JP2015224711A - Multi-way switching valve - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a multi-way switching valve that does not require complex configuration, has a small number of parts, and can reduce cost, and moreover, provides a number of types (directions) of switching and is applicable to a variety of uses and fields.SOLUTION: The multi-way switching valve comprises: a plurality of horizontal flow passages 44 formed in a valve body 12 so as to be separated mutually at a fixed central angle in the rotational direction of a ball valve element 20, and communicating with a valve chamber 14; a vertical flow channel 62 formed in the valve body 12 in the direction of a drive shaft 18 of the ball valve element 20, and communicating with the valve chamber 14; a horizontal communication flow passage 64 formed in the ball valve element 20 so as to provide communication between the horizontal flow passages 44 each other; and a vertical communication flow passage 66 formed in the ball valve element 20 so as to provide communication between one of the horizontal flow passages 44 and the vertical flow passage 62.

Description

  The present invention is used, for example, for fluid control of a refrigerant circulation circuit of an air conditioner such as an air conditioner or a refrigerator, a fluid in a plant, a gas in a gas field, etc. The present invention relates to a multi-way switching valve for switching.

  Conventionally, a ball valve has been widely used as a multi-way switching valve of this type, and this ball valve can be operated by simply rotating a rotating shaft connected to the ball valve body, by a flow path formed in the ball valve body. Since the flow path can be switched, there is an advantage that the operation is quick and simple.

  For example, in Patent Document 1 (Japanese Patent Laid-Open No. 59-013170), as a ball valve functioning as such a multi-way switching valve, a four-way ball valve in which there is no deviation of the ball valve body and valve leakage does not increase. Is disclosed.

  That is, as shown in FIG. 11, in the ball valve 100 of Patent Document 1, four horizontal flow paths 106 to 100 are spaced apart from each other at a central angle of 90 ° so as to communicate with the valve main body 102 and the valve chamber 104. 112 is formed. And cyclic | annular protrusion part 106a-110a is formed in the opening part of three horizontal direction flow paths 106-110 among these four horizontal direction flow paths.

  An annular valve seat member 114 is slidably fitted on the outer periphery of these protrusions 106a to 110a. Further, a seal member accommodation groove 116 is formed on the inner periphery of these valve seat members 114, and by attaching an O-ring 118 to the seal member accommodation groove 116, so-called back leakage from the high pressure side to the low pressure side is prevented. It is configured to prevent and maintain airtightness.

  Further, a pressing member comprising a washer 120 and a disc spring 122 is interposed between the rear end of the valve seat member 114 and the valve body 102, and presses the valve seat member 114 against the ball valve body 124 (pressing) To be configured).

  Further, the ball valve body 124 is formed with two communication channels (valve holes) 126 and 128, and two adjacent channels among the four horizontal channels 106 to 112 formed in the valve body 102. It is comprised so that it may communicate with. Further, the ball valve body 124 is formed with an insertion hole 130 in the vertical direction at the center thereof, and the rotating shaft 132 is inserted into the insertion hole 130.

  With this configuration, the rotating shaft 132 is not displaced even when receiving fluid pressure, and leakage is caused by applying the pressing force of the pressing member and the fluid pressure to the rear end of the valve seat member 114. Is configured not to occur.

  Patent Document 2 (Japanese Patent Laid-Open No. 2013-44354) discloses a four-way ball valve having a simpler structure than the ball valve 100 of Patent Document 1 as a ball valve that functions as a multi-way switching valve. Yes.

  That is, as shown in FIG. 12, in the ball valve 200 of Patent Document 2, four horizontal flow paths 206 spaced apart from each other at a central angle of 90 ° so as to communicate with the valve main body 202 and the valve chamber 204. , 208, 210, 212 are formed.

  Then, a valve seat member accommodating groove 214 is formed around the opening on the valve chamber 204 side of these horizontal flow paths 206, 208, 210, 212, and these valve seat member accommodating grooves 214 are formed in the valve seat member accommodating grooves 214. The valve seat member 216 and a seal member 220 that presses the valve seat member 216 against the ball valve body 218 are mounted.

  The ball valve body 218 is formed with two communication channels (valve holes) 222 and 224, and each of the four horizontal channels 206, 208, 210 and 212 formed in the valve body 202 is adjacent to each other. It is comprised so that it may communicate with two flow paths.

JP 59-013170 A JP 2013-043354 A

  However, such a conventional multi-way switching valve has the following problems.

  That is, in the ball valve 100 of Patent Document 1, there is no deviation of the ball valve body, and the rotation shaft 132 is accurately placed in the insertion hole 130 formed in the ball valve body 124 in order to prevent valve leakage. It must be penetrated, and the cost is high.

  Further, in the ball valve 100 of Patent Document 1, it is necessary to provide the annular protrusions 106a to 110a and the annular valve seat member 114, and an O-ring 118 attached to a seal member accommodation groove 116 for preventing so-called back leakage, In addition, it is necessary to provide a pressing member including a washer 120 and a disc spring 122 for urging the valve seat member 114 to the ball valve body 124, which requires a complicated configuration, increases the number of parts, and increases costs. become.

  Further, in the ball valve 100 of Patent Document 1, as shown in FIG. 11, two communication channels (valve holes) 126 and 128 formed in the ball valve body 124 are formed in four horizontal directions formed in the valve body 102. Of the flow paths 106, 108, 110, and 112, only two adjacent flow paths can communicate with each other, so the types (directions) of switching are limited, and thus the field and application are limited. It will be.

  In addition, the ball valve 200 of Patent Document 2 has a simple structure as compared with the ball valve 100 of Patent Document 1, but as shown in FIG. The communication flow paths (valve holes) 222 and 224 formed in the ball valve body 218 cannot communicate with two adjacent flow paths among the four horizontal flow paths 206 to 212 formed in the valve body 202. Therefore, the types of switching are limited, and this limits the field and application.

  In addition, both the ball valve 100 of Patent Document 1 and the ball valve 200 of Patent Document 2 need to form all the flow paths in the valve body as four horizontal flow paths. The ball valve will be enlarged.

