JP2004316858A - Liquid controlling solenoid valve - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a liquid controlling solenoid valve with a base having a mounting hole and an inlet side passage opening to the inner face of the middle of the mounting hole and with a valve housing inserted and fixed into the mounting hole and having a plurality of inlet ports communicating with a valve chamber formed in the valve housing, wherein a filter having an annular passage communicated with the inlet side passage and formed between the inner face of the mounting hole and itself is mounted on the outer periphery of the valve housing for filtering liquid in the annular passage and introducing it to the inlet port side, the filter being prevented from increasing its distribution resistance in a cold weather when the liquid has more viscosity. <P>SOLUTION: An annular recessed portion 60 forming part of the annular passage 35 and encircling the filter 40 is provided on the inner face of the middle of the mounting hole 32 so as to open the inlet side passage 36. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

[0001]
TECHNICAL FIELD OF THE INVENTION
The present invention relates to a liquid control solenoid valve, in particular, a base, provided with a mounting hole, an inlet-side passage opening in the inner surface of the intermediate portion of the mounting hole, inserted into the mounting hole, fixed to the valve housing, A plurality of inlet ports are provided to communicate with a valve chamber formed in the valve housing, and a filter that forms an annular path between the inlet side passage and the inner surface of the mounting hole filters liquid in the annular path. The present invention relates to an improvement of a liquid control solenoid valve mounted on the outer periphery of the valve housing so as to be introduced to the inlet port side.
[0002]
[Prior art]
Conventionally, such a liquid control solenoid valve is already known, for example, from Patent Document 1 and the like, in which a filter is formed by forming an annular path between the mounting hole and a straight inner surface at an intermediate portion of the mounting hole. It is mounted on the outer periphery of the housing.
[0003]
[Patent Document 1]
JP-A-9-60756
[Problems to be solved by the invention]
However, in the above conventional device, there is only a slight gap between the outer periphery of the filter and the inner surface of the mounting hole, and the width of the annular path surrounding the filter is narrow over the entire circumference. For this reason, when a liquid such as a brake fluid, which increases in viscosity in cold weather, is controlled by an electromagnetic valve, the liquid flowing from the inlet passage into the annular passage does not flow smoothly over the entire periphery of the annular passage, and the filter does not flow. The air flows only in a part in the circumferential direction, and the flow resistance in the filter may increase.
[0005]
The present invention has been made in view of such circumstances, and it is an object of the present invention to provide a liquid control solenoid valve in which the flow resistance in a filter does not increase even in cold weather when the viscosity of the liquid increases. Aim.
[0006]
[Means for Solving the Problems]
In order to achieve the above object, the present invention provides a valve housing, in which a base is provided with a mounting hole and an inlet-side passage opening in an inner surface of an intermediate portion of the mounting hole, and inserted and fixed in the mounting hole. A plurality of inlet ports are provided to communicate with a valve chamber formed in the valve housing, and a filter that forms an annular path between the inlet side passage and the inner surface of the mounting hole filters liquid in the annular path. In the liquid control solenoid valve mounted on the outer periphery of the valve housing so as to be introduced into the inlet port side, an annular concave part which forms a part of the annular path and surrounds the filter is formed in the inlet side passage. Is provided on the inner surface of the intermediate portion of the mounting hole so as to open the opening.
[0007]
According to such a configuration, the width of the annular passage surrounding the filter is relatively wide over the entire periphery thereof, so that the liquid flowing into the annular passage from the inlet passage smoothly flows over the entire periphery of the annular passage. Since the liquid can be evenly distributed in the circumferential direction, it is possible to prevent an increase in the flow resistance in the filter even in cold weather when the viscosity of the liquid increases.
[0008]
BEST MODE FOR CARRYING OUT THE INVENTION
Hereinafter, an embodiment of the present invention will be described based on an embodiment of the present invention shown in the attached drawings.
