JPH1124756A - Regulator for solenoid valve manifold - Google Patents

Abstract

(57) [Problem] To provide a pressure regulator for a solenoid valve manifold capable of securing a large flow rate without impairing compactness. SOLUTION: This solenoid valve manifold pressure regulator 2 comprises:
Specific one 4 of a plurality of solenoid valves 4A to 4E provided in series
This is for adjusting the pressure of the fluid supplied to and discharged from B. The pressure regulator main body 40 is arranged between the solenoid valves 4B and 4C and the manifold base 3. The first solenoid valve 4B participates in pressure regulation. The second solenoid valve 4C is not involved in pressure regulation and is adjacent to the first solenoid valve 4B. A second flow path group that connects the second solenoid valve 4C side and the manifold base 3 side is formed in a partial region of the pressure regulator main body 40. A first flow path group that connects the first solenoid valve 4B side and the manifold base 3 side is formed in the remaining area. A pressure regulating member having a main valve and a pressure receiving body is accommodated in a flow path belonging to the first flow path group.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a pressure regulator for a solenoid valve manifold.

[0002]

2. Description of the Related Art Conventionally, a device called a spacer regulator has been known as a kind of a solenoid valve manifold pressure regulator disposed between a manifold base and a solenoid valve. The spacer regulator is a device for reducing a fluid supplied to and discharged from a specific one of a plurality of solenoid valves connected in series to a predetermined pressure value. Here, FIGS. 10 and 11 show an example of a conventional spacer regulator 81. FIG.

The manifold base 82 includes five base blocks 83, one supply / exhaust block 84, and two end blocks 85. On an upper surface of each base block 83, a plurality of ports (not shown) communicating with the main flow path are formed. Except for the second one from the left in FIG. 10, solenoid valves 86 are directly installed on the upper surfaces of the other four base blocks 83. A plurality of ports (not shown) are formed on the lower surface of the solenoid valve 86 so as to correspond to the ports on the base block 83 side. On the other hand, on the upper surface of the second base block 83 from the left in FIG. 10, an electromagnetic valve 86 is indirectly installed via a spacer regulator 81.

As shown in FIG. 11, the spacer regulator 81 is constituted by a main body 87 having a width equal to the width of one solenoid valve 86. This body 8
7, a plurality of flow paths 91, 92, 93, 94, 95 are formed. These flow paths 91 to 95 communicate a port on the manifold base 82 side and a port on the solenoid valve 86 side. A pressure regulating member 99 including a main valve 96, a rod 97, and a piston 98 is slidably accommodated in the middle of one of the plurality of flow paths 91 to 95. A valve seat 100 is provided in the flow passage 93 so that a main valve 96 at one end of a rod 97 can be connected to and separated from the main valve 96. The fluid pressure in the flow passage 93 acts on the pressure receiving surface side of the piston 98 at the other end of the rod 97. As a result, the piston 98
Is pressed along the longitudinal direction of the main body 87. Piston 9
The coil spring 101 is provided on the non-pressure receiving surface side of 8. The spring force of the coil spring 101 acts in a direction opposite to the pressing force by the fluid. The spring force of the coil spring 101 can be adjusted by an operating body including an adjusting screw 102 and a lock nut 103.

Therefore, according to the spacer regulator 81 configured as described above, the adjusting screw 1
02 by rotating the main valve 96 and the valve seat 1.
The flow rate of the fluid flowing through 00 can be reduced.
Therefore, the fluid supplied to and discharged from the specific solenoid valve 86 can be reduced to a predetermined pressure value.

[0006]

In recent years, there has been a strong demand for a fluid pressure device capable of securing a large flow rate despite its compactness, and a solenoid valve 86 satisfying this kind of needs has been demanded. Has gradually appeared.

However, the spacer regulator 81
The pressure regulators satisfying the above requirements have not yet appeared. Therefore, even if the current spacer regulator 81 is simply scaled down, it is inevitable that the effective cross-sectional area of the flow path decreases due to the reduced size of each component. In this case, although the flow path is narrowed by the spacer regulator 81 and the electromagnetic valve 86 having a large flow rate is used, it is not possible to achieve the high performance as a whole.

