JP2011202707A - Flow passage opening and closing valve - Google Patents

Abstract

PROBLEM TO BE SOLVED: To suppress partial wear of a seat member on which a ball valve is seated in a flow passage opening and closing valve, and to always achieve stable sealability between the ball valve and the seat member.SOLUTION: The ball valve 14 is rotatably disposed in an inside of a body body 12, a pair of opening parts 44a and 44b having a through-hole 42 opened is formed in the ball valve 14, and first and second seal parts 46 and 48 abutting on first and second valve seats 16 and 18 respectively are formed in an outer radial direction of the one opening part 44b. The second seat part 48 is formed so that an upper seat 50 formed on the upper side while having a horizontal line D passing through the center of the through-hole 42 as the boundary has a smaller contact area with respect to the second valve seat 18 than a lower seat 52 formed on the lower side while having the horizontal line D as the boundary.

Description

  The present invention relates to a flow path opening / closing valve that switches a flow state of a fluid by opening and closing a flow path through which the fluid flows.

  2. Description of the Related Art Conventionally, for example, a channel opening / closing valve that is connected to a fluid flow channel and controls the fluid flow state by switching the communication state of the flow channel is known. In such a flow path opening / closing valve, a ball valve is provided inside the valve main body, and a through-hole of the ball valve is formed in the valve main body by rotating a connecting shaft connected to an upper portion of the ball valve. The pair of passages communicated with each other. Also, annular valve seat members are provided at the ends of the pair of passages, and are in sliding contact with the peripheral surface of the ball valve, so that fluid leakage between the peripheral surface and the passage is prevented. (For example, refer to Patent Document 1).

JP 2006-234104 A

  In the above-described flow path opening / closing valve, since the ball valve rotates when the flow path is opened and closed, the valve seat member that is in sliding contact with the peripheral surface of the ball valve is worn at the sliding contact portion with the peripheral surface. Will occur. In this valve seat member, more wear occurs on the upper side and the lower side that are substantially parallel to the rotation axis, and therefore, the degree of wear along the circumferential direction of the valve seat member is not equalized and uneven wear occurs.

  As a result, when the channel opening / closing valve is continuously used for a long period of time, there is a concern that a gap is generated between the ball valve and the valve seat member due to uneven wear, and fluid leaks through the gap.

  The present invention has been made in consideration of the above-described problems, and suppresses uneven wear of the seat member on which the ball valve is seated, and always obtains a stable sealing performance between the ball valve and the seat member. An object is to provide a possible flow path opening / closing valve.

In order to achieve the above object, the present invention includes a ball valve provided with a through hole,
A body main body having a chamber that rotatably accommodates the ball valve, a fluid inlet to which a fluid is supplied, and a fluid outlet from which the fluid is discharged;
A shaft that switches the communication state between the fluid inlet and the fluid outlet by rotating the ball valve in the chamber;
A drive source for rotating the shaft shaft;
A seat member rotatably provided at at least one of the fluid inlet and the fluid outlet, and abutting on an outer peripheral surface of the ball valve;
With
The seat member rotates with the rotation of the ball valve.

  According to the present invention, the ball valve connected to the shaft is rotated under the drive action of the drive source, thereby switching the flow state of the fluid supplied to the fluid inlet in the body body to the fluid outlet. At this time, the seat member in contact with the outer peripheral surface of the ball valve is rotationally displaced by the rotation of the ball valve.

  Therefore, when the ball valve is rotated in order to switch the flow state of the fluid, the seat member can be rotationally displaced in at least one of the fluid inflow port and the fluid outflow port in accordance with the rotation operation. It is avoided that the contact portion of the ball valve is always at the same position in the member, and the contact portion can be evenly contacted along the circumferential direction of the seat member. As a result, since the wear of the seat member due to the contact of the ball valve can be made substantially uniform along the circumferential direction of the seat member, the uneven wear of the seat member is prevented, and the uneven wear is caused by the uneven wear. It is possible to reliably prevent the fluid from leaking between the ball valve and the seat member. Moreover, since uneven wear of the sheet member is prevented, the replacement cycle can be extended.

