JPH08200235A - Oil hydraulic pump - Google Patents

Abstract

PURPOSE: To provide an oil hydraulic pump which can realize improving workability by eliminating additional work such as mounting a sound insulating material while decreasing operating noise can be attained by preventing generation of a metal sound. CONSTITUTION: An oil hydraulic pump 1 has valves 15, 16 of providing rubber molded parts 32b, 44b having flexibility in at least one of valve bodies 32, 44 and valve seats 24, 37.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a hydraulic pump used for supplying hydraulically controlled brake oil in an antilock brake system for a vehicle.

[0002]

2. Description of the Related Art As a hydraulic pump for supplying brake oil whose hydraulic pressure is controlled in an antilock brake system for a vehicle, one disclosed in Japanese Patent Laid-Open No. 4-350371 is known. In the hydraulic pump described in the above publication, when the shaft of the motor rotates, a cam-shaped bearing inner ring rotates with an eccentric center of rotation with respect to the shaft, and a bearing provided outside the bearing inner ring via a rolling element. Since the outer ring reciprocates while pressing the piston, the valve is actuated by the reciprocating motion of the piston to supply the brake oil to the master cylinder. As shown in FIG. 7, the valve includes a first valve 51 arranged on the intake side of the brake oil and a second valve 52 arranged on the discharge side of the brake oil, and a second valve on the discharge side. The valve 52 is the flow path 5 formed in the metal valve seat 53.
4 is a check valve that closes the flow path 54 by pressing a ball-shaped metal valve body 56 against the elastic force of the valve spring 55.

[0003]

In the conventional hydraulic pump described above, the second valve 52 has a structure in which the metal valve body 56 is brought into pressure contact with the flow path 54 of the metal valve seat 53. , The valve body 53 when the valve body 56 collides with the valve seat 53
There is a possibility that the seating sound of will become metallic noise, and in order to block the generation of metallic noise, sound insulating material etc. must be installed around the hydraulic pump, so in manufacturing,
It was accompanied by additional work for mounting sound insulation materials, etc., resulting in poor workability, making it difficult to improve productivity.

[0004]

SUMMARY OF THE INVENTION The hydraulic pump according to the present invention can reduce the operating noise by preventing the generation of metallic noise, and can improve the workability by eliminating the additional work such as mounting the sound insulating material. The purpose is to provide a hydraulic pump that can.

[0005]

Configuration of the Invention

[0006]

A hydraulic pump according to claim 1 of the present invention comprises a yoke, a magnet fixed to the inside of the yoke, an armature arranged on the inner peripheral side of the magnet, and rotating by energization. A pump case coupled to the yoke, a bearing inner ring disposed in the pump case, having an eccentric center of rotation with respect to the shaft of the armature and rotating integrally with the shaft, and a bearing inner ring via a rolling element. A piston that is housed in a bearing that has a bearing outer ring that is arranged on the outside of the cylinder and a cylinder that is arranged in the pump case, and that is reciprocated between top dead center and bottom dead center in a state of pressure contact with the bearing outer ring. The piston reciprocates between the top dead center and the bottom dead center, so that the flow path formed in the valve seat is resisted against the valve spring. A valve that is openable and closable, and has a valve that draws in the fluid by opening and closing the flow path and then delivers the fluid. The valve is a flexible rubber on at least one of the valve body and the valve seat. The hydraulic pump according to claim 2 of the present invention is characterized in that the valve body of the valve is integrally molded by the rubber molding portion. According to another aspect of the hydraulic pump of the present invention, the valve is provided with a tapered valve seat abutment surface on the side of abutment with the valve seat, the valve body having a truncated cone shape, and the taper of the valve body. The hydraulic pump according to claim 4 of the present invention is provided with a valve seat that forms a tapered valve element contact surface that is arranged so as to be capable of pressure contact with the valve seat contact surface. Is a symmetrical arrangement of a pair of truncated cones Comprising a valve body provided in, and the fact that forms a valve spring engaging portion in opposite valve spring side tapered valve seat abutment surface, a hydraulic pump according to claim 5 of the present invention,
The valve is cylindrical and has a flat valve seat abutment surface on the side of contact with the valve seat, and a valve spring locking part on the valve spring side opposite to the flat valve seat abutment surface. Is provided with a valve seat having a flat valve body contacting surface which is arranged so as to be capable of pressure contact with the flat valve seat contacting surface of the valve body. However, the valve body accommodating portion arranged to accommodate the valve body is provided with a base that faces the valve seat.