  In view of such a current situation, the present invention does not require a complicated configuration, has a small number of parts, can reduce costs, and has many types (directions) of switching, and can be applied to various fields and applications. The purpose is to provide a valve.

  Another object of the present invention is to provide a multi-way switching valve that prevents so-called back leakage from the high pressure side to the low pressure side, maintains airtightness, and provides stable performance.

  Furthermore, an object of the present invention is to provide a multi-way switching valve that can obtain a stable performance without causing a so-called liquid seal in the gap between the ball valve body and the valve main body and causing damage.

The present invention has been invented in order to achieve the problems and objects in the prior art as described above.
A multi-way switching valve that switches the flow of fluid by the operation of a valve body,
A ball valve body mounted in a valve chamber formed inside the valve body and configured to rotate in the valve chamber by rotation of a drive shaft;
A plurality of horizontal flow paths formed in the valve body so as to be spaced apart from each other at a constant central angle in the rotation direction of the ball valve body, and communicating with the valve chamber;
A vertical flow path formed in the valve body in the direction of the drive shaft of the ball valve body and communicating with the valve chamber;
A horizontal communication channel formed in the ball valve body and configured to communicate between the horizontal channels;
A vertical communication channel formed in the ball valve body and configured to communicate one of the horizontal channels and a vertical channel;
It is characterized by providing.

  With this configuration, the valve body has a plurality of horizontal flow paths formed so as to be spaced apart from each other at a constant central angle in the rotation direction of the ball valve body, and the direction of the drive shaft of the ball valve body The vertical direction flow path formed in the.

  Correspondingly, the ball valve body is formed so as to communicate a horizontal communication channel formed so as to communicate the horizontal channels, and one of the horizontal channels and the vertical channel. And a vertical communication channel.

  Therefore, by rotating the ball valve body in the valve chamber by the rotation of the drive shaft, the types (directions) of switching are greatly increased compared to conventional multi-way switching valves, and can be applied to various fields and applications. A multi-way switching valve can be provided.

  Moreover, not only the horizontal flow path in the horizontal direction is formed as in the conventional multi-way switching valve, but also the vertical flow path in the vertical direction is formed. Can be made compact without increasing the size.

  Therefore, according to the multi-way switching valve of the present invention, a complicated configuration is not required, the number of parts is small, the cost can be reduced, and there are many types (directions) of switching, which can be applied to various fields and applications. A switching valve can be provided.

The multi-way selector valve of the present invention is
Around the opening on the valve chamber side of the horizontal flow path of the valve body, a valve seat member housing groove is formed,
A valve seat member and a seal member that presses the valve seat member against the ball valve body are attached to the groove portion for accommodating the valve seat member,
A gap L is formed between the valve seat member and the valve seat member receiving groove portion in a state where no differential pressure is applied,
The gap L is set to be smaller than the compression amount d of the seal member (L <d) in a state where the differential pressure is not acting.

  With this configuration, the valve seat member receiving groove is mounted with a valve seat member and a seal member that presses the valve seat member against the ball valve body, and between the valve seat member and the valve seat member receiving groove. The gap L is formed when no differential pressure is applied, and the gap L is set smaller than the compression amount d of the seal member (L <d) when the differential pressure is not applied. Yes.

  Therefore, since the restoring force of the seal member is always generated and the valve seat member is pressed against the ball valve body, the sealing performance is good, even if an abnormal high pressure is applied, the low pressure from the high pressure side. So-called back leakage to the side is prevented, airtightness is maintained, and stable performance can be obtained.

  Further, even if the valve seat member swells and deforms, a gap L is formed between the valve seat member and the valve seat member housing groove portion in a state where no differential pressure is applied. Swelling deformation can be absorbed by the seal member. Therefore, the problem that the ball tightening force becomes abnormally high and the operability deteriorates does not occur.

  Further, a valve seat member receiving groove is formed around the opening on the valve chamber side of the horizontal flow path of the valve body, and the valve seat member storing groove portion includes a valve seat member and a valve seat member in the ball valve. A sealing member that presses against the body is mounted to ensure sealing performance, but in the vertical flow path formed in the valve body in the direction of the drive shaft of the ball valve body, such a valve seat member, A seal member that presses the valve seat member against the ball valve body is not mounted.

  Therefore, the fluid that has entered the gap between the ball valve body and the valve body is discharged through the vertical flow path, so that a so-called liquid seal is formed in the gap between the ball valve body and the valve body, resulting in damage and damage. Stable performance can be obtained.

  In the multi-way switching valve of the present invention, the valve body is provided with a valve seat holding member, and the horizontal flow path and the valve seat member housing groove are formed in the valve seat holding member. And

  As described above, when the valve seat holding member is attached to the valve body, and the horizontal flow path and the valve seat member receiving groove are formed in the valve seat holding member, the horizontal flow path and the valve seat are formed in the valve body. Since these can be separately processed into the valve seat holding member and detachably mounted on the valve body without processing the member accommodating groove, the processing is easy and the maintainability is improved.

  In the multi-way switching valve according to the present invention, the horizontal flow path of the valve body is formed of an odd number of horizontal flow paths.

  In this way, if the horizontal flow path of the valve body is formed of an odd number of horizontal flow paths, a horizontal communication flow path that connects the horizontal flow paths of the valve body to the ball valve body, and a valve A vertical communication channel that communicates one of the remaining horizontal channels of the main body with the vertical channel of the valve body can be formed.

  The multi-way switching valve of the present invention is characterized in that the horizontal flow path of the valve body is formed of three horizontal flow paths.

  Thus, in the conventional four-way ball valve of Patent Document 1 and Patent Document 2, it is necessary to provide four horizontal flow paths, whereas in the four-way multi-way switching valve of the present invention, the valve body Since the horizontal flow path only needs to be formed from three horizontal flow paths, a space can be afforded accordingly, and the ball valve can be made compact without increasing its size.

The multi-way selector valve of the present invention is
Center angle θ: θ formed by the horizontal flow paths with no differential pressure acting
Gap between the valve seat member and the valve seat member receiving groove: L
Compression amount of seal member: d
When
L · cos (θ / 2) <d
It is characterized by satisfy | filling the relationship of these.