Further, when the spacer regulator 81 is scaled down, the pressure receiving area of the piston 98 becomes small, and this has also been one of the causes of performance degradation.

The present invention has been made in view of the above circumstances, and an object of the present invention is to provide a regulator for a solenoid valve manifold capable of securing a large flow rate without impairing compactness.

[0010]

In order to solve the above-mentioned problems, the invention according to the first aspect of the present invention regulates the fluid supplied to and discharged from a specific one of a plurality of solenoid valves connected in series. A pressure regulator arranged between the manifold base and the solenoid valve for performing pressure, wherein said first solenoid valve is not involved in pressure regulation and said first solenoid valve is not involved in pressure regulation. A pressure regulator main body is arranged between a second solenoid valve adjacent to the pressure regulator and the manifold base, and a second region that communicates the second solenoid valve side and the manifold base side to a partial area of the pressure regulator main body. And a pressure regulating member having a main valve and a pressure receiving member, wherein a first flow path group communicating between the first solenoid valve side and the manifold base side is formed in the remaining area while forming a second flow path group. Is accommodated in a channel belonging to the first channel group. That the pressure regulator solenoid valve manifold as its gist.

According to a second aspect of the present invention, in the first aspect, the first flow path group is provided in a partial area of the pressure regulator main body having a width corresponding to the width of two solenoid valves. And the second channel group is formed in the remaining region.

According to a third aspect of the present invention, in the first or second aspect, the cross-sectional shape of the flow path constituting the flow path group is:
The solenoid valve has an elliptical or rectangular shape that is long along the width direction.

Hereinafter, the "action" of the present invention will be described. According to the first to third aspects of the present invention, the region in which the flow path group can be formed increases by increasing the lateral width of the pressure regulator as compared with the related art, and the layout of the flow path group becomes easy. More specifically, the second flow path group not involved in pressure regulation does not require a large area for formation as compared with the first flow path group involved in pressure regulation. Therefore, when forming the first flow path group in the remaining area of the pressure regulator main body, it is possible to protrude the first flow path group to some extent in the lateral width direction. Therefore, even if it is a compact pressure regulator, the flow path is not restricted, and a large flow rate is secured.

According to the second aspect of the present invention, since the width corresponds to the width of two solenoid valves, the pressure regulator becomes compact, and the size of the entire solenoid valve manifold can be minimized. .

According to the third aspect of the invention, when a plurality of flow paths having a large cross-sectional area are to be formed in a limited space, the flow path having such a shape is more advantageous than a flow path having a circular cross-section. It is. In addition, if the flow path has an elliptical cross section or the like, drilling is not so difficult, and a reduction in workability and cost can be avoided.

[0016]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment in which the present invention is embodied in a spacer regulator 2 for a solenoid valve manifold 1 will be described in detail with reference to FIGS.

FIGS. 1 and 2 show the solenoid valve manifold 1 of the present embodiment as a whole. The solenoid valve manifold 1 includes a manifold base 3 and solenoid valves 4A to 4E.
And a P port pressure reducing spacer regulator 2.

The manifold base 3 is composed of five base blocks 11, one supply / exhaust block 12, and two end blocks 13. The pair of end blocks 13 are located at both ends of each base block 11 and the supply / exhaust block 12. As shown in FIG. 3, through holes penetrating both left and right surfaces are formed at a plurality of locations of each base block 11. The same applies to the supply / exhaust block 12. These through holes form a first main flow path 14, a second main flow path 15, and the like when the blocks 11, 12, and 13 are connected in series. These main flow paths 14 and 15 are connected to a pressurized air supply source (not shown) as a fluid supply source.

Exhaust ports are provided at two positions of the supply / exhaust block 12, and a silencer 16 is attached to each of the exhaust ports. Silencer 16
Plays a role in reducing noise during exhaust.

A fixing portion is formed on the outer surface of both end blocks 13. Screws 17 on these fixing parts
Is concluded, each block 11, 12, 13
Are fixedly connected on a metal DIN rail 18.

