JP3059613B2 - Slide valve - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a slide valve, and more particularly to a slide valve capable of increasing the switching speed and reducing the size.

[0002]

2. Description of the Related Art A slide valve for switching a load includes, for example, a valve seat 103 which covers a lower surface of a valve chamber 102 formed in a valve box 101, as shown in a vertical side view of FIG. 104 which is inserted so that it can advance and retreat, and this spool
A valve element which is driven by the valve 104 and slides along the upper surface of the valve seat 103
105.

The valve seat 103 corresponds to an inlet port 106 opened on the upper surface, two load connecting outlet ports 107A and 107B which are alternatively connected to the inlet port 106, and outlet ports 107A and 107B. Two exhaust ports 108
A. 108B. In addition, outlet ports 107A and 107B are provided on the lower surface of the valve body 105, respectively.
The two passages 109A and 109B for switching connection to the exhaust port 108A and 108B corresponding to 6 are recessed side by side in the sliding direction of the valve body 105 (hereinafter simply referred to as sliding direction).

As shown in FIGS. 10 to 12, the valve 105 is driven by a spool 104 and slid so that the lower surface of a central portion between the two passages 109 A and 109 B of the valve 105 is provided.
By overlapping 110 with the portions 111A and 111B of the sliding surface 111 on either side of the sliding direction of the inlet port 106 of the valve seat 103, one of the outlet ports 107B (or 107A) is shut off from the inlet port 106 and And the corresponding exhaust port 108B (or 109A) via passage 109B (or 109A).
108A) and the other exit port 107A (or
107B) is communicated with the inlet port 106 via the passage 109A (or 109B).

The exhaust port 108A (or 108B) corresponding to the outlet port 107A (or 107B) which is in communication with the inlet port 106 by the valve body 105 has outlet ports corresponding to both ends in the sliding direction of the valve body 105. It is designed to shut off from 107A (107B) and the inlet port 106. In addition,
Various methods such as manual driving, electric driving, pneumatic driving, and hydraulic driving are used for driving the spool 104. Also, especially when switching valves at high speed is required,
The valve seat 107 and the valve element 108 are often made of ceramics having excellent wear resistance.

In this conventional slide valve, when the pressure management of each of the outlet ports 107A and 107B and each of the load circuits connected thereto is strict, for example, as shown in FIG. The central lower surface 110 covers the inlet port 106, the outlet ports 107A and 107B are simultaneously shut off from the inlet port 106, and the outlet ports 107A and 107B are respectively connected to the corresponding exhaust port 1.
08A and 108B are also cut off.

A valve 105 and a valve seat 10 are provided between the ports.
In order to secure the sealing property between the first and second members, a length longer than a certain length a in the sliding direction is required. Further, the flow path cross-sectional area of each port is determined by a required flow rate of a working fluid such as compressed air and a dimension in a direction perpendicular to a sliding direction of each port (hereinafter, referred to as a width direction). The dimension in the width direction is limited to a certain value or less corresponding to the dimension in the width direction of the solenoid valve given by a standard such as ISO.

The length of the valve element 105 in the sliding direction is determined by the length of the central lower surface 110 in the sliding direction and the passages 109A.
The length of the sliding direction of 109B and the stroke of the valve body 105
It is set to the total length of the double length and the length in the sliding direction of the sealing surfaces 111A and 111B required on both outer sides of both the exhaust ports 108A and 108B. Now, assuming that the length in the sliding direction required by each port to obtain a predetermined flow rate is b, the length of the lower surface 110 at the central portion is set to the length b in the sliding direction of the inlet port 106, and the valve Seat 105 strokes at inlet port 106
Is set to 2b or more, which is obtained by adding the length b of the lower surface 110 at the central portion to the length b in the sliding direction.