That is, L · cos (θ / 2) <d
For example, as shown in FIG. 8 and FIG. 9, the ball valve body 20 moves from the high pressure side to the low pressure side (B side) in the direction indicated by the arrow F in FIG. ), The crushing margin of the seal member 54 is secured on the high pressure side, and the restoring force of the seal member 54 is always applied, so that the valve seat member 56 is pressed against the ball valve body 20.
Thereby, sealing performance is ensured and high pressure fluid is effectively prevented from leaking from the high pressure side to the low pressure side (B side).

  Further, in the multi-way switching valve of the present invention, the gap L between the valve seat member and the valve seat member accommodating groove is L with respect to the compression amount d of the seal member in a state where no differential pressure is applied. It is characterized in that a relationship of / 2 <d is set.

  By configuring in this way, the horizontal flow path of the valve body is formed from three horizontal flow paths, and these horizontal flow paths are mutually fixed at a central angle of 120 ° in the rotation direction of the ball valve body. It is formed in the valve body so as to be separated from each other.

  Accordingly, the gap L between the valve seat member and the valve seat member receiving groove is set to a relationship of L / 2 <d with respect to the compression amount d of the seal member in a state where the differential pressure is not acting. Then, as will be described later, as shown in FIGS. 8 and 9, even if the ball valve body moves from the high pressure side to the low pressure side (B side), the crushing margin of the seal member is secured on the high pressure side. In this state, the restoring force of the seal member always acts and the valve seat member is pressed against the ball valve body.

  Thereby, sealing performance is ensured and high pressure fluid is effectively prevented from leaking from the high pressure side to the low pressure side (B side).

  According to the present invention, the valve body is formed in the direction of the drive axis of the ball valve body and the plurality of horizontal flow paths formed so as to be spaced apart from each other at a constant central angle in the rotation direction of the ball valve body. The vertical direction flow path was provided.

  Correspondingly, the ball valve body is formed so as to communicate a horizontal communication channel formed so as to communicate the horizontal channels, and one of the horizontal channels and the vertical channel. And a vertical communication channel.

  Therefore, by rotating the ball valve body in the valve chamber by the rotation of the drive shaft, the types (directions) of switching are greatly increased compared to conventional multi-way switching valves, and can be applied to various fields and applications. A multi-way switching valve can be provided.

  Moreover, not only the horizontal flow path in the horizontal direction is formed as in the conventional multi-way switching valve, but also the vertical flow path in the vertical direction is formed. Can be made compact without increasing the size.

  Therefore, according to the multi-way switching valve of the present invention, a complicated configuration is not required, the number of parts is small, the cost can be reduced, and there are many types (directions) of switching, which can be applied to various fields and applications. A switching valve can be provided.

FIG. 1 is a longitudinal sectional view of a multi-way switching valve in which a multi-way switching valve of the present invention is applied to a four-way ball valve, with a part thereof cut away. FIG. 2 is a cross-sectional view taken along the line II of FIG. FIG. 3 is a cross-sectional view taken along the line II of FIG. 1 for explaining the operating state of the multi-way selector valve of the present invention. 4 is a cross-sectional view taken along the line II of FIG. 1 for explaining the operating state of the multi-way selector valve of the present invention. FIG. 5 is an enlarged view of a portion II in FIG. FIG. 6 is an enlarged view of a portion II in FIG. 1 for explaining a state in which the valve seat member swells and deforms. FIG. 7 is a cross-sectional view taken along the line II of FIG. 1 for explaining the sealing state of the multi-way selector valve of the present invention. FIG. 8 is a cross-sectional view taken along the line II of FIG. 1 for explaining the sealing state of the multi-way selector valve of the present invention. FIG. 9 is a schematic view showing the relationship between the clearance L between the valve seat member 56 and the valve seat member housing groove 50 and the compression amount d of the seal member 54. FIG. 10 is a schematic view showing another embodiment of the multi-way selector valve 10 of the present invention. FIG. 11 is a cross-sectional view of a conventional ball valve 100. FIG. 12 is a cross-sectional view of a conventional ball valve 100.

Hereinafter, embodiments (examples) of the present invention will be described in more detail with reference to the drawings.
Example 1

  FIG. 1 is a longitudinal sectional view of a multi-way switching valve in which a multi-way switching valve of the present invention is applied to a four-way ball valve, with a part cut away, and FIG. 2 is a cross-sectional view taken along the line II of FIG. 3 to 4 are sectional views taken along the line II of FIG. 1 for explaining the operating state of the multi-way switching valve of the present invention, FIG. 5 is an enlarged view of a portion II in FIG. 1, and FIG. It is an enlarged view of the II part of Drawing 1 explaining the state where a member swells and deforms.

  1-4, the code | symbol 10 has shown the multiway switching valve 10 of this invention by the whole.

  As shown in FIGS. 1 to 4, the multi-way switching valve 10 of the present invention includes a valve body 12, and a substantially spherical valve chamber 14 is formed inside the valve body 12. In the valve chamber 14, for example, a ball valve body 20 connected to a drive shaft 18 of an actuator 16 constituted by a drive motor such as a direct current motor or a stepping motor is rotatably mounted.

  That is, as shown in FIG. 1, a slit 22 is formed at the center of the upper portion of the ball valve body 20, and an unillustrated non-rotating projecting portion formed at the lower end 24 of the drive shaft 18 in the slit 22. , The anti-rotation portion 26 is configured, and the drive shaft 18 and the ball valve body 20 are connected to each other.

  As shown in FIG. 1, an insertion hole 28 through which the drive shaft 18 is inserted is formed in the upper part of the valve main body 12, and is in a state communicating with the valve chamber 14. The insertion hole 28 includes an upper small diameter portion 30 and an enlarged diameter portion 32.

  As shown in FIG. 1, two flanges 34 formed on the upper portion of the drive shaft 18 are arranged in the small-diameter portion 30, and two seal members 36 made of O-rings are mounted between these flanges 34. By doing so, fluid is prevented from leaking to the outside.