[0007]

In the hydraulic pump according to the first aspect of the present invention, in the valve, the valve body having the rubber molding portion collides with the valve seat, or the valve body collides with the valve seat having the rubber molding portion. Therefore, it is unlikely that metallic noise is generated when the valve body and the valve seat collide with each other, and therefore it is not necessary to install a sound insulating material. In the hydraulic pump according to claim 2 of the present invention, in the valve, since the valve body having the rubber molding portion as a whole collides with the valve seat, a metallic seating sound is generated when the valve body collides with the valve seat. Therefore, it is not necessary to install a sound insulating material. In the hydraulic pump according to claim 3 of the present invention, in the valve, the tapered valve seat contact surface of the valve body having the truncated cone-shaped rubber molding portion collides with the tapered valve body contact surface of the valve seat. Therefore, it is unlikely that a metallic seating sound is generated when the valve body collides with the valve seat.
There is no need to install sound insulation material. According to a fourth aspect of the present invention, in the valve, the valve spring is locked to a valve spring locking portion of a valve body having a frustoconical rubber molded portion as a whole, and a tapered valve seat of the valve body. Since the contact surface collides with the tapered valve element contact surface of the valve seat, it is unlikely that a metallic seating noise will be generated when the valve element collides with the valve seat, so it is necessary to install a sound insulating material etc. Also disappears. In the hydraulic pump according to claim 5 of the present invention,
In the valve, the valve spring is locked to the valve spring locking part of the valve body that has the entire cylindrical rubber molded part, and the flat valve seat contact surface of the valve body contacts the flat valve seat of the valve seat. Since the valve body collides with the surface, it is unlikely that a metallic seating noise is generated when the valve body collides with the valve seat. Therefore, it is not necessary to attach a sound insulating material or the like.

[0008]

1 to 4 show a first embodiment of a hydraulic pump according to the present invention.

The illustrated hydraulic pump 1 is built in an actuator of an anti-lock brake system, and mainly includes a yoke 2, magnets 3, 4, an armature 5, a pump case 6, a first bearing (bearing) 7, and a first valve. (Valve) 15 and a second valve (valve) 16.

The yoke 2 is attached by crimping a disk-shaped end 2b to one end of a cylindrical tubular portion 2a, and a screw (not shown) is screwed into the pump case 6 at the other end of the tubular portion 2a. It is assembled by letting it. A second bearing 18 is attached to the center of the end 2b, and the second bearing 18 rotatably supports one end of a shaft 5a included in an armature 5 described later.

Magnets 3 and 4 are arranged inside the cylindrical portion 2a of the yoke 2, and both magnets 3 and 4 form a magnetic field inside.

An armature 5 is arranged on the inner peripheral side of the magnets 3, 4. Armature 5 is shaft 5
A magnetic armature core 5b and a commutator 5c are mounted on a, and the shaft 5a is rotatably supported by the second bearing 18 at one end side thereof and the pump case 6 at the other end side thereof. The third bearing 19 is extended to the inside and is rotatably supported by a third bearing 19 attached to the pump case 6.

A coil 5d having a predetermined number of slots is wound around the armature core 5b of the armature 5, and the winding of the coil 5d is electrically connected to a plurality of commutator pieces 5c1 provided in the commutator 5c. It is connected.