  Further, the rotation direction of the seat member may be set such that the rotation center thereof is orthogonal to the rotation center of the ball valve.

  Furthermore, it is preferable that a first contact portion and a second contact portion having different contact resistances with respect to the seat member are formed on the outer peripheral surface of the ball valve.

  Furthermore, the first and second contact portions may be formed by being divided using a base line passing through the center of the through hole as a boundary.

  Still further, the first and second contact portions may be set so that the contact areas in contact with the sheet member are different.

  Moreover, it is good to provide the curved part formed in the big radius with respect to the outer periphery radius of a ball valve in any one of a 1st contact part and a 2nd contact part.

  Furthermore, it is good to provide the hollow part hollow with respect to the outer peripheral surface of a ball valve in any one of a 1st contact part and a 2nd contact part.

  Furthermore, the first and second contact portions may be set so that the surface roughness of the contact surface contacting the sheet member is different.

  Furthermore, it is preferable to provide a rotation promoting means for promoting rotational displacement of the sheet member between at least one of the fluid inlet and the fluid outlet and the sheet member.

  According to the present invention, the following effects can be obtained.

  That is, when the ball valve is rotated and the flow state of the fluid is switched, the seat member can be rotationally displaced in at least one of the fluid inflow port and the fluid outflow port in accordance with the rotation operation. As a result, it is avoided that the contact portion of the ball valve is always in the same position in the seat member, and the seat member can be uniformly contacted along the circumferential direction of the seat member, thereby preventing uneven wear of the seat member. In addition, fluid leakage from between the ball valve and the seat member due to the uneven wear can be reliably prevented.

It is a partial cross section perspective view of the channel on-off valve concerning a 1st embodiment of the present invention. FIG. 2 is a partially sectional exploded perspective view of the flow path opening / closing valve shown in FIG. 1. It is a longitudinal cross-sectional view of the flow-path on-off valve shown in FIG. It is an external appearance perspective view of a ball valve and a shaft axis. FIG. 5 is a partially omitted front view of the ball valve and shaft shown in FIG. 4. It is a longitudinal cross-sectional view which shows the valve open state of the flow-path on-off valve of FIG. It is an expanded sectional view which shows the ball valve vicinity of FIG. It is the external appearance perspective view of the ball valve and shaft which comprised the flow-path on-off valve which concerns on a modification, and had several notch parts. FIG. 9 is a partially omitted front view of the ball valve and shaft shown in FIG. 8. FIG. 9 is an enlarged cross-sectional view showing the vicinity of the ball valve and a second valve seat in a valve open state in which a gas inlet and a gas outlet communicate with each other through the ball valve of FIG. 8. It is an external appearance perspective view of the ball valve and shaft which comprise the flow-path on-off valve which concerns on the 2nd Embodiment of this invention. FIG. 12 is a partially omitted front view of the ball valve and shaft shown in FIG. 11. In the flow path on-off valve according to the third embodiment of the present invention, an enlarged sectional view showing the vicinity of the ball valve and the second valve seat in a valve open state in which a gas inlet and a gas outlet communicate with each other through a ball valve. It is. It is an expanded sectional view showing the modification which provided the bearing in the perimeter side of the 2nd valve seat.

  A preferred embodiment of a flow path opening / closing valve according to the present invention will be described below and described in detail with reference to the accompanying drawings.

  In FIG. 1, reference numeral 10 indicates a flow path opening / closing valve according to the first embodiment of the present invention.

  As shown in FIGS. 1 to 7, the flow path opening / closing valve 10 is provided on a body main body 12, a ball valve 14 rotatably provided inside the body main body 12, and an outer peripheral surface 14 a of the ball valve 14. The first and second valve seats 16 and 18 are in contact with each other, and a driving force transmission mechanism 20 is provided on an upper portion of the body main body 12 and applies a rotational driving force to the ball valve 14.

