TW201708732A - Hydraulic pressure controller and method for manufacturing hydraulic pressure controller - Google Patents

Abstract

A purpose is to obtain a hydraulic pressure controller that can be downsized and a method for manufacturing such a hydraulic pressure controller. A hydraulic pressure controller that controls hydraulic pressure of a brake hydraulic circuit includes a base body 10 formed with a cylinder bore 40, one end of which in an axial direction communicates with a drive mechanism and the other end of which is opened, and a pump device 2 for regulating the hydraulic pressure. The pump device 2 includes a piston 41 that is disposed in the cylinder bore 40 and that reciprocates in an interlocking manner with an operation of the drive mechanism, a compression spring that is disposed in the cylinder bore 40 and urges the piston 41; and a suction-side check valve 46 that is disposed between the piston 4l and the other end of the cylinder bore 40 in the cylinder bore 40 so as to restrain a reverse flow of a brake fluid that is suctioned in the cylinder bore 40.

Description

Hydraulic controller and method of manufacturing hydraulic controller

The present invention relates to a hydraulic controller that controls the hydraulic pressure of a brake hydraulic line and a method of manufacturing the same.

Conventionally, in a vehicle such as a locomotive (two-wheel motor vehicle or three-wheel motor vehicle), when the hydraulic pressure in the brake hydraulic circuit filled with the brake fluid is changed by the operation of the brake lever by the passenger of the vehicle, The braking force is generated on the wheel. Further, a vehicle including a hydraulic controller that can freely open/close the regulating valve, a pump device that operates in an interlocking manner with the regulating valve, and the like as a means for changing the hydraulic pressure in the brake hydraulic circuit is available. of. The hydraulic controller is electronically controlled for automatic operation and the braking force generated on the wheel can be controlled by increasing or decreasing the hydraulic pressure in the brake hydraulic line.

This hydraulic controller is provided with a pump device for the purpose of increasing the hydraulic pressure of the brake fluid. The pump unit is driven by a drive mechanism (see, for example, PTL 1).

Reference list

Patent literature

PTL 1: JP-A-2 014-69663

In the technique disclosed in PTL 1, the check valve is independently provided intermediate the brake hydraulic line extending from the accumulator section toward the pumping means. There are conditions in which a cylinder member other than the above members is provided. Therefore, there is such a problem that each of the components such as the check valve and the cylinder member occupies a large capacity in the hydraulic controller, which results in unification of the unified hydraulic controller.

The present invention has been made in the context of the problems as described in the background, and thus has the object of obtaining a hydraulic controller that can be downsized. The invention also has the object of obtaining a method for manufacturing such a hydraulic controller.

The hydraulic controller of the present invention is a hydraulic controller that controls the hydraulic pressure of the brake hydraulic line, and the hydraulic controller includes a base body formed to have an inner diameter of the cylinder, an end of the inner diameter of the cylinder in the axial direction, and a driving mechanism Connected and the other end of the inner diameter of the cylinder is open; and a pumping device for regulating the hydraulic pressure. The pump device includes a piston disposed in the inner diameter of the cylinder and reciprocating in an interlocking manner with operation of the drive mechanism, and a compression spring disposed in the inner diameter of the cylinder and pushing the piston from the other end side of the piston to a distal end side; and a suction side check valve disposed between the piston and the other end in the inner diameter of the cylinder and restricting reverse flow of the brake fluid in the inner diameter of the suction cylinder.

In the method for manufacturing the hydraulic controller of the present invention, the hydraulic controller includes: a base body formed to have a cylinder inner diameter, the cylinder inner diameter being communicated with the drive mechanism at one end in the axial direction, and the cylinder The other end of the diameter is open; and a pumping device that adjusts the hydraulic pressure, the pump device comprising: a piston disposed in the inner diameter of the cylinder and reciprocating in an interlocking manner with the operation of the drive mechanism; the compression spring disposed in the The inner diameter of the cylinder, and the piston from the piston One end side is pushed to a distal end side; a suction side check valve is disposed between the piston and the other end in the inner diameter of the cylinder, and restricts the reverse flow of the brake fluid in the inner diameter of the suction cylinder; the discharge side check a valve disposed between the suction side check valve and the other end in the inner diameter of the cylinder and restricting reverse flow of brake fluid discharged from the inner diameter of the cylinder; and a cover closing the other end of the inner diameter of the cylinder, And the discharge side check valve includes a valve seat member disposed in the inner diameter of the cylinder and formed to have a recessed section for receiving the compression spring in a surface of the valve seat member on one end. A method for manufacturing a hydraulic controller includes: a first process for inserting a piston, a suction side check valve, and a compression spring from another end side into a cylinder bore; a second process for use in the first process Thereafter, the integrated discharge side check valve and cover are press-fitted into the inner diameter of the cylinder from the other end side, and the outer circumferential surface of the valve seat member is joined to the inner circumferential surface of the cylinder inner diameter; and a third process is used The inner circumferential surface of the inner diameter of the cylinder is joined to the outer circumferential surface of the cap by caulking after the second process.

In the hydraulic controller according to the present invention, the cylinder inner diameter is formed in the base body, and the suction side check valve is formed between the piston and the other end in the cylinder inner diameter. Therefore, the hydraulic controller is reduced in size.

Further, in the method for manufacturing a hydraulic controller according to the present invention, the manufacturing process of the hydraulic controller is simplified.