The length of each of the passages 109A and 109B in the sliding direction is determined by the distance a between each of the outlet ports 107A and 107B and the corresponding one of the exhaust ports 108A and 108B, and the length of each of the outlet ports 107A and 107B. It is necessary to set the length (a + 2b) or more to the sum of the length b in the sliding direction and the corresponding length b in the sliding direction of the exhaust ports 108A and 108B. Therefore, the length of the valve element 105 in the sliding direction is determined by the length b of the central lower surface 110 in the sliding direction and the passages 109A and 109B on both sides thereof.
Twice as long as the length (a + 2b) in the sliding direction of
5 twice the length of stroke 2b and each passage 109A ・ 1
The total length (4a + 9), which is twice as long as the length a in the sliding direction of the sealing surfaces 111A and 111B required on the outside of 09B.
b) The length of the valve seat 103 in the sliding direction is set to be equal to or longer than the length of the valve seat 105 plus the stroke 2b (4a + 11).
b) The above is set.

[0010]

Therefore, in a slide valve that requires a large flow rate, the length b of each port in the sliding direction is increased in order to obtain the required flow rate while complying with standards such as ISO. It is necessary to choose between accepting that the slide valve is enlarged in the sliding direction, accepting that the flow rate is insufficient to avoid enlargement, and ignoring the standards such as ISO. There is a disadvantage that there is no.

[0011] Of these, ignoring standards such as ISO impairs the generality of the product, so it is only allowed in extremely limited cases. Is unfavorably restricted. After all, in normal production, it is often accepted to increase the size. However, as the length of the valve seat 103 and the valve body 105 in the sliding direction increases, the valve body 10
5 is the area in sliding contact with the valve seat 103 (hereinafter referred to as the sliding area)
Increases, and the sliding resistance of the valve seat 105 increases.
The switching speed of the valve becomes slow, and the spool 104
It is necessary to increase the force (hereinafter referred to as thrust) for driving the valve 5 in the sliding direction, and therefore, the diameter of the spool 104 must be increased, which causes a problem that the slide valve becomes larger.

The inventor of the present invention has conducted various studies and experiments, and when the force for driving the valve body 105 in the sliding direction is applied from the spool 104, the valve body 105 is moved to the opposite end face and the valve seat 103.
A force that tries to separate the valve body 105 from the upper surface of the valve seat 103 (hereinafter, referred to as a prying force) acts on a point of intersection with the upper surface of the valve seat 103, and the prying force causes one end of the valve body 105 to move to the upper surface of the valve seat 103. It was found that when lifted from above, the sliding resistance of the valve body 105 was rapidly reduced and the switching speed of the valve was increased, and that the switching speed of the valve was increased as the prying force was increased.

The present invention has been completed based on the above findings, and has as its object to provide a slide valve capable of increasing the switching speed and reducing the size.

[0014]

According to the present invention, there is provided a valve seat which covers a lower surface of a valve chamber formed in a valve box, a spool which is inserted into and retractable from the valve chamber, and an upper surface of the valve seat which is driven by the spool. A valve body that slides along the inlet port, wherein the valve seat corresponds to an inlet port opened at the top surface, two load connecting outlet ports selectively connected to the inlet port, and each outlet port. One of the two outlet ports is alternatively connected to the inlet port by sliding of the valve body, and the other outlet port corresponds to the corresponding exhaust port. In order to achieve the above object, the following measures have been taken in the slide valve connected to.

That is, according to the present invention, an inlet port is opened at a side edge of an upper surface of the valve seat, and both outlet ports are opened at the center of the upper surface of the valve seat in a sliding direction. Exhaust ports respectively corresponding to both outer sides in the sliding direction of both outlet ports on the upper surface are opened, and the valve body is composed of two valve bodies divided in the sliding direction, and both outlet ports are provided between the two valve bodies. And an exhaust-side passage is formed in each valve element to communicate an outlet port, which is shut off from the valve chamber, to an exhaust port. It is.

