mechanism 111 is configured to the inner part for being formed as middle empty frames shape 112nd, ring rubber member 113 and the outer part 114 of middle empty frames shape is formed as.Moreover, it is configured in inner part 112 Periphery wall and outer part 114 internal perisporium between arranged in the state of ring rubber member 113 in outer part 114 Embedded inner part 112.

In addition, the external diameter of sealing mechanism 111 is less than the recess 101a of housing 101 internal diameter at least above Fig. 2 paper. Therefore, be configured to brake fluid can by the gap between the sealing mechanism 111 and the recess 101a of housing 101 above paper and Flowing.The gap forms discharge room 80, and the discharge pipeline 90 of the bottom of the recess 101a with being formed at housing 101 is connected. By such construction, discharge room 80 and discharge can be discharged braking by gear pump 19 by the use of pipeline 90 as discharge path Liquid.Moreover, when pump 19 works, outer part 114 is pressed to the side of gear pump 19 by the brake fluid pressure of the discharge side of high pressure, It can be further assured that sealing of the sealing mechanism 111 to an end face of gear pump 19.

In addition, the suction inlet 81 connected in space part 19c of the cylinder body 71 formed with the suction side with gear pump 19.The suction Mouth 81 extends to outer peripheral face, and the side of the recess 101a with being arranged at housing 101 from the end face of the side of gear pump 19 in cylinder body 71 The suction pipeline 91 in face connects.In addition, as shown in Fig. 2 and Fig. 4, the end face of the side of gear pump 19 in cylinder body 71 formed with The suction tank 71d for making centre bore 71a be connected with suction inlet 81.By such construction, gear pump 19 can be by suction pipeline 91 and suction inlet 81 as suction path and import brake fluid.

On the other hand, sealing mechanism 115 is also made up of the endless member with the central part inserted for rotary shaft 54.Utilize The sealing mechanism 115 presses outer rotor 39a and internal rotor 39b to the side of cylinder body 71, thus to the end face in gear pump 39 The position of the comparison low pressure of side is sealed with the position than higher pressure.Specifically, sealing mechanism 115 by with connector 72 The part for being accommodated with sealing mechanism 115 end face and outer rotor 39a, internal rotor 39b desired position abut and play Sealing function.

Sealing mechanism 115 is also configured to inner part 116, the ring rubber member 117 for being formed as middle empty frames shape And be formed as the outer part 118 of middle empty frames shape.Moreover, it is configured to the periphery wall and outer part in inner part 116 Arranged between 118 internal perisporium and be embedded in inner part 116 in outer part 118 in the state of ring rubber member 117.

The sealing mechanism 115 and the essential structure of sealing mechanism 111 are that identical constructs, but form the face of sealing as with it is upper The opposite side of sealing mechanism 111 stated, therefore change construction matingly with this.Specifically, sealing mechanism 115 is by relative to close The symmetric shape of sealing mechanism 111 is formed, and is staggered 180 ° of phase configurations relative to sealing mechanism 111 centered on rotary shaft 54. In addition, sealing mechanism 115 is to be constructed with the identical of sealing mechanism 111.

In addition, the external diameter of sealing mechanism 115 is less than the internal diameter of connector 72 at least below paper.Therefore, it is configured to brake Liquid energy is enough flowed by the gap between the sealing mechanism 115 and connector 72 below paper.The gap forms discharge room 82, and It is connected with the access 72b for being formed at connector 72 and the side for the recess 101a for being formed at housing 101 discharge pipeline 92. By such construction, gear pump 39 can will discharge room 82, access 72b and discharge by the use of pipeline 92 as discharge path and Discharge brake fluid.Moreover, when pump 39 works, by the brake fluid pressure of the discharge side of high pressure by outer part 118 to gear pump 39 sides press, and can be further assured that sealing of the sealing mechanism 115 to an end face of gear pump 39.

On the other hand, by other words supplying each rotor in sliding surface 71b, 71c for also serving as sealing surface performance function The face that 19a, 19b, 39a, 39b are slided, which abuts, gear pump 19,39, so as to the gear pump 19 in cylinder body 71, the end face of 39 sides Sealed (mechanical seal).Thus, to the position of the comparison low pressure of the other end surface side in gear pump 19,39 with than higher pressure Position sealed.

In addition, the suction inlet 83 connected in space part 39c of the cylinder body 71 formed with the suction side with gear pump 39.The suction Mouth 83 extends to outer peripheral face, and the side of the recess 101a with being arranged at housing 101 from the end face of the side of gear pump 39 in cylinder body 71 The suction pipeline 93 in face connects.By such construction, gear pump 39 can make suction pipeline 93 and suction inlet 83 Brake fluid is imported for suction path.

