JP3447459B2 - Brake fluid pressure control device - Google Patents

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a pair of reciprocating plunger pumps, which operate to control the brake fluid pressure of a wheel brake, built in a metal base body with their operating axes coaxial with each other. A motor housing of a motor common to the pumps is fastened to the base body with a rotation shaft rotatably supported at both ends of the motor housing orthogonal to the operation axes of the plunger pumps, and protrudes from the motor housing. The present invention relates to a brake fluid pressure control device in which a cam for applying a driving force to both plunger pumps is provided at an end of a rotary shaft.

[0002]

2. Description of the Related Art Conventionally, such a brake fluid pressure control device is
For example, it is already known from JP-A-7-291111.

[0003]

By the way, in the structure in which the rotating shaft of the motor is arranged orthogonally to the operating axis of the pair of reciprocating plunger pumps, the rotating shaft of the motor is not rotated during the operation. The force may cause vibration in the operating axis direction of the plunger pump. On the other hand, as disclosed in Japanese Utility Model Laid-Open No. 6-60268, a motor housing of a motor is generally formed by connecting a metal bracket to an open end of a metal housing body having a bottomed cylindrical shape. When such a motor is applied to the brake fluid pressure control device, the metal bracket is fastened to the metal base. However, when the rotary shaft vibrates in the direction of the operation axis of the plunger pump as described above, the bracket supporting the rotary shaft vibrates, and in addition to the noise accompanying the vibration of the bracket itself, Noise was generated due to metal contact when the bracket came into contact with the base body.

The present invention has been made in view of the above circumstances, and the brake hydraulic pressure is adapted to suppress the generation of noise accompanying the abutment of the bracket and the base body as much as possible even if the rotation shaft vibrates. An object is to provide a control device.

[0005]

In order to achieve the above object, the invention according to claim 1 provides a pair of reciprocating plunger pumps which operate to control the brake fluid pressure of a wheel brake. The motor housing of the motor, which is built into a metal base body with the axis coaxial, is common to both plunger pumps, and the rotation shaft rotatably supported at both ends of the motor housing is orthogonal to the operating axes of both plunger pumps. In the brake fluid pressure control device in which a cam for applying a driving force to both plunger pumps is provided at the end of the rotary shaft that is fastened to the base body and protrudes from the motor housing, one end of the motor housing is closed. A cylindrical housing main body and an opening end on the other end side of the housing main body that is fitted to penetrate the rotary shaft and
A bracket made of synthetic resin that supports the bearing for the rotating shaft
At the open end on the other end side of the housing main body.
Bulges outward at multiple locations spaced apart in the circumferential direction.
The flange and the bracket with the housing.
Integral flanges that overlap each other
And the bracket is in contact with the base body ,
The flanges superposed on each other are connected to
With a screw member inserted in the collar that penetrates the lunge
It is characterized in that it is fastened together with the base body .

The invention according to claim 2 is the above-mentioned claim 1.
In addition to the structure of the invention according to said bracket, a support tubular portion by interposing fitted to the base of the bearing between the <br/> rotary shaft and characterized in that it is provided integrally you.

[0007]

BEST MODE FOR CARRYING OUT THE INVENTION Hereinafter, an embodiment of the present invention will be described based on an embodiment of the present invention shown in the accompanying drawings.

1 to 6 show a first embodiment of the present invention. FIG. 1 is a hydraulic circuit diagram of a vehicle brake device, FIG. 2 is a side view of a brake hydraulic pressure control device, and FIG. Figure 2
3 is a sectional view taken along line 3-3, FIG. 4 is a front view taken along the arrow 4 of FIG. 2, FIG. 5 is a sectional view taken along line 5-5 of FIG. 2, and FIG. 6 is a sectional view taken along line 6-6 of FIG.