1‧‧‧Hydraulic controller

2‧‧‧ pump device

2A‧‧‧ drive mechanism

2B‧‧‧ pump components

3‧‧‧Regulator

3A‧‧‧First booster valve

3B‧‧‧First Pressure Reducing Valve

3C‧‧‧second booster valve

3D‧‧‧Second pressure reducing valve

4‧‧‧Internal channel

4A‧‧‧First internal channel

4B‧‧‧Second internal channel

4C‧‧‧ third internal channel

4D‧‧‧fourth internal channel

4E‧‧‧ fifth internal channel

4F‧‧‧ sixth internal channel

5A‧‧‧First flow limiter

5B‧‧‧Second flow limiter

6A‧‧‧First Accumulator Section

6B‧‧‧Second Accumulator Section

7‧‧‧Electronic Control Unit

8‧‧‧Detection section

8A‧‧‧First pressure sensor

8B‧‧‧Second pressure sensor

10‧‧‧Base body

20‧‧‧ front wheel

21‧‧‧ Front brake pads

22‧‧‧ Front wheel cylinder

23‧‧‧Brake fluid tube

24‧‧‧Handlebar

25‧‧‧First master cylinder

26‧‧‧First receptacle

27‧‧‧Brake fluid tube

30‧‧‧ Rear wheel

31‧‧‧ Rear brake pads

32‧‧‧ Rear wheel cylinder

33‧‧‧Brake fluid tube

34‧‧‧ pedal

35‧‧‧Second master cylinder

36‧‧‧Second receptacle

37‧‧‧Brake fluid tube

40‧‧‧Cylinder inner diameter

40a‧‧‧Piston holding section

40b‧‧‧Main housing section

40b1‧‧‧Small diameter inner circumference section

40b2‧‧‧large diameter inner circumference section

40b3‧‧‧ Large diameter main body receiving section

40c‧‧‧Cable housing section

40c1‧‧‧Guide section

41‧‧‧Piston

42‧‧O ring

43‧‧‧Piston Clamp

43a‧‧‧End section

43b‧‧‧Clamping channel

44‧‧‧Valve Clamp

44a‧‧‧ball basket

44b‧‧‧slit

44c‧‧‧ Sealing lip section

45‧‧‧Compressed coil spring

46‧‧‧Inhalation side check valve

46a‧‧ balls

46b‧‧‧ valve seat

46c‧‧‧Squeeze spring

47‧‧‧Drain side check valve

47a‧‧ balls

47b‧‧‧ valve seat

47c‧‧‧Squeeze spring

48‧‧‧ cover

48a‧‧‧Ball accommodation section

48b‧‧‧Outstanding section

48c‧‧‧ annular protruding section

48d‧‧‧large diameter outer circumference section

49‧‧‧ valve seat components

49a‧‧‧ annular protruding section

49b‧‧‧ recessed section

50‧‧‧Open section

100‧‧‧Hydraulic Control System

202‧‧‧ pump device

202B‧‧‧ pump components

210‧‧‧Base body

240‧‧‧ built-in inner diameter

245‧‧‧Compressed coil spring

246‧‧‧Inflow side check valve

250‧‧‧Cylinder components

C1‧‧‧Front wheel hydraulic line

C2‧‧‧ rear wheel hydraulic line

P‧‧‧埠

P1‧‧‧ first

P2‧‧‧Second

P3‧‧‧third

P4‧‧‧Fourth

1 is a schematic configuration diagram depicting a hydraulic control system including a hydraulic controller according to an embodiment of the present invention.

Fig. 2 is an exploded perspective view depicting a hydraulic controller in accordance with an embodiment of the present invention.

Fig. 3 is an explanatory view depicting a pump element according to an embodiment of the present invention.

Fig. 4 is an explanatory view showing a portion of a pump element according to an embodiment of the present invention.

Fig. 5 is an explanatory view showing a state in which a cover of a pump element is inserted according to an embodiment of the present invention.

Fig. 6 is an explanatory view depicting a pump element according to a comparative example.

The hydraulic controller according to the present invention will be described below by using a drawing.

Note that the hydraulic controller according to the present invention can be used for vehicles other than locomotives (for example, automobiles, rails, etc.).

In addition, each of the configurations, operations, and the like which will be described below is only an example, and the hydraulic controller according to the present invention is not limited to the condition having this configuration, the operation, and the like. For example, the hydraulic controller according to the present invention can perform operations other than as an anti-lock brake system (ABS).

Further, in each of the drawings, detailed portions are depicted in a simplified or omitted manner. Further, overlapping descriptions are appropriately simplified or omitted.

Example

<Overall Configuration of Hydraulic Control System 100>

1 is a schematic configuration diagram depicting a hydraulic control system 100 including a hydraulic controller 1 in accordance with an embodiment of the present invention.

The hydraulic control system 100 includes a hydraulic controller 1 that is mounted on a locomotive such as a locomotive In the vehicle and change the braking force of the locomotive. The locomotive includes a front wheel 20 and a rear wheel 30, and a handlebar 24 and a pedal 34 that are operated by a user driving the locomotive. When the handlebar 24 is operated, the braking force on the front wheel 20 is changed. When the pedal 34 is operated, the braking force on the rear wheel 30 is changed.

The hydraulic control system 100 includes a front wheel hydraulic line C1 through which brake fluid for generating a braking force on the front wheel 20 flows, and a rear wheel hydraulic line C2 for generating a braking force on the rear wheel 30. The brake fluid flows through the rear wheel hydraulic line. The front wheel hydraulic line C1 and the rear wheel hydraulic line C2 each include an internal channel 4 in the hydraulic controller 1, which will be described below. Any brake oil in the various brake oils can be used as the brake fluid.

As a mechanism for generating a braking force on the front wheel 20 or the like, the hydraulic control system 100 has the following configuration. More specifically, the hydraulic control system 100 includes a front brake pad 21 attached to the front wheel 20 and a front wheel cylinder 22 for moving the front brake pad 21 before the brake piston (not depicted) is provided in a freely slidable manner In the front wheel cylinder; and a brake fluid tube 23 connected to the front wheel cylinder 22. Note that the front brake pad 21 is provided with a floating rotor (not depicted) that is sandwiched to rotate with the front wheel 20. When being squeezed by the previous brake piston in the front wheel cylinder 22, the front brake pad 21 abuts against the floating rotor and generates friction. In this way, a braking force is generated on the front wheel 20 that rotates with the floating rotor.

The hydraulic control system 100 includes a first master cylinder 25 attached to the handlebar 24, a first reservoir 26 for storing brake fluid, and a brake fluid tube 27 coupled to the first master cylinder 25. Note that the master cylinder piston (not depicted) is provided in the first master cylinder 25 in a freely slidable manner. When the handlebar 24 is operated, the master cylinder piston in the first master cylinder 25 is moved. Since the pressure of the brake fluid applied to the front brake piston changes according to the position of the master cylinder piston, the force of the front brake pad 21 for sandwiching the floating rotor changes, and the braking force on the front wheel 20 also changes.

As a mechanism for generating a braking force on the rear wheel 30 or the like, the hydraulic control system 100 has the following configuration. More specifically, the hydraulic control system 100 includes a rear brake pad 31 attached to the rear wheel 30, a rear wheel cylinder 32, and a rear brake piston (not depicted) that moves the rear brake pad 31 to be provided in a freely slidable manner In the rear wheel cylinder; and a brake fluid tube 33 that is coupled to the rear wheel cylinder 32. Note that the rear brake pad 31 is provided with a floating rotor (not depicted) that is sandwiched to rotate with the rear wheel 30. When the brake piston is being pressed by the rear wheel cylinder 32, the rear brake pad 31 abuts against the floating rotor and generates a frictional force. In this way, a braking force is generated on the rear wheel 30 that rotates together with the floating rotor.

