JP2003042329A - Fluid pressure control device - Google Patents

Abstract

(57) [Problem] To provide a fluid pressure control device including an electromagnetic on-off valve and a controller for controlling a current supplied to a coil of an electric on-off valve, and to make the miniaturization possible and to linearly change the fluid pressure. Let it. An opposing surface (35a, 36a) of a fixed core (35) and an armature (36) is formed in a tapered surface, and a coil (39) is formed.
The energizing current to the power supply is controlled by the controller so as to be able to be controlled at ON / OFF and an intermediate value between ON / OFF.

Description

Description: BACKGROUND OF THE INVENTION [0001] 1. Field of the Invention [0002] The present invention relates to an improvement of a fluid pressure control device including an electromagnetic on-off valve and a controller for controlling a current supplied to a coil of the electromagnetic on-off valve. 2. Description of the Related Art Conventionally, such a fluid pressure control device is already known, for example, from a vehicle brake device disclosed in Japanese Patent Application Laid-Open No. 8-258690, and such a conventional vehicle brake fluid is used. The electromagnetic on-off valve of the brake fluid pressure control device in the pressure device is configured to switch between an open state and a closed state by being controlled on / off by a controller. [0003] However, in the above-mentioned prior art, a normally open electromagnetic on-off valve interposed between a master cylinder as a hydraulic pressure generating means and a wheel brake is controlled on / off. If this is done, kickback may occur on the hydraulic pressure generating means side, and the brake operation feeling may be reduced. Therefore, it is conceivable to control the brake fluid pressure of the wheel brakes by using a linear solenoid valve that changes the output fluid pressure linearly in accordance with the applied current. A conventional linear solenoid valve slides a spool. Therefore, the output hydraulic pressure is controlled relatively large, and there is a problem in mountability on a vehicle. The present invention has been made in view of such circumstances, and has as its object to provide a fluid pressure control device capable of linearly changing a fluid pressure while enabling downsizing. In order to achieve the above object, the present invention provides a fixed core, an armature that is spring-biased in a direction away from the fixed core and faces the fixed core, and an armature. A solenoid portion having a coil adsorbed on the fixed core side, a valve shaft having one end facing the output chamber and the other end being coaxially connected to the armature and slidably fitted to the valve housing, the output chamber; An electromagnetic on-off valve comprising a valve seat provided on the valve housing, and a valve part having a valve body provided at one end of the valve shaft so as to be able to sit on the valve seat; And a controller for controlling an energizing current; the opposing surfaces of the fixed core and the armature are formed as tapered surfaces, and the controller comprises: The present invention is characterized in that control of an energizing current to the coil is performed by enabling ON / OFF and an intermediate value between ON / OFF. According to such a configuration, the current flowing through the coil is controlled so as to take an intermediate value between on and off as well as on and off. The suction force between the armatures can be freely changed. In addition, since the opposing surfaces of the fixed core and the armature are tapered, the change in the opposing distance between the fixed core and the armature is made smaller than the axial stroke of the armature, and the change in the suction force generated between the opposing surfaces is reduced. By reducing the change in the directional stroke, the suction force between the fixed core and the armature can be made substantially flat within a practical range. Thus, the valve shaft has a force acting on one end of the valve shaft based at least on the fluid pressure of the output chamber, that is, the output fluid pressure of the solenoid on-off valve,
Since the suction force acting on the armature will operate in a balanced manner, the fluid pressure can be linearly controlled by the solenoid on-off valve, and the structure of the conventional solenoid on-off valve is only slightly changed, The fluid pressure control device that controls the fluid pressure linearly can be made compact. An embodiment of the present invention will be described below with reference to an embodiment of the present invention shown in the accompanying drawings. 1 to 5 show an embodiment of the present invention. FIG. 1 is a brake hydraulic circuit diagram of a brake device for a passenger vehicle, and FIG. 2 is a longitudinal sectional view of a normally-open solenoid valve. 3 is a diagram showing a change in suction force with respect to a change in stroke of the valve shaft, FIG. 4 is a diagram showing a configuration of a drive circuit of a normally-open solenoid valve in a controller, and FIG. FIG. First, in FIG. 1, a tandem-type master cylinder M has first and second output ports 1 and 2 for generating a brake fluid pressure according to a depression force applied to a brake pedal P by a vehicle driver. Hydraulic pressure control valve means VA and VB are interposed between the first output hydraulic pressure path 3 connected to the first output port 1 and the left front wheel brake BA and the right rear wheel brake BB, respectively. A second output hydraulic pressure path 4 connected to the second output port 2, and a right front wheel brake B