First, in FIG. 1, the tandem type master cylinder M is provided with a pair of output ports 13 ₁ and 13 ₂ for outputting a braking fluid pressure according to the depression of the brake pedal P, and a wheel brake B _FL for the left front wheel. , A proportional pressure reducing valve 14 _R connected to the right rear wheel wheel brake B _RR , a right front wheel wheel brake B _FR , and a proportional pressure reducing valve 14 _L connected to the left rear wheel wheel brake B _RL , and both outputs Ports 13 ₁ and 1
A brake fluid pressure control device 15 is provided between the fluid pressure passages 12 ₁ and 12 ₂ individually connected to 3 ₂ .

The brake fluid pressure control device 15 includes a wheel brake B _FL for the front left wheel, a wheel brake B _RR for the rear right wheel, a wheel brake B _FR for the front right wheel, and a wheel brake B _RL for the rear left wheel.
Normally open solenoid valves V _OFL , V _ORR ,
V _OFR , V _ORL and four check valves 17 _FL , 17 connected in parallel to each of the _normally open solenoid valves V _{OFL to} V _ORL
RR , 17 _FR , 17 _RL and the wheel brakes B _{FL to} B _RL
4 normally closed solenoid valves V _CFL , V _CRR ,
V _CFR , V _CRL , a pair of wheel brakes B _FL for the front left wheel and a wheel brake B _RR for the rear right wheel, and a pair of wheel brakes B _FR for the front right wheel and a wheel brake B _RL for the rear left wheel, respectively. Reservoirs 19 ₁ and 19 ₂ and a pair of reciprocating plunger pumps 21 ₁ and 21 connected to both reservoirs 19 ₁ and 19 ₂ via suction valves 20 ₁ and 20 _2.
2, a double plunger pump _21, 212 in a common single motor 22, the discharge valve 23 _1, a pair of dampers 24 ₁ connected 23 ₂ via the both plunger pumps 21 _1, 21 _2, 24 ₂ and hydraulic passages 12 ₁ and 12 ₂ individually connected to the output ports 13 ₁ and 13 ₂ of the master cylinder M, and orifices 25 ₁ and 25 _{2 provided} between the dampers 24 ₁ and 24 ₂ respectively. The normally open solenoid valves V _{OFL to} V _ORL and the normally closed solenoid valves V _{CFL to} V _CRL are demagnetized / excited by an electronic control unit 26.

The _normally open solenoid valve V _OFL is a master cylinder M
The normally open solenoid valve V _ORR is provided between the hydraulic pressure passage 12 ₁ connected to one of the output ports 13 ₁ and the left front wheel brake B _FL, and the normally open solenoid valve V _ORR is for the hydraulic pressure passage 12 ₁ and the right rear wheel. Wheel brake B
_The normally open solenoid valve V _{OFR, which} is interposed between the proportional pressure reducing valve 14 _R connected to the _RR , is a hydraulic passage 12 ₂ connected to the other output port 13 ₂ of the master cylinder M and the wheel brake for the right front wheel. is provided between the B _FR, normally open electromagnetic valve V _ORL is interposed between the hydraulic pressure passage 12 ₂ and the left rear wheel brake B _RL connected to the proportional pressure reducing valve 14 _L It The check valves 17 _{FL to} 17 _RL are connected in parallel to the _normally open solenoid valves V _{OFL to} V _ORL so as to allow only the flow of the brake fluid from the corresponding wheel brakes B _{FL to} B _RL .

The normally closed solenoid valve V _CFL is provided between the wheel brake B _FL for the left front wheel and the reservoir 19 ₁ and is a normally closed solenoid valve V _CRR.
Is between the proportional pressure reducing valve 14 _R and the reservoir 19 ₁ , the normally closed solenoid valve V _CFR is between the front wheel brake B _FR and the reservoir 19 ₂ , and the normally closed solenoid valve V _CRL is the proportional pressure reducing valve 1
4 _L and the reservoir 19 ₂ , respectively.