  Further, a spring holding flange 38 is formed at the lower end 24 of the drive shaft 18, and a compression spring 42 in a compressed state is interposed between the holding ring 40 provided on the upper portion of the drive shaft 18, The O-ring 36 is always compressed. In FIG. 1, reference numeral 11 denotes a PTFE ring as a thrust bearing.

  1 and 2, the valve body 12 is formed so as to be spaced apart from each other at a fixed central angle (120 ° in this embodiment) in the rotational direction of the ball valve body 20. A plurality of (in this embodiment, three) horizontal flow paths 44 (44a to 44c) communicating with the valve chamber 14 are formed.

  That is, in FIGS. 1 and 2, a first horizontal flow path 44 a is formed on the right side (A side) of the valve body 12. The first horizontal flow path 44a is formed in a valve seat holding member 48a attached to an opening 46a formed on the right side (A side) of the valve body 12 in FIGS. Yes.

  As shown in the enlarged view of FIG. 5, a valve seat member accommodating groove 50a is formed around the opening on the valve chamber 14 side of the valve seat holding member 48a. The valve seat member receiving groove 50a is formed with a seal groove 52a at the bottom thereof, and an O-ring shaped seal member 54a is attached to the seal groove 52a.

  Further, a valve seat member 56a is mounted on the valve chamber 14 side of the seal member 54a in the valve seat member accommodating groove 50a of the valve seat holding member 48a. A valve seat seal surface 58a is formed on the valve seat member 56a on the side in contact with the ball valve body 20, and the valve seat member 56a is pressed against the ball valve body 20 and sealed by the restoring force of the seal member 54a. It is comprised so that.

  That is, as shown in FIG. 5, a gap L is formed between the valve seat member 56a and the valve seat member receiving groove 50a in a state where no differential pressure is applied, and the differential pressure is applied. In the absence, the gap L is set smaller than the compression amount d of the seal member 54a (L <d).

  Therefore, since the restoring force of the seal member 54a is always generated and the valve seat member 56a is pressed against the ball valve body 20, the sealing performance is good, even if an abnormal high pressure is applied. So-called back leakage from the side to the low pressure side is prevented, airtightness is maintained, and stable performance is obtained.

  As shown in FIG. 6, even if the valve seat member 56a swells and deforms, there is a gap L between the valve seat member 56a and the valve seat member accommodating groove 50a in a state where no differential pressure is applied. Since it is formed (see FIG. 6A), the swelling deformation of the valve seat member can be absorbed by the seal member (see FIG. 6B). Therefore, the problem that the ball tightening force becomes abnormally high and the operability deteriorates does not occur.

  As shown in FIGS. 1 and 2, a seal member 60a is mounted between the opening 46a of the valve body 12 and the valve seat holding member 48a so that the sealing performance is maintained. Yes.

  Similarly, as shown in FIG. 2, the side portion (B side) of the valve body 12 that is spaced apart from the right side portion (A side) of the valve body 12 by a central angle of 120 ° counterclockwise. Is formed with a second horizontal flow path 44b. The second horizontal flow path 44b is formed in a valve seat holding member 48b attached to an opening 46b formed on the side (B side) of the valve body 12 in FIG.

  Further, a valve seat member housing groove 50b is formed around the opening on the valve chamber 14 side of the valve seat holding member 48b. The groove 50b for accommodating the valve seat member is formed with a seal groove 52b at the bottom, and an O-ring shaped seal member 54b is attached to the seal groove 52b.

  Further, a valve seat member 56b is mounted on the valve chamber 14 side of the seal member 54b in the valve seat member accommodating groove 50b of the valve seat holding member 48b. A valve seat seal surface 58b is formed on the valve seat member 56b on the side in contact with the ball valve body 20, and the valve seat member 56b is pressed against the ball valve body 20 and sealed by the restoring force of the seal member 54b. It is comprised so that.

  Similarly to the valve seat holding member 48a, a gap L is formed between the valve seat member 56b and the valve seat member housing groove 50b in a state where no differential pressure is applied, and the differential pressure is applied. In such a state, the gap L is set smaller than the compression amount d of the seal member 54b (L <d).

  As shown in FIG. 2, a seal member 60b is mounted between the opening 46b of the valve main body 12 and the valve seat holding member 48b so that the sealing performance is maintained.

  Further, similarly, as shown in FIG. 2, the valve body 12 is located on the side (C side) of the valve body 12 that is 120 ° apart from the right side (A side) of the valve body 12 in the clockwise direction. A third horizontal flow path 44c is formed. The third horizontal flow path 44c is formed in a valve seat holding member 48c attached to an opening 46c formed in the side portion (C side) of the valve body 12 in FIG.

  Further, a valve seat member accommodating groove 50c is formed around the side opening of the valve chamber 14 of the valve seat holding member 48c. The valve seat member receiving groove 50c is formed with a seal groove 52c at the bottom thereof, and an O-ring shaped seal member 54c is attached to the seal groove 52c.

  Further, a valve seat member 56c is mounted on the valve chamber 14 side of the seal member 54c in the valve seat member accommodating groove 50c of the valve seat holding member 48c. A valve seat seal surface 58c is formed on the valve seat member 56c on the side in contact with the ball valve body 20, and the valve seat member 56c is pressed against the ball valve body 20 by the restoring force of the seal member 54c. The seat seal surface 58c is configured to be sealed.

  Similarly to the valve seat holding member 48a, a gap L is formed between the valve seat member 56c and the valve seat member accommodating groove 50c in a state where no differential pressure is applied, and the differential pressure is applied. In such a state, the gap L is set smaller than the compression amount d of the seal member 54c (L <d).

  As shown in FIG. 2, a seal member 60c is mounted between the opening 46c of the valve body 12 and the valve seat holding member 48c so that the sealing performance is maintained.

  Further, as shown in FIG. 1, a vertical flow path 62 communicating with the valve chamber 14 is formed in the bottom (D side) of the valve body 12 in the direction of the drive shaft 18 (vertical direction) of the valve body 12. Has been.

  On the other hand, as shown in FIGS. 1 to 2, the ball valve body 20 has a horizontal communication flow formed so that the horizontal flow paths 44 (44 a to 44 c) formed in the valve body 12 communicate with each other. A path 64 is formed.