  Under the body main body 12, for example, a gas inlet 22 to which a gas containing vaporized fuel is supplied and a gas inlet 22 provided on the opposite side are provided, and the gas is led out to an internal combustion engine (not shown). A gas outlet 24 for circulation is provided. In the body main body 12, the gas inlet 22 and the gas outlet 24 are provided on a substantially straight line. Further, a communication chamber (chamber) 26 is formed in the body main body 12 between the gas inlet 22 and the gas outlet 24, and a substantially spherical ball valve 14 is rotatably disposed in the communication chamber 26. Established.

  A ring-shaped first valve seat 16 is provided between the communication chamber 26 and the gas inlet 22, and the first valve seat 16 has an annular first mounting groove whose diameter is larger than that of the gas inlet 22. 28 is attached. That is, the first valve seat 16 is disposed so that one end surface thereof faces the communication chamber 26 and abuts on the outer peripheral surface 14 a of the ball valve 14, and the other side surface thereof faces the gas inlet 22.

  In the first valve seat 16, a first communication hole 30 communicating with the gas inlet 22 is formed at the center and penetrates along the axial direction (arrows A and B directions). A first seat surface 32 with which the ball valve 14 abuts is formed on the end surface. The first seat surface 32 is formed to be recessed in a circular arc shape in a direction away from the ball valve 14 (arrow A direction), and the cross-sectional shape centering on the center line of the first communication hole 30 is a ball. It is formed with a predetermined radius corresponding to the outer peripheral surface 14a of the bulb 14, and is formed with the same cross-sectional shape along the circumferential direction. In other words, the surface area of the first seat surface 32 is formed to be uniform along the circumferential direction around the axis of the first valve seat 16.

  On the other hand, a spring 34 is interposed between the other side surface of the first valve seat 16 and the body body 12, and always urges the first valve seat 16 toward the ball valve 14 (in the direction of arrow B). ing.

  On the other hand, a ring-shaped second valve seat 18 is provided between the communication chamber 26 and the gas outlet 24, and the second valve seat 18 is provided between the gas outlet 24 and the communication chamber 26. It is mounted in the formed annular second mounting groove 36. The second valve seat 18 is rotatably provided with respect to the second mounting groove 36, one end surface thereof faces the communication chamber 26, contacts the outer peripheral surface 14 a of the ball valve 14, and the other side surface is the gas outlet 24. It is arranged to face. The second valve seat 18 is provided coaxially with the first valve seat 16 with the communication chamber 26 as the center.

  A second communication hole 38 communicating with the gas outlet 24 is formed at the center of the second valve seat 18, and penetrates along the axial direction (directions of arrows A and B). A second seat surface 40 with which the ball valve 14 abuts is formed on one end surface of the second valve seat 18. The second sheet surface 40 is formed to be recessed in a circular arc shape from one end surface toward the other end surface side, and the cross-sectional shape centering on the center line of the second communication hole 38 is the same shape along the circumferential direction. It is formed. In other words, the surface area of the second seat surface 40 is formed to be uniform along the circumferential direction around the axis of the second valve seat 18.

  On the other hand, the other end surface of the second valve seat 18 is formed in a substantially flat shape, and a pipe or the like (not shown) is connected to the gas outlet 24 so that the end of the pipe or the like is inside the second mounting groove 36. Displacement in the axial direction (arrow A, B direction) is restricted.

  The ball valve 14 is a sphere in which one curved surface and the other curved surface are removed so as to be orthogonal to the central axis, and a through hole 42 penetrating from one surface to the other surface along the central axis is formed. .

  On the outer peripheral surface 14a of the ball valve 14, a pair of opening portions 44a and 44b having both ends of the through hole 42 opened are formed, and the first and second seat portions 46, which are annular in the radially outward position, 48 are formed along the outer peripheral surface 14a. In the valve open state in which the through hole 42 of the ball valve 14 is arranged in line with the gas inlet 22 and the gas outlet 24 (see FIG. 6), the first seat portion 46 contacts the first valve seat 16. On the other hand, the second seat portion 48 comes into contact with the second valve seat 18.