Hydraulic pressure control valve means VC and VD are interposed between C and the rear left wheel brake BD, respectively. Each of the hydraulic pressure control valve means VA to VD includes an electromagnetic opening / closing unit corresponding to a left front wheel brake BA, a right rear wheel brake BB, a right front wheel brake BC and a left rear wheel brake BD. Normally open solenoid valve 5A as a valve
5D, check valves 7A to 7D connected in parallel to the normally open solenoid valves 5A to 5D, respectively, and normally closed solenoid valves 6A to 6D individually corresponding to the wheel brakes BA to BD. The normally open solenoid valves 5A and 5B corresponding to the first output hydraulic pressure path 3 are provided between the first output hydraulic pressure path 3 and the left front wheel brake BA and the right rear wheel brake BB. It is interposed. The normally closed solenoid valves 6A and 6B corresponding to the first output hydraulic pressure path 3 are provided with a single first
It is interposed between the reservoir 8A and the front left wheel brake BA and the rear right wheel brake BB. The first reservoir 8A is connected via a first suction valve 9A to a suction side of a first pump 10A capable of pumping brake fluid from the first reservoir 8A, and a discharge side of the first pump 10A is connected to a first discharge valve 11A. And the first output hydraulic path 3 via the first damper 12A. The normally open solenoid valves 5C and 5D corresponding to the second output hydraulic pressure path 4 are provided between the second output hydraulic pressure path 4 and the right front wheel brake BC and the left rear wheel brake BD. It is interposed in. The normally closed solenoid valves 6C and 6D corresponding to the second output hydraulic pressure path 4 include a single second reservoir 8B corresponding to the second output hydraulic pressure path 4, a right front wheel brake BC and a left rear wheel. Between the vehicle wheel brake BD. The second reservoir 8B is connected via a second suction valve 9B to a suction side of a second pump 10B capable of pumping brake fluid from the second reservoir 8B, and a discharge side of the second pump 10B is connected to a second discharge valve 11B. And the second output hydraulic path 4 via the second damper 12B. Each of the check valves 7A to 7D allows the flow of brake fluid from the corresponding wheel brakes BA to BD to the master cylinder M.
A to 5D are connected in parallel. The operation of the hydraulic pressure control valve means VA to VD, that is, the operation of each of the normally open solenoid valves 5A to 5D and each of the normally closed solenoid valves 6A to 6D, and the first and second pumps 10A and 10A
The operation of OB is controlled by the controller C. Each of the above-mentioned hydraulic pressure control valve means VA to VD is provided at the time of normal braking in which each wheel is not likely to be locked.
The controller C allows communication between the master cylinder M and the wheel brakes BA to BD and the wheel brake B
A to BD and the state in which the reservoirs 8A and 8B are shut off are controlled. That is, each of the normally-closed solenoid valves 6A to 6A is brought into a closed state by non-energization, and each of the normally-open solenoid valves 5A to 6A is closed.
A to 5A are opened by non-energization, and the brake fluid pressure output from the first output port 1 of the master cylinder M is applied to the left front wheel brake B via the normally open solenoid valve 5A.
A acts on the right rear wheel brake BB via the normally open solenoid valve 5B. The brake fluid pressure output from the second output port 2 of the master cylinder M is
It acts on the right front wheel brake BC via the normally open solenoid valve 5C and acts on the left rear wheel brake BD via the normally open solenoid valve 5D. When the wheel is about to enter the locked state during the braking, the hydraulic control valve means corresponding to the wheel about to enter the locked state among the hydraulic pressure control valve means VA to VD is: The master cylinder M
And the wheel brakes BA to BD are shut off and the wheel brakes BA to BD and the reservoirs 8A and 8B are controlled to communicate with each other. That is, each normally open solenoid valve 5A
5D, the normally-open solenoid valve corresponding to the wheel that is about to enter the locked state is closed by energization, and the normally-closed solenoid valve 6A to 6D corresponding to the wheel is normally closed. The type solenoid valve is opened by energization. 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. When the brake fluid pressure is kept constant, each of the fluid pressure control valve means VA to VD is controlled by the controller C so that the wheel brakes BA to BD are cut off from the master cylinder M and the reservoirs 8A and 8B. Controlled.
