CN1959115A - Vehicular brake device - Google Patents
Vehicular brake device Download PDFInfo
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- CN1959115A CN1959115A CN 200610142561 CN200610142561A CN1959115A CN 1959115 A CN1959115 A CN 1959115A CN 200610142561 CN200610142561 CN 200610142561 CN 200610142561 A CN200610142561 A CN 200610142561A CN 1959115 A CN1959115 A CN 1959115A
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- 238000003780 insertion Methods 0.000 claims abstract description 8
- 230000037431 insertion Effects 0.000 claims abstract description 8
- 239000012530 fluid Substances 0.000 claims description 46
- 239000007788 liquid Substances 0.000 claims description 33
- 239000004033 plastic Substances 0.000 claims description 3
- 238000012545 processing Methods 0.000 claims description 3
- 238000007789 sealing Methods 0.000 description 25
- 239000011347 resin Substances 0.000 description 12
- 229920005989 resin Polymers 0.000 description 12
- 230000037361 pathway Effects 0.000 description 9
- 230000002093 peripheral effect Effects 0.000 description 6
- 238000007599 discharging Methods 0.000 description 5
- 230000015572 biosynthetic process Effects 0.000 description 2
- 238000012423 maintenance Methods 0.000 description 2
- 238000010992 reflux Methods 0.000 description 2
- 238000013459 approach Methods 0.000 description 1
- 230000000712 assembly Effects 0.000 description 1
- 238000000429 assembly Methods 0.000 description 1
- 230000004323 axial length Effects 0.000 description 1
- 238000006243 chemical reaction Methods 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 230000008878 coupling Effects 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
- 238000005859 coupling reaction Methods 0.000 description 1
- 230000000994 depressogenic effect Effects 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 239000000284 extract Substances 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000007935 neutral effect Effects 0.000 description 1
- 238000003466 welding Methods 0.000 description 1
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- Valves And Accessory Devices For Braking Systems (AREA)
- Rotary Pumps (AREA)
- Regulating Braking Force (AREA)
Abstract
A pump body includes a cylindrical first case for housing the plurality of rotary pumps, a second case located coaxially with the first case, and a disk spring located between the first case and the second case. In addition, a fixing means located at an entrance of the concave portion of a housing presses the second case in the insertion direction of the pump body and fixes the second case.
Description
Technical field
The rotary pump that the present invention relates to a kind of use such as trochoid pump is carried out the Vehicular brake device of brake fluid pressure control.
Background technique
In recent years, people make great efforts to reduce gimp etc. at the brake fluid pressure control period such as ABS control always.For this purpose, will be used in such as the rotary pump of trochoid pump in the Vehicular brake device, as the pump that is used to carry out brake fluid pressure control.
Vehicular brake device with this rotary pump is set forth in Japan Patent publication No.2001-80498.Fig. 5 is arranged on the cross section view of the pump housing J100 of the rotary pump in the Vehicular brake device that is recorded in this publication.
As shown in Figure 5, pump housing J100 is a cell arrangement, two rotary pump J10 wherein and J13, and be used for live axle J54 of rotary pump J10 and J13 etc., be combined among cylindrical housings J71a to 71d, J72a and the 72b.The pump housing J100 that is configured to cell arrangement also is fixed in the shell J150 of Vehicular brake device.More particularly, pump housing J100 is inserted into the recessed portion J150a of shell J150.
In this case, because the high brake fluid pressure that the inflow of brake fluid and outflow can produce, so thereby need strong axial force prevent that the pump housing J100 from moving astatically in shell J150.
But, when above-mentioned axial force was produced by screw-thread securing, obvious variation can appear in axial force.Leaf spring J210 is arranged on end or the base position of pump housing J100, as the measure that overcomes this problem.Adopt this measure, axial force that can firm and stable pump housing J100.Simultaneously, the axial force that acts on the pump housing J100 also is suppressed to required minimum value, and it is excessive can not become.
Yet, for leaf spring J210 is arranged on end or base portion, will become big along the length of pump housing J100 axial direction.As a result, pump housing J100 and therefore Vehicular brake device can not make enough compactly.
Summary of the invention
In view of above-mentioned aspect content, the purpose of this invention is to provide a kind of Vehicular brake device that can reduce pump housing length, this pump housing is configured to comprise the unit of rotary pump etc.
To achieve these goals, the pump housing (100) comprises cylindrical first housing (71a, 71b, 71c, 73a, 73b) that is used to hold a plurality of rotary pumps, with second housing (71d) of the coaxial setting of first housing, and be arranged on elastic component (210) between first housing and second housing.In addition, the fixing device (200) that is positioned at the ingress of shell (150) recessed portion (150a) is suppressed second housing and is fixed second housing along the direction of insertion of the pump housing.
Because this elastic component is arranged between first housing and second housing, so compare with end that elastic component is arranged on the pump housing or base portion place, can more effectively utilize the space.The situation of line shaft when length (pump shaft length) therefore can be made to such an extent that be shorter than this elastic device and be arranged on the end of the pump housing or base portion that comprises the pump housing of elastic component.A kind of Vehicular brake device of pump length of the pump housing of the unit that can reduce to be configured to comprise rotary pump etc. correspondingly, can be provided.