The hydraulic control system 100 includes a second master cylinder 35 that is attached to the pedal 34, a second reservoir 36 that stores brake fluid, and a brake fluid tube 37 that is coupled to the second master cylinder 35. Note that the master cylinder piston (not depicted) is provided in the second master cylinder 35 in a freely slidable manner. When the pedal 34 is operated, the master cylinder piston in the second master cylinder 35 is moved. Since the pressure of the brake fluid applied to the rear brake piston changes according to the position of the master cylinder piston, the force of the rear brake pad 31 for sandwiching the floating rotor changes, and the braking force on the rear wheel 30 also changes.

<Description of the configuration of the hydraulic controller 1>

2 is an exploded perspective view depicting a hydraulic controller 1 in accordance with an embodiment of the present invention.

As depicted in Figures 1 and 2, the hydraulic controller 1 is incorporated in a vehicle such as a locomotive. The hydraulic controller 1 includes an internal channel 4 through which brake fluid flows, and a pump device 2 for feeding brake fluid in the internal channel 4 to the first master cylinder 25 and the second master cylinder 35 side The regulator valve 3, which is freely openable/closed, is provided in the front wheel hydraulic line C1 and the rear wheel hydraulic line C2, respectively. Note that the regulator valve 3 includes a first pressure increasing valve 3A, a first pressure reducing valve 3B, a second pressure increasing valve 3C, and a second pressure reducing valve 3D.

In addition, the hydraulic controller 1 includes: various cymbals P connected to respective fluid tubes such as the brake fluid tube 23; a first flow restrictor 5A and a second flow restrictor 5B, each of which restricts flow through the internal channel 4 The flow rate of the brake fluid; and the first accumulator section 6A and the second accumulator section 6B, each of which can store brake fluid. Please note that the various parameters P include a first node P1, a second node P2, a third node P3, and a fourth node P4.

Further, the hydraulic controller 1 includes an electronic control unit 7 having an electronic control board that controls opening/closing of each of the regulating valves 3 and the like, and a detecting section 8 including the front wheel cylinder 22 The first pressure sensor 8A of the pressure, the second pressure sensor 8B that detects the pressure of the rear wheel cylinder 32, and the like.

In the hydraulic controller 1, the internal channel 4, the pump device 2, the regulating valve 3, the various ports P, the first flow rate limiter 5A, the second flow rate limiter 5B, the first accumulator section 6A and the second accumulator The section 6B is integrated in the metal base body 10. In addition, the electronic control unit 7 is surrounded by an outer casing for covering the base body 10.

(internal channel 4)

The inner channel 4 is formed in the base body 10 and includes: a first inner channel 4A, a second inner channel 4B, and a third inner channel 4C that are part of the front wheel hydraulic line C1; and The fourth internal channel 4D, the fifth internal channel 4E, and the sixth internal channel 4F of a portion of the wheel hydraulic line C2.

The first internal passage 4A is connected to the outflow side of the brake fluid of the pump device 2, the first pressure increasing valve 3A, and the first weir P1. Further, the first internal channel 4A is provided with a first flow rate limiter 5A. The second internal channel 4B is connected to the first pressure increasing valve 3A, the first pressure reducing valve 3B, and the third weir P3. Further, the second internal channel 4B is provided with a first pressure sensor 8A. The third internal channel 4C is connected to the pump device The inflow side of the brake fluid of 2 and the first pressure reducing valve 3B. Further, the third inner channel 4C is provided with a first accumulator section 6A.

The fourth inner channel 4D is connected to the outflow side of the brake fluid of the pump device 2, the second pressure increasing valve 3C, and the second weir P2. Further, the fourth internal channel 4D is provided with a second flow rate limiter 5B. The fifth inner channel 4E is connected to the second pressure increasing valve 3C, the second pressure reducing valve 3D, and the fourth weir P4. Further, the fifth inner channel 4E is provided with a second pressure sensor 8B. The sixth inner channel 4F is connected to the inflow side of the brake fluid of the pump device 2 and the second pressure reducing valve 3D. Further, the sixth inner channel 4F is provided with a second accumulator section 6B.

(pump unit 2)

The pump device 2 includes a drive mechanism 2A which may include, for example, a DC motor or the like, and two pump elements 2B to which drive power is supplied to each of the two pump elements. The drive mechanism 2A includes a stator, a rotor, and the like, and the rotational frequency of the stator, the rotor, and the like is controlled by the electronic control unit 7. One of the pump elements 2B is for feeding the brake fluid in the front wheel hydraulic line C1. In addition, a pumping element 2B feeds the brake fluid in the third internal channel 4C to the first internal channel 4A side. Another pump element 2B is used to feed the brake fluid in the rear wheel hydraulic line C2. In addition, another pump element 2B feeds the brake fluid in the sixth inner channel 4F to the fourth inner channel 4D side.

(regulating valve 3)

The regulating valve 3 is a valve provided in the internal channel 4. The opening/closing of each of the regulating valves 3 is controlled by the electronic control unit 7. The regulator valve 3 includes a first pressure increasing valve 3A, a first pressure reducing valve 3B, a second pressure increasing valve 3C, and a second pressure reducing valve 3D. Each of the regulating valves 3 can be assembled by using a solenoid valve including a solenoid, and when the excitation of the solenoid valve is controlled by the electronic control unit 7, the opening/closing state of the solenoid valve is switched.

One side of the first boosting valve 3A is connected to the first internal channel 4A, and the other side of the first boosting valve is connected to the second internal channel 4B. The first boost valve 3A is a valve that opens during actuation of the ABS to boost the pressure of the brake fluid in the front wheel cylinder 22. That is, when the first boosting valve 3A is opened, the brake fluid on the first internal channel 4A side is fed to the first pressure by the first master cylinder 25 and a pumping element 2B corresponding to the first master cylinder 25. Two internal channels 4B side. Therefore, the pressure of the front wheel cylinder 22 is increased, the opening of the front brake pad 21 is reduced, and the braking force on the front wheel 20 is increased.

One side of the first pressure reducing valve 3B is connected to the third inner channel 4C, and the other side of the first pressure reducing valve is connected to the second inner channel 4B. The first pressure relief valve 3B is a valve that opens during actuation of the ABS to reduce the pressure of the brake fluid in the front wheel cylinders 22. That is, when the first pressure reducing valve 3B is opened, the brake fluid in the brake fluid tube 23 and the second inner channel 4B is sucked to the third internal channel 4C side by the action of a pumping element 2B. Therefore, the pressure of the front wheel cylinder 22 is reduced, the opening of the front brake pad 21 is increased, and the braking force on the front wheel 20 is reduced.