Each base block 11 constituting the manifold base 3 has one A port 19 and one B port 20 on the front side thereof. These ports 19, 2
0 has a so-called one-touch joint structure. The A port 19 and the B port 20 are connected to each actuator via piping (not shown). Accordingly, air depressurized to a predetermined pressure is supplied to and discharged from each actuator.

As shown schematically in FIG. 4, on the upper surface of each base block 11, a main flow path 14,
Plural ports 21, 22, 23, 2 communicating with 15 etc.
4 and 25 are formed respectively. These ports 2
1 to 25 are in the longitudinal direction of the base block 11 (that is, DI
(The short direction of the N rail 18). The port located in the middle of these ports 21 to 25 is the P port 23. In this embodiment, the width of each base block 11 is 10.5 mm, which is a conventional product (width = 16 mm pitch) shown as a reference example in FIG.
The pitch is set narrower than 2.

As shown in FIG. 1 and the like, the solenoid valve manifold 1 has a plurality (five in this embodiment) of solenoid valves 4.
A, 4B, 4C, 4D, and 4E. The solenoid valves 4A to 4E used in the present embodiment are two-position five-way valves,
It comprises a valve body having a spool and a solenoid. The solenoid valves 4A to 4E are configured to drive a spool by controlling the energization of a solenoid portion, and thereby switch the internal flow path. A plurality of ports 31, 32, 33, 34, 35 are provided on the lower surface side of each of the solenoid valves 4A to 4E. The port located in the middle of these ports 31 to 35 is the P port 33. The port 31 is located at a position corresponding to the port 21 on the base block 11 side. Similarly, the port 32 exists at a position corresponding to the port 22, the port 33 exists at a position corresponding to the port 23, the port 34 exists at a position corresponding to the port 24, and the port 35 exists at a position corresponding to the port 25. The width of the solenoid valves 4A to 4E is equal to that of the base block 11, and is set at a pitch of 10.5 mm.

In the present embodiment, the purpose is to regulate the pressure of only one specific one of the five solenoid valves 4A to 4E, that is, only the second solenoid valve 4B from the left in FIGS. Therefore, this solenoid valve 4B is defined as a first solenoid valve 4B involved in pressure regulation. In the figure, a solenoid valve 4C not involved in pressure regulation is adjacent to the right side of the first solenoid valve 4B, and is defined as a second solenoid valve 4C.

The other three solenoid valves 4A, 4D and 4E except for the first solenoid valve 4B and the second solenoid valve 4C are installed directly on the upper surface of the base block 11 as shown in FIG. ing. Therefore, pressurized air that has not been depressurized is directly supplied to these solenoid valves 4A, 4D, and 4E from the P port 23 on the base block 11 side. Meanwhile, the first
The spacer regulator 2 is installed between the lower surfaces of the solenoid valves 4B and 4C and the upper surface of the base block 11.

Next, the configuration of the spacer regulator 2 will be described in detail. As shown in FIG. 4, a regulator main body 40 as a pressure regulator main body forms a main part of the spacer regulator 2. The regulator body 40 of the present embodiment is formed so as to have a width exactly equal to the width of two solenoid valves 4B and 4C (FIG. 1).
reference). That is, in the present embodiment, the value of the width is 21 mm.

A second flow path group is formed in a part of the regulator body 40 (slightly less than half on the right side in FIG. 1). Further, a first flow path group is formed in the remaining area (an area slightly more than half on the left side in FIG. 1).

As shown in FIGS. 5 and 6, the second flow path group includes five flow paths 51, 52, 53, 54 and 55. These flow paths 51 to 55 communicate the second electromagnetic valve 4C side and the base block 11 side, respectively. Specifically, it is as follows. The flow path 51 is a base block 1
It exists at a position corresponding to the port 21 on the 1 side and the port 31 on the solenoid valve 4C side, and these 21 and 31 communicate with each other. Similarly, the flow path 52 exists at a position corresponding to the ports 22 and 32, and connects the ports 22 and 32 to each other. The channel 53 exists at a position corresponding to the ports 23 and 33, and connects the ports 23 and 33 to each other. Channel 5
4 is located at a position corresponding to the ports 24 and 34, and connects the ports 24 and 34 to each other. The flow path 55 exists at a position corresponding to the ports 25 and 35, and
5 communicate with each other.