Description of drawings
The present invention and other purposes of the present invention, feature and advantage will be by getting the best understanding in following specification, appended claim and the accompanying drawing.In the accompanying drawings:
Fig. 1 is the schematic partial cross-sectional view that illustrates according to the pipe configuration in the Vehicular brake device of first embodiment of the invention;
Fig. 2 is the cross section view of the pump housing, and this pump housing is arranged in Vehicular brake device and comprises rotary pump;
Fig. 3 A is the perspective view of the cylinder in the pump housing;
Fig. 3 B is the schematic anterior figure that watches the cylinder that obtains from the axial direction of the pump housing;
Fig. 4 is the cross section view that the line IV-IV along Fig. 2 is done; And
Fig. 5 is the cross section view of the pump housing in the conventional truck braking device.
Embodiment
Below with reference to the essential structure of Fig. 1 explanation according to the braking device of the embodiment of the invention.Internal pump (specifically, trochoid pump) is as the rotary pump of braking device shown in Figure 1.In following explanation, this braking device is applied to the four wheeler of four-wheel drive, and this automobile has the oil hydraulic circuit of X type, comprise be used for front right wheel and back revolver the two first pipe-line system and be used for before the two second pipe-line system of revolver and rear right wheel.But, this braking device also can be applicable to have the automobile of front and back formula oil hydraulic circuit, this front and back formula oil hydraulic circuit comprises and is used for the two pipe-line system of front right wheel and rear right wheel, and revolver and back the two another pipe-line system of revolver before being used for, and can be applicable to have the automobile of any other type oil hydraulic circuit.
As shown in Figure 1, brake petal 1 is connected with booster rocket 2, and this booster rocket amplifies brake pedal force etc.
That be connected with master cylinder 3 is main hydraulic accumulator 3a, the excessive brake fluid of this hydraulic accumulator in master cylinder 3 supply system hydrodynamics and collection master cylinder 3.
Master cylinder pressure is sent to the wheel cylinder 4 that is used for front right wheel via actuator and is used for the wheel cylinder 5 of back revolver, and this actuator control is used to carry out the brake fluid pressure of ABS control etc.Though following explanation relates to first pipe-line system that is used for front right wheel and back revolver, second pipe-line system of revolver and rear right wheel before it also can be applied to fully and be used for.
This braking device comprises the main pipe A that is connected with master cylinder 3.Linear differential pressure controlled valve 22 and one-way valve 22a are arranged among the pipeline A.Valve 22 is divided into two zones with pipeline A, i.e. pipeline A1 and pipeline A2.Pipeline A1 strides across the path between master cylinder 3 and the valve 22 and admits master cylinder pressure.Pipeline A2 strides across path between valve 22 and the wheel cylinder 4 and the path between valve 22 and the wheel cylinder 5.
In the normal running of braking device, valve 22 is set to and makes brake fluid pressure pass through the connected state that valve 22 transmits fully.When master cylinder pressure drop to be lower than predetermined pressure after, when wheel cylinder 4 and 5 applies unexpected braking and when carrying out tractive force control, valve 22 is set to the differential pressure state.Under the differential pressure state, the predetermined difference value in the brake fluid pressure is created between the master cylinder side and wheel cylinder side of valve 22.The predetermined pressure difference of valve 22 is linear adjustable.
Pipeline A2 branches into two paths.First pressure increases control valve 30 and is positioned at one of them of two paths and the brake fluid pressure that control puts on wheel cylinder 4.Second pressure increases the brake fluid pressure that another and control that control valve 31 is arranged in two paths put on wheel cylinder 5.
Be arranged in thirdly being connected with rotary pump 13 of pipeline A2 by reflux line C1.Rotary pump 13 is connected with accumulator 40 by the part of another reflux line C2 and pipeline B.Therefore, between the some P3 and accumulator 40 of rotary pump 13 in the fluid passage.Safety valve 13A is arranged among the pipeline C1, in other words, is in the output terminal oral-lateral of rotary pump 13, thereby the maintenance brake fluid can reverse flow.Rotary pump 13 also is connected with the motor 11 that is used for driving rotational pump 13.Second pipe-line system comprises rotary pump 10 (referring to Fig. 2), and this revolution pump structure is identical with rotary pump 13. Rotary pump 10 and 13 will be described in detail hereinafter.
Accumulator 40 comprises accumulator mouth 40a and 40b.Accumulator mouth 40a is connected with pipeline D and admits brake fluid from master cylinder 3.Accumulator mouth 40b is connected with pipeline B and admits the brake fluid that overflows from wheel cylinder 4 and 5.The position of ball valve 41 in accumulator 40 is darker than accumulator mouth 40a.Bar 43 attaches to ball valve 41 discretely and has the predetermined stroke that is used to move up and down ball valve 41.
In the 40c of accumulator chamber, be provided with and bar 43 related mobile pistons 44.In the 40c of accumulator chamber, also be provided with spring 45, be used for generation power piston 44 is pressed to ball valve 41 and thus brake fluid released hydraulic accumulator chamber 40c.
When hydraulic accumulator 40 is collected the brake fluid of prearranging quatity, ball valve 41 will be sitting on the valve seat 42 and stop brake fluid to flow into hydraulic accumulator 40 thus.Therefore, the amount of brake fluid inflow hydraulic accumulator chamber 40c can not surpass the feed liquor capacity of rotary pump 13.Therefore, can not apply high pressure to the liquid feeding side of rotary pump 13.