[0009]
1 to 5 show an embodiment of the present invention. FIG. 1 is a brake hydraulic circuit diagram of a vehicle brake device, FIG. 2 is a longitudinal sectional view showing a suction valve in a closed state, and FIG. FIG. 4 is a cross-sectional view corresponding to FIG. 2 when the second valve mechanism is in an open state, and FIG. 5 corresponds to FIG. 2 when the first valve mechanism is in an open state. FIG.
[0010]
First, in FIG. 1, a tandem type master cylinder M is provided with first and second output ports 1A and 1B for generating a brake fluid pressure according to a depression force applied to a brake pedal P by a vehicle driver, and is used for a left front wheel. Wheel brake 2A, right rear wheel brake 2B, right front wheel brake 2C, left rear wheel brake 2D, and first and second individually connected to the first and second output ports 1A, 1B. A brake hydraulic pressure control device 4 is provided between the output hydraulic pressure passages 3A and 3B.
[0011]
The brake fluid pressure control device 4 includes cut valves 5A and 5B, which are normally-open solenoid valves connected to the first and second output fluid pressure paths 3A and 3B, respectively, one of the cut valves 5A and the left front wheel brake. Inlet valves 6A and 6B, which are normally open solenoid valves provided between 2A and the right rear wheel brake 2B, respectively, and between the other cut valve 5B and the right front wheel brake 2C and the left rear wheel brake 2D. The inlet valves 6C and 6D, which are normally open solenoid valves, respectively, the check valves 7A to 7D connected in parallel to the respective inlet valves 6A to 6D, and the first and second output hydraulic lines 3A and 3B. Normally closed first and second reservoirs 8A and 8B respectively provided between the first reservoir 8A and the left front wheel brake 2A and the right rear wheel brake 2B. Outlet valves 9A and 9B which are solenoid valves, outlet valves 9C and 9D which are normally closed solenoid valves provided between the second reservoir 8B and the right front wheel brake 2C and the left rear wheel brake 2D, respectively. A first pump 10A whose suction side is connected to one reservoir 8A and whose discharge side is connected between cut valve 5A and inlet valves 6A and 6B, and a second reservoir 8B whose suction side is connected and whose discharge side is cut valve 5B and inlet. A second pump 10B connected between the valves 6C and 6D, one common electric motor 11 for driving the two pumps 10A and 10B, first and second output hydraulic lines 3A and 3B, and first and second Suction valves 12A and 12B, which are normally closed solenoid valves interposed between the suction sides of the pumps 10A and 10B, respectively, and the first and second pumps 10A and 10B. First and second dampers 13A and 13B to which the outlet sides are respectively connected, and first and second orifices 14A and 14B provided between the first and second pumps 10A and 10B and the first and second dampers 13A and 13B, respectively. And check valves 15A, 15B interposed between the first and second pumps 10A, 10B and the first and second reservoirs 8A, 8B so as to allow the flow of brake fluid to the respective pumps 10A, 10B. And a pressure sensor 16 attached to the second output hydraulic pressure passage 3B, and a pressure sensor 16 parallel to the cut valves 5A and 5B so as to allow the flow of the brake fluid only from the first and second output hydraulic pressure passages 3A and 3B. And one-way valves 18A, 18B connected to the cut valves 5A, 5B, and relief valves 19A, 19B connected in parallel to the cut valves 5A, 5B.
[0012]
The suction valves 12A and 12B are connected between the first and second pumps 10A and 10B and the check valves 15A and 15B, and the outlet valves 9A to 9D are connected between the check valves 15A and 15B and the first and second reservoirs 8A and 8B. Connected respectively. The cut valves 5A, 5B and the one-way valves 18A, 18B are provided between the hydraulic passages 20A, 20B and the output hydraulic passages 3A, 3B connected to the pumps 10A, 10B via orifices 14A, 14B and dampers 13A, 13B. Further, the relief valves 19A and 19B are interposed, and the relief valves 19A and 19B are opened according to the hydraulic pressure of the hydraulic passages 20A and 20B being equal to or higher than a predetermined value.