According to the brake fluid pressure control device 15 as described above, the normally open solenoid valves V _{OFL to} V _ORL are opened in the demagnetized state during the normal braking in which the wheels are not likely to be locked. In addition, each normally closed solenoid valve V _CFL ~ V
_CRL is demagnetized and closed. Therefore, the braking fluid pressure output from _one output port 13 ₁ of the master cylinder M acts on the wheel brake B _FL for the front left wheel via the _normally open solenoid valve V _OFL , and at the same time as the _normally open solenoid valve V _ORR and proportional. Wheel brake B for the right rear wheel via the pressure reducing valve 14 _R
The braking fluid pressure acting on _RR and output from the other output port 13 ₂ of the master cylinder M is the _normally open solenoid valve V _OFR.
It acts on the front wheel brake B _FR for the right front wheel through the _normally open solenoid valve V _ORL and the proportional pressure reducing valve 14 _L , and acts on the rear wheel brake B _RL for the left rear wheel.

At the time of anti-lock control when the wheels are about to enter the locked state during braking, the normally open type solenoid valves corresponding to the wheels of the _normally open type solenoid valves V _{OFL to} V _ORL that are about to enter the locked state. Is excited to close the valve, and at the same time, of the normally closed solenoid valves V _{CFL to} V _CRL , the normally closed solenoid valves corresponding to the wheels are excited and opened. Then, a part of the braking fluid pressure is released to the reservoir 19 ₁ or 19 ₂ to reduce the pressure. When the brake fluid pressure is maintained, the normally open solenoid valves V _{OFL to} V _ORL are excited to close the valve, and the normally closed solenoid valves V _{CFL to} V _CRL are demagnetized to maintain the closed state. Often, when increasing the braking fluid pressure, deenergize the normally open solenoid valves V _{OFL to} V _ORL and open them, and demagnetize the normally closed solenoid valves V _{CFL to} V _CRL to keep them closed. Good.

The motor 22 that drives the pair of plunger pumps 21 ₁ and 21 ₂ in common is operated during the antilock control, and the reservoirs 19 ₁ and 19
_The brake fluid released to ₂ is the plunger pump 21 ₁ ,
21 ₂ to dampers 24 ₁ and 24 ₂ and orifice 25
₁ , 25 ₂ and upstream of each of the normally open solenoid valves V _{OFL to} V _ORL , that is, the hydraulic pressure passage 121 connected to the master cylinder M ₁ ,
It is returned to the 12 ₂ side. Therefore, the reservoirs 19 ₁ , 19
_The depression amount of the brake pedal P in the master cylinder M does not increase by the amount released to _2, and the pulsation of the brake fluid sent from the plunger pumps 21 ₁ and 21 ₂ is the dampers 24 ₁ and 24 ₂ and the orifice 2.
It is damped by the action of 5 ₁ , 25 ₂ , and the pulsation of the brake pedal P is damped.

Whether the wheels are likely to enter the locked state in the electronic control unit 26 which controls the demagnetization / excitation of the normally open solenoid valves V _{OFL to} V _ORL and the normally closed solenoid valves V _{CFL to} V _CRL . Wheel speed sensors 27 _FL , 27 _RR , 27 _FR , which individually detect the wheel speed of each wheel in order to judge whether
27 The _RL detection signal is input, and the detection signal of the handbrake detection sensor 29 that detects whether or not the handbrake lever 28 is operated is also input, and when the electronic control unit 26 is in the antilock control state.
An alarm 30 such as a lamp activated by is connected to the electronic control unit 26.

In FIGS. 2 and 3, four _normally open solenoid valves V _OFL , V constituting the brake fluid pressure control device 15 are shown.
_ORR , V _OFR , V _ORL and 4 check valves 17 _FL , 1
7 _RR , 17 _FR , 17 _RL , and 4 normally closed solenoid valves V _CFL ,
V _CRR , V _CFR , and V _CRL, and a pair of reservoirs 19 ₁ , 1
9 ₂ , a pair of intake valves 20 ₁ , 20 ₂ , a pair of plunger pumps 21 ₁ , 21 ₂ , a motor 22, a pair of discharge valves 23 ₁ , 23 _2, and a pair of dampers 24 ₁ , 24.
₂ and the pair of orifices 25 ₁ and 25 ₂ are arranged in a block-shaped metal base 34.