[0016]

According to the present invention, the inlet port may be opened at both side edges in the width direction of the valve seat, or may be opened at only one side edge. The working fluid flowing into the chamber flows into one of the outlet ports from the inlet passage formed between the two valve bodies, and the working fluid from the outlet port blocked from the inlet passage is exhaust gas formed in the valve body. It will flow out to the corresponding exhaust port through the side passage.

Here, at the center of the upper surface of the valve seat in the width direction, four ports, that is, both outlet ports and both exhaust ports, are opened side by side in the sliding direction. In addition, since the length of the valve seat and the valve element in the sliding direction is shorter than that of the conventional example in which the inlet port is opened side by side in the sliding direction, the entire slide valve can be shortened in the sliding direction. In addition, the sliding area of the valve element is reduced, the sliding resistance of the valve element is reduced, and the switching speed of the valve can be increased.

Further, since the sliding resistance of the valve body is reduced,
Since the valve body can be driven with a weak thrust, the diameter of the spool can be reduced, and the entire slide valve can be reduced in the direction perpendicular to the sliding direction. When the thrust is applied from the spool to the valve body, the thrust-opening force is a straight line connecting the fulcrum and the fulcrum to which the thrust is applied, with the fulcrum being the intersection of the end face opposite to the end face to which the thrust is applied and the upper surface of the valve seat. This is considered to be a component force of the thrust generated in a direction perpendicular to the direction. Therefore, assuming that the included angle between the straight line and the upper surface of the valve seat is θ and the force applied to the force point is F, the prying force is F × sin θ.

In the present invention, since the valve element is constituted by two valve elements divided into two in the sliding direction, the sliding direction of each valve element is smaller than in the conventional example in which the valve elements are integrally formed. Is short, the fulcrum is close to the force point and θ increases, and the prying force for the thrust F of the same magnitude increases. This makes it easier for the end of the valve element on the force point side to float up from the upper surface of the valve seat than the conventional product, and one end of the valve body rises up from the upper surface of the valve seat in a short time after the thrust starts to act on the valve body. Since the sliding resistance of each valve rapidly decreases,
The switching speed of the valve can be increased.

From another point of view, one end of each valve body can be lifted from the upper surface of the valve seat with a smaller thrust than the conventional one, so that the diameter of the spool is reduced and the slide valve is moved in a direction perpendicular to the sliding direction. The size can be further reduced. In the present invention, in particular, when a decompression chamber partitioned from the valve chamber by the sealing member is formed between each of the valve bodies and the spool, and this decompression chamber is communicated with the exhaust-side passage through a vent hole, The pressure receiving area of the valve body on which the working fluid in the valve chamber presses the valve body against the valve seat is reduced, the pressure for pressing the valve body against the valve seat is reduced, and the sliding resistance of the valve body is reduced. Therefore, the moving speed of the valve body can be further increased with a smaller thrust than before, and the diameter of the spool can be reduced to further reduce the size of the slide valve in a direction perpendicular to the sliding direction.

[0021]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, a slide valve according to one embodiment of the present invention will be specifically described with reference to the drawings. However, the present invention is not limited to this embodiment, and is not limited to this specification and the accompanying drawings. The present invention extends widely over the true intended scope of the invention as apparent from the drawings.

A slide valve according to an embodiment of the present invention shown in a vertical side view of FIG. 1 and an exploded perspective view of FIG. 2 is a ceramic covering the lower surface of an inverted U-shaped valve chamber 2 formed in a valve box 1. And a spool 4 inserted in the valve chamber 2 so as to be able to advance and retreat, and two ceramic valve elements 5A and 5B driven by the spool 4 and sliding along the upper surface of the valve seat 3. Is provided.