Brushes 20 and 21 are pressed against respective commutator pieces 5c1 of the commutator 5c of the armature 5 by brush springs (not shown).
21 is electrically connected to an external ABS controller (anti-lock brake system controller) (not shown), so that when the brush controller 20 supplies a current to the brushes 20 and 21, the commutator pieces 5c of the armature 5 are not shown.
The coil 5d is sequentially excited via 1 to form a magnetic field, and the magnetic field formed by the armature 5 and the magnet 3,
It rotates by the magnetic field formed by 4.

The pump case 6 into which the shaft 5a of the armature 5 is inserted has a cylindrical opening-shaped bearing chamber 6a formed substantially in the center thereof, and the first and second cylinders are provided at the opposite positions of the bearing chamber 6a. Chambers 6b and 6c are formed. The first bearing 7 is housed in the bearing chamber 6a, and
A first valve 15 is housed in the cylinder chamber 6b, and a second valve 16 is housed in the second cylinder chamber 6c.

As shown in FIG. 2, the pump case 6 is provided with a fluid introduction passage 6d and a fluid introduction passage 6e, respectively, and one end of the fluid introduction passage 6d has the first cylinder chamber 6 at its one end.
b and the second cylinder chamber 6c are communicatively connected at a predetermined position, and the other end is communicatively connected to a reservoir (not shown) outside the pump case 6. Also, the fluid outlet path 6e
Has a first cylinder chamber 6b and a second cylinder chamber 6c at one of the predetermined positions independent of the fluid introduction passage 6d.
, And the other end is connected to the brake master cylinder outside the pump case 6 via a damper chamber (not shown).

The first bearing 7 housed in the bearing chamber 6a of the pump case 6 is a needle roller bearing, and the bearing inner ring 7a of the first bearing 7 is mounted on a shaft having an eccentric center of rotation. A collar portion 7a2 that is formed with the portion 7a1 and that projects toward the outside of the collar shape on one end side.
Is formed, and the shaft 5a of the armature 5 is press-fitted to the shaft mounting portion 7a1. Further, the bearing outer ring 7b of the first bearing 7 is provided outside the bearing inner ring 7a with the rolling element 7c in the shape of a roller interposed therebetween. ing. Since the shaft 5a of the armature 5 is press-fitted to the shaft mounting portion 7a1 of the bearing inner ring 7a, it is not necessary to stop the shaft 5a by forming the shaft 5a into a D shape or forming a D-shaped hole in the bearing inner ring 7a. Further, since it is not necessary to prevent the clevis pin from assembling, the shaft 5a and the bearing inner ring 7a can be assembled very easily.

In the first bearing 7, when the shaft 5a of the armature 5 rotates, the bearing inner ring 7a rotates eccentrically with respect to the shaft 5a, so that the outer surface of the bearing outer ring 7b is arranged such that its outer peripheral surface can move forward and backward. The first piston 10 provided in the first valve 15 described later is reciprocated by 7b between the top dead center A and the bottom dead center B, and the first piston 10 described later is horizontally opposed to the first piston 10. The second piston 11 provided in the second valve 16 also has a top dead center A and a bottom dead center B.
And reciprocate between.

A first cylinder 8 is housed in the first cylinder chamber 6b of the pump case 6. The first cylinder 8 is formed into a cylindrical liner shape, has an inner side having a piston hole 8a, and has an outer side through two O-rings (O-rings) 22 and 23 to form the first cylinder. Room 6
It is attached to b.

Further, both O-rings 2 of the first cylinder 8
Between 2 and 23, an annular groove 8b, which is an annular concave groove and serves as an inlet of the first valve 15, is formed. Two annular grooves 8b facing each other are formed through the circular hole 8c to form the first groove. Since it is communicated with the piston hole 8a of the cylinder 8, the piston hole 8a of the first cylinder 8 has a round hole 8c and an annular groove 8a.
It is connected to a reservoir (not shown) through b and the fluid introduction path 6d of the pump case 6. First cylinder 8
The first piston 10 is inserted into the piston hole 8a.