That is, the normally-open solenoid valves 5A to 5D are closed by energization, and the normally-closed solenoid valves 6A to 6D are closed by non-energization. When the brake fluid pressure is further increased, the normally-closed solenoid valves 6A to 6D are closed by non-energization, and the normally-open solenoid valves 5A to 5D are connected to the normally-open solenoid valves 5A to 5D. By controlling the applied current, the hydraulic pressure on the downstream side of the normally-open solenoid valves 5A to 5D is linearly controlled according to the applied current. Incidentally, the first and second pumps 10A,
10B is controlled by the controller C so as to operate at the time of the antilock brake control. The brake fluid in the first and second reservoirs 8A and 8B is supplied to the master cylinder M side by the first and second pumps 10A and 10B. Will be 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 absorption of the brake fluid into the first and second reservoirs 8A and 8B. Moreover, the first and second pumps 10
The pulsation of the discharge pressures of the first and second dampers A and 10B
A, 12B is absorbed, so that the operation feeling of the brake pedal P is not hindered by the recirculation. In the antilock brake control, the normally closed solenoid valves 6A to 6D are on / off controlled by the controller C, whereas the normally open solenoid valves 5A to 5D are controlled.
D is an on / off control and is also controlled by a current having an intermediate value between on and off, and the hydraulic pressure on each of the wheel brakes BA to BD is linearly changed according to the applied current having the intermediate value. Normally open solenoid valve 5 configured to change to
2A to 5D, the structure of the normally open solenoid valve 5A is shown in FIG.
This will be described below with reference to FIG. In FIG. 2, a normally-open solenoid valve 5A includes a solenoid portion 14 for exerting an electromagnetic force, and a solenoid portion 14
And a valve part 15 driven by a valve. The valve part 1 is inserted into a mounting hole 17 provided in the support block 16 so as to open on one surface 16a of the fixed support block 16.
5 is accommodated, and the solenoid portion 14 protrudes from one surface 16 a of the support block 16. The valve section 15 includes a valve housing 18 formed of a magnetic metal in a stepped cylindrical shape.
The valve housing 18 is provided with the mounting hole 1 of the support block 16.
7 is fitted. The inner surface of the mounting hole 17 near the opening end is engaged with the valve housing 18 so that the mounting hole 1 of the valve housing 18 is
A retaining ring 19 for preventing detachment from the fitting 7 is fitted. Two annular sealing members 20 and 21 are mounted on the outer surface of the valve housing 18 at intervals in the axial direction, and between the sealing members 20 and 21 between the support block 16 and the valve housing 18. An annular chamber 22 is formed. The valve housing 18 includes a cylindrical valve seat member 2.
3 is press-fitted and fixed. A valve shaft 24 made of a non-magnetic material is slidably fitted to the valve housing 18. An output chamber 25 is formed between one end of the valve shaft 24 and the valve seat member 23, and faces the output chamber 25. Thus, a spherical valve body 26 that can be seated on a valve seat 23 a formed on the valve seat member 23 is fixed to one end of the valve shaft 24. Moreover, one end of the valve shaft 24 and the valve seat member 2
A return spring 27 that biases the valve shaft 24, that is, the valve body 26, in a direction away from the valve seat member 23 is provided between the three. The valve housing 18 has a first output hydraulic line 3
The hydraulic passage 28 provided in the support block 16
The filter 29 is mounted so as to be interposed between the filter 29 and the valve seat member 23. A filter 30 is mounted on the outer periphery of the valve housing 18 at a portion facing the annular chamber 22,
A passage 31 is provided in the valve housing 18 for connecting the output chamber 25 to the annular chamber 22 through the filter 30. The annular chamber 22 communicates with the wheel brake BA, and the support block 16 is provided with a hydraulic passage 32 that allows the annular chamber 22 to communicate with the wheel brake BA. Further, the valve housing 18 is opened between the valve seat member 23 and the filter 29 when the pressure in the hydraulic passage 28 becomes lower than that of the annular chamber 22 to return the brake fluid in the annular chamber 22 to the hydraulic passage 28 side. A check valve 7A is provided. The solenoid portion 14 includes a fixed core 35, an armature 36 coaxially connected to the other end of the valve shaft 24 of the valve portion 15 and facing the fixed core 35, and the approach / separation of the armature 36 with respect to the fixed core 35. Guide tube 37 for guiding movement, and bobbin 3 surrounding guide tube 37
8, a coil 39 wound around the bobbin 38, a magnetic path frame 40 surrounding the coil 39, and a coil-shaped spring 41 interposed between the magnetic path frame 40 and the bobbin 38. The fixed core 35 is formed in a cylindrical shape.