Four _normally open solenoid valves V _OFL , V _ORR , V
_OFR and V _ORL have half of them on one surface of the base 34 (see FIG. 2).
And the base body 3 so as to project from the left end surface of FIG.
4 normally closed solenoid valves V _CFL , V _CRR , V
_{The CFR} and V _CRL are fitted to the base body 34 with their half portions protruding from the one surface, and both reservoirs 19 ₁ ,
19 ₂ and both dampers 24 ₁ and 24 ₂ are housed and arranged in the base 34 from the one surface side. Moreover, the normally open solenoid valves V _OFL , V _ORR , V _OFR , V
_ORL , normally closed solenoid valve V _CFL , V _CRR , V _CFR , V _CRL ,
Both reservoirs 19 ₁ and 19 ₂ and both dampers 24 ₁ and 24
_A cover 35 made of synthetic resin is fastened so as to cover ₂ and the like, and the base 34 is supported by support plates 36a and 36b fixed to a vehicle body (not shown) via mount means 37.

A pair of plunger pumps 21 ₁ and 21
₂ is each normally open solenoid valve V _OFL , V _ORR , V _OFR , V _ORL
Position of each normally closed solenoid valve V _CFL , V _CRR ,
It is built in the base 34 with the operating axis coaxial with the arrangement position of V _CFR and V _CRL .

One of the plunger pumps 21 ₁ has a base 3
4, a pump housing 38 fitted and fixed to the pump housing 4, and a plunger 40 slidably fitted to the pump housing 38 and forming a pump chamber 39 between the pump housing 38 and the plunger 40. Moreover, the plunger 40 is provided with a suction chamber 41 which is constantly in communication with the reservoir 19 ₁ (see FIG. 1), and the suction valve 20 which opens when the volume of the pump chamber 39 increases and communicates the suction chamber 41 with the pump chamber 39. ₁ is disposed in the pump chamber 39. Further, in the pump housing 38, a discharge chamber 42 that is in constant communication with the damper 24 ₁ (see FIG. 1) is provided.
Is provided, and the discharge valve 23 ₁ that opens when the volume of the pump chamber 39 is reduced to communicate the pump chamber 39 with the discharge chamber 42 ₁
Are arranged in the discharge chamber 42.

The other plunger pump 21 _2, a built-in suction valve 20 ₂ and the discharge valve 23 ₂ (see FIG. 1), the plunger pumps 21 ₁ has the same configuration as the both plunger pumps 21 _1, 21 ₂ shows the projecting ends of the plungers 40 ... From the pump housing 38 ...
The base body 34 is disposed on the base body 34 so as to be opened to the other surface (the right end surface in FIGS. 2 and 3) of the base body 34 so as to face the storage recess 43 provided in the base body 34.

The motor 22 is composed of the two plunger pumps 2
A rotary shaft 44 having an axis orthogonal to the operation axes of 1 ₁ and 21 ₂ and projected into the storage recess 43 is fastened to the other surface side of the base 34, and the tip of the rotary shaft 44 is provided. A bearing 45 as a cam is mounted on an eccentric shaft portion 44a provided in the portion, and the end portions of the plungers 40 of both plunger pumps 21 ₁ and 21 ₂ are brought into contact with the outer surface of the outer ring of the bearing 45. Since the eccentric shaft portion 44a has an axis decentered from the rotation axis of the rotation shaft 44, the rotation shaft 44a
From the rotation axis distance to the outer ring outer surface of the bearing 45 is different from the circumferential direction, the bearing 45 with the rotation of the rotary shaft 44 plays a cam action, both plunger pumps 21 _1, 21 ₂ plungers 40 ... in Reciprocating power is applied alternately.