The first piston 10 has a substantially T-shaped cross section, is a disk-shaped piston head 10b which is pressed against the bearing outer ring 7b of the first bearing 7, and a substantially cylindrical O-ring (O-ring). ) 46, and the skirt 10c inserted into the piston hole 8a through the boss 46.

The first piston 10 is the piston head 1
0b and the first cylinder 8 between one valve spring 13
The piston head 10b is pressed against the bearing outer ring 7b of the first bearing 7 by the elastic repulsive force of the valve spring 13.

The inner circumference of the skirt 10c of the first piston 10 is a first valve chamber 10d which is closed on the piston head 10b side, and the outer circumference of the skirt 10c has an annular groove 10e which is a concave groove. Is formed in this annular groove 1
Two points 0e facing each other are communicatively connected to the first valve chamber 10d via the round holes 10f.

Since the valve seat 24 is fitted on the opposite side of the first valve chamber 10d from the first piston 10 of the first cylinder 8, the valve seat 24 and the first piston 1 are opposed to each other.
A second valve chamber 25 is formed between 0 and 0.
In the second valve chamber 25, a first valve body 27 is arranged which is biased by a first valve spring 26 toward the side that closes the first valve chamber 10d.
When the hydraulic pressure of the brake oil introduced into the first valve chamber 10d exceeds a predetermined value due to the reciprocating movement of the first piston 10, the first valve spring 26
In order to communicate the first valve chamber 10d with the second valve chamber 25 against the above, it has a function of transferring the brake oil of the first valve chamber 10d to the second valve chamber 25.

A communication hole 24a, which serves as a flow path, is formed substantially in the center of the valve seat 24, and a base 28 is provided at an opposite position of the communication hole 24a via an O-ring (O-ring) 29. Since it is assembled in the cylinder chamber 6b of
A third valve chamber 30 is formed between the communication hole 24a and the base 28. A tapered valve body contact surface 24b is formed around the communication hole 24a of the valve seat 24, and the second valve body 32, which will be described later, contacts the valve body contact surface 24b. A second valve body (valve body) 32, which is urged by a second valve spring (valve spring) 31 toward the side that closes the communication hole 24a, is arranged in the third valve chamber 30. Valve body 32
When the hydraulic pressure of the brake oil introduced into the second valve chamber 25 exceeds a predetermined value, the second valve chamber 25 is forced to move against the second valve spring 31 and the third valve chamber 3
In order to communicate with 0, it has a function of transferring the brake oil of the second valve chamber 25 to the third valve chamber 30.

The base 28 has a third valve chamber 3
Since the outlet flow passage 28a serving as an outlet for communicating 0 with the fluid outlet passage 6e of the pump case 6 is formed, the brake oil introduced into the third valve chamber 30 is pumped from the pump passage 6a through the outlet flow passage 28a. Fluid discharge path 6e
And is transferred to the brake master cylinder via a damper chamber (not shown). Base 28 is pump case 6
It is pressed and fixed by a stopper 33 screwed in.

As shown in FIG. 3, in the second valve body 32, the entire valve body 32a, which is integrally provided by symmetrically arranging a pair of truncated cones, has a flexible rubber molding portion 32b. A tapered valve seat contact surface 32c is formed on the contact side of the valve body 32a with the valve seat 24.

On the valve spring side of the second valve body 32, which is opposite to the tapered valve seat contact surface 32c, a truncated cone-shaped valve spring locking portion 32d is formed. The rubber molded portion 32b is not limited to the entire valve body 32a, and may be only the tapered valve seat abutment surface 32c. The rubber molded portion 32a serves as a contact portion of the valve seat 24 with respect to the second valve body 32. It may be provided.

