WO2020195072A1

WO2020195072A1 - Valve device

Info

Publication number: WO2020195072A1
Application number: PCT/JP2020/002331
Authority: WO
Inventors: 鈴木　健司; 慶太松阪; 鈴木　淳
Original assignee: Ｋｙｂ株式会社
Priority date: 2019-03-26
Filing date: 2020-01-23
Publication date: 2020-10-01
Also published as: CN112005034B; CN112005034A; JP6741815B1; JP2020159464A

Abstract

This valve device (10) is provided with: a housing (20); a valve body (110) accommodated in the housing (20); a biasing member (9) that biases the valve body (110); an annular sheet member (130) that is disposed between the valve body (110) and the biasing member (9) and transmits the biasing force of the biasing member (9) to the valve body (110); an accommodating chamber (122) that is formed in the housing (20) and accommodates the biasing member (9) and the sheet member (130); a through-hole (123) that passes through the accommodating chamber (122) from an end surface of the housing (20); and a closing member (140) that is mounted to the through-hole (123) and closes the through-hole (123), wherein the sheet member (130) has a non-circular shape that has a first outer dimension greater than the inner diameter (Dh) of the through-hole (123) and a second outer dimension less than the inner diameter (Dh) of the through-hole (123).

Description

Valve device

The present invention relates to a valve device.

JP2018-119664A describes a valve device including a spool as a valve body inserted into a valve accommodating hole formed in a housing, and springs provided at both ends of the spool to hold the spool in a neutral position. There is.

In this valve device, the valve accommodating hole, the plug as a closing member screwed into the open end of the valve accommodating hole, the end face of the spool, the spring in the pilot chamber, and between the spring and the spool. Contains the spring seats to be placed.

In the valve device described in JP2018-119664A, it is necessary to increase the diameter of the opening end of the valve accommodating hole in order to insert the spring and the spring seat from the opening end of the valve accommodating hole and arrange them in the pilot chamber. As a result, there is a problem that the closing member screwed into the open end of the valve accommodating hole becomes large.

An object of the present invention is to reduce the size of the closing member.

According to an aspect of the present invention, the valve device is arranged and attached between the housing, the valve body housed in the housing, the urging member for urging the valve body, and the valve body and the urging member. An annular seat member that transmits the urging force of the urging member to the valve body, a storage chamber formed in the housing and accommodating the urging member and the seat member, a through hole penetrating from the end face of the housing to the accommodation chamber, and a through hole. The seat member has a non-circular shape in which the first outer dimension is larger than the inner diameter of the through hole and the second outer dimension is smaller than the inner diameter of the through hole. Is.

FIG. 1 is a diagram showing a configuration of a fluid pressure control device including a valve device according to an embodiment of the present invention. FIG. 2 is a partially enlarged cross-sectional view showing an enlarged portion II of FIG. FIG. 3 is a view of the spring seat seen from the axial direction of the spool, and shows the relationship between the size of the spring seat and the through hole. FIG. 4 is a diagram illustrating a method of arranging the spring seat in the accommodation chamber. FIG. 5 is a diagram showing a spring seat of the valve device according to the first modification of the present embodiment. FIG. 6 is a diagram showing a spring seat of the valve device according to the second modification of the present embodiment.

The valve device 10 according to the embodiment of the present invention will be described with reference to the drawings. Hereinafter, an example in which the valve device 10 is a counterbalance valve device will be described. The counter balance valve device is provided, for example, in a drive circuit of a hydraulic motor constituting a traveling device of a working machine such as a hydraulic excavator or a wheel loader, in order to suppress an impact generated at the time of starting and stopping.

The fluid pressure control device 100 provided with the valve device 10 will be described with reference to FIG. In the fluid pressure control device 100, hydraulic oil is used as the hydraulic fluid, but other fluids such as hydraulic water may be used as the hydraulic fluid.