  That is, the horizontal communication flow path 64 includes, for example, the second horizontal flow path 44b on the side (B side) of the valve body 12 and the valve when the ball valve body 20 is in the rotational position of FIG. It is formed so as to communicate with the third horizontal flow path 44 c on the side (C side) of the main body 12.

  As shown in FIG. 2, the horizontal communication channel 64 is, for example, the second horizontal direction on the side (B side) of the valve body 12 when the ball valve body 20 is in the rotational position of FIG. 2. The communication channel 64a communicates with the channel 44b, and the communication channel 64b communicates with the third horizontal channel 44c on the side (C side) of the valve body 12. That is, as shown in FIG. 2, the communication flow path 64a and the communication flow path 64b are separated from each other by a central angle of approximately 120 ° and communicate with each other.

  As shown in FIGS. 1 and 2, the ball valve body 20 communicates with one of the horizontal flow paths 44 (44 a to 44 c) formed in the valve body 12 and the vertical flow path 62. A vertical communication channel 66 is formed.

  That is, the vertical communication channel 66 is, for example, the first horizontal channel 44a on the right side (A side) of the valve body 12 when the ball valve body 20 is in the rotational position of FIG. The valve body 12 is formed so as to communicate with the vertical flow path 62 at the bottom (D side) of the valve body 12.

  As shown in FIGS. 1 to 2, the vertical communication channel 66 is formed on the right side (A side) of the valve body 12 when the ball valve body 20 is at the rotational position of FIG. 2, for example. A communication channel 66a formed in the horizontal direction communicating with the first horizontal channel 44a and a vertical communication channel 66b communicating with the vertical channel 62 on the bottom (D side) of the valve body 12; The communication channel 66a communicates with the communication channel 66b and the communication channel 66b.

  The operation of the multi-way selector valve 10 of the present invention configured as described above will be described with reference to FIGS.

  First, when the ball valve body 20 is in the rotational position of FIG. 2, as described above, the side portion (B side) of the valve body 12 passes through the horizontal communication flow path 64 of the ball valve body 20. The second horizontal flow path 44b communicates with the third horizontal flow path 44c on the side (C side) of the valve body 12. That is, a channel in the B⇔C direction is formed.

  When the ball valve body 20 is in the rotational position of FIG. 2, as described above, the right side portion (A side) of the valve body 12 via the vertical communication channel 66 of the ball valve body 20. ) Communicates with the vertical flow path 62 at the bottom (D side) of the valve body 12. That is, a flow path in the A⇔D direction is formed.

  Then, from the state where the ball valve body 20 is at the rotational position of FIG. 2, the actuator 16 is driven to rotate the ball valve body 20 connected to the drive shaft 18 by 120 ° counterclockwise in FIG. Thus, the ball valve body 20 is brought into a state of being in the rotational position of FIG.

  In this state, as shown in FIG. 3, the first horizontal flow path 44 a on the right side (A side) of the valve body 12 via the horizontal communication flow path 64 of the ball valve body 20, The third horizontal flow path 44c on the side (C side) of the valve body 12 communicates. That is, a flow path in the A⇔C direction is formed.

  Further, when the ball valve body 20 is in the rotational position of FIG. 3, the second horizontal direction of the side portion (B side) of the valve body 12 via the vertical communication channel 66 of the ball valve body 20. The flow path 44b communicates with the vertical flow path 62 at the bottom (D side) of the valve body 12. That is, a channel in the B⇔D direction is formed.

  Subsequently, the actuator 16 is driven from the state in which the ball valve body 20 is at the rotational position in FIG. 3, and the ball valve body 20 connected to the drive shaft 18 is rotated by 120 ° counterclockwise in FIG. Thus, the ball valve body 20 is in a state of being in the rotational position of FIG.

  In this state, as shown in FIG. 4, the first horizontal flow path 44 a on the right side (A side) of the valve body 12 via the horizontal communication flow path 64 of the ball valve body 20, The second horizontal flow path 44b on the side (B side) of the valve body 12 communicates. That is, a flow path in the A⇔B direction is formed.

  Further, when the ball valve body 20 is in the rotational position of FIG. 4, the third horizontal direction of the side portion (C side) of the valve body 12 via the vertical communication channel 66 of the ball valve body 20. The flow path 44c communicates with the vertical flow path 62 at the bottom (D side) of the valve body 12. That is, a channel in the C⇔D direction is formed.

  With this configuration, the valve body 12 includes a plurality of horizontal flow paths 44 formed so as to be spaced apart from each other at a constant central angle in the rotation direction of the ball valve body 20, and the ball valve body 20. And a vertical flow path 62 formed in the direction of the drive shaft 18.

  Correspondingly, the ball valve body 20 has a horizontal communication channel 64 formed so as to communicate with the horizontal channels 44 (44a to 44c), and a horizontal channel 44 (44a to 44c). And a vertical communication channel 66 formed so as to communicate with the vertical channel 62.

  Therefore, by rotating the drive shaft 18, the ball valve body 20 is rotated in the valve chamber 14, so that the number of switching types (directions) is remarkably increased compared to the conventional multi-way switching valve. It is possible to provide a multi-way switching valve that can be applied to applications.

  Moreover, since not only the horizontal flow path in the horizontal direction but also the vertical flow path 62 in the vertical direction is formed as in the conventional multi-way switching valve, a space can be afforded accordingly, and the ball The valve can be made compact without increasing its size.

  Therefore, according to the multi-way switching valve of the present invention, a complicated configuration is not required, the number of parts is small, the cost can be reduced, and there are many types (directions) of switching, which can be applied to various fields and applications. A switching valve can be provided.

  The sealing state of the multi-way selector valve 10 of the present invention configured as described above will be described below.

  FIGS. 7-8 is sectional drawing in the II line | wire of FIG. 1 explaining the sealing state of the multiway switching valve of this invention.

  7 to 8 show a state in which the entire multi-way switching valve 10 of the present invention is rotated 30 ° counterclockwise from the state of FIG. 2 for convenience of explanation. For convenience of explanation, the hatching of the cross section is omitted, and instead, the portion of the high-pressure fluid is shown by hatching.