In Fig. 2, the pump housing 100 attaches to the shell 150 of the actuator that control brake hydraulic pressure uses, so that the Vertical direction of this figure is corresponding to the Vertical direction of vehicle.The general structure of the pump housing 100 is described hereinafter with reference to Fig. 2.
As mentioned above, braking device comprises two systems, that is, and and first pipe-line system and second pipe-line system.The pump housing 100 comprises rotary pump 13 that is used for first pipe-line system shown in Figure 1 and the rotary pump 10 that is used for second pipe-line system shown in Figure 2. Rotary pump 10 and 13 is driven by live axle 54.
The housing that forms the pump housing 100 profiles comprises a plurality of cylinders (or, a plurality of side plates) and cylindrical center plate.Described a plurality of cylinder comprises the first cylinder 71a, the second cylinder 71b, the 3rd cylinder 71c and the 4th cylinder 71d.Center plate comprises the first center plate 73a and the second center plate 73b.
The first cylinder 71a, the first center plate 73a, the second cylinder 71b, the second center plate 73b and the 3rd cylinder 71c align according to said sequence, and each is adjacent to connecting by welding in the periphery of these two right opposed face in them.These weld assemblies 71a, 73a, 71b, 73b and 71c form the assembly of elements that is used as first housing.The disc spring 210 that is used as elastic component is inserted into the 3rd cylinder 71c of first housing and is used as between the 4th cylinder 71d of second housing.The 4th cylinder 71d and the coaxial setting of first housing.Therefore, realize the overall structure of the pump housing 100.
Have the above-mentioned integrally-built pump housing 100 and be inserted into columniform basically recessed portion 150a, this cylindrical part is formed on the shell 150 of the actuator that is used for control brake hydraulic pressure.
Annular externally threaded item 200 is screwed into the internal whorl 150b of the ingress that is formed on recessed portion 150a, and thus, the pump housing 100 is fixed in shell 150.More particularly, the second recessed portion 150c with toroidal is formed in the zone of recessed portion 150a of shell 150.This area surface is to the end of live axle 54, and this end is the part of the pump housing 100 along the front end of its direction of insertion.The diameter of the second recessed portion 150c is greater than the diameter of live axle 54, but less than the external diameter of the first cylinder 71a.The end of live axle 54 promptly, is set in the second recessed portion 150c towards the outstanding part of second recessed portion from the end surfaces of the first cylinder 71a, and contacts with the end face of the first cylinder 71a except the part of the second recessed portion 150c of recessed portion 150a bottom.Therefore the pump housing 100 admits axial force when externally threaded item 200 is screwed into internal thread 150b.
In the structure that is used for the pump housing 100 is fixed in the recessed portion 150a of shell 150, disc spring 210 as described below operations.
Thereby must produce strong axial force the pump housing 100 being fixed in shell 150, in other words, is in order to prevent that the pump housing 100 from can not carry out unsettled motion because of the high brake fluid pressure that produces in shell 150 when the pump housing 100 sucks and discharges brake fluid.
Yet, obtain above-mentioned axial force and can in axial force, produce tangible deviation by tightening externally threaded item 200 fully.
In order to address this problem, in existing embodiment, disc spring 210 is arranged between the third and fourth cylinder 71c and the 71d.The 4th cylinder 71d compares to some extent with other parts of the 4th cylinder 71d in the face of the diameter of the end of the 3rd cylinder 71c and reduces.This end is inserted into the 3rd center hole 72c of the 3rd cylinder 71c then.The diameter that cylinder 71d is inserted into this end of the 3rd center hole 72c is set to the diameter that is substantially equal to or is slightly less than the 3rd center hole 72c.Therefore, the 3rd center hole 72c of the 3rd cylinder 71c is gone in a part of loose fit of the 4th cylinder 71d.
When externally threaded item 200 was screwed into internal thread 150b, the elastic force of the disc spring 210 between the 4th cylinder 71d and the 3rd cylinder 71c became the axial force that is enough to the pump housing 100 is fixed in the recessed portion 150a of shell 150.In other words, axial force generation as described below.Disc spring 210 compactings are arranged at the bottom surface of each parts on the 3rd cylinder 71c right side among Fig. 2 against recessed portion 150a.Disc spring 210 is also pressed to externally threaded item 200 with the 4th cylinder 71d.As a result, acting on axial force on the pump is stablized and is suppressed to be required minimum value.Therefore the distortion of the pump housing 100 can be suppressed.
First to fourth cylinder 71a to 71d comprises the first, second, third and the 4th center hole 72a, 72b, 72c and 72d respectively.Bearing 51 is installed on the interior week that is formed on the first center hole 72a on the first cylinder 71a.Another bearing 52 is installed on the interior week that is formed on the 3rd center hole 72c on the 3rd cylinder 71c.Bearing 51 and 52 comprises that width is narrower than the ball bearing of needle bearing.
Bearing 51 and 52 has sealing plate 51a and 52a respectively.Sealing plate 51a is positioned at the end (that is the front end of direction of insertion) of the bearing 51 that more approaches live axle 54 heads.Sealing plate 52a is positioned at the end of bearing 52 towards the 4th cylinder 71d.