As shown in FIG. 1, the fluid pressure control device 100 according to the present embodiment is provided between the hydraulic pump 1 for discharging hydraulic oil and the hydraulic motor 2 as a fluid pressure actuator, and controls the drive of the hydraulic motor 2. To do. The fluid pressure control device 100 controls the flow of hydraulic oil from the hydraulic pump 1 to the hydraulic motor 2, and switches the operating direction (rotation direction) of the hydraulic motor 2. The direction switching valve 3, the direction switching valve 3, and the hydraulic motor. It is provided with a valve device 10 provided in a pair of supply /

discharge flow paths

22a and 22b connecting the two.

The hydraulic motor 2 is used as a hydraulic motor for traveling. The hydraulic motor 2 is rotationally driven by supplying the hydraulic oil discharged from the hydraulic pump 1. The hydraulic motor 2 is switched between forward rotation and reverse rotation by the direction switching valve 3. The hydraulic motor 2 rotates forward to move the work equipment forward, and the hydraulic motor 2 rotates in the reverse direction to move the work equipment backward.

The work machine is provided with a negative type parking brake 2a to which the brake release flow path 23 is connected. The parking brake 2a springs when the pressure in the brake release flow path 23 is less than the brake release pressure, the brake is activated by the urging force of the spring, and the pressure in the brake release flow path 23 becomes equal to or higher than the brake release pressure. The brake is released when the piston moves against the urging force of.

The direction switching valve 3 has a forward position (A) for guiding the hydraulic oil discharged from the hydraulic pump 1 to the hydraulic motor 2 through the supply / discharge flow path 22a, and the hydraulic oil discharged from the hydraulic pump 1 through the supply / discharge flow path 22b. It includes a retracted position (B) that leads to the hydraulic motor 2, and a neutral position (C) that communicates the hydraulic pump 1 and the hydraulic motor 2 with the tank T. The directional control valve 3 is switched by the pilot pressure guided to the

pilot chambers

3a and 3b according to the operation of the operating lever.

The valve device 10 includes a rectangular parallelepiped housing 20. The housing 20 includes valve-

side passages

14a and 14b that communicate with the direction switching valve 3 through the supply /

discharge passages

22a and 22b, and actuator-

side passages

15a and 15b that communicate with the hydraulic motor 2 through the supply /

discharge passages

22a and 22b. Is formed.

The valve device 10 includes a control valve 11 that controls the flow of hydraulic oil between the

valve side passages

14a and 14b and the

actuator side passages

15a and 15b when the direction switching valve 3 is switched, and the

valve side passages

14a and 14b. It is provided with

check valves

17a and 17b that allow only the flow from the

actuator side passages

15a and 15b.

The control valve 11 has a spool 110 as a valve body accommodated in a valve accommodating hole 120 formed so as to penetrate the housing 20, and open ends (through holes 123 described later) on both sides of the valve accommodating hole 120 in the axial direction. The first plug 140a and the second plug 140b as closing members to be closed, the first coil spring 9a and the second coil spring 9b provided at both ends of the spool 110 and holding the spool 110 in the neutral position, and the spool 110 and the first A first spring seat 130a and a second spring seat 130b arranged between the first and

second coil springs

9a and 9b are provided. The first and second spring seats 130a and 130b are annular seat members that transmit the urging force of the first and

second coil springs

9a and 9b to the spool 110.

A first pressure chamber 16a is provided on one axial direction of the spool 110, and a second pressure chamber 16b is provided on the other axial direction of the spool 110. The first and

second pressure chambers

16a and 16b are the first and

second plugs

140a and 140b mounted on the valve accommodating hole 120 of the housing 20 and the opening end (through hole 123 described later) of the valve accommodating hole 120, respectively. And the end of the spool 110.

The valve accommodating hole 120 includes a spool hole 121 on which the spool 110 slides, and first and second accommodating chambers 122a in which the first and

second coil springs

9a and 9b and the first and second spring seats 130a and 130b are accommodated. , 122b, and first and second through

holes

123a, 123b penetrating the first and

second storage chambers

122a, 122b from the end face of the housing 20. The first and second through

holes

123a and 123b have an inner diameter slightly larger than the outer diameter of the spool 110 so that the spool 110 can be inserted from the outside of the housing 20.