During the actuation of the ABS, when the first pressure reducing valve 3B is opened, the first pressure increasing valve 3A is closed, and when the first pressure increasing valve 3A is opened, the first pressure reducing valve 3B is closed.

The second boosting valve 3C also has a configuration and function corresponding to the configuration and function of the first boosting valve 3A. One side of the second boosting valve 3C is connected to the fourth internal channel 4D, and the other side of the second boosting valve is connected to the fifth internal channel 4E. The second boost valve 3C is a valve that opens during actuation of the ABS to boost the pressure of the brake fluid in the rear wheel cylinder 32. That is, when the second boosting valve 3C is opened, the brake fluid on the fourth internal channel 4D side is fed to the working pressure of the second master cylinder 35 and the other pumping element 2B corresponding to the second master cylinder 35 to The fifth inner channel 4E side. Therefore, the pressure of the rear wheel cylinder 32 is increased, the opening of the rear brake pad 31 is reduced, and the pressure is increased. Braking force on the rear wheel 30.

The second pressure reducing valve 3D also has a configuration and a function corresponding to the configuration and function of the first pressure reducing valve 3B. One side of the second pressure reducing valve 3D is connected to the sixth inner channel 4F, and the other side of the second pressure reducing valve is connected to the fifth inner channel 4E. The second pressure reducing valve 3D is a valve that opens during actuation of the ABS to reduce the pressure of the brake fluid in the rear wheel cylinders 32. That is, when the second pressure reducing valve 3D is opened, the brake fluid in the brake fluid tube 33 and the fifth inner passage 4E is sucked to the sixth inner channel 4F side by the action of the other pumping element 2B. Therefore, the pressure of the rear wheel cylinder 32 is reduced, the opening of the rear brake pad 31 is increased, and the braking force on the rear wheel 30 is reduced.

During the actuation of the ABS, when the second pressure reducing valve 3D is opened, the second pressure increasing valve 3C is closed, and when the second pressure increasing valve 3C is opened, the second pressure reducing valve 3D is closed.

(various 埠P)

The various turns P include: a first turn P1 corresponding to a drive mechanism such as the handlebar 24; a second turn P2 corresponding to a drive mechanism such as the pedal 34; and a third turn P3 corresponding to, for example, the front brake pad 21 a drive mechanism; and a fourth turn P4 corresponding to a drive mechanism such as the rear brake pad 31. The first turn P1 is connected to the brake fluid tube 27 and the first internal channel 4A. The second turn P2 is connected to the brake fluid tube 37 and the fourth internal channel 4D. The third turn P3 is connected to the second internal channel 4B and the brake fluid tube 23. The fourth turn P4 is connected to the fifth inner channel 4E and the brake fluid tube 33.

(first flow rate limiter 5A and second flow rate limiter 5B)

The first flow restrictor 5A is provided in a portion of the first internal channel 4A on the brake fluid outflow side of a pump element 2B. The second flow restrictor 5B is provided in a portion of the fourth internal channel 4D on the brake fluid outflow side of the other pump element 2B. Due to the action of the first flow restrictor 5A, the brake fluid flows out from the side of the pump element 2B to the side of the first main cylinder 25 so as to be able to The rapid boosting of the pressure of the brake fluid in the first master cylinder 25 is suppressed. The second flow rate limiter 5B also has a function corresponding to the first flow rate limiter 5A, and thus the rapid pressure increase of the pressure of the brake fluid in the second master cylinder 35 can be suppressed.

(first accumulator section 6A and second accumulator section 6B)

The first accumulator section 6A is provided in the third inner channel 4C. The first accumulator section 6A is used to, for example, maintain the hydraulic pressure of the brake fluid in the front wheel hydraulic line C1 or the like. The second accumulator section 6B is provided in the sixth inner channel 4F. The second accumulator section 6B is used to, for example, maintain the hydraulic pressure of the brake fluid in the rear wheel hydraulic line C2 or the like.

(electronic control unit 7 and detection section 8)

The electronic control unit 7 receives the signal from the detecting section 8, and controls the rotation frequency of the driving mechanism 2A of the pump device 2, the opening/closing of each of the regulating valves 3, and the like. During actuation of the ABS, the electronic control unit 7 controls the opening/closing of each of the regulating valves 3 in order to avoid locking of the front wheels 20 and the rear wheels 30.

<Details of the pump device>

FIG. 3 is an explanatory view depicting a pump element 2B according to an embodiment of the present invention.

4 is an explanatory view depicting a portion of a pump element 2B in accordance with an embodiment of the present invention.

As depicted in Figures 2 and 3, the pump device 2 includes a drive mechanism 2A and a pump element 2B.

The drive mechanism 2A includes a DC motor or the like as described above. The drive mechanism 2A includes a stator, a rotor, and the like, and the rotational frequency of the stator, the rotor, and the like is controlled by the electronic control unit 7.

A pump element 2B is used to feed the brake fluid in the front wheel hydraulic line C1. In addition, another pump element 2B is used to feed the brake fluid in the rear wheel hydraulic line C2. Description will be made below by proposing a pump element 2B as an example.

Pump element 2B is provided in cylinder bore 40.

In the cylinder inner diameter 40, the pump element 2B includes a piston 41, an O-ring 42, a piston holder 43, a valve holder 44, a compression coil spring 45, a suction side check valve 46, a discharge side check valve 47, and a cover. 48.

The compression coil spring 45 corresponds to the "compression spring" of the present invention.

The cylinder inner diameter 40 has a hollow cylindrical shape and is formed in the base body 10. The inner diameter of the cylinder is in communication with the drive mechanism 2A at one end in the axial direction, and the other end of the inner diameter of the cylinder is opened, that is, the other end of the inner diameter of the cylinder is in communication with the opening section 50. The cylinder bore 40 includes a coaxial piston receiving section 40a, a body receiving section 40b, and a lid receiving section 40c.

The piston accommodating section 40a is formed on one end side of the cylinder inner diameter 40 that communicates with the drive mechanism 2A, and accommodates the piston 41.