  The first and second sheet portions 46, 48 are an upper sheet (first contact portion) 50 formed on the upper side (arrow E direction) with a horizontal line (base line) D passing through the center C of the through hole 42 as a boundary, A lower sheet (second contact portion) 52 formed on the lower side (in the direction of arrow F) with the horizontal line D as a boundary.

  In addition, the ball valve 14 is formed on the outer peripheral side of the opening 44b in the second seat portion 48 with a larger radius than the outer peripheral surface 14a of the ball valve 14, and on the upper side with respect to the horizontal line D (in the direction of arrow E) The curved portion 54 is formed only in (). That is, as shown in FIG. 5, when the ball valve 14 is viewed from the opening 44 b side of the through hole 42, the curved portion 54 is a half that is about 180 ° so as to cover the upper side of the through hole 42. It is formed in a circular shape.

  Thus, by providing the curved portion 54 at the position facing the upper seat 50 on the other surface of the ball valve 14, the surface area G 1 of the upper seat 50 in the second seat portion 48 becomes the surface area G 2 of the lower seat 52. On the other hand, it becomes smaller (G1 <G2).

  That is, when the second seat portion 48 contacts the second valve seat 18, the contact area H1 of the upper seat 50 with respect to the second seat surface 40 is smaller than the contact area H2 with the lower seat 52 (H1 < H2).

  On the other hand, since the curved portion 54 is not provided in the first seat portion 46, the surface areas of the upper seat 50 and the lower seat 52 are substantially the same, and the first seat portion 46 contacts the first valve seat 16. In this case, the contact areas of the upper sheet 50 and the lower sheet 52 with respect to the first sheet surface 32 are substantially the same (H1≈H2).

  A concave portion 56 having a rectangular cross section is formed at the top of the ball valve 14, and an end portion of a shaft shaft 58 to be described later is inserted into the concave portion 56. The recess 56 extends in a direction orthogonal to the axis of the through hole 42.

  The driving force transmission mechanism 20 is connected to a shaft shaft 58 connected to the top of the ball valve 14, a rotary yoke 60 connected to the upper end of the shaft shaft 58, and an upper part of the body main body 12. And a drive source 62 that rotationally drives the shaft shaft 58 via a shaft.

  The shaft 58 is rotatably supported by a pair of bearings 64 a and 64 b provided inside the body body 12, and a lower end portion of the shaft shaft 58 is formed in a rectangular shape in the communication chamber 26. Inserted. Further, the upper end portion of the shaft shaft 58 is inserted through a substantially central portion of the rotary yoke 60 and is fixed by tightening the nut 66.

  The drive source 62 is composed of, for example, a stepping motor or a rotary actuator that is rotationally driven under an energization action, and the rotational driving force is transmitted to the shaft shaft 58 via the rotary yoke 60, thereby being coupled to the shaft shaft 58. The ball valve 14 is rotated in a predetermined direction.

  The flow path opening / closing valve 10 according to the first embodiment of the present invention is basically configured as described above. Next, the operation and effects thereof will be described. Here, as shown in FIGS. 1 and 3, the through hole 42 of the ball valve 14 is located at a position orthogonal to the gas inlet 22 and the gas outlet 24, and the first and second valve seats 16, A description will be given assuming that the valve closed state in which the first and second communication holes 30, 38 are closed by the ball valve 14 is the initial position.

  In the initial position described above, a gas (not shown) is supplied to the gas inlet 22. However, since the ball valve 14 is in contact with the first seat surface 32 of the first valve seat 16, the first valve seat 16. The valve is in a closed state in which the flow of the gas into the communication chamber 26 is blocked. Similarly, since the ball valve 14 is in contact with the second seat surface 40 of the second valve seat 18, the communication between the gas outlet 24 and the communication chamber 26 is also blocked.