The valve device 10 is formed in a symmetrical shape. Therefore, hereinafter, the first coil spring 9a and the second coil spring 9b are collectively referred to as a coil spring 9, and the first spring seat 130a and the second spring seat 130b are collectively referred to as a spring seat 130. Further, the first accommodation chamber 122a and the second accommodation chamber 122b are collectively referred to as the accommodation chamber 122, the first through hole 123a and the second through hole 123b are collectively referred to as the through hole 123, and the first plug 140a and the first through hole 123b The two plugs 140b are collectively referred to as the plug 140. The cross-sectional shapes of the spool hole 121, the accommodation chamber 122, and the through hole 123 are circular shapes concentric with the central axis of the spool 110, respectively.

As shown in FIG. 2, a female screw is formed on the inner circumference of the through hole 123. The plug 140 has a flange 141 that abuts on the end face of the housing 20, and a shaft portion 142 that protrudes from the flange 141. The shaft portion 142 has a diameter smaller than that of the flange 141, and a male screw screwed into the female screw of the through hole 123 is formed on the outer periphery thereof. The plug 140 is attached to the through hole 123 by screwing the shaft portion 142 into the through hole 123. A sealing member is arranged between the flange 141 and the open end of the through hole 123, and the sealing member seals the gap between the through hole 123 and the plug 140.

The coil spring 9 is an urging member that urges the spool 110 in the axial direction, and expands and contracts as the spool 110 moves in the axial direction to increase or decrease the urging force on the spool 110. As shown in FIG. 1, the first coil spring 9a is arranged in a compressed state in the first pressure chamber 16a, and the second coil spring 9b is arranged in a compressed state in the second pressure chamber 16b. The first coil spring 9a urges the spool 110 against the urging force of the hydraulic oil in the second pressure chamber 16b against the spool 110. The second coil spring 9b urges the spool 110 against the urging force of the hydraulic oil in the first pressure chamber 16a against the spool 110.

The spool 110 has a main body 111 that slides through the spool hole 121 of the housing 20, and projecting portions 112 (112a, 112b) that project axially from both ends of the main body 111. The cross-sectional shapes of the main body portion 111 and the protruding portion 112 are circular shapes concentric with the central axis of the spool 110, respectively. The main body 111 has a plurality of land portions, and an annular groove is provided between the land portions. Therefore, depending on the axial displacement of the main body 111, adjacent flow paths may communicate with each other through the annular groove, or the flow paths may be blocked by the land portion.

The protruding portion 112a abuts on the first plug 140a and defines the maximum amount of movement (maximum stroke) of the spool 110 in one axial direction (left side in the drawing). The protrusion 112b abuts on the second plug 140b and defines the maximum amount of movement (maximum stroke) of the spool 110 in the other axial direction (to the right in the drawing).

As shown in FIG. 2, the inner diameter of the accommodation chamber 122 is larger than the inner diameter of the spool hole 121. Therefore, a step portion 124 is formed between the inner peripheral surface of the accommodating chamber 122 and the inner peripheral surface of the spool hole 121. The outer diameter of the protruding portion 112 is smaller than the outer diameter of the main body portion 111. Therefore, a step portion 119 is formed between the outer peripheral surface of the protruding portion 112 and the outer peripheral surface of the main body portion 111. The step portion 124 of the housing 20 and the step portion 119 of the spool 110 function as a contact portion with which the spring seat 130 abuts.

The coil spring 9 is arranged so that the protruding portion 112 is inserted inside. An annular spring seat 130 is arranged between the step portion 119 of the spool 110 and the coil spring 9. The spring seat 130 has a circular opening into which the protrusion 112 is inserted. The coil spring 9 is arranged in a state where one end is in contact with the spring seat 130 and the other end is in contact with the plug 140, and the spool 110 is axially urged via the spring seat 130.

As shown in FIG. 1, inside the spool 110, regardless of the position of the spool 110, there is always a communication passage 13a that communicates the valve side passage 14a and the first pressure chamber 16a, regardless of the position of the spool 110. , A communication passage 13b that communicates the valve side passage 14b and the second pressure chamber 16b is always provided. The

communication passages

13a and 13b are provided with

throttles

12a and 12b that limit the flow by imparting resistance to the flow of hydraulic oil passing through.