Further, the lower surfaces of the valve seat 3 and the valve box 1 are covered with a valve seat retainer 12 also serving as an interface, and a pipe mount 13 is fixed to the lower surface of the valve box 1. On the upper surface 14 of the valve seat 3, inlet ports 6.6 are respectively opened on both side edges in the width direction, and two outlet ports 7A and 7B slide in the center of the upper surface 14 of the valve seat 3. Opened side by side. Exhaust ports 8A and 8B corresponding to the outlet ports 7A and 7B are opened at both sides in the sliding direction of the outlet ports 7A and 7B at the center in the width direction of the upper surface 14 of the valve seat 3.

The spool 4 has a large diameter portion in the axial direction, that is, a center portion and both ends in the sliding direction, and is provided below the small diameter portions 4A and 4B between these large diameter portions. Each valve element 5A
5B is arranged, and an inlet-side passage 9 which connects the valve chamber 2 to the two outlet ports 7A and 7b alternatively is formed between the two valve bodies 5A and 5B. As shown in the schematic diagrams of FIGS. 3 to 5, the length of the inlet side passage 9 in the sliding direction is determined by each of the outlet ports 7A and 7 required to secure a required flow rate.
B and the length b in the sliding direction of the exhaust ports 8A and 8B are set to the same length.

As shown in FIG. 4, the interval between the two outlet ports 7A and 7B of the valve seat 3 is such that the two outlet ports 7A and 7B are simultaneously cut off from the inlet side passage 9 in the transition period. In order to do so, the groove width of the entrance side passage 9,
That is, the length b in the sliding direction of each of the outlet ports 7A and 7B.
Is set to the same length as. Exhaust-side passages 10A and 10B for connecting the outlet ports 7A and 7B, which are cut off from the inlet-side passages 9 by the valve bodies 5A and 5B, to the corresponding exhaust ports 8A and 8B are formed in the lower surfaces of the valve bodies 5A and 5B. You.

As will be described later, the length of each of the exhaust-side passages 10A and 10B in the sliding direction is determined by the distance a between each of the outlet ports 7A and 7B and the corresponding exhaust port 8A and 8B, The length (a + 2) obtained by adding the length b in the sliding direction of 7A and 7B and the length b in the sliding direction of the exhaust ports 8A and 8B.
b) More length is required. In this embodiment, since the distance between the outlet ports 7A and 7B is set to b, the length of each of the exhaust-side passages 10A and 10B in the sliding direction is equal to this length (a + 2b). From the length (a + 3b) including the distance b provided between the ports 7A and 7B, the sealing surfaces 15A and 15B necessary for ensuring the sealing performance between the inlet-side passage 9 and the exhaust-side passages 10A and 10B. Is set to the length 3b obtained by subtracting the length a in the sliding direction.

Further, the exhaust side passage 10 of each of the valve bodies 5A and 5B is provided.
The inlet side passage 9 or the valve chamber 2 is provided on both sides of the A and 10B in the sliding direction.
Each of the sealing surfaces 16A and 16B necessary for ensuring the sealing performance between the valve body 5A and the exhaust side passage 10A and 10B is provided, so that the length of each of the valve bodies 5A and 5B in the sliding direction is (2a + 3).
b) is set. As shown in FIGS. 3 to 5, the stroke of each of the valve bodies 5A and 5B may be such that the inlet side passage 9 is selectively overlapped with the two outlet ports 7A and 7B in the vertical direction. It is set to a length 2b obtained by subtracting the length b in the sliding direction of the inlet side passage 9 from the distance b in the sliding direction between the two outlet ports 7A and 7B and the length b in the sliding direction of the two outlet ports 7A and 7B. You.

Therefore, the length of the valve seat 3 in the sliding direction is
The length in the sliding direction of the two valve elements 5A and 5B is 2 × (2a + 3
b), the distance b between the two valve bodies 5A and 5B, and the length (4a +
9b), and the length of the conventional valve seat 103 (4a + 11b)
By making the length 2b shorter than that of the above, the slide valve can be made smaller in the sliding direction.