  First, when the drive source 62 is energized, a rotational driving force is transmitted to the shaft 58 via the rotary yoke 60, and the openings 44 a and 44 b of the through holes 42 are respectively connected to the gas inlet 22 and the gas outlet 24. The ball valve 14 rotates so as to approach. 6 and 7, the through hole 42 is aligned with the gas inlet 22 and the gas outlet 24 under the rotating action of the ball valve 14, so that the gas flow through the through hole 42 is achieved. The valve 22 is in an open state in which the inlet 22 and the gas outlet 24 communicate with each other. As a result, the gas supplied to the gas inlet 22 flows through the through hole 42 of the ball valve 14 toward the gas outlet 24 and is introduced into an internal combustion engine (not shown).

  In addition, since the upper seat 50 and the lower seat 52 of the first valve seat 16 are in contact with the first seat portion 46 of the ball valve 14, the gas that passes between the ball valve 14 and the first valve seat 16 is used. Leakage is prevented. On the other hand, since the upper seat 50 and the lower seat 52 of the second valve seat 18 are in contact with the second seat portion 48 of the ball valve 14, the gas that has passed between the ball valve 14 and the second valve seat 18. Leakage is prevented.

  At this time, the second seat portion 48 of the ball valve 14 is in a state where the upper seat 50 is in contact with the lower seat 52 with a small contact area (H1 <H2) (see FIG. 7).

  On the other hand, when the flow path opening / closing valve 10 is closed, the rotation transmitted from the drive source 62 to the shaft 58 is reversed by reversing the control signal input to the drive source 62. The transmission direction of the driving force is reversed, and the ball valve 14 rotates about the shaft shaft 58 in the opposite direction.

  At this time, as the ball valve 14 rotates, the sliding resistance differs between the upper seat 50 and the lower seat 52 having different contact areas with respect to the second valve seat 18, and the contact area is large and the sliding resistance is large. Sliding between the lower side of the second valve seat 18 in contact with the lower seat 52 and the upper side of the second valve seat 18 in contact with the upper seat 50 having a small contact area and a small sliding resistance. A rotational force is generated by the difference in dynamic resistance.

  Specifically, as shown in FIG. 5, when the ball valve 14 is viewed from the second seat portion 48 side, the ball valve 14 is rotated when the opening 44b of the through hole 42 is turned to the left side. The lower side of the second valve seat 18 having a large sliding resistance is pulled in the clockwise direction (arrow R direction) as the ball valve 14 rotates. In other words, a rotational force in the clockwise direction (arrow R direction) is applied to the second valve seat 18 as the ball valve 14 rotates.

  As a result, the second valve seat 18 rotates by a predetermined angle along the inner peripheral surface of the second mounting groove 36 as the ball valve 14 rotates. At this time, the rotation direction of the second valve seat 18 rotates so that the rotation center thereof is orthogonal to the rotation center of the ball valve 14.

  Then, the through hole 42 of the ball valve 14 is rotated to a position substantially orthogonal to the axes of the gas inlet 22 and the gas outlet 24, whereby the first and second valve seats are formed by the outer peripheral surface 14a of the ball valve 14. The valve closed state in which the communication of the first and second communication holes 30 and 38 of the 16 and 18 is cut off, and the rotation operation of the ball valve 14 is stopped. Along with this, the rotation operation of the second seat valve is also stopped. As a result, the communication between the gas inlet 22 and the gas outlet 24 is blocked, and an initial position where the gas supplied to the gas inlet 22 is prevented from flowing toward the gas outlet 24 is obtained.

  As described above, in the first embodiment, the ball valve 14 that is rotationally displaced under the drive action of the drive source 62 is provided, and the ball valve 14 has the through hole 42 that includes the gas inlet 22 and the gas outlet. In a valve open state in which 24 is communicated, a second seat portion 48 that abuts on the second valve seat 18 is provided. In the second seat portion 48 of the ball valve 14, a curve formed with a large radius with respect to the outer peripheral surface 14 a of the ball valve 14 at a position on the upper side with a horizontal line D passing through the center C of the through hole 42 as a boundary. By providing the portion 54, the upper seat 50 above the horizontal line D is set such that the contact area between the upper seat 50 and the second valve seat 18 relative to the lower seat 52 below the horizontal line D is reduced. (H1 <H2).