Since the second valve body 32 has a flexible rubber molded portion 32b as the whole of the valve body 32a, as shown in FIG. 4, it is biased by the second valve spring 31. As a result, the taper valve element contacting surface 24b of the valve seat 24 is brought into close contact with the valve seat 24, and the hydraulic pressure of the brake oil exceeds a predetermined value. The seating sound generated when the vehicle collides after being separated is not attenuated by the rubber molding portion 32b and becomes a metallic noise.

The first cylinder 8, the first piston 10,
The valve seat 24, the first check ball 27, the first valve spring 26, the second valve body 32, the second valve spring 31, the base 28, and the stopper 33 form the first valve 15.

On the other hand, the second valve 16 housed in the second cylinder chamber 6c of the pump case 6 has the same structure as the first valve 15 described above, and the second cylinder 34 is
It has a piston hole 34a and two O-rings (O
Ring) 35, 36 are arranged, an annular groove 34b serving as an inlet and a round hole 34c are formed, the second piston 11 is inserted into the piston hole 34a of the second cylinder 34, and the second piston 11 is , O-ring with piston head 11b pressed against bearing outer ring 7b
Skirt 1 inserted into piston hole 34a through 47
4c which is integrally provided with 1c and in which the valve spring 14 serving as the other piston pressing means is arranged between the piston head 11b and the second cylinder 34, and which is arranged to face the first valve chamber 10d. 11d, annular groove 11e, round hole 1
1f is formed and has a valve seat 37 having a communication hole 37a that serves as a flow path and a lead-out flow path 38a that serves as an outlet, and a second cylinder chamber 6c via an O-ring 39.
To the base 38, the stopper 33, the fifth valve chamber 40 arranged to face the second valve chamber 25, the third valve spring 41, the third valve body 42, and the third valve chamber 30. It is provided with a sixth valve chamber 43, a fourth valve body (valve body) 44, and a fourth valve spring (valve spring) 45 which are arranged to face each other.

Also in the fourth valve body 44, as shown in FIG. 3, the entire valve body main body 44a integrally provided by symmetrically arranging a pair of truncated cones has a flexible rubber molding portion 44b. A tapered valve seat abutment surface 44c is formed on the side of the valve body 44a that abuts on the valve seat 37, and on the valve spring side opposite to the tapered valve seat abutment surface 44c,
A valve spring locking portion 44d having a truncated cone shape is formed. The rubber molded portion 44b is not limited to the entire valve body main body 44a, and may be only the tapered valve seat abutment surface 44c. The rubber molded portion 44b may be a contact portion of the valve seat 37 with respect to the fourth valve body 44. May be provided.

Like the second valve body 32, the fourth valve body 44 has a rubber molded portion 44 in which the entire valve body 44 is flexible.
b, as shown in FIG. 4, by being biased by the fourth valve spring 45, the taper valve element abutment surface 37b of the valve seat 37 is brought into good contact with the brake oil and the brake oil The seating sound generated when the hydraulic pressure exceeds a predetermined value and is separated from the tapered valve body contact surface 37b of the valve seat 37 and collides with the seat 37 is attenuated by the rubber molding portion 44b to become metallic noise. Never.

When the shaft 5a of the armature 5 rotates, the bearing inner ring 7a of the first bearing 7 is eccentrically rotated with respect to the shaft 5a so that the first and second valves 15 and 16 are pressed against the bearing outer ring 7b. The first piston 10 and the second piston 11 are
Reciprocates between each.

When the first piston 10 moves from the bottom dead center B to the top dead center A, the second valve body 32 causes the communication hole 2 of the valve seat 24.
4a is closed, so that the second valve chamber 25 in a negative pressure is connected to the annular groove 8b and the circular hole 8c of the first cylinder 8 from the fluid introduction path 6d of the pump case 6 and the annular shape of the first piston 10. Brake oil is sucked into the first valve chamber 10d through the groove 10e and the round hole 10f, and the brake oil is sucked and moved from the first valve chamber 10d to the second valve chamber 25.