In addition, in fig. 2, the suction pipeline C of pipeline 91 and discharge pipeline 90 equivalent to Fig. 1, suction pipeline 93 and discharge pipeline G of the pipeline 92 equivalent to Fig. 1.

In addition, the ratio clutch shaft bearing 51 in the centre bore 71a of cylinder body 71 is more accommodated with by direction of insertion rear and possesses footpath It is the close of the ring rubber member 120b in the cyclic resin part 120a of U-shaped and embedded ring-type resin component 120a to section Seal part 120.The sealing between two systems in the centre bore 71a of cylinder body 71 is carried out by the seal member 120.

In addition, the centre bore 72a of connector 72 is formed by internal diameter from direction of insertion front towards three stage of rear undergauge For stairstepping, seal member 121 is accommodated with the first paragraph end difference as its direction of insertion rearmost side.The seal member 121 be the ring-type that will be made up of elastomeric elements such as rubber elastic ring 121a be embedded in formed with to be radially used as the groove of depth direction The resin component 121b of the ring-type in portion seal member, by elastic ring 121a elastic force come press resin component 121b and with rotation Rotating shaft 54 contacts.

In addition, the second segment end difference of the section adjacent as the section for being configured with seal member 121 in centre bore 72a It is accommodated with above-mentioned sealing mechanism 115.Above-mentioned access 72b is formed to the outer peripheral face of connector 72 from the end difference.In addition, The 3rd section of end difference press-in as direction of insertion forefront side in centre bore 72a has the direction of insertion rear side of cylinder body 71 End.Part in the centre bore 72a of insertion connector 72 in cylinder body 71 reduced diameter compared with the other parts of cylinder body 71.Should The axial dimension of three section end difference of the axial dimension of the part of reduced diameter in cylinder body 71 more than centre bore 72a, therefore When cylinder body 71 is pressed into the centre bore 72a of connector 72, connector 72 front position formed with based on cylinder body 71 and connector 72 and caused groove portion 74c.

In addition, the centre bore 72a of connector 72 partly becomes big at direction of insertion rear also diameter, the part possesses oil sealing (seal member) 122.So, oil sealing 122 more is being configured by the side of motor 60 than seal member 121, so as to basically by sealing Part 121 prevents the brake fluid to outside for having passed through centre bore 72a from leaking, and by oil sealing 122, more reliably obtains the effect Fruit.

In the periphery of the pump main body 100 so formed, possess to carry out the sealing of each several part as annular sealing portion O-ring 73a~73d of part.Above-mentioned O-ring 73a~73d between the system for two systems for being formed at housing 101, each system Brake fluid between the discharge path of system and suction path etc. is sealed.O-ring 73a is configured at discharge room 80 and discharge is used Pipeline 90 and suction inlet 81 and suction are used between pipeline 91.O-ring 73b be configured at suction inlet 81 and suction pipeline 91 with Suction inlet 83 and suction are used between pipeline 93.O-ring 73c is configured at suction inlet 83 and suction pipeline 93 and discharge room 82 And discharge is between pipeline 92.O-ring 73d be configured at discharge room 82 and discharge pipeline 92 and housing 101 outside it Between.O-ring 73a, 73c, 73d using by rotary shaft 54 as center and around a circumferential circle in a manner of be simply configured to toroidal, But O-ring 73b by by centered on rotary shaft 54 and around circumference O-ring axially offsetting configuration, can realize and rotate Size reduction in the axial direction of axle 54.

In addition, possesses groove portion 74a~74d in the periphery of pump main body 100, so as to configure O-ring 73a~73d.Groove portion 74a, 74b are formed by making the periphery local dent of cylinder body 71.Groove portion 74c by the part of the depression of the periphery of cylinder body 71 and The fore-end of connector 72 is formed.Recess 74d is formed by making the periphery local dent of connector 72.In such each groove portion 74a~74d inserts pump main body 100 in the recess 101a of housing 101 in the state of being embedded in O-ring 73a~73d, so as to Each O-ring 73a~73d is flattened in recess 101a internal face, function is played as seal.

In addition, the outer peripheral face of connector 72 at direction of insertion rear by undergauge, form end difference.The external screw thread of above-mentioned ring-type Part 102 is flush-mounted in the part of the undergauge, fixed pump main body 100.