The total length 2 × (2a + 3b) of the valve elements 5A and 5B in the sliding direction is shorter than the conventional length (4a + 9b) of the integral valve element 105 in the sliding direction.・
Since the sliding resistance of the valve 5B is reduced, the sliding resistance of the valve elements 5A and 5B is reduced, and the switching speed of the valve can be increased with a small thrust. Further, since the thrust of the spool 4 can be reduced, the diameter of the spool 4 can be reduced, and the size of the slide valve can be reduced in the direction perpendicular to the sliding direction.

As shown in FIG. 6, for example, when a thrust F acts on the valve elements 5A (5B) and 105 from the spool 4, the valve element 5A on the opposite side of the point of application of the thrust F is applied.
(5B) The intersection P1 between the end surface of 105 and the upper surface 14 of the valve seat 3
With P2 as a fulcrum, a force for lifting the valve element 5A (5B) .105 from the upper surface 14 of the valve seat 3, that is, a prying force F1 or F2 is generated.

The opening force F1 (or F2) is defined by the angle θ1 between the straight line connecting the point of force and the fulcrum with the upper surface 14 of the valve seat 3.
(Or θ2), the force F1 acting in the sliding direction
(Or F2) multiplied by sin θ1 (or sin θ2), and therefore, the value becomes larger as the distance between the power point and the fulcrum P1 (or P2) becomes shorter. Therefore, in this embodiment in which the valve elements 5A and 5B are divided into two, the distance between the power point and the fulcrum P1 is shorter than the distance between the power point and the fulcrum P2 of the conventional example in which the valve element 105 is formed integrally, and the valve element 105 is integrated. A larger prying force F1 is generated as compared with the conventional example, and the valve can be switched at a higher speed.

In addition, since the length (2a + 3b) of each of the valve elements 5A and 5B in the sliding direction is smaller than half the length (4a + 9b) of the conventional integral valve element 105 in the sliding direction.
It is possible to obtain the same or higher prying force with the conventional thrust than the conventional one. Therefore, the thrust can be made smaller than before, and the diameter of the spool 4 can be made smaller, so that the slide valve can be made smaller in the direction perpendicular to the sliding direction.

Next, as shown in the cross-sectional view of FIG. 7, the small diameter portions 4A and 4B of the spool 4 are formed in a substantially semi-cylindrical shape with a flat lower surface. U-shaped grooves 17A and 17B having flat bottom surfaces corresponding to the small diameter portions 4A and 4B of the spool 4 are formed. Each U-shaped groove 17A ・ 17
In B, gaskets 18A and 18B made of an elastic material such as rubber and gasket retainers 19A and 19B for preventing the gaskets 18A and 18B from protruding when a high-pressure working fluid flows are inserted vertically. By pressing the gaskets 18A and 18B against the lower surface of the small diameter portion of the spool 4, as shown in FIG.
A vacuum chambers 20A and 20B are formed between the vacuum chambers A and 5B. The decompression chambers 20A and 20B are connected to the exhaust passage 10A by vent holes 21A and 21B formed in the valve bodies 5A and 5B.
・ Communicated with 10B.

Thus, the pressure receiving area in which the internal pressure of the valve chamber 2 acts on each of the valve elements 5A and 5B is reduced by the valve seat 3 of each of the pressure reducing chambers 20A and 20B.
, And each valve element 5A, 5B becomes a valve seat 3
Is reduced, the sliding resistance of each valve element 5A, 5B is reduced, and the switching speed of the valve is further increased. Moreover, even when the internal pressure of the valve chamber 2 is low, the valve members 5A, 5B
Is pressed against the upper surface 14 of the valve seat 3, and the valve bodies 5A and 5B and the valve seat 3
Since the sealing property between them is ensured, they can be used for both high pressure and low pressure, and the versatility of the valve can be improved.