Shown in Fig. 3 A and 3B, the 3rd center hole 72c has part that internal diameter equals bearing 52 external diameters and diameter another part less than the outer diameter of bearing 52.These parts form the single order step-portion.When bearing 52 is pushed to arrive the stepped portion timesharing, bearing 52 is assemblied in the inboard of the 3rd center hole 72c, and a cavity remains on the 4th cylinder 71d side of the 3rd center hole 72c.The part of the 4th cylinder 71d is inserted in this cavity.
The 3rd cylinder 71c also forms liquid entering hole 62, and this will be elaborated hereinafter.
Hereinafter, rotary pump 10 and 13 structure describe with reference to Fig. 2 and 4.
More particularly, rotary pump 10 comprises the rotating part with external rotor 10a and internal rotor 10b.Internal gear segments was formed on the interior week of external rotor 10a.External gear partly is formed on the periphery of internal rotor 10b.Live axle 54 is inserted into the hole of passing among the internal rotor 10b.Key 54b is fitted into the elliptical aperture 54a (referring to Fig. 2) that is formed on the live axle 54.Torque is sent to internal rotor 10b by key 54b from live axle 54.
Thereby being formed on internal tooth portion on external rotor 10a and the internal rotor 10b and outer toothed portion meshes respectively and forms a plurality of gap portion 10c.Along with the rotation according to live axle 54 of the size of gap portion 10c changes, rotary pump 10 sucks and discharges brake fluid.
The first cylinder 71a comprises the liquid entering hole 60 that some the gap portion 10c on the liquid feeding side with rotary pump 10 are communicated with.Liquid entering hole 60 forms the surface, opposite end that end surfaces on rotary pump 10 sides of the first cylinder 71a extends to the first cylinder 71a.Therefore, brake fluid is imported into from opposing end surface.
The second cylinder 71b comprises exhaust port 61, and some the gap portion 10c on the discharge side of this exhaust port and rotary pump 10 are connected.Exhaust port 61 extends to the periphery of rotary pump 10 from the end surfaces of the rotating part of covering rotary pump 10.More particularly, the structure of exhaust port 61 is as described below.
The second cylinder 71b has ring groove (first ring groove) 61a in the face of the end surfaces of the rotating part of rotary pump 10, and this annular groove forms around this live axle 54.
In addition, the footpath of Sealing 171 contact ring connected in star 61a is week inwardly, and the outer radial periphery of contact ring connected in star 61a partly.One space forms by a part of annular groove 61a, this part groove than Sealing 171 more near outer radial periphery and do not contact with Sealing 171.Brake fluid can flow into this space.On the second cylinder 71b, passage 61b extends the part from circular groove 61a.Therefore exhaust port 61 is formed by space and the passage 61b of the annular groove 61a of above-mentioned structure.
In addition, the second cylinder 71b comprises exhaust port 63, and this exhaust port is positioned on the end face of second cylinder and is relative with the end face that forms exhaust port 61.Exhaust port 63 is communicated with the gap portion that rotary pump 13 is discharged side.
The 3rd cylinder 71c has the liquid entering hole 62 that is communicated with gap portion on rotary pump 13 liquid feeding sides.
Liquid entering hole 62 passes the 3rd cylinder 71c, till the end face on from the end face on rotary pump 31 sides of the 3rd cylinder 71c to its opposite side.Liquid entering hole 62 extends to the outer surface of the 3rd cylinder 71c from the end face on the above-mentioned opposite side.
More particularly, liquid entering hole 62 is formed by the 3rd center hole 72c of the 3rd cylinder 71c.The diameter of the 3rd center hole 72c is extended, and therefore, a groove is formed on the part place on the 3rd center hole 72c.Shown in Fig. 3 A and 3B, the 3rd center hole 72c of the 3rd cylinder 71c (the dark side among Fig. 3 A) on rotary pump 13 sides has ellipse (perhaps elongated) shape.The position of live axle 54 makes upper end portion semicircle parallel of top profile and elliptical shape of its cross section.The semicircular diameter of the underpart of elliptical shape partly further is extended to the diameter greater than live axle 54.The diameter of enlarged is greater than the diameter of bearing 52 peripheries.The underpart of elliptical shape can be substituted by rectangular shape.
The 3rd center hole 72c enlarges at the place, neutral position along the 3rd cylinder 71c axial direction, thereby makes its diameter equal the diameter of bearing 52.The underpart of elliptical shape is connected with the groove of the outer surface that extends to the 3rd cylinder 71c.This attachment portion is formed on the end on the 3rd cylinder 71c side relative with rotary pump 13 sides.The cross section of this groove can have rectangular shape or half elliptic shape, but cross section in the present embodiment is a rectangular shape.
Liquid entering hole 62 comprises the crescent part that is not covered by bearing 52.Liquid entering hole 62 also comprises the groove that is formed on the 3rd cylinder 71c and the rotary pump 13 side opposing end faces.This groove extends to the outer surface of the 3rd cylinder 71c.Therefore brake fluid is introduced from the outer surface as the 3rd cylinder 71c that enters the mouth.Liquid entering hole 62 is connected with feed pathway 153 in being formed on shell 150.This connection realizes that via the annular groove 164 that is formed on the recessed portion 150a part this part is around the whole periphery of the pump housing 100 parts, and this part of the pump housing comprises the inlet of liquid entering hole 62.