  That is, in the ball valve 14, the contact area of the second valve seat 18 between the upper seat 50 on the upper side and the lower seat 52 on the lower side with respect to the horizontal line D passing through the axis of the through hole 42. H1 and H2 are set to be different.

  As a result, when the ball valve 14 is rotated, a rotational force due to the contact area difference between the upper seat 50 and the lower seat 52 is generated along with the rotation operation, so the second valve seat 18 is attached to the second valve seat 18. It can be rotated along the inner peripheral surface of the groove 36. Therefore, in the second valve seat 18, it is avoided that the contact position of the second seat surface 40 with which the ball valve 14 abuts is always the same position, and the second valve seat 18 is equally applied along the circumferential direction of the second seat surface 40. It is possible to contact.

  As a result, the wear of the second seat surface 40 due to the sliding contact of the ball valve 14 can be made substantially uniform along the circumferential direction of the second seat surface 40, so that the uneven wear of the second valve seat 18 is prevented. Accordingly, it is possible to reliably prevent gas leakage between the ball valve 14 and the second valve seat 18 due to the uneven wear.

  In addition, since uneven wear of the second valve seat 18 is prevented, the replacement cycle of the second valve seat 18 can be extended.

  The configuration in which the surface areas of the upper seat 50 and the lower seat 52 in the ball valve 14 are made different is not limited to the case where the semicircular curved portion 54 is provided as described above. For example, FIGS. As shown in FIG. 5, a plurality of (for example, three) notches 82 a to 82 c may be provided along the opening 44 b of the through hole 42 on the outer peripheral surface 80 a of the ball valve 80. The notches 82 a to 82 c are formed in a triangular cross section that is recessed at a predetermined depth with respect to the outer peripheral surface 80 a of the ball valve 80, and are provided in the range of the upper seat 50 in the second seat portion 48. Further, the notches 82 a to 82 c are provided so as to be spaced apart from each other at equal intervals along the circumferential direction of the through hole 42.

  When a plurality of notches 82a to 82c are provided on the outer peripheral surface 80a of the ball valve 80 as described above, the second valve seat 18 can be secondly changed by changing the number, shape, etc. of the notches 82a to 82c. It becomes possible to easily change the contact area of the upper sheet 50 of the sheet portion 48. As a result, the contact areas of the upper seat 50 and the lower seat 52 of the ball valve 80 with respect to the second valve seat 18 are easily varied, and the second valve seat 18 is reliably and easily moved under the rotating action of the ball valve 80. Can be rotated.

  That is, when the quantity of the notches 82a to 82c is increased or the shape of the notches 82a to 82c is increased, the contact area of the upper seat 50 with respect to the second valve seat 18 becomes smaller, and accordingly. Thus, it is possible to set a large difference in contact area with the lower sheet 52, and conversely, when the number of the notches 82a to 82c is reduced or the shape of the notches 82a to 82c is reduced. The contact area of the upper seat 50 with respect to the second valve seat 18 becomes larger, and the difference in the contact area with the lower seat 52 can be set small.

  Next, a flow path opening / closing valve 100 according to a second embodiment is shown in FIGS. The same components as those in the flow path opening / closing valve 10 according to the first embodiment described above are denoted by the same reference numerals, and detailed description thereof is omitted.

  In the flow path opening / closing valve 100 according to the second embodiment, for example, in the ball valve 102, the surface roughness K1 of the lower seat 106 in the second seat portion 104 is larger than the surface roughness K2 of the upper seat 108. The set point (K1> K2) is different from the channel on / off valve 10 according to the first embodiment. The lower seat 106 of the ball valve 102 is processed, for example, by sandblasting, so that the surface roughness is larger than that of the upper seat 108.