[0013]
Such a brake fluid pressure control device 4 communicates between the master cylinder M and the wheel brakes 2A to 2D during normal braking when there is no possibility that each wheel locks, and also connects between the wheel brakes 2A to 2D and the reservoirs 8A and 8B. Cut off. That is, with the cut valves 5A and 5B demagnetized and opened, and the suction valves 12A and 12B demagnetized and closed, the inlet valves 6A to 6D are demagnetized and opened, and the outlet valves 9A to 9D are changed. The brake fluid pressure output from the first output port 1A of the master cylinder M is demagnetized and closed, and is applied to the left front wheel and right rear wheel brakes 2A and 2B via the cut valve 5A and the inlet valves 6A and 6B. Works. The brake fluid pressure output from the second output port 1B of the master cylinder M acts on the right front wheel and left rear wheel brakes 2C, 2D via the cut valve 5B and the inlet valves 6C, 6D.
[0014]
When the wheels are about to enter the locked state during the braking, the brake fluid pressure control device 4 establishes a connection between the master cylinder M and the wheel brakes 2A to 2D at a portion corresponding to the wheels about to enter the locked state. It shuts off and communicates between the wheel brakes 2A to 2D and the reservoirs 8A and 8B. That is, among the inlet valves 6A to 6D, the inlet valve corresponding to the wheel which is about to enter the locked state is excited and closed, and the outlet valve corresponding to the wheel among the outlet valves 9A to 9D is excited and opened. Is done. As a result, a part of the brake fluid pressure of the wheel that is about to enter the locked state is absorbed by the first reservoir 8A or the second reservoir 8B, and the brake fluid pressure of the wheel that is about to enter the locked state is reduced. Will be.
[0015]
When the brake fluid pressure is kept constant, the brake fluid pressure control device 4 enters a state in which the wheel brakes 2A to 2D are cut off from the master cylinder M and the reservoirs 8A and 8B. That is, the inlet valves 6A to 6D are excited and closed, and the outlet valves 9A to 9D are demagnetized and closed. When the brake fluid pressure is further increased, the inlet valves 6A to 6D may be demagnetized and opened, and the outlet valves 9A to 9D may be demagnetized and closed.
[0016]
By demagnetizing and opening the cut valves 5A and 5B and demagnetizing and closing the suction valves 12A and 12B in this manner, the demagnetization and excitation of each of the inlet valves 6A to 6D and each of the outlet valves 9A to 9D are controlled. Thus, braking can be efficiently performed without locking the wheels.
[0017]
By the way, during the above-described antilock brake control, the electric motor 11 rotates and the first and second pumps 10A and 10B are driven by the operation of the electric motor 11, so that the first and second pumps are driven. The brake fluid absorbed by the reservoirs 8A, 8B is sucked into the first and second pumps 10A, 10B, and then passes through the first and second dampers 13A, 13B to the first and second output hydraulic lines 3A, 3B. It is refluxed. By such a return of the brake fluid, it is possible to prevent an increase in the amount of depression of the brake pedal P due to the absorption of the brake fluid in the first and second reservoirs 8A and 8B. In addition, the pulsation of the discharge pressure of the first and second pumps 10A and 10B is suppressed by the functions of the first and second dampers 13A and 13B and the first and second orifices 14A and 14B. The ring is not disturbed.
[0018]
Further, the brake fluid pressure control device 4 drives the first and second pumps 10A and 10B by the electric motor 11 when the brake is not operated, and controls the opening and closing of the cut valves 5A and 5B in addition to the above-described antilock brake control. Thus, it is possible to perform side slip control and traction control of the vehicle.
[0019]
The pressure sensor 16 detects whether or not the hydraulic pressure is output from the master cylinder M, that is, whether or not the brake pedal P is depressed. It is used for controlling the number of revolutions of the electric motor 11 according to the output hydraulic pressure of M, and the like.
[0020]
Thus, for example, during side slip control, the cut valves 5A and 5B are energized and closed, the suction valves 12A and 12B are energized and opened, and the first and second pumps 10A and 10B are operated by the operation of the electric motor 11. When driven, the inlet valves other than the inlet valve corresponding to the wheel to be braked among the inlet valves 6A to 6D are excited and closed.