Each of the flow paths 51 to 55 constituting the second flow path group
Have the same cross-sectional shape everywhere, and are all elliptical along the width direction of the solenoid valve 4C. Each channel 51-5
5 is an upper surface 40 a and a lower surface 40 of the regulator body 40.
It is formed in a straight shape so as to penetrate b. Further, these flow paths 51 to 55 are provided in the regulator body 40.
Are arranged substantially in a straight line along the longitudinal direction. The flow paths 51 to 55 can be formed by a conventionally known hole processing such as counterboring. In addition, when the regulator body 40 is viewed from the front side, the second
The area occupied by the flow path group is not as large as the area occupied by the first flow path group, and is equal to or less than half of the regulator body 40.

On the other hand, as shown in FIGS.
Also includes five flow paths 41, 42, 43, 44, and 45. These flow paths 41 to 45 are connected to the first solenoid valve 4B.
Side and the base block 11 side communicate with each other.
Specifically, it is as follows. The flow path 41 exists at a position corresponding to the port 21 on the base block 11 side and the port 31 on the electromagnetic valve 4B side, and connects the ports 21 and 31 to each other. Similarly, the flow path 42 exists at a position corresponding to the ports 22 and 32, and connects the ports 22 and 32 to each other. The channel 43 exists at a position corresponding to the ports 23 and 33, and connects the ports 23 and 33 to each other. The flow path 44 exists at a position corresponding to the ports 24 and 34,
These 24 and 34 communicate with each other. The channel 45 is
Existing at positions corresponding to ports 25 and 35,
5, 35 communicate with each other.

The four flow paths 41 constituting the first flow path group,
Although the cross-sectional shapes of 42, 44, and 45 are not the same cross-sectional shape, they are all elliptical along the lateral width direction of the solenoid valve 4B. These four flow paths 41, 42, 4
4 and 45 are formed in a straight shape so as to penetrate the upper surface 40 a and the lower surface 40 b of the regulator body 40. However, the openings at the upper and lower ends are formed somewhat larger in diameter than the inside. The flow paths 41, 42, 4
The reference numerals 4 and 45 are arranged substantially in a straight line along the longitudinal direction of the regulator body 40.

A flow path 43 communicating with the P ports 23 and 33
Has a more complicated shape than the other flow paths 41, 42, 44 and 45. At the center of the regulator body 43,
A space 43a is formed to extend along the longitudinal direction. The pressure adjusting member 61 is slidably accommodated in the space 43a. The space 43 a has a circular cross section and forms a part of the flow path 43. That is, the space 43a communicates with the elliptical opening on the upper surface 40a side. The space 43a communicates with a curved groove-shaped opening on the lower surface 40b side.

As shown in FIG. 4, the pressure regulating member 61 of this embodiment includes a main valve 62, a rod 63 as a transmission member, and a piston 64 as a pressure receiving member. Rod 6
Reference numeral 3 denotes a metal rod-shaped member having a circular cross section. In the figure, the main valve 62 is connected to the right end of the rod 63, and the piston 64 is connected to the left end. Therefore, the main valve 62,
The rod 63 and the piston 64 are
Can be integrally moved along the longitudinal direction of the. A valve seat 65 is formed on an inner wall of a portion that partitions the space 43a. The valve seat 65 and the main valve 62 are in a positional relationship such that they can come and go with each other. When the pressure adjusting member 61 is moving rightward in FIG. 4, the gap between the valve seat 65 and the main valve 62 is large. Conversely, when the pressure adjusting member 61 is moving to the left in FIG. 4, the gap formed between the valve seat 65 and the main valve 62 becomes smaller.