Construction forms gear pump arrangement as more than.Next, the shell to forming above-mentioned gear pump 19,39 Sliding surface 71b, 71c detailed configuration of cylinder body 71 of a part illustrate.In addition, sliding surface 71b, 71c are formed as phase Same structure, therefore sliding surface 71b, 71c both sides' identical structure is illustrated in Fig. 4 and Fig. 5.

By in cylinder body 71 across gear pump 19,39 and sealing mechanism 111,115 opposite side end face pie graph 4 with And sliding surface 71b, 71c as shown in Figure 5.Specifically, in the middle position of the end face formed with centre bore 71a, and Across centre bore 71a both sides formed be configured at suction inlet 81,83 and discharge room 80,82 corresponding positions discharge Groove 71e.Moreover, centre bore 71a, suction inlet 81 in the end face and the part beyond discharge groove 71e turn into gear pump 19, Sliding surface 71b, the 71c slided during 39 driving for two rotor 19a, 19b, 39a, 39b.

In sliding surface 71b, 71c formed with the grinding rib 71f for forming fluid lead-in groove.Rib 71f is ground for example, by grinding Process and formed.In the present embodiment, ground by from the center of gear pump 19,39 in a manner of radiated entends formed with a plurality of Grind rib 71f.Herein, the center using the center of gear pump 19,39 as centre bore 71a, but relative to centre bore 71a with radial Form grinding rib 71f, it is not necessary to centered on specific position is set.

A plurality of grinding rib 71f respectively with the position more more outward than outer rotor 19a, 39a in rotor chamber 100a, 100b (hereinafter referred to as periphery high-pressure area) connects.Moreover, for a plurality of grinding rib 71f, the portion that is connected with periphery high-pressure area Divide and do not connected with the centre bore 71a as area of low pressure, suction inlet 81,83 and suction tank 71d.In the situation of present embodiment Under, the end of the inner circumferential side in a plurality of grinding rib 71f is away from centre bore 71a, suction inlet 81,83 and suction tank 71d.

As described above, cylinder body 71 sliding surface 71b, 71c formed with grinding rib 71f.

In the case where foring the grinding rib 71f of such structure, grinding rib 71f and the discharge pressure for being formed as high pressure The connection of periphery high-pressure area, therefore the brake fluid of high pressure is imported in grinding rib 71f.Accordingly, it is capable to access based on high pressure What brake fluid pressure pushed back gear pump 19,39 pushes back effect.Moreover, even if grinding rib 71f is set to be connected with periphery high-pressure area, also not Grinding rib 71f is set to be connected with as each several part of area of low pressure.Therefore, it is possible to which high pressure will be remained in grinding rib 71f, can press down System pushes back effect reduction.Therefore, it is possible to prevent from losing the reduction of the minimizing effect of moment of torsion, loss moment of torsion can be made further to subtract It is few.

(second embodiment)

Second embodiment of the present invention is illustrated.Present embodiment is changed and ground relative to first embodiment Rib 71f is ground, it is other identical with first embodiment, therefore only a pair part different from first embodiment illustrates.

As shown in Fig. 6 and Fig. 7, in the present embodiment, with from the center of gear pump 19,39 with the side of radiated entends Formula forms a plurality of grinding rib 71f, and make in grinding rib 71f can be connected with space part 19c, 39c of low-pressure state it is low Splenium 71fa separates from the high-voltage section 71fb with the periphery high-pressure area connection than its outer peripheral side.

Specifically, the Fluid pressure of each several part in gear pump 19,39 shows exist and be imported into discharge as shown in Figure 8 The high-pressure area Ra of pressure, the area of low pressure Rb for being imported into suction pressure and the intermediate pressure region Rc as their centre. Moreover, gear pump 19,39 and the pressure between sliding surface 71b, 71c of cylinder body 71 are shown as shown in Figure 9.Therefore, based on Fig. 8 with And the pressure dependence shown in Fig. 9, low voltage section 71fa are formed at the scope for including area of low pressure Rb, high-voltage section 71fb is not formed at low Intermediate pressure section Rb.

As shown in figure 8, suction inlet 81,83, suction tank 71d and centre bore 71a turn into low pressure.Moreover, space part 19c, 39c when being connected with suction inlet 81,83, suction tank 71d, and since being connected with them to during before volume increase As low-pressure state.Therefore, using grind rib 71f in can with the place that space part 19c, 39c of low-pressure state are connected as Low voltage section 71fa, using the place that the gap between the periphery of outer rotor 19a, 39a with high pressure conditions and cylinder body 71 connects as High-voltage section 71fb, and low voltage section 71fa and high-voltage section 71fb is separated.