Since the first piston 10 which has reached the top dead center A is moved toward the bottom dead center B, the first valve body 27 does not move the first valve chamber 10d into the second valve chamber 25. The brake oil transferred to the second valve chamber 25 in the communication state is transferred to the third valve chamber 30 because the second valve body 32 opens the communication hole 24a of the valve seat 24, and the brake oil is transferred to the third valve chamber 30. The brake oil in the valve chamber 30 is discharged from the base 28 through the flow passage 2
It is sent out to the fluid discharge path 6e of the pump case 6 through 8a.

Since the first piston 10 reciprocates between the top dead center A and the bottom dead center B with the rotation of the bearing inner ring 7a of the first bearing 7, the first valve chamber 10d,
Brake oil is sucked from the fluid introduction passage 6d of the pump case 6 through the second valve chamber 25 and the third valve chamber 30 and sent out from the fluid discharge passage 6e.

The second piston 11 is also the first piston 10
In the same manner as above, the reciprocating motion is performed between the top dead center A and the bottom dead center B, and the fourth valve chamber 11d, the fifth valve chamber 40, and the sixth valve chamber 11d.
Fluid introduction path 6d of the pump case 6 through the valve chamber 43 of
The brake oil is sucked from and discharged from the fluid discharge path 6e.

The hydraulic pump 1 having such a structure is built in the actuator of the antilock brake system, the fluid introduction path 6d of the pump case 6 is connected to the reservoir, and the fluid is discharged from the pump case 6 through the damper chamber. The path 6e is communicatively connected to the brake master cylinder, and the brushes 20 and 21 are electrically connected to an external ABS controller and mounted on the vehicle.

When the brake is operated, the ABS controller generates a holding signal when the slip state of the wheel is recognized, and when the brake of the wheel is recognized to be large, a decompression signal is generated, and the ABS signal is generated. When it is recognized that the slip has become smaller, a pressure increase signal is generated and each signal is transferred to the actuator. When the pressure reduction signal is generated, current is supplied to both brushes 20 and 21 of the hydraulic pump 1.

When the pressure reducing signal is generated from the ABS controller, the pressure increasing solenoid valve and the pressure reducing solenoid valve that are connected to the wheel cylinder are activated, so that the pressure increasing solenoid valve has its port closed and the pressure reducing solenoid is closed. The valve opens the port. In the hydraulic pump 1, the current is supplied to the brushes 20 and 21, and the armature 5 rotates, so that the first bearing 7
When the inner ring 7a of the bearing rotates, the first piston 10 and the second piston 11, which are respectively in pressure contact with the outer ring 7b of the bearing, reciprocate, and the brake oil in the wheel cylinder is stored through the solenoid valve for pressure reduction. By sucking the brake oil from the existing reservoir and returning it to the brake master cylinder, the pressure of the brake oil in the wheel cylinder is reduced to make the wheel slip proper.
The hydraulic pressure of the brake oil is controlled so that excessive slip does not occur.

While the hydraulic pump 1 is operating, the second and fourth valve bodies 32 and 44 are urged by the second and fourth valve springs 31 and 45 so that the valve seat 24,
The tapered valve element contact surfaces 24b, 37b of the valve seat 37, 37b are in close contact with each other, and the hydraulic pressure of the brake oil exceeds a predetermined value.
The metallic seating sound is not generated when the vehicle collides after being separated from b and 37b.

5 and 6 show a second embodiment of the hydraulic pump according to the present invention, and FIGS. 5 and 6 show the first embodiment.
Only the valve 15 and the second valve 16 parts of are shown.