  The state of FIG. 7 is the same as the state of FIGS. 1 to 2, and the first horizontal flow path 44 a on the right side (A side) of the valve body 12 and the bottom (D side) of the valve body 12. The vertical flow path 62 formed on the side of the valve body 12 is on the high pressure side, the second horizontal flow path 44b on the side (B side) of the valve body 12 and the third on the side (C side) of the valve body 12. This is a case where the horizontal flow path 44c has a low pressure, and the following state is obtained.

That is, the high-pressure fluid introduced from the first horizontal flow path 44a on the right side (A side) of the valve body 12 is formed in the ball valve body 20 as shown by hatching in FIG. It flows into the vertical flow path 62 formed in the bottom part (D side) of the valve main body 12 through the vertical communication flow path 66.
In addition, since the valve seat member is not attached to the vertical flow path 62 as will be described later, the high-pressure fluid introduced from the first horizontal flow path 44 a is between the ball valve body 20 and the valve body 12. Also flows into the gap S.

  On the other hand, the low-pressure fluid from the second horizontal channel 44b on the side (B side) of the valve body 12 passes through the horizontal communication channel 64 formed in the ball valve body 20 to the valve body 12 side. Part (C side) flows into the third horizontal flow path 44c.

In this case, in the gap S between the ball valve body 20 and the valve body 12, the gaps S1 to S3 are all at a high pressure as shown by hatching in FIG. On the other hand, the second horizontal channel 44b on the side (B side) of the valve body 12, the horizontal communication channel 64 formed in the ball valve body 20, and the side (C side) of the valve body 12 The third horizontal flow path 44c has a low pressure.
Accordingly, the valve seat members 56b and 56c that separate the high-pressure fluid and the low-pressure fluid in an airtight manner are pressed against the ball valve body 20 by the restoring forces of the seal members 54b and 54c. Thereby, the sealing performance between the ball valve body 20 and the valve seat seal surfaces 58b and 58c of the valve seat members 56b and 56c is maintained, and the high-pressure fluid and the low-pressure fluid are hermetically separated.

  By the way, a valve seat member accommodation groove 50 is formed around the opening on the valve chamber 14 side of the horizontal flow path 44 of the valve body 12, and the valve seat member accommodation groove 50 includes a valve seat member 56 and The sealing member 54 that presses the valve seat member 56 against the ball valve body 20 is mounted to ensure sealing performance, but the bottom (D side) of the valve main body 12 in the direction of the drive shaft 18 of the ball valve body 20. Such a valve seat member 56 and the seal member 54 that presses the valve seat member 56 against the ball valve body 20 are not attached to the vertical flow path 62 formed in the above.

  Therefore, for example, when the ball valve body 20 is in the rotational position of FIGS. 1 to 2, the first horizontal flow path 44 a on the right side (A side) of the valve body 12 is on the high pressure side. When the second horizontal flow path 44b on the side (B side) of the main body 12 and the third horizontal flow path 44c on the side (C side) of the valve main body 12 are at low pressure, the following is performed. It becomes a state.

  That is, the high-pressure fluid introduced from the first horizontal flow path 44a on the right side (A side) of the valve body 12 is formed in the ball valve body 20 as shown by hatching in FIG. The high-pressure fluid flows into the gap S between the ball valve body 20 and the valve body 12 via the vertical communication channel 66.

  In this case, the vertical flow path 62 formed on the bottom (D side) of the valve body 12 includes the valve seat member 56 and the valve seat member 56 that are mounted on the horizontal flow paths 44a, 44b, and 44c. Since the seal member 54 that presses the ball valve body 20 is not mounted, the gap between the ball valve body 20 and the valve body 12 is interposed via the vertical communication channel 66 as shown by the arrow E in FIG. The fluid that has entered S is discharged. Accordingly, a so-called liquid seal does not occur in the gap S between the ball valve body 20 and the valve body 12, and damage and damage are prevented, and stable performance can be obtained.

  On the other hand, the state of FIG. 8 is the same as the state of FIG. 3, and the first horizontal flow path 44a on the right side (A side) of the valve body 12 and the side (C side) of the valve body 12. The third horizontal flow path 44c is the high pressure side, the second horizontal flow path 44b on the side (B side) of the valve body 12 and the vertical formed on the bottom (D side) of the valve body 12. This is a case where the directional flow path 62 has a low pressure, and the following state is obtained.

  That is, the high-pressure fluid introduced from the first horizontal flow path 44a on the right side (A side) of the valve body 12 is formed in the ball valve body 20 as shown by hatching in FIG. It flows into the third horizontal flow path 44 c on the side portion (C side) of the valve body 12 through the horizontal communication flow path 64.

  On the other hand, the low-pressure fluid from the second horizontal channel 44b on the side (B side) of the valve body 12 passes through the vertical communication channel 66 formed in the ball valve body 20 to the bottom of the valve body 12. It flows into the vertical flow path 62 formed on the (D side). As described above, since the valve seat member is not attached to the vertical flow path 62, the low-pressure fluid also flows into the gap S between the ball valve body 20 and the valve body 12.

  Therefore, in this case, the high-pressure fluid in the first horizontal flow path 44a on the right side (A side) of the valve body 12, the high-pressure fluid in the horizontal communication flow path 64 formed in the ball valve body 20, and The high pressure fluid in the third horizontal flow path 44c on the side (C side) of the valve body 12, the low pressure fluid in the horizontal flow path 44b on the side (B side) of the valve body 12, and the ball valve body 12 The ball valve body 20 moves in the direction indicated by the arrow F in FIG. 8 by the action of the pressure difference between the valve body 12 and the low-pressure fluid in the gap S.

  Therefore, if the degree of close contact between the valve seat seal surfaces 58a and 58c of the valve seat members 56a and 56c with respect to the ball valve body 20 is not maintained, high-pressure fluid leaks into the gap S between the ball valve body 20 and the valve body 12. The valve leaks to the vertical flow path 62 formed at the bottom (D side) of the valve body 12 on the low pressure side and the second horizontal flow path 44b on the side (B side) of the valve body 12. It will be.