Referring also to FIGS. 4 and 5, the motor housing 46 of the motor 22 has a bracket made of synthetic resin on the other end of a bottomed cylindrical metal housing body 47 whose one end is closed. 48 is connected. At the other end of the housing main body 47, that is, at the opening end, flanges 47a, 47b, 47c projecting outward at a plurality of, for example, three places spaced apart in the circumferential direction are imaginary lines connecting the tips of the flanges 47a to 47c. Are integrally formed so as to form an isosceles triangle. On the other hand, the bracket 48 includes the flanges 47a to 47a of the housing main body 47.
A flange 48a, 48b, 48c that overlaps with 47c is integrally formed and fitted into the open end of the housing main body 47, and an annular seal member 49 is interposed between the housing main body 47 and the bracket 48.

Flanges 47a-47c, which overlap each other,
48a to 48c are fastened together with the base member 34 by screw members 51, and the other surfaces of the base member 34 receive the flanges 47a to 47c and 48a to 48c and screw the screw members 51 ... Boss parts 52 ₁ , 52 ₂ ,
52 ₃ is projected.

Each flange 48a to 48 of the bracket 48
In c, a collar 50 into which each screw member 51 is inserted,
There are press-fitted, said collar 50 ..., the abutting flange portion 50a in the boss portion 52 _{1-52 3} with engaging a portion opposite to the boss portion 52 _{1-52 3} each Fufuranji 48a through 48c ... Is provided. Also, the motor housing 46
In order to temporarily fix the bracket 48 to the housing main body 47 before mounting the bracket to the base body 34, the flange portions 48a to 48c of the bracket 48 have projections 48e, 48 penetrating the respective flanges 47a to 47c of the housing main body 47.
f and 48g are integrally provided so as to project, and each projection 48e ...
A chrysanthemum washer 6 that engages the outer surface of each of the flanges 47a to 47c at the protruding portion from each of the flanges 47a to 47c of 48g.
7 ... is attached.

By the way, the rotary shaft 44 of the motor 22
One end of the bearing is rotatably supported via a bearing 53 in a cylindrical bearing portion 47d provided at a closed end of the housing main body 47. On the other hand, the bracket 48 has a through hole 54 through which the rotary shaft 44 is rotatably pierced, and a cylindrical support cylindrical portion 48 that is coaxial with the through hole 54 and projects toward the base body 34.
d and the rotary shaft 44 and the support cylindrical portion 48.
A bearing 55 is interposed between d.

Further, a commutator 56 is provided on the rotary shaft 44 near the bracket 48 in the motor housing 46, and a plurality of brushes 5 slidably contacting the commutator 56.
7 are held by the bracket 48. That is, a plurality of guide grooves 58 extending along the radial direction of the commutator 56 are provided at a plurality of positions on the inner surface side of the bracket 48 in the circumferential direction of the commutator 56, and the brushes 57 ... A spring 58, which is slidably fitted and contracted with the bracket 48, is urged in a direction of sliding contact with the commutator 56. Moreover, holding plates 60 for holding the brushes 57 in the guide grooves 58 are fastened to the inner surface of the bracket 48.

Referring also to FIG. 6, on the surface of the base 34 on the motor 22 side, a cylindrical receiving portion 61 coaxial with the storage recess 43 is provided.
The support cylindrical portion 48 d protruding from the bracket 48 is fitted into the cylindrical receiving portion 61 with the bearing 55 interposed between the cylindrical receiving portion 61 and the rotary shaft 44. . In addition, an annular seal member 62 is attached to the inner edge of the tip end of the cylindrical receiving portion 61 so as to contact the outer edge of the base end portion of the support tubular portion 48d over the entire circumference.

Further, the bracket 48 is integrally provided with a pair of vibration suppressing arms 63 ₁ and 63 ₂ extending outwardly along the operation axes of the plunger pumps 21 ₁ and 21 ₂ .
Abutment support portions 64 ₁ and 64 ₂ for abutting and supporting both vibration suppressing arms 63 ₁ and 63 ₂ are provided on the base body 34 on both sides of the rotary shaft 44 along the operating axes of the plunger pumps 21 ₁ and 21 _2. Then, the rotary shaft 44 is integrally formed in a circular arc shape centering on the rotary shaft line. Moreover the contact supporting portion 64 _1, 64 ₂ of the protrusion amount, the bracket 48 are a plurality of respective boss portions 52 ₁ to 52
It is desirable that the vibration suppression arms 63 ₁ and 63 ₂ be set so as to be preloaded when they are tightened to ₃ .