Because the 3rd center hole 72c is as the part of liquid entering hole 62, so brake fluid is transported to live axle 54, bearing 52 etc.This allows the level and smooth rotation of live axle 54 again.In addition, the position of liquid entering hole 62 than exhaust port 63 more near motor 11 (perhaps, more near the outside of shell 150).Therefore, near the brake fluid pressure at the part place the exhaust port 63 is suppressed.
The second center hole 72b of the second cylinder 71b has the part of diameter greater than live axle 54 diameters.In the part of this enlarged, be provided with Sealing 80 and sealing part first rotary pump 10 and second rotary pump 13 are separated.Sealing 80 comprises ring elastic parts (hereinafter being referred to as O shape ring 81) and annular resin spare 82.Resin piece 82 comprises the groove part that digs along the radial direction of resin piece 82.O shape ring 81 is assemblied in (more particularly, in groove part) in this resin piece.The elastic force of O shape ring 81 is pressed into resin piece 82 into contacting with live axle 54.
The second center hole 72b of the resin piece 82 and the second cylinder 71b has D shape cross section (not shown) basically similarly, wherein, and rounded ends cut and formation arc and string shape.Resin piece 82 also is assemblied among the second center hole 72b of the second cylinder 71b.Therefore, the cutting-out of resin piece 82 is partly as suppressing the key that Sealing 80 rotates with respect to the second cylinder 71b.
The 4th cylinder 71d is being recessed into the surperficial facing surfaces place that is provided with disc spring 210.Live axle 54 protrudes from this recessed portion.The attachment portion 54c that has key shape on the end face of the projection of live axle 54.This attachment portion 54c is inserted into the live axle 11a of motor 11.Correspondingly, single live axle 54 is rotated by motor 11 via live axle 11a, successively driving rotational pump 10 and 13.
In addition, the inlet diameter on the recessed portion of the 4th cylinder 71d equals to be formed on the diameter of the hole 11c on the support 11b of motor 11.Space between the recessed portion of the 4th cylinder 71d and the hole 11c is minimized, thereby bearing 180 is arranged in this space axially mounting live axle 11a.Though live axle 11a is by bearing 180 axially mountings, live axle 54 can replace live axle 11a by axially mounting.
As mentioned above, bearing 180 is positioned on the recessed portion of the hole 11c of support 11b and the 4th cylinder 71d.Therefore motor 11 and the 4th cylinder 71d are suitably located, and axially not lining up of live axle 11a and live axle 54 can be minimized.
In addition, O shape ring 74a, 74b, 74c and 74d are respectively along circumferentially being arranged on the outer surface of first to fourth cylinder 71a to 71d.O shape ring 74a to 74d sealing is formed on feed pathway 151,153 in the shell 150 and the brake fluid in the discharge route 152,154.O shape ring 74a to 74d is separately positioned between feed pathway 151 and the discharge route 152, between discharge route 152 and the discharge route 154, between discharge route 154 and the feed pathway 153 and between feed pathway 154 and the shell 150.In Fig. 3 A, the groove that is fitted into O shape ring 74c does not illustrate for convenience of explanation.
The diameter of the outer radial periphery of the 4th cylinder 71d the 4th cylinder 71 the inlet side edge of recessed portion reduce.Therefore, the stepped portion branch is formed on the periphery of the 4th cylinder 71d.Thereby this reduced diameter portion branch is fitted into and makes the pump housing 100 fixing in the above-mentioned annular external thread piece 200.
The operation of the braking device and the pump housing 100 will be described below.
This braking device drives pump housing 100 and sucks the brake fluid in hydraulic accumulators 40 and discharge this brake fluid in some cases, and these situations comprise: first kind of situation, when wheel shows locking trend and ABS control when correspondingly operating; Second kind of situation is when the big braking force of needs.Second kind of situation for example can appear at, when the braking force of coupling brake pedal force can't obtain, perhaps when brake petal 1 is operated in large quantities.The brake fluid of discharging can increase the pressure of wheel cylinder 4 and 5.
In these cases, the pump housing 100 is carried out basic pump operated, and promptly rotary pump 10 and 13 sucks brake fluid by feed pathway 151 and 153 respectively, and discharges brake fluid by discharge route 152 and 154 respectively.
Basic pump operated during, become very big of rotary pump 10 and 13 brake fluid pressures of discharging sides.Therefore, brake fluid applies power along the direction that the pump housing 100 leaves shell 150.But as mentioned above, the axial force of the pump housing 100 is firm by disc spring 210 and externally threaded item 200.Therefore, the pump housing 100 is held and does not carry out unsettled motion in shell 150.
In the present embodiment, the cylinder part of the formation pump housing 100 profiles is made of the parts more than.More particularly, the position of the pump housing 100 between rotary pump 10 and motor 11 is divided into two parts, just, and the 3rd cylinder 71c and the 4th cylinder 71d.In addition, disc spring 210 is between the 3rd cylinder 71c and the 4th cylinder 71d.
In conventional truck braking device shown in Figure 5, the cylinder part that forms pump housing profile is made of the single part between rotary pump and the motor and has a liquid entering hole.Because bearing and Sealing must be arranged in the cylinder part, has tangible axial length inevitably so have this cylinder part of conventional construction.But, more what be not set near each location of pump housing periphery than bearing or Sealing.Therefore, described each zone becomes dead angle (dead space).