The valve seat retainer 12 has an inlet corresponding to one inlet port 22, two outlet ports 23A and 23B, and two exhaust ports 24A and 24B which open on the upper surface of the pipe mount 13. A passage 25, outlet passages 26A and 26B, and exhaust passages 27A and 27B are provided. The inlet passage 25 is branched forward and backward in the valve retainer 12, and is opened at the upper surface of the valve retainer 12 into a long hole extending in the width direction reaching both ends in the width direction. Are formed at both side edges of the valve seat 3 through an inlet passage 25.
It communicates with the two inlet ports 6.6.

Although the slide valve can be configured to be switched by manual operation, in this embodiment, cylinder chambers 28A and 28B are formed on both sides of the valve chamber 11, and the cylinder chambers 28A Piston inserted into 28B
The spool 4 is driven by supplying and discharging compressed air to and from pressure receiving chambers 30A and 30B formed on both outer sides of 29A and 29B via pilot solenoid valves 31A and 31B.

In this case, since the thrust of the spool 4 can be reduced as described above, the diameters of the cylinder chambers 28A and 28B and the pistons 29A and 29B can also be reduced, and the entire slide valve including these operating devices can be used. It can be small. In another embodiment of the present invention shown in the perspective view of FIG. 8, guide holes 33A and 33B are formed in the small diameter portions 32A and 32B of the spool 32.
Guide shaft connected to the upper surface of each valve body 34A / 34B on A / 33B
35A and 35B are inserted.

Further, by inserting sealing members 36A and 36B made of, for example, O-rings between the upper end surfaces of the guide holes 33A and 33B and the upper end surfaces of the guide shafts 35A and 35B, the spool 32
A decompression chamber sealed by the sealing members 36A and 36b is formed between the valve body 34A and the valve bodies 34A and 34B. Furthermore, each valve body 34A
Vent hole 37A penetrating 34B and each guide shaft 35A / 35B
By 37B, each decompression chamber communicates with the exhaust-side passages 38A and 38B recessed from the lower surface of each of the valve bodies 34A and 34B.

Other configurations, operations and effects of this embodiment are the same as those of the above-described embodiment, and therefore, detailed description thereof will be omitted to avoid duplication.

[0040]

As described above, according to the present invention, the inlet port is opened at the side edge of the upper surface of the valve seat, and the two outlet ports are arranged at the center of the upper surface of the valve seat in the sliding direction. Exhaust ports are respectively opened on both outer sides of the upper surface of the valve seat in the sliding direction of the two outlet ports, and the valve body comprises two valve bodies divided in the sliding direction. An inlet-side passage for selectively communicating both outlet ports with the valve chamber is formed, and an exhaust-side passage for connecting the outlet port shut off from the valve chamber to the exhaust port is formed in each valve element. Therefore, the length of the valve body and the valve seat in the sliding direction can be reduced as compared with the conventional example in which the five ports are opened side by side in the sliding direction. can do.

Further, since the length of the valve body in the sliding direction can be reduced, the sliding resistance of the valve body is reduced, and the switching speed of the valve can be increased. Further, since the sliding resistance of the valve body is reduced, the thrust of the spool can be reduced, and the diameter of the spool can be reduced so that the entire slide valve can be downsized even in a direction perpendicular to the sliding direction.

Further, in the present invention, since the valve element is formed by dividing the valve element into two parts in the sliding direction, the prying force is increased with respect to the thrust acting on each valve element, and the valve element slides in a short time. The dynamic resistance can be rapidly reduced, and the switching speed of the valve can be further increased. Further, since the prying force with respect to the thrust increases, the thrust can be reduced, and the diameter of the spool can be further reduced, and the entire slide valve can be further reduced in the direction perpendicular to the sliding direction.

Further, in the present invention, in particular, a decompression chamber partitioned from the valve chamber by the sealing member is formed between each of the valve bodies and the spool, and the decompression chamber is communicated with the exhaust side passage through a vent hole. In such a case, the pressure receiving area of the valve body receiving the pressure of the working fluid in the valve chamber is reduced by the projected area of the pressure reducing chamber onto the valve seat, and the force for pressing the valve body against the valve seat is reduced. As a result, the sliding resistance of the valve element is further reduced, so that the switching speed of the valve element can be further increased, and the effect that the entire diameter of the slide valve can be further reduced by reducing the diameter of the spool can be obtained.