One end of the valve housing 18 is coaxially and integrally connected to the center. The guide cylinder 37 is formed of a nonmagnetic material, for example, stainless steel, and has a thin bottomed cylindrical shape with one end being a hemispherical closed end. And the other end of the guide cylinder 37 is fixed to the fixed core 35 by, for example, welding. Moreover, the guide cylinder 37 protrudes from the one surface 16a of the support block 16 when the valve housing 18 is mounted in the mounting hole 17. The bobbin 38 has a center hole 38a through which the guide cylinder 37 is inserted, and is formed of a synthetic resin. A coil 39 is wound around the bobbin 38. The magnetic path frame 40 includes the bobbin 38 and the coil 3
9 is provided. A ring-shaped magnetic path plate 43 that abuts on the bobbin 38 is swaged and engaged with one end of the magnetic path cylinder 42 such that the closed end of the guide cylinder 37 projects from the center. On the other hand, the other end of the magnetic path cylinder 42 has a fixed core 3
A ring plate-shaped contact plate portion 42a, which is in contact with one end of the valve housing 18, around the periphery of the valve housing 5, is integrally connected, and the base of the fixed core 35 is fitted to the inner periphery of the contact plate portion 42a. You. The other end of the coil-shaped spring 41 having one end abutting on the abutting plate portion 42a is abutted on the bobbin 38. An armature 36 capable of moving toward and away from the fixed core 35 is housed in the guide cylinder 37. One end of the valve shaft 24 movably penetrating the fixed core 35 is connected to the armature 36. Is coaxially abutted.
By the way, the valve shaft 24 is urged in a direction away from the valve seat member 23 by the spring force of the return spring 27, and the other end of the valve shaft 24 is always in contact with the armature 36, Valve shaft 2 according to the axial movement of armature 36
4, that is, the valve element 26 also moves in the axial direction. That is, the fixed core 35 is attached to the armature 36.
The armature 36 is in a retracted position until it is received by the one-end closing portion of the guide cylinder 37 by the spring force of the return spring 27 in a state where no magnetic attraction force acts on the valve body 26. It is separated from the seat member 23, and the normally-open solenoid valve 5A is in an open state. The armature 36 is fixed to the fixed core 35 side until the valve body 26 is seated on the valve seat member 23.
Is magnetically attracted, the normally open solenoid valve 5A is closed. The output chamber 2 is connected to one end of the valve shaft 24.
While the resultant force of the hydraulic pressure and the spring force of the return spring 27 acts on the hydraulic pressure of 5, the other end of the valve shaft 24 exerts a magnetic attractive force for attracting the armature 36 to the fixed core 35 side. That is, the valve shaft 24 performs a stroke operation so that the resultant force of the liquid pressure and the spring force and the magnetic attraction force are balanced. Therefore, by controlling the amount of current supplied to the coil 39 to an intermediate value between on and off by, for example, duty control, the controller C changes the magnetic attractive force for attracting the armature 36 to the fixed core 35 side. On the other hand, the fixed core 35 and the armature 3
The opposed surfaces 35 a and 36 a of 6 are formed as tapered surfaces that become larger in diameter as they move away from the output chamber 25. When the opposing surfaces 35a and 36a of the fixed core 35 and the armature 36 are formed as tapered surfaces, the distance between the fixed core 35 and the armature 36 (the distance between the fixed core 35 and the armature 36) The change in the suction force generated between the opposed surfaces 35a and 36a becomes smaller than the change in the stroke in the axial direction. Moreover, the suction force actually acting in the axial direction is a sine component of the suction force generated between the opposed surfaces 35a and 36a, and the sharper the angle of the tapered surface is, the more the suction force between the opposed surfaces 35a and 36a is changed. The change in the suction force in the axial direction is reduced. Thus, as shown by the solid line in FIG. 3, the suction force between the fixed core 35 and the armature 36 can be made substantially flat in the practical range between the fully closed state and the fully opened state of the valve portion 15. . On the other hand, when the opposing surfaces of the fixed core 35 and the armature 36 are flat surfaces perpendicular to the axial direction, the opposing distance between the fixed core 35 and the armature 36 changes proportionally according to the axial stroke of the valve shaft 24. Therefore, as shown by the chain line in FIG. 3, the suction force between the fixed core 35 and the armature 36 greatly changes even in a practical range. The controller C has a drive circuit as shown in FIG. 4 for driving the normally-open solenoid valve 5A. This drive circuit controls the energization and cutoff of the coil 39. Power supply 45 and coil 3
9 and the coil 39
And a switch 47 provided between the diode 47 and the ground, and a diode 47 connected between the power supply 45 and the ground. The power supply control means 46 includes a PNP transistor 51 having an emitter connected to the power supply 45, resistors 52, 53 and an NPN connected in series between the power supply 45 and the ground.