_{One of} the vibration suppressing arms 63 ₁ and 63 ₂ 63 ₁
A connection terminal 65 that communicates with the pump housing 46 via a conductor (not shown) embedded in the bracket 48,
A connector 66 that faces 65 is integrally provided.

Next, the operation of the first embodiment will be described. The motor housing 46 of the motor 22 common to both plunger pumps 21 ₁ and 21 ₂ built in the metal base 34 has a housing whose one end is closed. A bracket 48 made of synthetic resin is joined to the other end of 47, and the bracket 48 is fastened to the base body 34. Therefore, the axis of the rotary shaft 44 is made orthogonal to the operation axes of the plunger pumps 21 ₁ and 21 _2. The vibration of the bracket 48 itself due to the vibration of the rotary shaft 44 of the motor 22 due to the motor housing 46 being fastened to the base 34 can be suppressed, and the vibration noise of the bracket 48 itself can be reduced. And
Moreover, since the bracket 48 made of synthetic resin comes into contact with the base body 34 made of metal even if the entire motor housing 46 is vibrated, the noise generated by the contact of the bracket 48 with the base body 34 is conventionally generated. It can be significantly reduced as compared with the case of metal contact.

Moreover, as disclosed in Japanese Utility Model Laid-Open No. 6-60268, in a conventional motor in which a metal bracket is coupled to an open end of a metal housing body having a bottomed cylindrical shape, the brush 57 ... While a seal member is required between the brush holder and the housing main body, and between the brush holder and the bracket, which are made of synthetic resin for holding the bracket, the bracket 48 is made of synthetic resin. It suffices that the seal member 49 is interposed only between the housing 48 and the housing main body 47, which can contribute to the reduction of the number of parts.

The rotary shaft 44 of the motor 22 is supported by the bearing portion 47d of the housing main body 47 via the bearing 53, and the bearing 5 is attached to the support cylinder portion 48d of the bracket 48.
5, the two plungers 21 ₁ , of the parts of the rotary shaft 44 corresponding to the two bearings 53, 55 are supported.
The reaction force from 21 ₂ is larger than that of the bearing 55.
Is a part corresponding to. However, the support cylindrical portion 48d that supports the bearing 55 is formed of synthetic resin integrally with the bracket 48, and is fitted into the cylindrical receiving portion 61 of the base body 34, so that it is a portion corresponding to the bearing 55. It is possible to suppress the vibration of the rotating shaft 44 of
By supporting the support cylinder portion 48 by the cylinder receiving portion 61 of the metal base 34, the rigidity of the support cylinder portion 48 made of synthetic resin can be improved.

Furthermore, both plunger pumps 21 ₁ and 21 ₂
The brackets 48 of the motor housing 46 are supported on both sides of the output shaft 44 along the operation axis of the motor housing 46, so that the support strength of the motor housing 46 in the direction along the operation axis of the plunger pumps 21 ₁ and 21 ₂ is increased. Is possible. In addition, the bracket 48 is integrally provided with a pair of vibration suppressing arms 63 ₁ and 63 ₂ extending outwardly along the operation axes of the plunger pumps 21 ₁ and 21 ₂ .
Both vibration suppressing arms 63 ₁ and 63 ₂ contact the supporting portions 64 ₁ and 64.
Since the bracket 48 abuts and is supported by the _second shaft ₂ , the bracket 48 comes into contact with the supporting portions 64 ₁ , 6 at a position relatively distant from the axis of the rotating shaft 44.
4 is intended to be supported by _two, both plunger pump 21
It is possible to further enhance the support strength of the motor housing 46 in the direction along the operation axis direction of ₁ , 21 ₂ . Therefore, it is possible to effectively suppress the vibration of the motor 22 along the operation axis direction of the two plunger pumps 21 ₁ and 21 ₂ , and it is possible to prevent the generation of the operation noise accompanying the vibration and It is possible to more effectively suppress the generation of noise associated with the operation of the plunger pump 21 ₁ ,
It is possible to stabilize the stroke of the plunger 40 in 21 ₂ and maintain high pump efficiency.