The main body accommodating section 40b is formed on the other end side of the cylinder inner diameter 40 away from the piston accommodating section 40a. The main body accommodating section 40b accommodates the piston holder 43, the valve holder 44, the compression coil spring 45, the suction side check valve 46, and the discharge side check valve 47. The main body receiving section 40b is an inner diameter having a larger diameter than the piston receiving section 40a. The main body accommodating section 40b has a small-diameter inner circumferential section 40b1 on one end side of the cylinder inner diameter 40, and also has a large outer diameter side of the cylinder inner diameter 40 away from the small-diameter inner circumferential section 40b1. The inner circumferential section 40b2 of the diameter.

The cover receiving section 40c is formed to be formed at the other end of the cylinder inner diameter 40 and accommodates the cover 48. The cover accommodating section 40c is an aperture having a larger diameter than the main body accommodating section 40b.

The piston 41 has a cylindrical shape that is coaxial with the axis of the cylinder inner diameter 40 and is received in the piston receiving section 40a of the cylinder inner diameter 40. A region of the piston 41 on the other end side of the cylinder inner diameter 40 protrudes to the main body receiving section 40b. Piston 41 has a piston receiving section 40a is substantially the same diameter and reciprocates axially in unison with the eccentric rotational movement of the drive mechanism 2A on one of the end sides of the cylinder inner diameter 40.

As depicted in FIG. 4, the O-ring 42 is attached to a region of the piston 41 that projects to the body receiving section 40b of the cylinder bore 40. The O-ring 42 is disposed at a position closest to one end side of the cylinder inner diameter 40 in the main body accommodating section 40b. The O-ring 42 suppresses the brake fluid flowing in the third internal passage 4C from leaking to the drive mechanism 2A that communicates with one end of the cylinder inner diameter 40.

In the main body accommodating section 40b, the piston holder 43 is housed on the other end side of the cylinder inner diameter 40 away from the piston 41. When the end section 43a located on one end side of the cylinder inner diameter 40 holds the piston 41, the piston holder 43 is attached to the piston 41 and integrally reciprocates together with the piston 41 in the axial direction.

The end section 43a of the piston holder 43 is inserted into the small diameter inner circumferential section 40b1 of the body accommodating section 40b of the cylinder inner diameter 40.

The piston holder 43 is formed to have a clamp channel 43b into which brake fluid from the third internal channel 4C of the first accumulator section 6A flows. The clamp channel 43b communicates with an opening formed in the sidewall of the piston holder 43. The opening is opposed to the third inner channel 4C in the base body 10 in a state where a gap is formed between the third inner channel 4C and the inner wall of the main body accommodating portion 40b, and the third inner channel 4C is formed as a cylinder The axial direction of the inner diameter 40 is orthogonal. The holder channel 43b extends from the opening in a manner orthogonal to the axial direction of the cylinder inner diameter 40 and extends from the axial direction of the cylinder inner diameter 40 from the T-shaped section formed at the center of the piston holder 43. . The opening in the end surface of the piston holder 43 on the other end side of the cylinder inner diameter 40 serves as the valve seat 46b of the suction side check valve 46.

In the main body receiving section 40b, the valve holder 44 is housed in the cylinder inner diameter 40 It is away from the other end side of the piston holder 43. The valve holder 44 meshes with the piston holder 43 and reciprocates integrally with the piston 41 and the piston holder 43 in the axial direction.

The valve holder 44 holds the suction side check valve 46 by the end section of the valve holder on the other end side of the cylinder inner diameter 40 when receiving the end of the compression coil spring 45.

The valve holder 44 has a ball basket 44a for holding the ball 46a of the suction side check valve 46 on the inner side of the compression coil spring 45. The ball basket 44a is formed to have a plurality of slits 44b in the axial direction of the cylinder inner diameter 40, and the brake fluid can freely flow between the inner side and the outer side of the ball basket 44a.

The outer circumferential section of the valve holder 44 is provided with a sealing lip section 44c that slides over the inner circumferential surface of the body receiving section 40b of the cylinder inner diameter 40. The sealing lip section 44c separates the brake fluid flowing in the third inner channel 4C into the piston holder 43 from the brake fluid in the main body receiving section 40b.

The sealing lip section 44c corresponds to the "sealing section" of the present invention.

The compression coil spring 45 is housed in the main body accommodating portion 40b of the cylinder inner diameter 40, and one end of the compression coil spring in the axial direction of the cylinder inner diameter 40 is in contact with the valve holder 44, and the other of the compression coil springs The end is in contact with the valve seat member 49 of the discharge side check valve 47.

The outer diameter of the compression coil spring 45 is smaller than the inner diameter of the main body accommodating portion 40b of the cylinder inner diameter 40, and thus the compression coil spring 45 is not in contact with the inner circumferential surface of the main body accommodating portion 40b.

Since the other member is not disposed between the inner circumferential surface of the main body accommodating portion 40b of the cylinder inner diameter 40 and the compression coil spring 45, the main body accommodating portion 40b can be reduced by reducing the inner diameter of the main body accommodating portion 40b. capacity. Here, when the hydraulic controller 1 is attached to the vehicle, evacuation for removing air in the brake hydraulic line in the hydraulic controller 1 is performed to fill the brake hydraulic line with the brake fluid. The main body accommodating section 40b of the cylinder inner diameter 40 due to the structure of the main body accommodating section The air in the air cannot be completely removed. However, since the capacity of the main body accommodating section 40b can be reduced in this embodiment, the remaining amount of air can be reduced.

The suction side check valve 46 is disposed on the other end side of the piston 41 which is away from the cylinder inner diameter 40 of the cylinder inner diameter 40, and restricts the reverse flow of the brake fluid in the main body housing section 40b of the suction cylinder inner diameter 40. .

The suction side check valve 46 includes a ball 46a, a valve seat 46b, and a pressing spring 46c. The ball 46a is held in the ball basket 44a of the valve holder 44. The valve seat 46b is formed in an opening on the other end side of the cylinder inner diameter 40 of the end surface of the piston holder 43. In the ball basket 44a of the valve holder 44, the pressing spring 46c presses the ball 46a against the valve seat 46b on the other end side away from the cylinder inner diameter 40.

Since the suction side check valve 46 is disposed on the other end side of the piston 41 which is away from the cylinder inner diameter 40 of the cylinder inner diameter 40, the volume of the base body 10 can be reduced.