In other words, grinding rib 71f is not formed in defined region.Specifically, as shown in Fig. 6 and Fig. 8, in space Not connected with any one of high-pressure area Ra position and area of low pressure Rb position and as centre in portion 19c, 39c Scope present in intermediate pressure section Rc pocketed oil portion 19d, 39d does not form grinding rib 71f.In other words, in pocketed oil portion 19d, 39d Grinding rib 71f is not formed by the scope of track.In addition, turning into the region of low-pressure state more outward than space part 19c, 39c The scope of motion track of the week side of boss along space part 19c, 39c does not form grinding rib 71f.

Described pocketed oil portion 19d, 39d mean part when volume in space part 19c, 39c turns into maximum herein.Tool For body, on the direction of rotation of gear pump 19,39, space part 19c, 39c move from the position connected with suction inlet 81,83 Volume turns into maximum during untill the position connected with discharge room 80,82, space part 19c, 39c when this is turned into maximum Referred to as pocketed oil portion 19d, 39d.

In addition, space part 19c, 39c also have volume turn into it is minimum when pocketed oil portion 19e, 39e, pocketed oil portion 19e, the 39e with Grind rib 71f low voltage section 71fa connections.Pocketed oil portion 19e, 39e small volume, therefore even if being connected with low voltage section 71fa, pressure becomes Dynamic etc. influence is also small.Therefore, though making low voltage section 71fa be connected with pocketed oil portion 19e, 39e, the region, which can not also possess, grinds Grind rib 71f.

So, can also be so that with the area of low pressure Rb of suction inlet 81,83 etc. the low voltage section 71fa connected and with discharging room 80th, the mode of the high-voltage section 71fb separation of 82 etc. high-pressure area Ra connections forms grinding rib 71f.If in such manner, it is possible to further Suppress high-pressure fluid to reveal from high-pressure area to area of low pressure side.Therefore, it is possible to further prevent from losing the minimizing effect of moment of torsion Reduction, loss moment of torsion can be made further to reduce.

(the 3rd embodiment)

Third embodiment of the present invention is illustrated.Present embodiment is changed and ground relative to second embodiment Rib 71f is ground, it is other identical with second embodiment, therefore only a pair part different from second embodiment illustrates.

As shown in Figure 10, in the present embodiment, the radial curve structure by extending from the center of gear pump 19,39 Into grinding rib 71f.For each grinding rib 71f low voltage section 71fa, high-voltage section 71fb, intermediate position is compared with both ends Positioned at the front of the direction of rotation of gear pump 19,39.That is, low voltage section 71fa, high-voltage section 71fb is made to bend and turn into convex form, it is convex Front of the portion towards direction of rotation.

So, if forming low voltage section 71fa, high-voltage section 71fb by radial curve, rotated in gear pump 19,39 When the part that bends play the effect of wedge, turn into and be imported into the obstruction that the brake fluid of inside flows along interior circumferential direction.Therefore, grind Brake fluid in rib 71f is not easy to reveal from high-pressure area to area of low pressure side, is able to maintain that grinding rib 71f high pressure conditions.By This, can further prevent from losing the reduction of the minimizing effect of moment of torsion, loss moment of torsion can be made further to reduce.

(the 4th embodiment)

4th embodiment of the present invention is illustrated.Present embodiment changes grinding relative to first embodiment Rib 71f, it is other identical with first embodiment, therefore only a pair part different from first embodiment illustrates.

As shown in figure 11, in the present embodiment, single dotted broken line table in being set in the center of gear pump 19,39 by figure The imaginary circle C shown, grinding rib 71f is set in a manner of the tangential direction extension along imaginary circle C.Specifically, to grind rib The mode in front of the end of the inner circumferential side of the gear pump 19,39 in 71f compared with the end of outer circumferential side positioned at direction of rotation is set Put grinding rib 71f.Imaginary circle C size is arbitrary, below centre bore 71a diameter.

So, even if being formed as making grinding rib 71f be laid out along the tangential direction extension relative to imaginary circle C is such, It can obtain and first embodiment identical effect.In addition, to grind the end of the inner circumferential side of the gear pump 19,39 in rib 71f Mode of the portion positioned at the front of direction of rotation compared with the end of outer circumferential side sets grinding rib 71f.Therefore, based on gear pump 19, 39 rotary motion, the brake fluid flowed into from the end of outer circumferential side easily flow to the end of inner circumferential side.Therefore, in grinding rib 71f whole region is it is easy to ensure that high pressure conditions, can further obtain the effect shown in first embodiment.