In this case, the first and second valves 15, 16
The second and fourth valve bodies 32 and 44 are formed in a cylindrical shape, and the flat valve seat abutment surface 32 is provided on the abutment side of the valve seats 24 and 37.
e, 44e are formed, and the planar valve seat contact surface 32e,
The valve spring locking portions 32f and 44f are formed on the valve springs 31 and 45 opposite to 44e,
The valve seats 24 and 37 are provided with the planar valve body contact surfaces 24c and 37c which are arranged so as to be in pressure contact with the planar valve seat contact surfaces 32e and 44e of the second and fourth valve bodies 32 and 44, respectively. Has been done. Then, the base 38, 38 is formed in a concave shape, and the valve body accommodating portion 38 is arranged so as to accommodate the second and fourth valve discs 32, 44.
b and 38b are arranged to face the valve seats 24 and 37.

In this case also, the second and fourth valve bodies 32, 44
As shown in FIG. 5, the valve body 32 has a cylindrical shape.
a, 44a are rubber molding parts 32b, 4 having flexibility as a whole.
4b, and the flat valve seat contact surfaces 32e, 44 are provided on the contact sides of the valve body bodies 32a, 44a with the valve seats 24, 37.
e is formed, and the flat valve seat contact surfaces 32e, 4
Since the valve spring locking portions 32f and 44f are formed on the sides of the second valve springs 31 and 45 opposite to 4e, they are urged by the second valve springs 31 and 45 as shown in FIG. By the valve seat 2
The flat valve element contacting surfaces 24c, 37c of the valve seats 24, 37 are in close contact with each other and the hydraulic pressure of the brake oil exceeds a predetermined value.
The seating sound generated when the vehicle collides after being separated from c and 37c is not attenuated by the rubber molding portions 32b and 44b and becomes metallic noise. Rubber molding parts 32b, 44b
Is not limited to the entire valve body 32a, 44a, but may be only the flat valve seat abutment surfaces 32e, 44e, and the rubber molded parts 32a, 44a may be replaced by the second and fourth valve seats 24, 37. You may provide in the contact part with respect to the valve bodies 32 and 44.

[0046]

As described above, according to the hydraulic pump according to the first aspect of the present invention, in the valve, the valve body having the rubber molding portion collides with the valve seat or has the rubber molding portion. Since the valve body collides with the valve seat, it is unlikely that metallic noise is generated when the valve body collides with the valve seat, so that it is not necessary to install a sound insulating material. Claim 2 of this invention
According to the hydraulic pump of the present invention, in the valve, the valve body having the rubber molding portion as a whole collides with the valve seat. Therefore, when the valve body collides with the valve seat, a metallic seating noise may be generated. Since it is low, it is not necessary to install a sound insulating material. According to the hydraulic pump of claim 3 of the present invention, the valve is
Since the tapered valve seat abutment surface of the valve body having the frustoconical rubber molding part collides with the tapered valve body abutment surface of the valve seat,
Since it is less likely that a metallic seating noise will be generated when the valve body collides with the valve seat, it is not necessary to install a sound insulating material or the like. According to the hydraulic pump of claim 4 of the present invention, in the valve, the valve spring is engaged with the valve spring engaging portion of the valve body having the frustoconical rubber molding portion as a whole, and the valve valve has a tapered valve. Since the seat abutment surface collides with the tapered valve body abutment surface of the valve seat, it is less likely that a metallic seating noise will be generated when the valve body collides with the valve seat. There is no need. According to the hydraulic pump of claim 5 of the present invention, in the valve, the valve spring is engaged with the valve spring engaging portion of the valve body having the cylindrical rubber molding portion as a whole, and the flat valve of the valve body is provided. Since the seat abutment surface collides with the flat valve body abutment surface of the valve seat, it is less likely that a metallic seating noise will be generated when the valve body collides with the valve seat. According to the hydraulic pump of the present invention, it is not necessary to reduce the operation noise by preventing the generation of metallic noise, and the workability is improved by eliminating the additional work such as mounting the sound insulating material. It has an excellent effect that

[Brief description of drawings]

FIG. 1 is a vertical sectional front view of a first embodiment of a hydraulic pump according to the present invention.

FIG. 2 is a vertical sectional side view of the hydraulic pump shown in FIG.