For this reason, in the multi-way switching valve 10 of the present invention, as shown in FIGS. 8 and 9, the clearance L between the valve seat member 56 and the valve seat member housing groove 50 and the compression amount of the seal member 54 are as follows. The relationship with d is set as follows.
In FIG. 9, for convenience of explanation, only the valve seat members 56b and 56c are illustrated, and the valve seat member 56a is not illustrated.

  In a state where the differential pressure is not acting, the valve seat members 56a to 56c attached to the valve seat member receiving grooves 50a to 50c of the valve seat holding members 48a to 48c are formed on the side portions (A to C side) of the valve body 12. As for 56c, the clearance gap L is formed between the valve-seat members 56a-56c and the groove part 50a-50c for valve-seat member accommodation, respectively.

  Therefore, when the ball valve body 20 moves in the direction indicated by the arrow F in FIG. 8, the movement amount of the ball valve body 20 is the distance of the gap L at the maximum.

  In this case, as shown in FIGS. 8 and 9C, on the side (C side) of the valve body 12, the valve seat member 56b mounted in the valve seat member housing groove 50c of the valve seat holding member 48c. If the restoring force of the seal member 54c is not acting, the valve seat seal surface 58c is not pressed against the ball valve body 20 and leakage occurs.

  That is, as described above, when the ball valve body 20 moves in the direction indicated by the arrow F in FIG. 8, as shown in FIGS. Thus, the valve seat holding member 48b is displaced in the direction of the gap L.

On the other hand, when the ball valve body 20 moves in the direction indicated by the arrow F in FIG. 8, the valve seat member 56c and the valve seat member 56a are displaced in directions away from the valve seat holding member 48c and the valve seat holding member 48a, respectively. To.
In this case, the maximum displacement amount X depends on the center angle θ (see FIG. 8) formed by the horizontal flow paths 44a to 44c.

That is, when the movement amount of the ball valve body 20 is A, the displacement amount X of the valve seat member 56c and the valve seat member 56a is expressed by a relational expression of X = A · cos (θ / 2).
The angle θ is preferably in the range of 0 ° <θ ≦ 180 ° in order to be a multi-way switching valve.

Further, when the number of horizontal flow paths 44 is an odd number (for example, as in this embodiment, when three horizontal flow paths 44a to 44c and one vertical flow path 62 are provided), 0 <θ In this embodiment, the number of horizontal flow paths is three, that is, the horizontal flow paths 44a to 44c, and the central angle θ is 120 °. Therefore, X = A · cos 60 ° = A · 1/2.

In the case of this embodiment, when the ball valve body 20 moves in the direction indicated by the arrow F in FIG. 8 due to the differential pressure acting on the ball valve body 20, the maximum movement amount A of the ball valve body 20 is the valve seat member. L (A = L), which is a gap between 56b and the valve seat holding member 48b (see FIGS. 9A and 9B).
Therefore, as shown by the arrow in FIG. 9A, the valve seat member 56b is also displaced in the direction of the valve seat holding member 48b by the gap L.

  On the other hand, the valve seat member 56c and the valve seat member 56a are also displaced, and the directions thereof are directions away from the valve seat member holding portion 48c and the valve seat member holding portion 48a, respectively, and the displacement amount X is L / L at the maximum. 2 (see FIGS. 9A and 9C).

  That is, since the central angle θ between the horizontal flow paths 44a to 44c is 120 °, the compression amount d of the seal member 54c is the amount of movement in the Y-axis direction as shown in FIG. 9B. If it is not larger than L / 2, the valve seat seal surface 58c is not pressed against the ball valve body 20 and leakage occurs. Therefore, this relationship can be expressed by the following formula.

  That is, in the case of this embodiment, the gap L between the valve seat member 56 and the valve seat member accommodating groove 50 is L / L relative to the compression amount d of the seal member 54 in a state where the differential pressure is not acting. It is necessary that the relationship 2 <d is set.

  As described above, the gap L between the valve seat member 56 and the valve seat member accommodation groove 50 is L / 2 <d with respect to the compression amount d of the seal member 54 in a state where the differential pressure is not acting. If the relationship is set, as shown in FIGS. 8 and 9, even if the ball valve body 20 moves from the high pressure side to the low pressure side (B side) in the direction indicated by the arrow F in FIG. On the high-pressure side, the crushing margin of the seal member 54 is ensured, the restoring force of the seal member 54 is always applied, and the valve seat member 56 is pressed against the ball valve body 20.

Therefore, this relationship can be expressed by the following general formula.
That is,
Center angle θ formed between the horizontal flow paths 44: θ
Gap between the valve seat member 56 and the valve seat member housing groove 50: L
Compression amount of the seal member 54: d
When
L · cos (θ / 2) <d
Satisfy this relationship.

Thereby, sealing performance is ensured, and high pressure fluid is effectively prevented from leaking from the high pressure side to the low pressure side (B side and D side).
(Example 2)

  FIG. 10 is a schematic view showing another embodiment of the multi-way selector valve 10 of the present invention.

The multi-way switching valve 10 of this embodiment has basically the same configuration as that of the multi-way switching valve 10 of the first embodiment shown in FIGS. 1 to 10, and the same components are denoted by the same reference numerals. Detailed description thereof will be omitted.
In FIG. 10, the valve seat holding member 48, the valve seat member accommodating groove portion 50, the seal groove portion 52, the seal member 54, the valve seat member 56, etc. are omitted for convenience of explanation. It is shown.

  In the first embodiment, a plurality of valves are formed in the valve body 12 so as to be spaced apart from each other at a constant central angle (120 ° in the case of the first embodiment) in the rotation direction of the ball valve body 20 and communicate with the valve chamber 14. (In Example 1, three) horizontal flow paths 44 (44a to 44c) are formed.

  In contrast, in this embodiment, the valve body 12 is formed so as to be spaced apart from each other at a constant central angle (72 ° in the case of the second embodiment) in the rotation direction of the ball valve body 20. A plurality of (in the second embodiment, five) horizontal flow paths 44 (44a to 44e) communicating with 14 are formed.