  As described above, in the flow path opening / closing valve 100 according to the second embodiment, the upper seat 108 and the lower seat 106 of the second seat portion 104 in the ball valve 102 are formed with different surface roughnesses, thereby When the ball valve 102 is rotated, the second valve seat 18 can be rotated according to the difference in surface roughness. As a result, uneven wear of the second valve seat 18 can be reliably prevented with a simple configuration in which the surface roughness of the upper and lower seats 108 and 106 is set separately, and can be realized at low cost. Can do.

  Further, when the ball valve 102 is formed, it is possible to set the surface roughness to be different by forming the material surface without processing only the lower seat 106 and processing other portions including the upper seat 108. . In this case, it is not necessary to process the lower sheet 106, so that the processing cost can be reduced.

  As described above, the surface roughness K1 of the lower sheet 106 is not limited to the case where the surface roughness K2 of the upper sheet 108 is set larger than the surface roughness K2. The surface roughness K1 of the lower sheet 106 may be set larger (K1 <K2).

  Next, a flow path opening / closing valve 150 according to a third embodiment is shown in FIGS. In addition, the same referential mark is attached | subjected to the component same as the flow-path on-off valves 10 and 100 which concern on 1st and 2nd embodiment mentioned above, and the detailed description is abbreviate | omitted.

  In the flow path opening / closing valve 150 according to the third embodiment, as shown in FIG. 13, a lubricant 152 (for example, grease) is provided between the outer peripheral surface of the second valve seat 18 and the second mounting groove 36. Is applied, and the frictional resistance between the second mounting groove 36 is reduced, and the second mounting groove 36 is rotatably provided. Then, when the ball valve 14 rotates under the rotating action of the shaft 58, the second valve seat 18 can be rotated more smoothly as the ball valve 14 rotates.

  Further, instead of applying the lubricant 152 between the second valve seat 18 and the second mounting groove 36, a bearing 154 is mounted on the second mounting groove 36 as shown in FIG. You may make it hold | maintain the outer peripheral surface of the said 2nd valve seat 18 via the bearing 154. FIG. Also in this case, the ball valve 14 rotates under the rotating action of the shaft 58, whereby the second valve seat 18 can be rotated more smoothly with the rotation of the ball valve 14.

  That is, the lubricant 152 or the bearing 154 provided in the second mounting groove 36 functions as a rotation promoting means for rotating and displacing the second valve seat 18 more smoothly, and such a lubricant 152 or the bearing 154 is provided. Therefore, uneven wear that occurs in the second valve seat 18 can be reliably prevented.

  In the above description, the case where the lubricant 152 or the bearing 154 is provided in the second mounting groove 36 in which the second valve seat 18 is provided has been described. However, the present invention is not limited to this. Instead of the mounting groove 36, the lubricant 152 or the bearing 154 may be provided for the first mounting groove 28 to rotate the first valve seat 16, or the first and second mounting grooves 28, 36. Both the first and second valve seats 16 and 18 may be smoothly rotated by providing the lubricant 152 or the bearing 154 on both of them.

  Moreover, in the flow path on-off valves 10, 100, 150 according to the first to third embodiments described above, the upper seat 50 and the lower seat 52 in the second seat portion 48 that contacts the second valve seat 18. However, the present invention is not limited to this. For example, instead of the second sheet portion 48, the upper sheet 50 and the lower sheet 52 in the first sheet portion 46 may be provided. It is good also as a structure which provides the difference of a contact area and rotates the 1st valve seat 16, and the difference of a contact area between any upper sheet | seat 50 and the lower sheet | seat 52 of the said 1st and 2nd seat parts 46 and 48 is good. The first and second valve seats 16 and 18 may be rotated together.

  Furthermore, instead of providing a difference in surface area or a difference in surface roughness between the upper seat 50 and the lower seat 52 in the ball valves 14, 80, 102, for example, the ball valves 14, 80, 102 abut. In the first and second valve seats 16 and 18, a difference in surface area may be provided between the upper side and the lower side of the first and second seat surfaces 32 and 40, respectively. Also in this case, a difference in contact area occurs in the circumferential direction between the ball valves 14, 80, 102 and the first and second valve seats 16, 18. The first and second valve seats 16 and 18 can be rotated under the rotating action.