The pressure of the air flowing through the flow passage 43 acts on the pressure receiving surface side (the right end surface side in FIG. 4) of the piston 64. As a result, the piston 64 is pressed to the left. A coil spring 66 and a spring disk 67 as urging means are arranged on the non-pressure receiving surface side (the left end surface side in FIG. 4) of the piston 64. One end of the coil spring 66 is in contact with the right end surface of the spring disk 67, and the other end is in contact with the left end surface of the piston 64. Therefore, the piston 64 is constantly urged in a direction opposite to the pressing force, that is, rightward.

On the front end face of the regulator body 40,
A cover 68 and a lock nut 69 are provided. A screw insertion hole having a female screw groove is formed in the cover 68 and the lock nut 69. An adjusting screw 70 is rotatably inserted into the screw insertion hole. The cover 68, the lock nut 69, and the adjusting screw 70 constitute one operation body. The tip of the adjusting screw 70 is in contact with the left end surface of the spring disc 67. When the screwing amount of the adjusting screw 70 is increased, the spring disk 67 moves rightward, and the coil spring 6
The compression amount of No. 6 increases. As a result, the spring force of the coil spring 66 increases. Conversely, when the screwing amount of the adjusting screw 70 is reduced, the spring disk 67 moves to the left, and the compression amount of the coil spring 66 decreases. As a result, the spring force of the coil spring 66 decreases. That is, by changing the screwing amount by rotating the adjusting screw 70, the set pressure at the time of pressure reduction can be arbitrarily adjusted.

Now, the characteristic effects of this embodiment will be listed below. (A) In the solenoid valve manifold 1, the spacer regulator 2 is configured to be disposed between the base block 11 and the first and second solenoid valves 4B and 4C. Therefore, despite the use of the narrow pitch solenoid valves 4A to 4E and the base block 11, the width of the regulator body 40 is larger than that of the conventional product (see FIGS. 7 and 8). For this reason, the regulator body 40
The area in which the flow path group can be formed increases, and the layout of the first and second flow path groups becomes easier than before. More specifically, the second flow path group including the flow paths 51 to 55 not involved in the pressure regulation is more difficult to form than the first flow path group including the flow paths 41 to 45 involved in the pressure regulation. Does not require a large area. Therefore, when forming the first flow path group in the remaining area of the regulator main body 40, the first flow path group can be protruded to some extent in the lateral width direction. Therefore, even when the compact spacer regulator 2 is used, the flow paths 41 to 45 and 51 to 5
5 does not decrease, and the flow paths 41 to 45, 51 to 5
5 will not be squeezed. Therefore, a large flow rate can be secured in the spacer regulator 2.

(B) In this solenoid valve manifold 1, the width of the regulator body 40 is equivalent to the sum of the widths of the first solenoid valve 4B and the second solenoid valve 4C (just the width pitch of two solenoid valves). doing. Therefore, the solenoid valve manifold 1 can be made more compact as compared to a case in which it is equivalent to three or more horizontal pitches, and the size of the entire solenoid valve manifold 1 can be minimized. Further, since there is no gap between the side surface of the regulator body 40 and the side surfaces of the solenoid valves 4A and 4D, it is possible to reliably prevent the appearance of the entire device from deteriorating.

(C) In this solenoid valve manifold 1, the cross-sectional shape of each of the flow paths 41, 42, 44, 45, 51 to 55 is an elliptical shape that is long along the width direction of the solenoid valves 4B and 4C. With such a cross-sectional shape, waste of space can be reduced as compared with, for example, a circular cross-sectional shape. Accordingly, in the limited space of the regulator body 40, the plurality of flow paths 41, 4 having a large cross-sectional area are provided.
2, 44, 45, 51 to 55 can be formed relatively easily. In addition, flow paths 41, 42, 4 having an elliptical cross section
If it is 4, 45, 51 to 55, drilling is not so difficult. Therefore, there is an advantage that reduction in workability and cost can be avoided.

(D) According to the configuration of this embodiment, the space 4
Since it is possible to increase the cross-sectional area of 3a to some extent, it is possible to increase the pressure receiving area of the piston 64 as the pressure receiving body. In this case, the setting of the reduced pressure value by the operating tool can be performed more accurately.