The spool 110 moves in the axial direction according to the pressure of the first pressure chamber 16a and the second pressure chamber 16b. When the pressure difference between the first pressure chamber 16a and the second pressure chamber 16b is less than a predetermined value, the spool 110 is held in the neutral position shown in FIG. 1 by the first and

second coil springs

9a and 9b as centering springs. Will be done. At this time, the first spring seat 130a abuts on the step portion 124 (124a) of the housing 20, and the second spring seat 130b abuts on the step portion 124 (124b) of the housing 20, so that the positioning accuracy of the neutral position of the spool 110 is accurate. Is improved.

When the pressure in the first pressure chamber 16a rises above the pressure in the second pressure chamber 16b and the pressure difference becomes a predetermined value or more, the spool 110 moves to the right in the drawing. At this time, the first spring seat 130a comes into contact with the step portion 124 (124a) of the housing 20 and its movement is restricted, so that the first spring seat 130a is separated from the step portion 119 (119a) of the spool 110. Further, the second spring seat 130b is pressed by the step portion 119 (119b) of the spool 110 and moves to the right in the drawing, and is separated from the step portion 124 (124b) of the housing 20. Therefore, the second coil spring 9b contracts as the second spring seat 130b moves.

When the pressure in the second pressure chamber 16b rises above the pressure in the first pressure chamber 16a and the pressure difference becomes equal to or greater than a predetermined value, the spool 110 moves to the left in the drawing. At this time, the second spring seat 130b comes into contact with the step portion 124 (124b) of the housing 20 and its movement is restricted, so that the second spring seat 130b is separated from the step portion 119 (119b) of the spool 110. Further, the first spring seat 130a is pressed by the step portion 119 (119a) of the spool 110 and moves to the left in the drawing, and is separated from the step portion 124 (124a) of the housing 20. Therefore, the first coil spring 9a contracts as the first spring seat 130a moves.

When the directional control valve 3 is in the neutral position (C), the first and

second pressure chambers

16a and 16b communicate with the tank T. Therefore, the control valve 11 is held in a neutral position as shown by the urging forces of the first and

second coil springs

9a and 9b provided on both sides.

In the control valve 11, when the direction switching valve 3 is switched to the forward position (A), the hydraulic oil discharged from the hydraulic pump 1 passes through the supply / discharge flow path 22a, the valve side passage 14a, and the communication passage 13a to the first pressure chamber 16a. The spool 110 moves to the right in the drawing by being guided by. In the control valve 11, when the direction switching valve 3 is switched to the retracted position (B), the hydraulic oil discharged from the hydraulic pump 1 passes through the supply / discharge flow path 22b, the valve side passage 14b, and the communication passage 13b, and the second pressure chamber 16b. The spool 110 moves to the left in the drawing by being guided by.

Next, as an example of the operation of the valve device 10 and the fluid pressure control device 100, the operation of the valve device 10 and the fluid pressure control device 100 when the working machine is advanced will be described.

When the operator operates the operation lever toward the forward side, the pilot pressure according to the amount of operation is guided to the pilot chamber 3a. As a result, the direction switching valve 3 is switched to the forward position (A), and the hydraulic oil discharged from the hydraulic pump 1 flows into the valve side passage 14a of the valve device 10 through the supply / discharge flow path 22a.

A part of the hydraulic oil that has flowed into the valve side passage 14a of the valve device 10 flows into the first pressure chamber 16a through the communication passage 13a. As a result, the spool 110 of the control valve 11 moves to the right in the drawing. At this time, the hydraulic oil flowing through the communication passage 13a is restricted by the throttle 12a, so that the hydraulic oil gently flows into the first pressure chamber 16a. As a result, the spool 110 of the control valve 11 gently moves to the right in the drawing.