[Brief description of the drawings]

FIG. 1 is a vertical side view of one embodiment of the present invention.

FIG. 2 is an exploded perspective view of a main part of one embodiment of the present invention.

FIG. 3 is a schematic view of a valve seat and a valve element according to an embodiment of the present invention when A is connected.

FIG. 4 is a schematic view of a valve seat and a valve element according to an embodiment of the present invention in a transition period.

FIG. 5 is a schematic view of a valve seat and a valve element according to an embodiment of the present invention when B is connected.

FIG. 6 is a schematic diagram comparing the prying force of the present invention and a conventional example.

FIG. 7 is a sectional view of a spool and a valve body according to one embodiment of the present invention.

FIG. 8 is an exploded perspective view of a main part of another embodiment of the present invention.

FIG. 9 is a longitudinal sectional side view of a conventional example.

FIG. 10 is a schematic view of a conventional valve seat and a valve element when B is connected.

FIG. 11 is a schematic diagram of a conventional valve seat and a valve element in a transition period.

FIG. 12 is a schematic view of a conventional valve seat and a valve element when A is connected.

[Description of sign]

 DESCRIPTION OF SYMBOLS 1 ... Valve box 2 ... Valve chamber 3 ... Valve seat 4 ... Spool 5A / 5B ... Valve 6 ... Inlet port 7A / 7B ... Outlet port 8A / 8B ... Exhaust port 9 ... Inlet side passage 10A / 10B ... Exhaust side passage 14 ... Top surface 18A / 18B ... Gasket 20A / 20B ... Decompression chamber 21A / 21B ... Vent hole 32 ... Spool 34A / 34B ... Valve element 36A / 36B ... Sealing member 37A / 37B ... Vent hole 38A / 38B ... Exhaust side passage

Continuation of front page (56) References JP-A-54-29123 (JP, A) JP-A 63-187777 (JP, U) JP-A 62-86482 (JP, U) JP-A 59-191470 (JP) , U) Japanese Utility Model Showa 62-8468 (JP, U) Japanese Utility Model Showa 62-8467 (JP, U) (58) Fields investigated (Int. Cl. ⁷ , DB name) F16K 3/00-3/36 F16K 11/00-11/24 F16K 27/00-27/04 F16K 31/12-31/165

Claims (2)

(57) [Claims] 1. A valve seat that covers a lower surface of a valve chamber formed in a valve box, a spool that is inserted into the valve chamber so as to advance and retreat, and a valve body that is driven by the spool and slides along the upper surface of the valve seat. The valve seat has an inlet port opened on the upper surface, two load connecting outlet ports selectively connected to the inlet port, and two exhaust ports corresponding to each outlet port. In the slide valve in which one of the two outlet ports is alternatively connected to the inlet port and another one of the outlet ports is connected to the corresponding exhaust port by sliding the valve body, An inlet port is opened at the side edge of the upper surface of the valve seat, and both outlet ports are opened in the center of the upper surface of the valve seat in a sliding direction, and the sliding direction of the two outlet ports on the upper surface of the valve seat is provided. The corresponding exhaust ports are opened on both outer sides of the The valve body is composed of two valve bodies divided in the sliding direction, and between the two valve bodies, an inlet side passage for selectively communicating both outlet ports with the valve chamber is formed. A slide valve, wherein an exhaust-side passage for connecting an outlet port, which is shut off from a valve chamber, to an exhaust port is formed. 2. A decompression chamber partitioned from the valve chamber by a sealing member is formed between each of the valve bodies and the spool, and the decompression chamber is communicated with an exhaust-side passage through a vent hole. The slide valve according to claim 1.