FIG. 3 is a vertical sectional view around a valve in the hydraulic pump shown in FIG.

4 is an external perspective explanatory view showing an assembling relationship between a valve body and a valve seat in the hydraulic pump shown in FIG.

FIG. 5 is a vertical sectional view around a valve in a second embodiment of the hydraulic pump according to the present invention.

6 is an external perspective view showing the assembly relationship between the valve body and the valve seat in the hydraulic pump shown in FIG.

FIG. 7 is a vertical cross-sectional view around a valve of a conventional hydraulic pump.

[Explanation of symbols]

 1 Hydraulic Pump 2 Yoke 3 Magnet 4 Magnet 5 Armature 5a Shaft 6 Pump Case 7 (Bearing) First Bearing 7a Bearing Inner Ring 7b Bearing Outer Ring 7c Rolling Element 8 (Cylinder) First Cylinder 10 (Piston) First Piston 11 (Piston) Second piston 15 (Valve) First valve 16 (Valve) Second valve 24 Valve seat 24a (Flow path) communication hole 24b Tapered valve body contact surface 24c Flat valve body contact surface 30 (Valve spring) Second valve spring 32 (Valve body) Second valve body 32b Rubber molded portion 32c Tapered valve seat contact surface 32d Valve spring locking portion 32e Flat valve seat contact surface 32f Valve spring locking Part 34 (Cylinder) Second Cylinder 37 Valve Seat 37a (Flow Path) Communication Hole 37b Tapered Valve Body Contact Surface 37 Planar valve body abutting surface 38 Base 38b Valve body accommodating portion 44 (Valve body) Fourth valve body 44b Rubber molded portion 44c Tapered valve seat abutting surface 44d Valve spring locking portion 44e Flat valve seat abutting surface 44f Valve spring locking part 45 (Valve spring) Fourth valve spring

Claims (5)

[Claims] 1. A yoke, a magnet fixed to the inside of the yoke, an armature arranged on the inner peripheral side of the magnet and rotated by energization, a pump case connected to the yoke, and a pump case in the pump case. And a bearing inner ring that has an eccentric center of rotation with respect to the shaft of the armature and that rotates integrally with the shaft, and a bearing outer ring that is arranged outside the bearing inner ring via a rolling element. A bearing and a piston, which is housed in a cylinder arranged in the pump case and is reciprocated between a top dead center and a bottom dead center in a pressure contact state with the bearing outer ring,
This piston is equipped with a valve element that is arranged to open and close against the valve spring by opening and closing the flow passage formed in the valve seat by reciprocating between top dead center and bottom dead center. Is provided with a valve for inhaling the fluid and then delivering the fluid, wherein the valve has a flexible rubber molding portion on at least one of a valve body and a valve seat. 2. The hydraulic pump according to claim 1, wherein a valve body of the valve is integrally molded by a rubber molding portion. 3. A valve is provided with a tapered valve seat abutment surface on the side of abutting against the valve seat, and a frustoconical valve body is provided, and the tapered valve seat abutment of the valve body is provided. The hydraulic pump according to claim 2, further comprising a valve seat that forms a tapered valve body contact surface that is arranged so as to be capable of being pressed against the surface. 4. A valve includes a valve body integrally provided by symmetrically arranging a pair of truncated cones, and forming a valve spring locking portion on a valve spring side opposite to a tapered valve seat contact surface. The hydraulic pump according to claim 3. 5. The valve has a cylindrical shape and has a flat valve seat abutment surface on the side abutting on the valve seat, and a valve spring on the valve spring side opposite to the flat valve seat abutment surface. A valve body having a locking portion is provided, and a valve seat having a planar valve body contact surface disposed so as to be capable of pressure contact with the planar valve seat contact surface of the valve body is provided. 3. The hydraulic pump according to claim 2, further comprising: a base having a valve body accommodating portion which is concave and is arranged so as to accommodate the valve body and which is arranged so as to face the valve seat.