When the spool 110 moves from the neutral position to the right in the drawing, the hydraulic oil discharged from the hydraulic pump 1 is supplied to the hydraulic motor 2 through the supply / discharge flow path 22a. Further, the hydraulic oil discharged from the hydraulic motor 2 is returned to the tank T through the supply / discharge flow path 22b. The hydraulic oil discharged from the hydraulic pump 1 is guided from the control valve 11 to the parking brake 2a through the brake release flow path 23, and the parking brake 2a is released. As a result, the hydraulic motor 2 rotates in the forward direction, and the working machine moves forward. Since the spool 110 of the control valve 11 moves slowly, the impact generated at the time of starting is suppressed.

When the operator returns the operating lever to the neutral position, the pilot chamber 3a communicates with the tank T, and the directional control valve 3 is returned to the neutral position (C) by the urging force of the spring.

When the direction switching valve 3 is returned to the neutral position (C), the hydraulic oil in the first pressure chamber 16a is discharged to the tank T through the communication passage 13a, the valve side passage 14a, the supply / discharge flow path 22a, and the direction switching valve 3. To. At this time, the hydraulic oil flowing through the communication passage 13a is gently discharged from the first pressure chamber 16a because the flow is restricted by the throttle 12a. As a result, the spool 110 of the control valve 11 is gradually returned to the neutral position, so that the hydraulic motor 2 is prevented from suddenly stopping, and the impact generated at the time of stopping is suppressed.

When the spool 110 of the control valve 11 is returned to the neutral position, the hydraulic oil in the parking brake 2a is discharged to the tank T, and a braking force is applied to the hydraulic motor 2 by the urging force of the spring. As a result, the parking brake is applied to the work machine.

As described above, in the valve device 10, as shown in FIG. 2, the coil spring 9 that urges the spool 110 in the axial direction and the spring seat 130 that transmits the urging force of the coil spring 9 to the spool 110 are housings. It is housed in a storage room 122 formed in 20. The coil spring 9 and the spring seat 130 are inserted through the through hole 123 and arranged in the accommodating chamber 122, and the through hole 123 is closed by the plug 140.

Here, when the outer diameter of the spring seat 130 is circular, the through hole 123 needs to be formed so that the inner diameter thereof is larger than the outer diameter of the spring seat 130. As a result, there is a problem that the plug 140 attached to the through hole 123 becomes large. When the plug 140 screwed into the opening end of the valve accommodating hole 120 of the control valve 11 is large, the valve accommodating holes formed next to the valve accommodating holes 120 (for example,

check valves

17a and 17b (see FIG. 1)). It may be necessary to increase the distance from the valve body (accommodating hole), and as a result, the valve device 10 may become large. Further, the plug 150 screwed into the opening end of the valve accommodating hole (for example, the accommodating hole accommodating the valve body of the

check valves

17a and 17b (see FIG. 1)) without the spring seat (see FIG. 1). There is a risk that the cost will be high because it cannot be shared with.

On the other hand, as shown in FIG. 3, the outer shape of the spring seat 130 according to the present embodiment has a first outer dimension (outer dimension in the first direction) X that is larger than the inner diameter Dh of the through hole 123, and is the first. The outer dimension (outer dimension in the second direction) Y of 2 is a non-circular shape smaller than the inner diameter Dh of the through hole 123.

The spring seat 130 according to the present embodiment has an elliptical outer shape, the major axis which is the length of the major axis corresponds to the first outer dimension X, and the length of the minor axis orthogonal to the major axis. The minor axis corresponds to the second outer dimension Y.

As described above, the spring seat 130 according to the present embodiment is formed so that the second outer dimension Y, which is the maximum outer dimension in at least one direction, is smaller than the inner diameter Dh of the through hole 123. As a result, as shown in FIG. 4, the spring seat 130 can be slanted and passed through the through hole 123 to be arranged in the accommodation chamber 122, so that the spring seat 130 is attached to the inner diameter Dh of the through hole 123 and the through hole 123. The size of the plug 140 can be reduced. As a result, the valve device 10 can be downsized.

Further, by using the same plug as the other plug (for example, a small plug 150 attached to the opening end of the valve accommodating holes of the

check valves

17a and 17b shown in FIG. 1) as the plug 140, parts can be standardized. Cost reduction can be achieved. Further, since the degree of freedom in selecting the size of the plug 140 is improved, it is possible to reduce the cost by using a standard product.