[0021]
Accordingly, both pumps 10A and 10B suck the brake fluid of the master cylinder M from the first and second output ports 1A and 1B via the first and second output hydraulic pressure paths 3A and 3B and the suction valves 12A and 12B. The brake fluid is supplied to the selected one of the wheel brakes 2A to 2D via the opened one of the inlet valves 6A to 6D, and the brake fluid flows back to the master cylinder M side. Is prevented by the cut valves 5A and 5B being closed.
[0022]
During such side slip control or traction control, if the discharge pressure of the first and second pumps 10A and 10B, that is, the hydraulic pressure between the cut valves 5A and 5B and the inlet valves 6A to 6D exceeds a specified value, the relief valve 19A , 19B, the excess hydraulic pressure is released to the master cylinder M side, thereby preventing the excessive hydraulic pressure from acting on the inside of the wheel brake on which the brake pressure is acting or within the hydraulic pressure control device 4.
[0023]
By the way, the suction valves 12A and 12B are configured according to the present invention, and the details thereof will be described below. However, since both suction valves 12A and 12B have the same configuration, one suction valve 12A Only the details of the configuration will be described, and description of the other suction valve 12B will be omitted.
[0024]
2, a suction valve 12A has a thin cylindrical valve housing 22 provided with an outlet port 27 at one end and a plurality of inlet ports 28, 28,. A fixed core 23 fixed to the valve housing 22 so as to close the end in a liquid-tight manner; a movable core 24 housed in the valve housing 22 opposite to the fixed core 23; A first return spring 25 which exerts a spring force for separating the core 23 from the core 23; a coil 26 which exerts an electromagnetic force for attracting the movable core 24 to the fixed core 23 during excitation; an outlet port 27 and inlet ports 28, 28 .. Are provided with first and second valve mechanisms 29 and 30 interposed therebetween.
[0025]
Referring to FIG. 3 as well, an enlarged diameter portion 22b bulging radially outward while forming a stepped portion 22a which is tapered and faces the other end in the axial direction, for example, is formed at an intermediate portion in the axial direction of the valve housing 22. The enlarged diameter portion 22b is formed in a plurality of steps, for example, three steps so as to gradually decrease in diameter toward one end side in the axial direction of the valve housing 22, and is provided at an intermediate portion of the enlarged diameter portion 22b. The plurality of inlet ports 28 are provided.
[0026]
One end of the valve housing 22 is inserted into and fixed to the base 31. The base 31 has a mounting hole 32 for inserting one end of the valve housing 22 including the stepped portion 22a and the enlarged diameter portion 22b. Is provided. The mounting hole 32 includes a small-diameter hole 32a, a medium-diameter hole 32b having a diameter larger than the small-diameter hole 32a, and a large-diameter hole 32c having a diameter larger than the medium-diameter hole 32b. The small-diameter hole portion 32a is formed so as to have a diameter capable of fitting one end of the valve housing 22 deviated from the enlarged-diameter portion 22b, and the large-diameter hole portion is formed. The other end of 32c is opened to the outer surface of the base 31.
[0027]
A ring-shaped pressing member 33 is mounted on the outer periphery of the valve housing 22 so as to abut and engage the other ends of the step portion 22a and the enlarged diameter portion 22b. When the retaining ring 34 mounted on the inner surface near the outer end of 32a comes into contact with and engages with the pressing member 33, the valve housing 22 is prevented from being detached from the mounting hole 32, and is inserted and fixed into the base 31. You.
[0028]
The base 31 is provided with an inlet passage 36 communicating with the first output hydraulic pressure passage 3 </ b> A, and is connected to the outlet port 27 of the valve housing 22 so as to be coaxial with the small diameter hole 32 a of the mounting hole 32. An outlet passage 37 is connected to the suction side of the first pump 10A.