It should be noted that the present invention is not limited to the above-described embodiment, but can be modified to another form as follows, for example. It may be configured as another example of the solenoid valve manifold 76 shown in FIG. The solenoid valve manifold 76 includes five solenoid valves 74A, 74B, 74C, 74D, and 74E. Two of the solenoid valves 74B and 74D are first solenoid valves 74B and 74D involved in pressure regulation, and a solenoid valve 74C located therebetween is a second solenoid valve 7 not involved in pressure regulation.
4C. In the case of the spacer regulator 77 used in the solenoid valve manifold 76, the width of the regulator body 40 corresponds to the width of three solenoid valves 74B, 74C, and 74D. That is, the value of the width is 31.
It is set to 5 mm. And the regulator body 40
Are formed with two first flow path groups composed of flow paths 41 to 45. Therefore, the regulator body 40 has a pair of right and left pressure regulating members 61 therein, and the adjusting screw 70 is
One is provided. In a region located between the two first flow path groups, one second flow path group including the flow paths 51 to 55 is formed. With this configuration, the pressure of the fluid supplied to and discharged from the two solenoid valves 74B and 74D can be individually adjusted by only one spacer regulator 76.

The rod 63 having a circular cross section may be formed into a vertically long and short cross section. The rod 6
Preferably, the cross-sectional area of No. 3 is maintained at the same level as the current state. With this configuration, space saving in the regulator body 40 is achieved. As a result, when forming the first and second flow path groups, it is possible to easily secure a large flow rate.

The manifold base 3 is not limited to a plurality of base blocks 11, a supply / exhaust block 12, and the like, and may be an integrally molded product. The solenoid valves 4A to 4E and 74A to 74E are not limited to the two-position five-way valve as in the embodiment, but may be other types of solenoid valves such as a three-position five-way valve. .

流 路 Flow paths 41 to 45, 5 constituting flow path group
The cross-sectional shape of 1 to 55 may be not only an elliptical shape that is long along the width direction of the solenoid valve, but also, for example, a rectangle that is long along the width direction of the solenoid valve.

The present invention provides a spacer regulator 2, 77 for reducing the pressure of a fluid supplied to or discharged from a specific solenoid valve.
Not only that, the present invention may be embodied as, for example, an in-stop valve or the like for the purpose of flowing and shutting off a fluid to be supplied to and discharged from a specific solenoid valve.

Here, in addition to the technical ideas described in the claims, the technical ideas grasped by the above-described embodiments are listed below together with their effects. (1) The second flow path group according to claim 1, wherein two first flow path groups are formed in a partial area of the pressure regulator main body having a width corresponding to three widths of the solenoid valves. A pressure regulator for an electromagnetic valve manifold, wherein one second flow path group is formed in a region located between one flow path group.
With this configuration, the pressure of the fluid supplied to and discharged from the two solenoid valves can be individually adjusted by only one pressure regulator.

(2) The pressure regulator according to any one of claims 1 to 3, wherein the pressure regulator is a spacer regulator for reducing the pressure of a fluid supplied to and discharged from a specific solenoid valve to an arbitrary pressure value. Pressure regulator for solenoid valve manifold. With this configuration, it is possible to realize a compact and large flow rate spacer regulator.

(3) The pressure regulator according to any one of claims 1 to 3, wherein the pressure regulator is an in-stop valve capable of flowing and shutting off a fluid to be supplied to and discharged from a specific solenoid valve. Characteristic pressure regulator for solenoid valve manifold.
With this configuration, a compact and high flow rate in-stop valve can be realized.

(4) The valve seat according to any one of (1) to (3) and (1) to (3), wherein the valve seat is provided in the flow passage at a position capable of coming in contact with and separating from the main valve. A transmitting member for connecting the main valve and the pressure receiving member so as to be integrally movable, a biasing means for biasing the pressure receiving member along a longitudinal direction of the transmission member, and changing a biasing force of the biasing means; And an operating body for adjusting a flow rate of a fluid flowing through the main valve and the valve seat. According to this configuration, the pressure can be reliably adjusted by changing the urging force of the urging means by operating the operating body.