As shown in FIG. 2, the inner diameter Dc of the accommodation chamber 122 is larger than the inner diameter Dh of the through hole 123. As a result, as shown in FIG. 3, the first outer dimension X of the spring seat 130 can be made larger than the inner diameter Dh of the through hole 123.

Further, the first outer diameter X of the spring seat 130 is larger than the outer diameter Ds of the coil spring 9. Further, in the present embodiment, as shown in FIG. 2, the spring seat 130 is in contact with the step portion 119 of the spool 110, and the first outer diameter X of the spring seat 130 is the outer diameter of the main body portion 111. It is larger than the outer diameter of the step portion 119). That is, the spring seat 130 is formed so that both end portions in the first direction project outward from the step portion 119. According to such a configuration, it is possible to sufficiently secure an area on the spring seat 130 on which the urging force of the coil spring 9 acts. As a result, the spring seat 130 can stably transmit the urging force of the coil spring 9 to the spool 110.

According to the above-described embodiment, the following effects are exhibited.

The spring seat 130 has a non-circular shape in which the first outer dimension X is larger than the inner diameter Dh of the through hole 123 and the second outer dimension Y is smaller than the inner diameter Dh of the through hole 123. Therefore, since the spring seat 130 can be slanted and passed through the through hole 123 to be arranged in the accommodation chamber 122, the inner diameter Dh of the through hole 123 and the plug 140 mounted on the through hole 123 can be miniaturized. Can be done.

Further, in the present embodiment, since the spring seat 130 has a simple elliptical shape, the manufacturing cost of the spring seat 130 can be reduced.

The following modifications are also within the scope of the present invention, and it is possible to combine the configurations shown in the modifications with the configurations described in the above-described embodiments, or to combine the configurations described in the following different modifications. Is.

<Modification example 1>
In the above embodiment, an example in which the spring seat 130 has an elliptical shape has been described, but the present invention is not limited thereto. The spring seat 130 may have a non-circular shape in which the first outer dimension X is larger than the inner diameter Dh of the through hole 123 and the second outer dimension Y is smaller than the inner diameter of the through hole 123. For example, as shown in FIG. 5, the spring seat 230 may be formed so as to have an outer shape having a rectangular corner cut out.

<Modification 2>
In the above embodiment, the length (major axis) of the major axis parallel to the first direction corresponds to the first outer dimension X, and the length (minor axis) of the minor axis parallel to the second direction orthogonal to the first direction. ) Corresponds to the second outer dimension Y, but the present invention is not limited thereto. As shown in FIG. 6, the first direction, which is the reference of the first outer dimension X, and the second direction, which is the reference of the second outer dimension Y, do not have to be orthogonal to each other. In the spring seat 330, the minimum value of the external dimensions (second outer dimension Y) is smaller than the inner diameter Dh of the through hole 123, and the maximum value of the outer dimensions (first outer dimension X) is smaller than the inner diameter Dh of the through hole 123. It may be a large shape.

<Modification example 3>
In the above embodiment, an example of applying the present invention to a counter balance valve device for suppressing an impact at the time of starting and stopping of a work machine including a hydraulic motor as a traveling motor has been described, but the present invention is limited thereto. Not done. The present invention may be applied to a valve device for suppressing a sudden drop of the boom or the like due to its own weight when the boom of the working machine is operated in the downward direction. Further, the valve device is not limited to the counterbalance valve device. For example, the present invention may be applied to a reversing prevention valve device that prevents a reversing operation of a hydraulic motor used as a swirling motor of a swivel device of a working machine.

<Modification example 4>
In the above embodiment, the valve device in which the valve body urged by the spring is a spool has been described, but the present invention is not limited thereto. The present invention can be applied to a valve device having various valve bodies such as a poppet as a valve body urged by a spring.

The configuration, action, and effect of the embodiment of the present invention configured as described above will be collectively described.