  Accordingly, in the case of the first embodiment, one horizontal communication channel 64 is formed in the ball valve body 20, but in this embodiment, two horizontal communication channels 64 are provided in the ball valve body 20. 64 is formed.

  In the case of the multi-way selector valve 10 of this embodiment, when the horizontal flow path 44a is at a low pressure and the other horizontal flow paths 44b to 44e are at a high pressure, the ball valve element is moved in the direction of arrow G in FIG. 20 will move.

Therefore, in this case, leakage occurs from the horizontal flow path 44c and the horizontal flow path 44d to the horizontal flow path 44a on the low pressure side.
Therefore, also in this case, the above general formula,
L · cos (θ / 2) <d
Satisfy this relationship.

  Thus, in the multi-way selector valve 10 of the present invention, it is possible to form it from three or more odd number of horizontal flow paths.

  Thus, if the horizontal flow path 44 of the valve body 12 is formed of an odd number of horizontal flow paths 44, the horizontal direction in which the horizontal flow paths 44 of the valve body 12 communicate with the ball valve body 20. A vertical communication channel 66 that communicates the communication channel 64 with one of the remaining horizontal channels 44 of the valve body 12 and the vertical channel 62 of the valve body 12 can be formed.

  Although the preferred embodiment of the present invention has been described above, the present invention is not limited to this. For example, in the above embodiment, the horizontal flow path 44 is formed on the side of the valve body 12. However, it is also possible to form the horizontal flow path 44 directly in the valve body 12.

  Further, the high pressure side, the low pressure side, and the flow direction of the fluid are not particularly limited, and various changes can be made without departing from the object of the present invention.

  The present invention is used, for example, for fluid control of a refrigerant circulation circuit of an air conditioner such as an air conditioner or a refrigerator, a fluid in a plant, a gas in a gas field, etc. It can be applied to a multi-way switching valve for switching.

DESCRIPTION OF SYMBOLS 10 Multiway switching valve 11 Thrust bearing 12 Valve main body 14 Valve chamber 16 Actuator 18 Drive shaft 20 Ball valve body 22 Slit 24 Lower end 26 Anti-rotation prevention part 28 Insertion hole 30 Small diameter part 32 Large diameter part 34 Flange 36 Seal member 38 Spring holding flange 40 retaining ring 42 compression spring 44 horizontal flow path 44a first horizontal flow path 44b second horizontal flow path 44c third horizontal flow path 46 opening 46a opening 46b opening 46c opening 48 valve seat Holding member 48a Valve seat holding member 48b Valve seat holding member 48c Valve seat holding member 50 Valve seat member receiving groove 50a Valve seat member receiving groove 50b Valve seat member receiving groove 50c Valve seat member receiving groove 52a Seal groove 52b Seal Groove 52c Seal groove 54 Seal member 54a Seal member 54b Seal member 54c Valve member 56a Valve seat member 56a Valve seat member 56b Valve seat member 56c Valve seat member 58 Valve seat seal surface 58a Valve seat seal surface 58b Valve seat seal surface 58c Valve seat seal surface 60a Seal member 60b Seal member 60c Seal member 62 Vertical direction Channel 64 Horizontal communication channel 64a Communication channel 64b Communication channel 66 Vertical communication channel 66a Communication channel 66b Communication channel 66c Communication channel 100 Ball valve 102 Valve body 104 Valve chamber 106-112 Horizontal channel 106a-110a Projection 114 Valve seat member 116 Seal member receiving groove 118 O-ring 120 Washer 122 Belleville spring 124 Ball valve body 126, 128 Communication channel (valve hole)
130 Insertion hole 132 Rotating shaft 200 Ball valve 202 Valve body 204 Valve chamber 206-212 Horizontal flow path 214 Valve seat member housing groove 216 Valve seat member 218 Ball valve body 220 Seal member d Compression amount L Clearance L / 2 Movement amount S gap S1-S3 gap

Claims (7)

A multi-way switching valve that switches the flow of fluid by the operation of a valve body,
A ball valve body mounted in a valve chamber formed inside the valve body and configured to rotate in the valve chamber by rotation of a drive shaft;
A plurality of horizontal flow paths formed in the valve body so as to be spaced apart from each other at a constant central angle in the rotation direction of the ball valve body, and communicating with the valve chamber;
A vertical flow path formed in the valve body in the direction of the drive shaft of the ball valve body and communicating with the valve chamber;
A horizontal communication channel formed in the ball valve body and configured to communicate between the horizontal channels;
A vertical communication channel formed in the ball valve body and configured to communicate one of the horizontal channels and a vertical channel;
A multi-way switching valve comprising: Around the opening on the valve chamber side of the horizontal flow path of the valve body, a valve seat member housing groove is formed,
A valve seat member and a seal member that presses the valve seat member against the ball valve body are attached to the groove portion for accommodating the valve seat member,
A gap L is formed between the valve seat member and the valve seat member receiving groove portion in a state where no differential pressure is applied,
2. The multi-way selector valve according to claim 1, wherein the gap L is set to be smaller than a compression amount d of the seal member (L <d) in a state where no differential pressure is applied.   3. The valve seat holding member is mounted on the valve body, and the horizontal flow path and the valve seat member receiving groove are formed in the valve seat holding member. The multi-way selector valve described in 1.   4. The multi-way selector valve according to claim 1, wherein the horizontal flow path of the valve body is formed of an odd number of horizontal flow paths.   The multi-way switching valve according to claim 4, wherein the horizontal flow path of the valve body is formed of three horizontal flow paths. Center angle θ: θ formed by the horizontal flow paths with no differential pressure acting
Gap between the valve seat member and the valve seat member receiving groove: L
Compression amount of seal member: d
When
L · cos (θ / 2) <d
The multi-way switching valve according to claim 1, wherein the multi-way switching valve is configured to satisfy the relationship:   The gap L between the valve seat member and the valve seat member receiving groove is set to a relationship of L / 2 <d with respect to the compression amount d of the seal member in a state where the differential pressure is not acting. The multi-way switching valve according to claim 5, wherein the multi-way switching valve is provided.

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