By comparison, in the present embodiment, disc spring 210 is between the 3rd cylinder 71c and the 4th cylinder 71d.Therefore, can effectively utilize the space.Therefore the line shaft of the pump housing 100 comprises the 3rd cylinder 71c, the 4th cylinder 71d and disc spring 210 to length (pump shaft length), compares and can be shortened with the pump housing that wherein disc spring 210 is positioned at the end position place of the pump housing 100.
If the top surface of disc spring 210 in the face of rotary pump 10 and 13 and the bottom surface of disc spring 210 in the face of motor 11 sides, following problems may appear so.
The reaction forces that produce when the pump housing 100 presses the bottom surface of recessed portion 150a etc. are transferred into disc spring 210 via the outer peripheral portion of outer peripheral portion, the second center plate 73b and the 3rd cylinder 71c of the outer peripheral portion of the first cylinder 71a, the first center plate 73a, the second cylinder 71b.At that time, this load must be by the top surface supporting of disc spring 210.In this case, this load acts on the outer circumferential side of the 3rd cylinder 71c, and this load simultaneously is actual to be bearing in more position near interior all sides of the 3rd cylinder 71c.As a result, this displacement setting can make the 3rd cylinder 71c produce distortion.
But in the present embodiment, load can be by the bottom surface supporting of disc spring 210, the just outer circumferential side of the 3rd cylinder 71c.Therefore, this load can be bearing in the bottom surface of disc spring 210 reliably, and the distortion of the 3rd cylinder 71c is suppressed.
In addition, as shown in Figure 3, the 3rd cylinder 71c has simple shape, promptly has only the 3rd center hole 72 to be formed on cylinder shape (cylinder-like) parts.Therefore, the 3rd cylinder 71c can only be formed by simple plastic processing.Do not need to form liquid entering hole 62 by periphery boring from the 3rd cylinder 71c.
From traditional pump housing as seen, liquid entering hole comprises two oil circuits, and they extend and vertical mutually the meeting in its end with outer radial periphery from the axial end portion of cylinder respectively.Therefore, can produce the burr that must remove at the part place that oil circuit meets.In the present embodiment, thisly remove operation and do not need.
Equally, the 4th cylinder 71d also has simple shape, promptly only is formed on the cylinder shape parts with center hole 72d.Therefore, the 4th cylinder 71d can only form by simple plastic processing.
Owing to can avoid burr and can construct third and fourth cylinder 71c and the 71d simply, also can avoid being mixed into the variety of issue that brake fluid produces by burr.
And according to present embodiment, bearing 51 and 52 is made of ball bearing.Therefore, compare, can reduce the pump housing 100 size in axial direction with the pump housing that uses needle bearing.
Do not discuss and embodiment illustrated in the accompanying drawings above the present invention should not be confined to, can under the situation that does not deviate from thought of the present invention, adopt variety of way to implement yet.
For example, live axle 54 can be arranged to be formed on center hole 72c on the semicircle of tip portion of elliptical shape contact.
According to the foregoing description, the pump housing 100 is fixed in shell 150 by the internal thread groove 150b that externally threaded item 200 is screwed among the recessed portion 150a that is formed on shell 150.But the pump housing 100 can be fixed by the calking (caulking) of other modes such as the inner peripheral surface of recessed portion 150a.
Though the foregoing description has illustrated that one is used two rotary pumps 10 and 13 examples, also can use to surpass two rotary pump.
Claims (14)
1, a kind of Vehicular brake device comprises:
A plurality of rotary pumps (10,13), each rotary pump comprises:
Rotating part, this rotating part comprises internal rotor (10b, 13b) and external rotor (10a, 13a), described internal rotor has the external tooth part on this internal rotor periphery, described external rotor has interior toothed portion on week in this external rotor, wherein, thus toothed portion and described external tooth partly mesh and form a plurality of gap portions (10c) in described;
Liquid entering hole (60,62), this liquid entering hole is used for brake fluid is imported described rotating part; With
The brake fluid that exhaust port (61,63), this exhaust port are used for flowing out from described rotating part is discharged,
It is characterized in that:
The pump housing (100) is used to hold live axle (54) and described a plurality of rotary pump and is used for described each internal rotor by the described a plurality of rotary pumps of described drive shaft, and the described pump housing comprises:
Be used to hold cylindrical first housing (71a, 71b, 71c, 73a, 73b) of described a plurality of rotary pumps;
Second housing (71d) with the coaxial setting of described first housing; And
Be arranged on the elastic component (210) between described first housing and described second housing;
Shell (150), this shell have recessed portion (150a), and the described pump housing inserts this recessed portion, and described first housing and the described pump housing are the most approaching along the front end of direction of insertion; And
Fixing device (200), this device are arranged on the inlet of the female part, are used for suppressing described second housing and being used for fixing described second housing along direction of insertion.
2, Vehicular brake device according to claim 1, wherein:
Described a plurality of rotary pump comprises first rotary pump (10) and second rotary pump (13);
Described first housing comprises:
First cylinder (71a), first hole (72a) are formed on this first cylinder, and described live axle inserts this first hole;
First plate (73a), this first plate is close to described first cylinder, is used to hold the rotating part of described first rotary pump;
Second cylinder (71b), contiguous described first plate of this second cylinder, second hole (72b) is formed on described second cylinder, and described live axle inserts this second hole;
Second plate (73b), this second plate is close to described second cylinder, is used to hold the rotating part of described second rotary pump; And
The 3rd cylinder (71c), contiguous described second plate of the 3rd cylinder, the 3rd hole (72c) is formed on described the 3rd cylinder, and described live axle inserts the 3rd hole;
Described first cylinder, described first plate, described second cylinder, described second plate and described the 3rd cylinder form integrated unit;
Described second housing comprises the 4th cylinder (71d) of contiguous described the 3rd cylinder, and the 4th hole (72d) is formed on described the 4th cylinder, and described live axle inserts this hole; And
Described elastic component is arranged between described the 3rd cylinder and described the 4th cylinder.