The valve device 10 includes a housing 20, a valve body (spool 110) housed in the housing 20, an urging member (coil spring 9) for urging the valve body (spool 110), and a valve body (spool 110). An annular seat member (spring seats 130, 230, 330) arranged between the urging member (coil spring 9) and transmitting the urging force of the urging member (coil spring 9) to the valve body (spool 110). , The accommodating chamber 122 formed in the housing 20 and accommodating the urging member (coil spring 9) and the seat member (spring seats 130, 230, 330), and the through hole 123 penetrating from the end surface of the housing 20 into the accommodating chamber 122. The seat member (spring seats 130, 230, 330) includes a closing member (plug 140) that is attached to the through hole 123 and closes the through hole 123, and the first outer dimension X is the inner diameter of the through hole 123. It is a non-circular shape that is larger than Dh and has a second outer dimension Y smaller than the inner diameter Dh of the through hole 123.

In this configuration, the seat members (spring seats 130, 230, 330) can be slanted and passed through the through hole 123 to be arranged in the accommodation chamber 122, so that they are mounted on the inner diameter of the through hole 123 and the through hole 123. The size of the closing member (plug 140) can be reduced.

The valve device 10 has an elliptical shape in which the seat member (spring seat 130) has a major axis of the first outer diameter X and a minor axis of the second outer dimension Y.

In this configuration, since the seat member (spring seat 130) has a simple elliptical shape, the manufacturing cost of the seat member (spring seat 130) can be reduced.

In the valve device 10, the inner diameter of the accommodation chamber 122 is larger than the inner diameter Dh of the through hole 123.

In the valve device 10, the urging member is the coil spring 9, and the first outer dimension X of the seat member (spring seats 130, 230, 330) is larger than the outer diameter Ds of the coil spring 9.

The valve device 10 has a valve body as a spool 110, and the spool 110 has a main body 111 that slides on the spool hole 121 of the housing 20, and a protruding portion 112 that projects axially from the main body 111. The outer diameter of the protruding portion 112 is smaller than the outer diameter of the main body portion 111, and a step portion 119 is formed between the main body portion 111 and the protruding portion 112 so that the seat members (spring seats 130, 230, 330) come into contact with each other. The first outer diameter X of the members (spring seats 130, 230, 330) is larger than the outer diameter of the main body 111.

With these configurations, it is possible to sufficiently secure an area on the seat members (spring seats 130, 230, 330) on which the urging force of the urging member (coil spring 9) acts. As a result, the seat member (spring seats 130, 230, 330) can stably transmit the urging force of the urging member (coil spring 9) to the valve body (spool 110).

Although the embodiments of the present invention have been described above, the above embodiments are only a part of the application examples of the present invention, and the technical scope of the present invention is limited to the specific configuration of the above embodiments. Absent.

The present application claims priority based on Japanese Patent Application No. 2019-0591969 filed with the Japan Patent Office on March 26, 2019, and the entire contents of this application are incorporated herein by reference.

Claims

With the housing
The valve body housed in the housing and
The urging member that urges the valve body and
An annular seat member arranged between the valve body and the urging member and transmitting the urging force of the urging member to the valve body.
A storage chamber formed in the housing and accommodating the urging member and the seat member, and
A through hole penetrating from the end face of the housing to the accommodation chamber,
A closing member mounted on the through hole and closing the through hole is provided.
The seat member is a valve device having a non-circular shape in which the first outer dimension is larger than the inner diameter of the through hole and the second outer dimension is smaller than the inner diameter of the through hole.
The valve device according to claim 1.
The seat member is an elliptical valve device having a major axis having the first outer diameter and a minor diameter having the second outer diameter.
The valve device according to claim 1.
A valve device in which the inner diameter of the accommodation chamber is larger than the inner diameter of the through hole.
The valve device according to claim 1.
The urging member is a coil spring.
A valve device in which the first outer dimension of the seat member is larger than the outer diameter of the coil spring.
The valve device according to claim 1.
The valve body is a spool and
The spool
The main body that slides the spool hole of the housing and
It has a protruding portion that protrudes in the axial direction from the main body portion, and has.
The outer diameter of the protruding portion is smaller than the outer diameter of the main body portion, and a step portion with which the sheet member comes into contact is formed between the main body portion and the protruding portion.
A valve device in which the first outer dimension of the seat member is larger than the outer diameter of the main body.