(5) The transmission member according to any one of claims 1 to 3 and technical ideas 1 to 4, wherein a cross section of the transmission member for connecting the valve body and the pressure receiving body so as to be integrally movable is made vertically long and short. A pressure regulator for a solenoid valve manifold characterized by being formed. With this configuration, the space in the pressure regulator main body can be saved, so that a large flow rate can be more easily secured.

The technical terms used in this specification are defined as follows. "Fluids: nitrogen, oxygen, carbon dioxide, argon, hydrogen,
Gases such as air, water, oil,
It refers to liquids such as alcohol, critical fluids, and others having properties similar to these. "

[0051]

As described above in detail, according to the first to third aspects of the present invention, it is possible to provide a pressure regulator for a solenoid valve manifold capable of securing a large flow rate without impairing compactness. it can.

According to the second aspect of the invention, the size of the entire solenoid valve manifold can be minimized. According to the third aspect of the present invention, it is possible to relatively easily form a plurality of flow paths having a large cross-sectional area because wasteful space is reduced, and to avoid a reduction in workability and cost. it can.

[Brief description of the drawings]

FIG. 1 is a front view showing a solenoid valve manifold according to an embodiment of the present invention.

FIG. 2 is a plan view showing the solenoid valve manifold of FIG.

FIG. 3 is a sectional view taken along line AA of the solenoid valve manifold of FIG. 1;

FIG. 4 is a sectional view showing a spacer regulator.

FIG. 5A is a partial schematic plan view of a regulator body,
(B) is a partial schematic cross-sectional view of the regulator main body, and (c) is a partial schematic bottom view of the regulator main body.

6A is a sectional view taken along line BB in FIG. 5C,
(B) is a sectional view taken along the line CC, and (c) is also a DD line.
(D) is a sectional view taken along the line E-E, and (e) is a sectional view
-F line sectional drawing.

FIG. 7 is a partial schematic front view showing a conventional solenoid valve manifold.

FIG. 8 is a partial schematic front view showing the solenoid valve manifold of the embodiment.

FIG. 9 is a partial schematic front view showing another example of a solenoid valve manifold.

FIG. 10 is a front view showing a conventional solenoid valve manifold.

11A is a plan view of a conventional spacer regulator, and FIG. 11B is a cross-sectional view thereof.

[Explanation of symbols]

2, 77: spacer regulator as a regulator for solenoid valve manifold, 4B, 74B, 74D: first solenoid valve, 4C, 74C: second solenoid valve, 11: manifold base, 40: regulator as regulator body Body,
41 to 45... Channels constituting the first channel group 51 to 55
... Channels constituting the second channel group, 61..
... Main valve, 64 ... Piston as pressure receiving body.

Claims (3)

[Claims] A pressure regulator disposed between a manifold base and a solenoid valve for regulating the pressure of a fluid supplied to and discharged from a specific one of a plurality of solenoid valves connected in series. A pressure regulator main body disposed between the first solenoid valve involved in pressure regulation and a second solenoid valve not involved in pressure regulation and adjacent to the first solenoid valve and the manifold base; Forming a second flow path group for communicating the second solenoid valve side and the manifold base side in a partial area of the pressure regulator main body, and forming a second flow path group in the remaining area. A first flow path group that communicates with the manifold base side is formed, and a pressure regulating member including a main valve and a pressure receiving member is formed by the first pressure regulating member.
A pressure regulator for an electromagnetic valve manifold, wherein the pressure regulator is housed in a flow path belonging to the flow path group. 2. The pressure regulator according to claim 1, wherein one of the first flow passage groups is formed in a partial area of the pressure regulator main body having a width corresponding to two of the electromagnetic valves. The pressure regulator for a solenoid valve manifold according to claim 1, wherein one flow path group is formed. 3. A cross-sectional shape of a flow path constituting the flow path group,
The pressure regulator for an electromagnetic valve manifold according to claim 1, wherein the pressure regulator is an elliptical shape or a rectangular shape elongated in a width direction of the electromagnetic valve.