[0029]
On the outer periphery of the valve housing 22, a filter 40 for forming an annular passage 35 between the annular passage 35 and the inner surfaces of the medium-diameter hole portion 32b and the large-diameter hole portion 32c in the mounting hole 32 is provided. Are filtered and introduced into the inlet ports 28, 28... Side. Moreover, an annular concave portion 60 that forms a part of the annular passage 35 and surrounds the filter 40 is provided on the inner surface of the mounting hole 32 in the middle of the large-diameter hole portion 32c so as to open the inlet-side passage 36.
[0030]
An O-ring 38 is mounted on the outer periphery of the other end of the valve housing 22 between the annular passage 35 and the outlet side passage 37, and an O-ring 39 sandwiching the annular passage 35 between the annular passage 35 and the O-ring 38 is provided in the valve housing 22. It is mounted on the other end of the enlarged diameter portion 22b, that is, on the outer periphery of the largest diameter portion.
[0031]
As described above, the diameter of the O-ring 38 that resiliently contacts the inner surface of the mounting hole 32 is smaller than the diameter of the O-ring 39 that resiliently contacts the inner surface of the mounting hole 32. Thus, when the valve housing 22 is inserted into the mounting hole 32 and assembled, the O-ring 38 can be prevented from being damaged by contact with the inner surface of the mounting hole 32 as much as possible. Since the force required for inserting and assembling is small, it is easy to insert and assemble.
[0032]
The fixed core 23 is liquid-tightly welded to the other end of the valve housing 22 by laser welding or the like. The portion of the valve housing 22 protruding from the base 31 and the fixed core 23 are inserted through the bobbin 41, and the coil 26 is wound around the bobbin 41. A coil case 42 made of a magnetic material and covering the bobbin 41 and the coil 26 is magnetically coupled to the fixed core 23. Thus, the movable core 24 is attracted toward the fixed core 23 by the electromagnetic force exerted by the coil 26 when the coil 26 is excited.
[0033]
The first valve mechanism 29 is provided with a movable seat member 44 that enables axial relative movement within a limited range with respect to the movable core 24 and faces the movable core 24 on a side opposite to the fixed core 23, A second return spring 45 that biases the spring 44 away from the movable core 24, and is provided on the movable core 24 in a valve chamber 43 formed in the valve housing 22 through the inlet ports 28. A spherical first valve portion 46, a first valve seat 47 provided on the movable seat member 44 so that the first valve portion 46 can be seated, and one end communicating with the outlet port 27 and the other end The first valve hole 48 is provided in the movable seat member 44 so as to open at the center of the one valve seat 47.
[0034]
A cylindrical guide cylinder 49 disposed in the valve chamber 43 is coaxially fixed to one end of the movable core 24, and a plurality of guide cylinders 49 are provided on the guide cylinder 49 so as not to partition the valve chamber 43. The communication holes 50 are provided. An end of the movable sheet member 44 on the movable core 24 side is inserted into the guide cylinder 49 so as to be movable in the axial direction. One end of the guide cylinder 49 is connected to the movable sheet member 44 from the side opposite to the movable core 24. An engaging flange 49a that regulates the maximum distance between the movable core 24 and the movable sheet member 44 by being in contact with and engaging with the movable core 24 is provided. That is, the movable sheet member 44 is opposed to the movable core 24 with the axial relative movement range with respect to the movable core 24 being regulated by the guide cylinder 49.
[0035]
A communication groove 51 is provided on the outer surface of the movable core 24 to allow the space between the movable core 24 and the fixed core 23 to communicate with the valve chamber 43.
[0036]
The second valve mechanism 30 forms a valve chamber 43 between the movable core 24 and the valve seat member 52 fitted and fixed to one end of the valve housing 22, and coaxially with the first valve seat 47. A second valve seat 53 is disposed on the valve seat member 52 so as to face the valve chamber 43, and has a larger diameter than the first valve hole 48, communicates with the outlet port 27, and has the center of the second valve seat 53. A second valve hole 54 is provided in the valve seat member 52 so as to open to the portion, and a second valve portion 55 is provided on the outer periphery of the movable seat member 44 so as to be able to sit on the second valve seat 53. You.