Moreover, in order to suppress the above-mentioned vibration, the base 34
The surface of the motor 22 on the side of the motor 22 does not need to be a flat surface, and a plurality of boss portions 52 _{1 to} 52 for fastening the bracket 48 are fastened.
₃ and the contact support portions 64 ₁ and 64 ₂ that come into contact with both the vibration suppressing arms 63 ₁ and 63 ₂ may be provided on the base body 34 so that the surface of the base body 34 on the motor 22 side has an uneven shape. It is possible to reduce the thickness of unnecessary parts, which contributes to the reduction in size and weight.

7 to 9 show a second embodiment of the present invention. FIG. 7 is a front view corresponding to FIG. 4, FIG. 8 is an enlarged sectional view taken along line 8-8 of FIG. 7, and FIG. FIG. 9 is an enlarged sectional view taken along line 9-9 of FIG. 7.

Motor housing 46 'of motor 22'
Is attached to the other end of a bottomed cylindrical metal housing main body 47 'with one end closed and a bracket 4 made of synthetic resin.
8'is connected to the housing main body 47
The flanges 47a ', 47b', 47c 'projecting outward at a plurality of, for example, three, spaced apart in the circumferential direction.
Are provided integrally. On the other hand, the bracket 48 'is integrally fitted with the flanges 47a' to 48c 'of the housing main body 47' and is fitted to the other end of the housing main body 47 '. Moreover, the flanges 47a 'to 47c' of the housing main body 47 are
And each flange 48a 'to 48c' of the bracket 48 '
And are connected to each other by rivets 68 .... Further, the flanges 47a 'to 47c' correspond to the corresponding flanges 48a '.
Cylindrical collars 50 'to be fitted respectively to ~ 48c'
, Which are integrally projected, and have mutually overlapping flanges 4
7a 'to 47c' and 48a 'to 48c' are each color 5
The screw members 51, which are inserted through 0 ', are fastened together with the base body 34.

According to the second embodiment, the same effect as that of the first embodiment can be obtained.

Although the embodiments of the present invention have been described in detail above, the present invention is not limited to the above embodiments, and various design changes can be made without departing from the present invention described in the claims. It is possible to do.

[0040]

As described above, according to the first aspect of the invention, the motor housing has a cylindrical housing main body with one end closed and an open end on the other end side of the housing main body.
Is fitted to penetrate the rotary shaft of the motor and
It consists a synthetic resin bracket for supporting the bearings
At the open end on the other end side of the housing,
There are flanges that project outwards at multiple locations spaced apart.
Also, the bracket has a heavy weight on each flange mainly of the housing.
Mating flanges are provided integrally with each other, and in the state where the bracket is in contact with the base body, the flanges overlap each other.
Is attached to the collar that passes through each flange of the bracket.
Co-tighten the base body with the threaded member through the threaded member
Since the order to suppress the vibration of the bracket itself due to the rotation shaft motor housing are perpendicular to the axis of the rotating shaft to the actuation axis of the plunger pumps due to being fastened in the base body vibrates, The vibration noise of the bracket itself can be reduced, and even if the motor housing vibrates, the bracket made of synthetic resin comes into contact with the base body made of metal, and is caused by the contact of the bracket with the base body. Noise can be reduced significantly compared to conventional metal contact.

[0041] According to the second aspect of the invention, the said blanking <br/> racket, since the supporting cylinder unit which is fitted to the substrate by interposing a bearing between the rotating shaft is provided integrally , It is possible to suppress the vibration of the rotating shaft at the part where a relatively large reaction force acts from the plunger pump by the support cylinder part, and support the support cylinder part made of synthetic resin by the metal base. Ru can improve the rigidity of the support cylinder portion by.