  Further, in the flow path opening / closing valves 10, 100, 150 according to the first to third embodiments described above, for example, in order to further improve the sealing performance, for example, the first valve seat 16 and the second valve seat 18 An elastic member such as an O-ring may be provided on at least one of the outer peripheral surfaces. Accordingly, when at least one of the first valve seat 16 and the second valve seat 18 rotates inside the body main body 12, the first valve seat 16 and the second valve seat 18 and the body main body 12 are not connected. The leakage of the pressure fluid through is more reliably prevented by the elastic member.

  Further, in the flow path opening / closing valves 10, 100, 150, when the first valve seat 16 and / or the second valve seat 18 are rotated with the rotation of the ball valves 14, 80, 102, the ball valves 14, 80, 102 are rotated. And the rotation amount (rotation angle) of the first valve seat 16 and / or the second valve seat 18 do not necessarily coincide with each other. For example, the first valve seat 16 and / or the second valve seat 18 may be rotated slightly behind the rotation of the ball valves 14, 80, 102.

  In addition, the flow path on-off valve according to the present invention is not limited to the above-described embodiment, and it is needless to say that various configurations can be adopted without departing from the gist of the present invention.

DESCRIPTION OF SYMBOLS 10, 100, 150 ... Flow path on-off valve 12 ... Body main body 14, 80, 102 ... Ball valve 16 ... 1st valve seat 18 ... 2nd valve seat 20 ... Driving force transmission mechanism 26 ... Communication chamber 42 ... Through-hole 44a, 44b ... opening 46 ... first sheet portion 48, 104 ... second sheet portion 50, 108 ... upper sheet 52, 106 ... lower sheet 54 ... curved portion 58 ... shaft shaft 62 ... drive source 64a, 64b, 154 ... bearing 82a -82c ... Notch 152 ... Lubricant

Claims (9)

A ball valve with a through hole;
A body main body having a chamber that rotatably accommodates the ball valve, a fluid inlet to which a fluid is supplied, and a fluid outlet from which the fluid is discharged;
A shaft that switches the communication state between the fluid inlet and the fluid outlet by rotating the ball valve in the chamber;
A drive source for rotating the shaft shaft;
A seat member rotatably provided at at least one of the fluid inlet and the fluid outlet, and abutting on an outer peripheral surface of the ball valve;
With
The flow path opening / closing valve, wherein the seat member rotates in accordance with the rotation operation of the ball valve. The flow path opening / closing valve according to claim 1,
The flow path on-off valve characterized in that the rotation center of the seat member is perpendicular to the rotation center of the ball valve. In the flow path on-off valve according to claim 1 or 2,
A flow path on-off valve, wherein a first contact portion and a second contact portion that face the seat member and have different contact resistances with respect to the seat member are formed on an outer peripheral surface of the ball valve. In the flow path on-off valve according to claim 3,
The flow path opening / closing valve, wherein the first and second contact portions are divided and formed with a base line passing through a center of the through hole as a boundary. In the flow path on-off valve according to claim 3 or 4,
The flow path on-off valve, wherein the first and second contact portions are set so that the contact areas in contact with the sheet member are different. The flow path opening / closing valve according to claim 5,
One of the first contact portion and the second contact portion is provided with a curved portion formed with a radius larger than the outer radius of the ball valve. The flow path opening / closing valve according to claim 5,
One of the first contact portion and the second contact portion is provided with a recessed portion that is recessed with respect to the outer peripheral surface of the ball valve. In the flow path on-off valve according to claim 3 or 4,
The flow path on-off valve, wherein the first and second contact portions are set such that the surface roughness of the contact surface that contacts the sheet member is different. In the flow path on-off valve according to any one of claims 1 to 8,
A flow path on-off valve, characterized in that a rotation promoting means for promoting rotational displacement of the sheet member is provided between at least one of the fluid inlet and the fluid outlet and the sheet member.

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