A transistor 54 and resistors 56 and 57 connected in series between the control signal input terminal 55 and the ground;
The connection points 2 and 53 are connected to the base of the PNP transistor 51, and the connection point of the resistors 56 and 57 is connected to the base of the NPN transistor 54. In the energization control means 46, the NPN transistor 54 is turned on in response to the input of a high-level control signal to the control signal input terminal 55, and the PNP transistor 51 is turned on. The coil 39 is connected to the collector of the PNP transistor 51, and the coil 39 is grounded via the resistor 58. The diode 47 is connected to the collector of the PNP transistor 51 so as to allow a current to flow toward the power supply 45. The switch means 48 includes a PNP transistor 59 having an emitter connected to the diode 47 and resistors 60 and 61 connected in series between the diode 47 and the ground.
And NPN transistor 62 and control signal input terminal 6
3 and resistors 64 and 65 connected in series between the ground and the ground.
And the connection point of the resistors 64 and 65 is NPN
Connected to the base of transistor 62. In such a switch means 48, the NPN transistor 62 is turned on in response to the input of a high-level control signal to the control signal input terminal 63, so that the PNP transistor 59 is turned on. An amplifier 66 is connected to both ends of the resistor 58, and the output of the amplifier 66 is output from a terminal 67.
The output from the terminal 67 is used for feedback control of the current supplied to the coil 39. In such a drive circuit, the diode 47 is for gradually lowering the current flowing through the coil 39 when the current supply to the coil 39 is stopped. When the switch 47 is turned off, the diode 47 performs the above function, but when the switch means 48 cuts off the connection between the diode 47 and the ground, the diode 47 does not perform the above function. That is, the switching means 48 is connected to the diode 4
5 and the ground, the current flowing through the coil 39 when the power supply to the coil 39 is stopped gradually decreases as shown in FIG. 5A, whereas the switch means 48 connects the diode 47 and the ground. When the power supply to the coil 39 is stopped, the current flowing through the coil 39 when the power supply to the coil 39 is stopped rapidly decreases as shown in FIG. The other normally-open solenoid valves 5B, 5C and 5D have the same configuration as the normally-open solenoid valve 5A. Next, the operation of this embodiment will be described. The master cylinder M and the wheel brakes BA to BD
In the normally open solenoid valves 5A to 5D interposed therebetween, opposed surfaces 35a and 36 of the fixed core 35 and the armature 36 are provided.
“a” is formed on the tapered surface, and the amount of energization to the coil 39 is controlled by the controller C so that it can be controlled at ON / OFF and an intermediate value between ON / OFF. Therefore, in the normally open solenoid valves 5A to 5D, the suction force between the fixed core 35 and the armature 36 can be freely changed, and the opposing surfaces 35a, 36a of the fixed core 35 and the armature 36 are tapered. Therefore, the change in the facing distance between the fixed core 35 and the armature 36 is made smaller than the axial stroke amount of the armature 36, and the fixed core 35 and the armature 36
The suction force between them can be made almost flat in a practical range as shown in FIG. The valve shaft 24 acts on one end of the valve shaft 24 based on the hydraulic pressure of the output chamber 25, that is, the output hydraulic pressure of the normally open solenoid valves 5A to 5D, and acts on the armature 36. The operation is performed so that the suction force is balanced, and the brake fluid pressure can be linearly controlled by the normally-open solenoid valves 5A to 5D, and the fluid pressure on the wheel brakes BA to BD can be changed linearly. Therefore, kickback does not occur in the master cylinder M, and the brake operation feeling by the brake pedal P can be improved. Also, normally closed solenoid valves 6A to 6D interposed between the reservoirs 8A and 8B and the wheel brakes BA to BD.