[0037]
The valve seat member 52 is formed in a cylindrical shape so as to form a second valve hole 54 having a larger diameter than the first valve hole 48 over the entire length in the axial direction, and is pressed into one end of the valve housing 22 by press fitting or the like. Fitted and fixed. A second valve seat 53 is provided on an end surface of the valve seat member 52 on the valve chamber 43 side, and a second valve portion 55 is provided on an outer periphery of an intermediate portion of the movable seat member 44.
[0038]
The movable seat member 44 is integrally provided with a cylindrical guide portion 57 that is slidably fitted in the second valve hole 54, and an outer surface of the guide portion 57 and an inner surface of the second valve hole 54. In the meantime, when the second valve portion 55 is seated on the second valve seat 53, the second valve portion 55 is disconnected from the valve chamber 43, but when the second valve portion 55 is separated from the second valve seat 53, the valve chamber 43 is closed. An annular passage 58 communicating with the guide portion 57 is formed.
[0039]
In such a suction valve 12A, when the coil 26 is in the demagnetized state, the movable core 24 moves to the side away from the fixed core 23 by the spring force of the first return spring 25 as shown in FIGS. In this state, the first valve portion 46 is seated on the first valve seat 47 and the first valve mechanism 29 is closed, and the second valve portion 55 is seated on the second valve seat 53 and the second valve mechanism The valve 30 is closed, and the connection between the master cylinder M and the first pump 10A is in a shut-off state.
[0040]
When the coil 26 is excited while the master cylinder M is not operated, the movable core 24 is attracted to the fixed core 23 as shown in FIG. As a result, the movable seat member 44 abutting and engaging with the engagement flange 49a of the guide cylinder 49 is also attracted to the fixed core 23 side, and the first valve portion 46 is separated from the first valve seat 47. As a result, the first valve mechanism 29 is opened, the second valve portion 55 is separated from the second valve seat 53, the second valve mechanism 30 is opened, and the communication between the master cylinder M and the first pump 10A is established. It becomes. In this state, the flow passage area between the inlet ports 28, 28,... And the outlet port 27 is relatively large, so that a relatively large amount of brake fluid is sucked from the master cylinder M to the first pump 10A.
[0041]
When the coil 26 is further excited in the operation state of the master cylinder M, the movable core 24 is attracted to the fixed core 23 side as shown in FIG. 5, but the movable core 24 is moved by the hydraulic pressure acting on the valve chamber 43 from the master cylinder M. The liquid pressure that presses the second valve portion 55 of the seat member 44 against the second valve seat 53 becomes larger than the electromagnetic force that attracts the movable core 24 to the fixed core 23 side. As a result, the second valve portion 55 is seated on the second valve seat 53 and the second valve mechanism 30 is closed, but the first valve portion 46 is moved by the spring force of the second return spring 45 and the electromagnetic attraction force of the coil 26. The first valve mechanism 29 is opened by separating from the first valve seat 47. Therefore, the flow passage area between the inlet ports 28, 28,... And the outlet port 27 becomes relatively small, and the brake fluid supplied from the master cylinder M to the first pump 10A is throttled.
[0042]
Next, the operation of this embodiment will be described. In the movable seat member 44, while the second valve portion 55 is seated on the second valve seat 53, the movable seat member 44 is cut off from the valve chamber 43, but the second valve seat 53 In a state where the second valve portion 55 is separated, an annular passage 58 communicating with the valve chamber 43 is formed between the second valve hole 54 and the inner surface of the second valve hole 54 so as to be slidably fitted in the second valve hole 54. The guide part 57 is provided integrally, and the guide part 57 is provided with communication paths 59... That allow the annular path 58 to communicate with the inside of the guide part 57.
[0043]
Therefore, the movable seat member 44 is guided by the guide portion 57 slidably fitted in the second valve hole 54 so as not to be inclined with respect to the axes of the movable core 24 and the second valve seat 53. . As a result, the axis of the movable seat member 44 is prevented from inclining, which also enables the seating seal between the first valve portion 46 and the first valve seat 47 and the sealing between the second valve portion 55 and the second valve seat 53. Any of the seat sealing properties can be reliably maintained.