3, Vehicular brake device according to claim 2, wherein, described elastic component is a disc spring.
4, Vehicular brake device according to claim 3, wherein:
The first surface of described disc spring is in the face of described first housing, and the periphery of described first surface is as the part that supports the load that is applied by described first housing; And
The second surface of described disc spring is in the face of described second housing, and the interior week of described second surface is as the part that supports the load that is applied by described second housing.
5, Vehicular brake device according to claim 3, wherein:
Described the 4th cylinder has swedged part in its side in the face of described the 3rd cylinder, and the diameter of this part is less than the diameter of another part of described the 4th cylinder; And
Described disc spring is arranged on the part place that described diameter reduces.
6, Vehicular brake device according to claim 5, wherein:
In the face of the internal diameter of the part in described the 3rd hole of described the 4th cylinder equals or slightly greater than the diameter parts that reduces of described the 4th cylinder; And
The reducing diameter parts and can insert described the 3rd hole of described the 4th cylinder.
7, Vehicular brake device according to claim 5, wherein:
Seal arrangement (90) is arranged on reducing between diameter parts place and described the 4th hole and the described live axle of described the 4th cylinder; And
Described disc spring is arranged on the outer circumferential side of the part that is provided with described seal arrangement in described the 4th cylinder.
8, Vehicular brake device according to claim 1, wherein:
Described fixing device comprises threaded part (200), and these parts are screwed into and are fixed in the inlet of the female part and suppress described second housing along direction of insertion.
9, Vehicular brake device according to claim 1, wherein:
Described first housing comprises a plurality of cylinder parts (71a to 71c), is used to form the side plate of described a plurality of rotary pumps;
Described a plurality of cylinder parts and described second housing immediate one (71) are formed with patchhole, and described live axle inserts this and inserts in the hole;
Described patchhole along its radial direction at least in part greater than the diameter of described live axle; And
One of them liquid entering hole (62) that is used for the liquid entering hole (60,62) of described rotary pump (10,13) and the immediate rotary pump of described second housing (13) forms the cavity between described live axle and the described patchhole.
10, Vehicular brake device according to claim 9, wherein:
The bearing (52) that is used to support described live axle is arranged on described inserting in the hole; And
Described immediate liquid entering hole is made of the part of the inwall of the periphery of described bearing and described patchhole, and this part is radially elongated from described bearing periphery.
11, Vehicular brake device according to claim 9, wherein, described immediate liquid entering hole forms by a groove, at this groove, described patchhole partly be enlarged into rectangular shape and half-oval shaped one of them.
12, Vehicular brake device according to claim 9, wherein, described immediate liquid entering hole comprises the oil circuit that is communicated with the outer surface of described cylinder parts at the immediate end place of described cylinder parts and described second housing.
13, Vehicular brake device according to claim 9, wherein, described cylinder parts form by plastic processing.
14, Vehicular brake device according to claim 9, wherein:
Described a plurality of rotary pump comprises first rotary pump (10) and second rotary pump (13);
Described first housing comprises:
First cylinder (71a), first hole (72a) are formed on this first cylinder, and described live axle inserts this first hole;
First plate (73a), this first plate is close to described first cylinder, is used to hold the rotating part of described first rotary pump;
Second cylinder (71b), contiguous described first plate of this second cylinder, second hole (72b) is formed on described second cylinder, and described live axle inserts this second hole;
Second plate (73b), this second plate is close to described second cylinder, is used to hold the rotating part of described second rotary pump; And
The 3rd cylinder (71c), contiguous described second plate of the 3rd cylinder, the 3rd hole (72c) is formed on described the 3rd cylinder, and described live axle inserts the 3rd hole;
Described first, second constitutes described a plurality of cylinder parts with the 3rd cylinder;
Described the 3rd cylinder is described immediate cylinder;
Described first cylinder, described first plate, described second cylinder, described second plate and described the 3rd cylinder form integrated unit;
Described second housing comprises the 4th cylinder (71d) of contiguous described the 3rd cylinder, and the 4th hole (72d) is formed on described the 4th cylinder, and described live axle inserts this hole.