Is an on / off control, and the normally open solenoid valve 5
The valve is closed during the linear control of the hydraulic pressure by A to 5D to reliably prevent the leakage of the brake fluid, and the brake pressure control accuracy of the wheel brakes BA to BD can be improved. Further, the normally-open solenoid valves 5A to 5D are of a linear type with a slight improvement over the conventional on / off normally-open solenoid valves, and are not enlarged. It is possible to avoid an increase in the size of the hydraulic pressure control valve means VA to VD. A drive circuit for driving the normally-open solenoid valves 5A to 5D in the controller C is provided with a power supply control means 46 provided between the power supply 45 and the coil 39 so as to control the supply and cutoff of the coil 39. And a diode 47 connected between the power supply 45 and the ground, bypassing the coil 39, and a switch means 48 provided between the diode 47 and the ground. The state in which the diode 47 exhibits its function and the diode 47
Can be switched to a state in which is substantially inactivated. Therefore, the state in which the current flowing through the coil 39 is gently reduced and the state in which the current flowing through the coil 39 is rapidly reduced can be easily switched by the on / off switching of the switch means 48. Smooth control in a state in which the amount of electricity supplied to the coil 39 is controlled at an intermediate value between the two to control the hydraulic pressures of the wheel brakes BA to BD linearly, and from ON (closed state) to OFF (opened state)
And the control for promptly shifting to. 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 appended claims. It is possible. For example, in the above embodiment, the normally open solenoid valve 5
Although the present invention is applied to A to 5D, it is also possible to apply the present invention to a normally closed solenoid valve. As described above, according to the present invention, the fluid pressure can be linearly controlled by slightly changing the structure of the conventional solenoid on-off valve, and the fluid pressure control device is compact. Is possible.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a brake hydraulic circuit diagram of a brake device for a passenger vehicle. FIG. 2 is a longitudinal sectional view of a normally-open solenoid valve. FIG. 3 is a diagram showing a change in suction force with respect to a change in stroke of a valve shaft. FIG. 4 is a diagram illustrating a configuration of a drive circuit of a normally-open solenoid valve in a controller. FIG. 5 is a diagram showing a change in terminal voltage of a coil due to conduction / interruption of a switch means. [Description of Signs] 5A to 5D: Normally-open solenoid valve 14 as an electromagnetic on-off valve 14: Solenoid unit 15: Valve unit 18: Valve housing 23a: Valve seat 24: Valve Shaft 25 ... output chamber 26 ... valve element 35 ... fixed cores 35a, 36a ... facing surface 36 ... armature 39 ... coil C ... controller

   ────────────────────────────────────────────────── ─── Continuation of front page    (72) Inventor Hidetoshi Kobori             1-4-1 Chuo, Wako-shi, Saitama Stock Association             Inside the Honda Research Laboratory F term (reference) 3D049 BB16 BB39 CC02 HH20 HH53                       JJ08 NN00                 3H106 DA03 DA12 DA13 DA23 DB02                       DB12 DB23 DB32 DC04 DC17                       DD03 EE07 FA01 FB11 GA13                       GA15 GA23 HH06 KK22

Claims (1)

Claims: 1. Fixed core (35), said fixed core (35)
The armature (36) which is biased by a spring in a direction away from the armature (36) and faces the fixed core (35), and the coil (3) for attracting the armature (36) to the fixed core (35) side.
A solenoid section (14) having a 9) and an output chamber (25)
And one end of the armature (3
6) coaxially connected to the valve housing (18) and slidably fitted to the valve housing (18), and a valve seat (2) provided on the valve housing (18) facing the output chamber (25).
3a) and a valve element (2) provided at one end of the valve shaft (24) so as to be able to sit on the valve seat (23a).
A fluid pressure control device comprising: an electromagnetic on-off valve (5A to 5D) constituted by a valve part (15) having 6); and a controller (C) for controlling a current supplied to the coil (39). Opposing surfaces (35a, 36a) of the fixed core (35) and the armature (36) are formed as tapered surfaces, and the controller (C) enables on / off and control at an intermediate value between on / off. A fluid pressure control device for controlling a current supplied to the coil (39).