When the ball 46a is separated from the valve seat 46b by the negative pressure generated in the brake fluid in the main body accommodating section 40b when the piston 41 moves to one end side of the cylinder inner diameter 40, the urging force against the squeezing spring 46c is separated from the valve seat 46b. Suction side check valve 46. In this way, the brake fluid in the third internal passage 4C flows into the piston holder 43. Conversely, when the ball 46a rises due to the hydraulic pressure of the brake fluid in the main body accommodating section 40b which occurs when the piston 41 moves to the other end side of the cylinder inner diameter 40, and contacts the valve due to the urging force of the squeezing spring 46c At the seat 46b, the suction side check valve 46 is closed. In this way, the reverse flow in the brake fluid in the main body receiving section 40b to the gripper channel 43b of the piston holder 43 is restricted.

The discharge side check valve 47 is disposed on the other end side of the cylinder inner diameter 40 away from the suction side check valve 46 in the cylinder inner diameter 40, and restricts the brake fluid discharged from the main body accommodation section 40b of the cylinder inner diameter 40. The reverse flow.

The discharge side check valve 47 includes a ball 47a, a valve seat member 49 having a valve seat 47b, and a pressing spring 47c. The ball 47a is a valve body that is held in the ball receiving section 48a of the cover 48. The valve seat member 49 is disposed on an end side of the cylinder inner diameter 40 away from the ball 47a, and is fixed to the base body 10. The valve seat member 49 has an opening formed at the center of the main body receiving portion 40b of the cylinder inner diameter 40, that is, the valve seat 47b. In the ball receiving portion 48a of the cover 48, the pressing spring 47c presses the ball 47a against the valve seat 47b on the other end side away from the cylinder inner diameter 40.

When the ball 47a is separated from the valve seat 47b by the urging force of the pressing spring 47c due to the pressure increase of the hydraulic fluid in the main body accommodating section 40b when the piston 41 moves to the other end side of the cylinder inner diameter 40, The discharge side check valve 47. In this way, the brake fluid in the main body accommodating section 40b of the cylinder inner diameter 40 flows out into the first inner passage 4A. Conversely, when the ball 47a contacts the valve seat 47b due to the negative pressure generated in the brake fluid in the main body accommodating section 40b when the piston 41 moves to one end side of the cylinder inner diameter 40 and due to the urging force of the pressing spring 47c At this time, the discharge side check valve 47 is closed. In this manner, the reverse flow in the first internal channel 4A is limited to the reverse flow in the body receiving section 40b of the cylinder inner diameter 40.

The valve seat member 49 includes an annular projecting section 49a and a recessed section 49b. The outer circumferential surface of the annular projecting section 49a is press-fitted to the large diameter main body receiving section 40b3 of the cylinder inner diameter 40, and the diameter of the large diameter main body receiving section 40b3 is larger than the main body receiving section 40b. The concave section 49b is formed on the inner side of the annular projecting section 49a, and the recessed section receives the compression coil spring 45 at a surface on one end side of the cylinder inner diameter 40. The opening of the valve seat member 49 serving as the valve seat 47b of the discharge side check valve 47 is formed in the surface of the valve seat member 49 on the other end side of the cylinder inner diameter 40. The opening is coaxial with the axis of the cylinder bore 40. In addition, the opening has a tapered shape.

In a state projected on a surface orthogonal to the axial direction of the cylinder inner diameter 40, the concave section 49b The projection line of the inner surface is located on the inner side of the projection line of the inner circumferential surface of the main body accommodating section 40b in the cylinder inner diameter 40. The recessed section 49b has a circular cross-sectional shape in a direction orthogonal to the axial direction of the cylinder inner diameter 40, and is coaxial with the cylinder inner diameter 40. Therefore, the compression coil spring 45 is restrained from coming into contact with the inner circumferential surface of the cylinder inner diameter 40 in a state restricted by the concave portion 49b.

The cover 48 closes the cylinder bore 40 at the other end of the cylinder bore 40.

A ball accommodating portion 48a recessed to the other end side of the cylinder inner diameter 40 is formed at the center of the surface of the cover 48 on one end side of the cylinder inner diameter 40. A projecting section 48b for restricting the pressing spring 47c of the discharge side check valve 47 is provided in the end surface of the ball receiving section 48a on the other end side of the cylinder inner diameter 40. The cover 48 is received in the cover receiving section 40c of the cylinder inner diameter 40.

The cover 48 has an annular projecting section 48c that protrudes to one of the end sides of the cylinder inner diameter 40. The annular projecting section 48c surrounds the outer circumference of the valve seat member 49, which is formed to have an annular projecting section 49a, and the cover 48 is fitted to the valve seat member 49. Further, a gap for communicating between the ball accommodating portion 48a and the first inner channel 4A is formed between the cover 48 and the valve seat member 49. The cover 48 is slid and fixed to the base body 10 in a state of being housed in the cylinder inner diameter 40.

<Operation of Pump Element 2B>

In the pump element 2B having the configuration described above, the piston 41 reciprocates by the eccentric rotational movement of the drive mechanism 2A. When the piston 41 moves to the other end side of the cylinder inner diameter 40, the hydraulic pressure of the brake fluid in the main body accommodating section 40b is boosted, and the discharge side check valve 47 is opened to discharge the brake fluid to the first internal passage. 4A. Conversely, when the piston 41 moves to one end side of the cylinder inner diameter 40, the suction side check valve 46 is opened by the negative pressure of the hydraulic pressure of the brake fluid in the main body accommodating section 40b, and the brake fluid is supplied from the third interior. The channel 4C is inhaled. As described above The cycle is repeated and the hydraulic pressure of the brake fluid in the first internal channel 4A is boosted.

<Method for manufacturing a pump element 2B>

(first process)

The piston 41 to which the O-ring 42 is attached, the piston holder 43 that clamps the piston 41, and the integrated component and compression screw of the valve holder 44 that meshes with the piston holder 43 and clamps the suction side check valve 46 The spring 45 is sequentially inserted into the cylinder bore 40 from the other end side of the cylinder opening inner diameter opening section 50.

(second process)

Fig. 5 is an explanatory view showing an inserted state of a cover 48 of a pump element 2B according to an embodiment of the present invention. Note that in FIG. 5, in a state in which the large-diameter outer circumferential section 48d of the cover 48 starts to be inserted into the end section of the guide section 40c1 on the other end side of the cylinder inner diameter 40, each member is The solid line depicts, and in the state in which the insertion of the large-diameter outer circumferential section 48d of the cover 48 on the end section of the guide section 40c1 on one end side of the cylinder inner diameter 40 is completed, the cross section and compression of the cover 48 The cross section of the end section of the coil spring 45 is depicted by a double dotted chain.