(other embodiments)

The present invention is not limited to above-mentioned embodiment, can suitably become in the scope described in claims More.

For example, the example for possessing radial grinding rib 71f is listed as fluid lead-in groove, but can also be by grinding The groove beyond rib 71f is ground to form fluid lead-in groove.For example, it is also possible to by being formed based on the laser processing groove of Laser Processing Fluid lead-in groove.In the case where being formed as laser processing groove, due to machining, caused such burr will not produce, Therefore not because of influence that burr is brought.In addition, in the case of Laser Processing, in the case of the deep-lying position of machined surface Also it can process, therefore can also realize the formation facilitation of fluid lead-in groove.

In addition, in the respective embodiments described above, by the tooth with two gear pumps 19,39 being made up of internal gear pump Wheel pump installation is enumerated as example.It may, however, also be only using the gear pump arrangement of a gear pump.In addition, in above-mentioned each reality Apply in mode, turn into the gear pump arrangement for possessing two gear pumps 19,39, by housing 101, cylinder body 71 and connector 72 come shape Into the shell for the incorporating section (rotor chamber 100a, 100b) for forming each gear pump 19,39.However, this simply shows an example, example Such as shell only can also be formed by the part for the profile for forming pump main body 100.

In addition, though the end face in cylinder body 71 forms suction tank 71d but it is also possible to be the construction for not possessing suction tank 71d. In such a situation it is preferred that grinding rib 71f is also formed in the part present in suction tank 71d.

The explanation of reference

100... pump main body；101... housing；101a... recess；19th, 39... rotary pumps；Turn outside 19a, 39a... Son；19b, 39b... internal rotor；54... rotary shaft；71... cylinder body；71a... centre bores；71b, 71c... sliding surface； 71d... suction tanks；71e... discharges groove；71f... grinds rib；71fa... low voltage sections；71fb... high-voltage sections；72... connector； 80th, 82... discharges room；81st, 83... suction inlets；90th, 92... discharges pipeline；91st, 93... suctions pipeline；111、 115... sealing mechanism.

Claims (6)

1. a kind of gear pump arrangement, it possesses：

Gear pump, it possesses：Outer rotor with interior teeth portion and form multiple space parts with the outer rotor and engage Internal rotor, the rotation of the axle based on the centre bore for being inserted through the internal rotor makes the outer rotor and the internal rotor rotate from And carry out the suction discharging operation of fluid；

Shell, it forms the incorporating section for storing the gear pump；And

Sealing mechanism, it is disposed between an end face of the pump axial end in the shell and the gear pump, divides institute State the low-pressure side for including sucking around the suction side and the axle of the fluid in gear pump and including discharging the stream The high-pressure side of the part in the gap between the periphery and the shell of the discharge side of body and the outer rotor,

It is described that pressing force based on the sealing mechanism is connected to another end face of the pump axial end in the gear pump The sliding surface of shell, so as to be sealed between the low-pressure side of the gear pump of the end and high-pressure side,

The gear pump arrangement is characterised by,

There is fluid lead-in groove in the sliding surface, the fluid lead-in groove by from the center of the gear pump with radiated entends Rib is formed, and is imported into as the fluid in the gap between the periphery of the on high-tension side outer rotor and the shell,

The fluid lead-in groove is away from the centre bore and the suction side.

2. gear pump arrangement according to claim 1, it is characterised in that

The volume that the fluid lead-in groove is not formed in the multiple space part turns into the scope present in maximum pocketed oil portion.

3. gear pump arrangement according to claim 1 or 2, it is characterised in that

The fluid lead-in groove in the multiple space part by can be with being communicated in the suction side and as low-pressure state The part of partially communicating place forming as low voltage section, by with the periphery of the outer rotor as high pressure conditions with it is described outer The place of gap connection between shell is separated as high-voltage section, the low voltage section with the high-voltage section.

4. according to gear pump arrangement according to any one of claims 1 to 3, it is characterised in that

The fluid lead-in groove is made up of radial curve, compared with the respective both ends of fluid lead-in groove, positioned at the both ends Between centre position be located at the gear pump direction of rotation front.

5. according to gear pump arrangement according to any one of claims 1 to 3, it is characterised in that

The fluid lead-in groove is formed as setting imaginary circle in the center of the gear pump, and along the tangent line side of the imaginary circle To the radial of extension.

6. gear pump arrangement according to claim 5, it is characterised in that

The fluid lead-in groove is formed as the end of inner circumferential side and the end of outer circumferential side of the gear pump in the fluid lead-in groove Compare positioned at the front of the direction of rotation of the gear pump in portion.