[Brief description of drawings]

FIG. 1 is a hydraulic circuit diagram of a vehicle brake device in a first embodiment.

FIG. 2 is a side view of a brake fluid pressure control device.

FIG. 3 is a sectional view taken along line 3-3 of FIG.

FIG. 4 is a front view taken along the arrow 4 of FIG.

5 is a sectional view taken along line 5-5 of FIG.

6 is a sectional view taken along line 6-6 of FIG.

FIG. 7 is a front view corresponding to FIG. 4 of the second embodiment.

8 is an enlarged sectional view taken along line 8-8 of FIG.

9 is an enlarged sectional view taken along line 9-9 of FIG.

[Explanation of symbols]

15 ... Brake fluid pressure control device 21 ₁ , 21 ₂ ... Plunger pump 22, 22 '... Motor 34 ... Base body 44 ... Rotating shaft 45 ... Bearing 46, 46' as cam ... motor housing 47, 47 '... housing main 48, 48' ... bracket 48d ... supporting cylinder unit 55 ... bearing 64 _1, 64 ₂ ... contact supporting portion B _FL, B _RR ; B _FR , B _RL ... Wheel brake M ... Master cylinder

─────────────────────────────────────────────────── ─── Continuation of the front page (56) References JP-A-6-255474 (JP, A) JP-A-8-282459 (JP, A) Actual development Sho-63-17547 (JP, U) (58) Field (Int.Cl. ⁷ , DB name) B60T 8/34

Claims (2)

(57) [Claims] 1. Wheel brakes (B _FL , B _RR ; B _FR ,
A pair of reciprocating plunger pumps (21 ₁ , 21 ₂ ) that operate to control the brake fluid pressure of B _RL ) are built in a metal base body (34) with their operating axes being coaxial, The motor housing (46, 4) of the motor (22, 22 ') common to the pumps (21 ₁ , 21 ₂ ).
6 ') makes the rotary shaft (44) rotatably supported at both ends of the motor housing (46, 46') orthogonal to the operating axes of the plunger pumps (21 ₁ , 21 ₂ ). The motor housing (4
6, 46 '), a cam (45) for applying a driving force to both plunger pumps (21 ₁ , 21 ₂ ) is provided at an end of the rotary shaft (44), The motor housing (46, 46 ') includes a cylindrical housing main body (47, 47') with one end closed , and
Fit into the open end on the other end of the housing body (47, 47 ')
The rotary shaft (44) and the rotary shaft (44)
An opening end on the other end side of the housing main body (47, 47 ') , which comprises a synthetic resin bracket (48, 48' ) for supporting a bearing (55) for the (44)
Is stretched outwards at multiple locations spaced in the circumferential direction.
Outlet flange (47a, 47b, 47c; 47a ', 4
7b ', 47c') and also the brackets (48, 4)
8 ') includes each of the housing main bodies (47, 47').
Flange (47a, 47b, 47c; 47a ', 47
b ', 47c') overlapping flanges (48a, 48c)
b, 48c; 48a ', 48b', 48c ') respectively
And the flanges (47a, 4 ') which are integrally formed with each other and are superposed on each other in a state where the brackets (48, 48') are in contact with the base body (34).
7b, 47c, 48a, 48b, 48c; 47a ', 4
7b ', 47c', 48a ', 48b', 48c ')
Are the flanges (4) of the brackets (48, 48 ').
8a, 48b, 48c; 48a ', 48b', 48
Inserted in the collar (50, 50 ') that penetrates c')
A brake fluid pressure control device, characterized in that it is fastened together with the base body (34) with a screw member (51) . To wherein said bracket (48, 48 ') are
The rotating shaft the bearing supporting tube portion (55) to be interposed fitted to said base body (34) between (44) (48d)
There characterized in that it is formed integrally, the brake fluid pressure GoSo location according to claim 1.