After the first process, the integrated member of the valve seat member 49 and the cover 48 combined with the discharge side check valve 47 is press-fitted from the other end side of the cylinder inner diameter to the cylinder inner diameter 40, and the annular projection of the valve seat member 49 The outer circumferential surface of the segment 49a is joined to the inner circumferential surface of the large diameter main body receiving portion 40b3 of the cylinder inner diameter 40.

Here, the guiding section 40c1 of the large-diameter outer circumferential section 48d of the guiding cover 48 is formed in the inner diameter 40 of the cylinder accommodating section 40c of the cylinder inner diameter 40 when the cover 48 is inserted into the inner side of the cylinder inner diameter 40. In the area on the other end side. The length L of the guiding section 40c1 in the axial direction of the cylinder inner diameter 40 is closer to the closest from the piston 41 by the reciprocating motion The compression length S of the natural length of the compression coil spring 45 in the state of the position on one end side of the cylinder inner diameter 40 is long. Further, the length L of the guiding section 40c1 in the axial direction of the cylinder inner diameter 40 is preferably smaller than the compression from the state in which the piston 41 is moved to the position closest to the other end side of the cylinder inner diameter 40 by the reciprocating motion. The natural length of the coil spring 45 has a long compression length S.

That is, when the cover 48 is inserted into the cylinder inner diameter 40 after the first process, the large diameter outer circumferential section 48d of the cover 48 is guided by the guide section 40c1. Subsequently, in the initial stage of the large-diameter outer circumferential section 48d of the cover 48 guided by the guiding section 40c1, the recessed section 49b of the valve seat member 49 does not receive the compression coil spring 45 in the natural length, and thus a space Formed between the concave section and the compression coil spring. Note that, as depicted in FIG. 5, a state in which the end section of the compression coil spring 45 in the natural length can be located on the inner side of the annular projecting section 49a can be employed.

Thereafter, when the cover 48 is pressed by the length L of the guiding portion 40c1, in the intermediate stage, the concave portion 49b of the valve seat member 49 is brought into a state of receiving the compression coil spring 45 in the natural length. Subsequently, the compression coil spring 45 is compressed, and the outer circumferential surface of the annular projecting portion 49a of the valve seat member 49 is press-fitted and joined to the inner circumferential surface of the large-diameter main body receiving portion 40b3 of the cylinder inner diameter 40.

Subsequently, at a stage after the press fitting, the concave section 49b of the valve seat member 49 that receives the end section of the compression coil spring 45 compresses the compression coil spring 45 by the compression length S.

(third process)

After the second process, the inner circumferential surface of the cap accommodating section 40c of the cylinder inner diameter 40 is joined to the outer circumferential surface of the cover 48 by the splicing.

That is, a portion of the guiding section 40c1 of the cap accommodating section 40c of the cylinder inner diameter 40 is partially The engagement is joined to the outer circumferential surface of the cover 48.

<The role of hydraulic controller 1>

FIG. 6 is an explanatory view depicting a pump element 202B according to a comparative example.

In the pump element 202B according to the comparative example, the inflow side check valve 246 is provided intermediate the third inner channel 4C extending from the accumulator section toward the pump device 202. In addition, a cylinder member 250 for surrounding and holding the compression coil spring 245 is provided in the built-in inner diameter 240 formed in the base body 210. Therefore, each of the components such as the inflow side check valve 246 and the cylinder member 250 occupies a large capacity inside the base body 210, which results in amplification of the unified hydraulic controller.

In contrast, according to the embodiment, the cylinder inner diameter 40 is formed in the base body 10, the pump element 2B is assembled in the cylinder inner diameter 40 without the cylinder member, and the suction side check valve 46 is in the cylinder inner diameter 40. Positioned between the piston 41 and the other end of the cylinder bore 40. With this configuration, the capacity of the base body 10 increased by each of the components such as the cylinder member and the suction side check valve can be reduced, and thus the unified hydraulic controller 1 can be downsized.

Preferably, in a state projected on a surface orthogonal to the axial direction of the cylinder inner diameter 40, the projection line of the inner surface of the concave portion 49b of the valve seat member 49 is located in the main body receiving area in the cylinder inner diameter 40. On the inner side of the projection line of the inner circumferential surface of the segment 40b. With this configuration, in a state where the concave section 49b receives the end section of the compression coil spring 45 on the other end side of the cylinder inner diameter 40, the compression coil spring 45 is suppressed from being opposed to the body of the cylinder inner diameter 40 The inner circumferential surface of the receiving section 40b is in contact. Therefore, the abutment of the compression coil spring 45 against the inner circumferential surface of the main body accommodating portion 40b and the generation of abrasion powder or the like are suppressed.

Preferably, the recessed section 49b of the valve seat member 49 is at the axis of the cylinder inner diameter 40 It has a circular cross-sectional shape in the orthogonal direction and is coaxial with the cylinder inner diameter 40. With this configuration, the manufacturability of the recessed section 49b of the valve seat member 49 is improved, and the cost performance of the hydraulic controller 1 is improved.

Preferably, the length L of the guide portion 40c1 in the axial direction of the cylinder inner diameter 40 is larger than that from the compression coil spring in a state where the piston 41 is moved to the position closest to one end side of the cylinder inner diameter 40 by the reciprocating motion. The natural length of 45 has a compression length S long. With this configuration, the state in which the cover 48 is guided by the guide section 40c1 of the cover accommodating section 40c can be achieved in a state where the compression coil spring 45 has a natural length. Therefore, when the press fit is started in the second process, the necessity of positioning the cover 48 when inserting the cover 48 into the inner side of the cover accommodating section 40c in a manner of being pressed against the compression coil spring 45 is reduced, and thus the assembly is improved. Processability.

Preferably, the length L of the guiding portion 40c1 in the axial direction of the cylinder inner diameter 40 is larger than the compression spiral from the state in which the piston 41 is moved to the position closest to the other end side of the cylinder inner diameter 40 by the reciprocating motion. The compression length S of the natural length of the spring 45. With this configuration, the state in which the cover 48 is guided by the guide section 40c1 of the cover accommodating section 40c can be achieved in a state where the compression coil spring 45 has a natural length irrespective of the position of the piston 41. Therefore, the improvement of assembly processability is ensured.

Preferably, at least a portion of the guiding section 40c1 is joined to the outer circumferential surface of the cover 48 by the engagement. With this configuration, the sealing state can be ensured without the need for another component, the manufacturability can be improved, and the cost performance of the hydraulic controller 1 can be improved.