Applications Claiming Priority (10)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2005318439A JP4682807B2 (en) | 2005-11-01 | 2005-11-01 | Brake device for vehicle using rotary pump |
| JP318439/05 | 2005-11-01 | ||
| JP318438/05 | 2005-11-01 | ||
| JP2005318438A JP4508083B2 (en) | 2005-11-01 | 2005-11-01 | Brake device for vehicle using rotary pump |
| JP2006101951A JP4978041B2 (en) | 2006-04-03 | 2006-04-03 | Pump device and vehicle brake device using the same |
| JP101951/06 | 2006-04-03 | ||
| JP2006101949A JP4725395B2 (en) | 2006-04-03 | 2006-04-03 | Pump device |
| JP101950/06 | 2006-04-03 | ||
| JP2006101950A JP4811092B2 (en) | 2006-04-03 | 2006-04-03 | Pump device |
| JP101949/06 | 2006-04-03 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1959115A true CN1959115A (en) | 2007-05-09 |
| CN1959115B CN1959115B (en) | 2010-09-22 |
Family
ID=38070943
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2006101425610A Expired - Fee Related CN1959115B (en) | 2005-11-01 | 2006-10-30 | Vehicular brake device |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP4508083B2 (en) |
| CN (1) | CN1959115B (en) |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102072147A (en) * | 2009-11-19 | 2011-05-25 | 株式会社爱德克斯 | Rotary pump device and vehicle brake control system |
| CN102079304A (en) * | 2009-11-19 | 2011-06-01 | 株式会社爱德克斯 | Structure for coupling rotary shafts and pump device of rotary type |
| CN102444719A (en) * | 2010-09-30 | 2012-05-09 | 株式会社爱德克斯 | Shaft sealing apparatus, pump apparatus and brake hydraulic pressure control device using same |
| CN102906471A (en) * | 2010-05-20 | 2013-01-30 | 株式会社爱德克斯 | Rotation device provided with seal structure |
| CN103338990A (en) * | 2011-01-31 | 2013-10-02 | 罗伯特·博世有限公司 | Method for circuit separation testing in a double gearwheel pump |
| CN106256623A (en) * | 2015-06-22 | 2016-12-28 | 罗伯特·博世有限公司 | Be particularly useful for motor vehicles can the power brake equipment of slidable adjustment electronically |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102019118697A1 (en) * | 2019-07-10 | 2021-01-14 | Ipgate Ag | Gear pump |
| CN114810577B (en) * | 2022-04-20 | 2023-10-31 | 中国北方车辆研究所 | Oil supplementing device and closed system |
Family Cites Families (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE4102162A1 (en) * | 1991-01-25 | 1992-07-30 | Bosch Gmbh Robert | Quiet running electric fuel pump for motor vehicle - has gear shaped impeller with sloping teeth for controlled axial thrusts |
| JPH06211124A (en) * | 1993-01-19 | 1994-08-02 | Toyota Motor Corp | Brake stroke simulator |
| JPH11343982A (en) * | 1998-05-30 | 1999-12-14 | Suzuki Motor Corp | Trochoid oil pump |
| DE10032848B4 (en) * | 1999-07-09 | 2009-04-09 | Denso Corp., Kariya-shi | Vehicle brake device with rotary pump |
| JP3899785B2 (en) * | 1999-07-09 | 2007-03-28 | 株式会社デンソー | Brake device for vehicle |
| JP4069698B2 (en) * | 2002-07-24 | 2008-04-02 | 株式会社アドヴィックス | Oil seal structure |
| KR100536282B1 (en) * | 2003-11-25 | 2005-12-14 | 주식회사 만도 | Pump of electronic control brake system |
-
2005
- 2005-11-01 JP JP2005318438A patent/JP4508083B2/en not_active Expired - Fee Related
-
2006
- 2006-10-30 CN CN2006101425610A patent/CN1959115B/en not_active Expired - Fee Related
Cited By (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102072147A (en) * | 2009-11-19 | 2011-05-25 | 株式会社爱德克斯 | Rotary pump device and vehicle brake control system |
| CN102079304A (en) * | 2009-11-19 | 2011-06-01 | 株式会社爱德克斯 | Structure for coupling rotary shafts and pump device of rotary type |
| CN102072147B (en) * | 2009-11-19 | 2015-01-07 | 株式会社爱德克斯 | Rotary pump device and vehicle brake control system |
| CN102906471A (en) * | 2010-05-20 | 2013-01-30 | 株式会社爱德克斯 | Rotation device provided with seal structure |
| CN102906471B (en) * | 2010-05-20 | 2015-04-29 | 株式会社爱德克斯 | Rotation device provided with seal structure |
| CN102444719A (en) * | 2010-09-30 | 2012-05-09 | 株式会社爱德克斯 | Shaft sealing apparatus, pump apparatus and brake hydraulic pressure control device using same |
| US9187072B2 (en) | 2010-09-30 | 2015-11-17 | Advics Co., Ltd. | Shaft sealing apparatus, pump apparatus and brake hydraulic pressure control device using same |
| CN102444719B (en) * | 2010-09-30 | 2016-01-20 | 株式会社爱德克斯 | The pump-unit of gland seal device and this gland seal device of use and brake liquid-pressure control device |
| CN103338990A (en) * | 2011-01-31 | 2013-10-02 | 罗伯特·博世有限公司 | Method for circuit separation testing in a double gearwheel pump |
| CN103338990B (en) * | 2011-01-31 | 2016-03-23 | 罗伯特·博世有限公司 | The method detected is separated in loop for duplex geared pump |
| CN106256623A (en) * | 2015-06-22 | 2016-12-28 | 罗伯特·博世有限公司 | Be particularly useful for motor vehicles can the power brake equipment of slidable adjustment electronically |
Also Published As
| Publication number | Publication date |
|---|---|
| CN1959115B (en) | 2010-09-22 |
| JP4508083B2 (en) | 2010-07-21 |
| JP2007125929A (en) | 2007-05-24 |
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