[0044]
When the second valve portion 55 is separated from the second valve seat 53 and the second valve mechanism 30 is opened, the outlet port from the valve chamber 43 passes through the annular passage 58, the communication passage 59, and the inside of the guide portion 57. A channel leading to 27 is secured.
[0045]
Further, the base 31 is provided with a mounting hole 32 and an inlet-side passage 36 that opens into the inner surface of the intermediate portion of the mounting hole 32, and the valve housing 22 inserted and fixed into the mounting hole 32 is provided with a valve in the valve housing 22. Are provided with a plurality of inlet ports 28 communicating with the chamber 43, and a filter 40 which forms an annular passage 35 communicating with the inlet side passage 36 between the inner surface of the mounting hole 32 and the filter 40 filters the brake fluid in the annular passage 35. Is mounted on the outer periphery of the valve housing 22 so as to be introduced into the inlet ports 28, 28..., And the annular recess 60 forming a part of the annular passage 35 and surrounding the filter 40 is The opening 36 is provided on the inner surface of the intermediate portion of the mounting hole 32 so as to open.
[0046]
Therefore, the width of the annular passage 35 surrounding the filter 40 can be made relatively wide over the entire periphery thereof, and the brake flowing into the annular passage 35 from the inlet side passage 36 flows smoothly over the entire periphery of the annular passage 35, The brake fluid can be distributed evenly in the circumferential direction of the filter 40. This can prevent the flow resistance in the filter 40 from increasing even in cold weather when the viscosity of the brake fluid increases.
[0047]
Although the embodiments of the present invention have been described above, the present invention is not limited to the above embodiments, and various design changes can be made without departing from the present invention described in the claims. It is.
[0048]
For example, in the above-described embodiment, the suction valves 12A and 12B have been described. However, in the present invention, a filter that forms an annular passage leading to the inlet side passage and the inner surface of the mounting hole is mounted on the outer periphery of the valve housing. It can be widely implemented in connection with solenoid valves.
[0049]
【The invention's effect】
As described above, according to the present invention, the liquid flowing from the inlet-side passage into the annular passage smoothly flows over the entire circumference of the annular passage, and the flow resistance of the filter increases even in cold weather when the viscosity of the liquid increases. Can be prevented.
[Brief description of the drawings]
FIG. 1 is a brake hydraulic circuit diagram of a vehicle brake device.
FIG. 2 is a longitudinal sectional view showing the suction valve in a closed state.
FIG. 3 is an enlarged view of a main part of FIG. 2;
FIG. 4 is a cross-sectional view corresponding to FIG. 2 when a second valve mechanism is in an open state;
FIG. 5 is a longitudinal sectional view corresponding to FIG. 2 when the first valve mechanism is in a valve open state.
[Explanation of symbols]
12A, 12B Suction valve 22 as solenoid valve 22 Valve housing 28 Inlet port 31 Base 32 Mounting hole 36 Inlet passage 35 Annular passage 40 ... Filter 43 ... Valve chamber 60 ... Circular recess

Claims (1)

A base (31) is provided with a mounting hole (32) and an inlet-side passage (36) opening in the inner surface of an intermediate portion of the mounting hole (32), and the valve housing is inserted and fixed in the mounting hole (32). The (22) is provided with a plurality of inlet ports (28) communicating with a valve chamber (43) formed in the valve housing (22), and the annular passage (35) communicating with the inlet-side passage (36) is formed in the annular passage (35). A filter (40) formed between the valve housing (22) and the inner surface of the mounting hole (32) filters the liquid in the annular passage (35) and introduces the liquid into the inlet port (28). In the liquid control solenoid valve mounted on the outer periphery of the filter, an annular concave portion (60) which forms a part of the annular passage (35) and surrounds the filter (40) opens the inlet side passage (36). In the mounting hole (32) Liquid control solenoid valve, characterized in that provided on the portion surface.

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