Preferably, the outer circumferential section of the valve holder 44 is formed to have a sealing lip section 44c that slides over the inner circumferential surface of the body receiving section 40b of the cylinder inner diameter 40. That is, the brake fluid flowing into the piston holder 43 in the third inner channel 4C A sealing lip section 44c that is separated from the brake fluid in the main body receiving section 40b is integrally provided in the valve holder 44. With this configuration, the configuration is simplified and the cost performance of the hydraulic controller 1 is improved.

Preferably, an electronic control unit 7 for controlling the pump device 2 is further included. With this configuration, each component can be unified, and thus the hydraulic controller 1 is further compacted.

Preferably, the hydraulic controller 1 is preferably incorporated in the locomotive. The need for downsizing of the hydraulic controller 1 is particularly high for locomotives. In the hydraulic controller 1, a cylinder inner diameter 40 is formed in the base body 10. In addition, the suction side check valve 46 is disposed between the piston 41 and the other end of the cylinder inner diameter 40 in the cylinder inner diameter 40. In this way, the hydraulic controller 1 is downsized. This is especially advantageous for installation in a locomotive.

Further, according to the embodiment, the hydraulic controller 1 is manufactured by a process in which the piston 41, the suction side check valve 46, and the compression coil spring 45 are inserted into the cylinder inner diameter 40 from the other end side of the cylinder inner diameter. a second process in which the integrated discharge side check valve 47 and the cover 48 are press-fitted from the other end side of the cylinder inner diameter to the cylinder inner diameter 40, and the outer circumferential surface of the valve seat member 49 is engaged after the first process To the inner circumferential surface of the cylinder inner diameter 40; and a third process in which the inner circumferential surface of the cylinder inner diameter 40 is joined to the outer circumferential surface of the cover 48 by the engagement after the second process. Therefore, the manufacturing process is simplified, and the cost performance and the like of the hydraulic controller 1 are improved.

Claims (10)

A hydraulic controller that controls hydraulic pressure of a brake hydraulic line, the controller comprising: a base body formed to have an inner diameter of the cylinder, the inner diameter of the inner diameter of the cylinder being in communication with a driving mechanism at an end And the other end of the inner diameter of the cylinder is open; and a pump device that adjusts the hydraulic pressure, wherein the pump device comprises: a piston disposed in the inner diameter of the cylinder and operating in one of the driving mechanisms Interlocking mode reciprocating; a compression spring disposed in the inner diameter of the cylinder and pushing the piston from the other end side of the piston to a distal end side; and a suction side check valve in the cylinder A bore is disposed between the piston and the other end and restricts a flow of one of the brake fluids drawn into the inner diameter of the cylinder to flow in the opposite direction. The hydraulic controller of claim 1, wherein the pump device further comprises: a discharge side check valve disposed between the suction side check valve and the other end in the inner diameter of the cylinder, and Restricting a reverse flow of one of the brake fluids discharged from the inner diameter of the cylinder, the discharge side check valve comprising: a valve seat member disposed in the inner diameter of the cylinder and formed to have a concave section for use Receiving the compression spring in a surface of the valve seat member on the one end side; and in a state of being projected on a surface orthogonal to the axial direction of the inner diameter of the cylinder, the recess One of the projection lines of one of the inner surfaces of the segment is located on one of the projection lines of one of the circumferential surfaces of one of the inner diameters of the cylinder. The hydraulic controller of claim 2, wherein the recessed section has a circular cross-sectional shape in a direction orthogonal to the axial direction of the cylinder inner diameter and is coaxial with the cylinder inner diameter. The hydraulic controller according to any one of claims 1 to 3, wherein the pump device further comprises: a cover inserted into the inner diameter of the cylinder from the other end side, and closing the inner diameter of the cylinder The other end, a guiding section that guides an outer circumferential surface of the cover at a time when the cover is inserted into the inner diameter of the cylinder, the guiding section being formed at the other end of the inner diameter of the cylinder, and The length of the guiding section in the axial direction of the inner diameter of the cylinder is greater than the natural length of the compression spring in a state in which the piston is moved to a position closest to the one end side by the reciprocating motion Long length. The hydraulic controller of claim 4, wherein the length of the guiding section in the axial direction of the inner diameter of the cylinder is from the movement of the piston to the side closest to the other end by the reciprocating motion The compressed length of the natural length of the compression spring in a state of a position is long. A hydraulic controller according to claim 4 or 5, wherein at least a portion of the guiding section is joined to the outer circumferential surface of the cover by a convergence. The hydraulic controller of any one of claims 1 to 6, wherein the pump device further comprises: a holder attached to the other end side of the piston in the inner diameter of the cylinder, and Holding the suction side check valve when receiving the compression spring, and A sealing section that slides over the inner circumferential surface of the inner diameter of the cylinder, the sealing section being formed in an outer circumferential section of the holder. A hydraulic controller according to any one of claims 1 to 7, further comprising: an electronic control panel that controls the pump device. A hydraulic controller according to any one of claims 1 to 8, which is incorporated in a locomotive. A method for manufacturing a hydraulic controller, the controller comprising: a base body formed to have a cylinder inner diameter, the inner diameter of the cylinder is connected to a drive mechanism at an end in an axial direction, and the cylinder The other end of the diameter is open; and a pumping device that adjusts the hydraulic pressure, the pump device comprising: a piston disposed in the inner diameter of the cylinder and reciprocating in an interlocking manner with operation of one of the drive mechanisms; a compression spring disposed in the inner diameter of the cylinder and pushing the piston from the other end side of the inner diameter of the cylinder to a distal end side; a suction side check valve disposed in the inner diameter of the cylinder a reverse flow between the piston and the other end and restricting suction into one of the brake fluids in the inner diameter of the cylinder; a discharge side check valve disposed in the suction side check valve in the inner diameter of the cylinder Between the other ends, and restricting reverse flow of one of the brake fluid discharged from the inner diameter of the cylinder; and a cover for closing the other end of the inner diameter of the cylinder, and the discharge side check valve Including: a valve seat member, Disposed in the cylinder inner diameter, and having a concave section is formed to use Receiving the compression spring in a surface of the valve seat member on the end side, the method for manufacturing the hydraulic controller includes: a first process for the piston, the suction side a check valve and the compression spring are inserted into the inner diameter of the cylinder from the other end side; a second process for integrating the discharge side check valve and the cover from the other after the first process a tip side press fit into the inner diameter of the cylinder and engaging an outer circumferential surface of one of the valve seat members to an inner circumferential surface of one of the inner diameters of the cylinder; and a third process for borrowing after the second process The inner circumferential surface of the inner diameter of the cylinder is joined to the outer circumferential surface of one of the covers by the convergence.