JP2019019975A - Double-eccentric valve - Google Patents

Abstract

To provide a double-eccentric valve which can reduce slide resistance generated between a valve seat and a valve body.SOLUTION: This double-eccentric valve has a valve seat 13 including a valve hole 16 and an annular seat face 17 formed at an edge of the valve hole 16, a valve body 14 which is formed into a disc plate shape, and in which an annular seal face 18 corresponding to the seat face 17 is formed at an external periphery, and a rotating shaft 15 for turning the valve body 14. An axial line L1 of the rotating shaft 15 extends in parallel with the valve body 14 and a radial direction of the valve hole 16, and is arranged while being decentered to the radial direction of the valve hole 16 from a center P1 of the valve hole 16, and the seal face 18 is arranged while being decentered to a direction in which an axial line L2 of the valve body 14 extends from the axial line L1 of the rotating shaft 15. The valve seat 13 comprises a rubber seal part 13a in which the seat face 17 is formed, and a fastening margin TM between the valve seat 13 and the valve body 14 becomes minimum at a valve position PO5 at an end part in a direction parallel with a direction in which the axial line L1 of the rotating shaft 15 extends, being the radial direction of the valve body 14 at the valve body 14.SELECTED DRAWING: Figure 8

Description

  The present disclosure relates to a double eccentric valve in which a rotation center of a valve body is arranged eccentrically from a center of a valve hole of a valve seat, and a seal surface of the valve element is arranged eccentrically from a rotation center of the valve body. is there.

  As a prior art, there is a double eccentric valve as disclosed in Patent Document 1. The double eccentric valve includes a valve seat including a valve hole and an annular seat surface formed at an edge of the valve hole, a valve body having an annular seal surface corresponding to the seat surface formed on the outer periphery, and a valve body And a rotating shaft for rotating the. The axis (center axis) of the rotating shaft extends parallel to the radial direction of the valve body and the valve hole, and is eccentric from the center of the valve hole in the radial direction of the valve hole. Further, the sealing surface of the valve body is arranged eccentrically in the direction in which the axis of the valve body extends from the axis of the rotating shaft. In the double eccentric valve having such a structure, the valve element is rotated about the axis of the rotation shaft, whereby the sealing surface is in a fully closed position where the sealing surface comes into surface contact with the seat surface, and the sealing surface is the most from the seat surface. It can move between the fully open positions.

International Publication No. 2016/002599

  When the double eccentric valve described above is provided with a rubber seal at the contact portion of the valve seat with the valve body in order to improve the sealing (sealability) between the valve seat and the valve body, the valve is opened and closed. Sometimes, the sliding resistance generated between the valve seat and the valve body may increase due to the frictional force of the rubber seal portion. For this reason, the rubber seal portion is unevenly worn, the durability of the rubber seal portion is lowered, and the sealing performance between the valve seat and the valve body may be lowered.

  Accordingly, the present disclosure has been made to solve the above-described problems, and an object thereof is to provide a double eccentric valve that can reduce sliding resistance generated between a valve seat and a valve body.

  One form of the present disclosure made to solve the above problems is a valve seat including a valve hole and an annular seat surface formed at an edge of the valve hole, and has a disc shape, and corresponds to the seat surface. And a rotary shaft for rotating the valve body, and the axis of the rotary shaft is parallel to the radial direction of the valve body and the valve hole. The seal surface is eccentrically disposed in the direction in which the axis of the valve body extends from the axis of the rotary shaft, and the valve body is disposed in an eccentric manner in the radial direction of the valve hole from the center of the valve hole. Is configured to be movable between a fully closed position where the seal surface comes into surface contact with the seat surface and a fully opened position which is farthest away from the seat surface. In the eccentric valve, the valve seat or the valve body is the seat surface or the A rubber seal portion formed with a seal surface, and a tightening margin between the valve seat and the valve body is a radial direction of the valve body in the valve body and a direction parallel to a direction in which the axis of the rotating shaft extends It is characterized in that it is minimized at the position of the end portion in the rotation axis direction.

  According to this aspect, the tightening margin between the valve seat and the valve body is reduced at the position where the valve body and the valve seat are in contact with each other at the longest when the valve is opened and closed (the end portion in the rotational axis direction of the valve body). The contact range between the valve seat and the valve body during the opening / closing operation of the valve can be reduced. Therefore, the sliding range between the valve seat and the valve body can be reduced, and the sliding resistance generated between the valve seat and the valve body can be reduced.

  In the above aspect, the valve seat includes a rubber seal portion on which the seat surface is formed, and the valve body includes a notch at a position of the end portion in the rotation axis direction. And

  According to this aspect, at the position of the portion of the valve body that contacts the valve seat the longest during the opening and closing operation of the valve body, the notch portion is provided, thereby reducing the tightening margin with the valve seat and opening and closing the valve. The range of contact with the valve seat during operation can be reduced. Therefore, the sliding range between the valve seat and the valve body can be reduced, and the sliding resistance generated between the valve seat and the valve body can be reduced.

  In the above aspect, the valve body is formed in an elliptical shape having a direction parallel to a direction in which the axis of the rotating shaft extends as a minor axis direction.

  According to this aspect, the interference between the valve seat and the valve body is gradually reduced along the circumferential direction of the valve body, and the contact range between the valve seat and the valve body during the opening / closing operation of the valve can be further reduced. Therefore, the sliding range between the valve seat and the valve body can be further reduced, and the sliding resistance generated between the valve seat and the valve body can be reduced.

  Another form of the present disclosure made in order to solve the above problems is a valve seat including a valve hole and an annular seat surface formed at an edge of the valve hole, and a disc shape, A valve body having a corresponding annular sealing surface formed on the outer periphery, and a rotating shaft for rotating the valve body, and the axis of the rotating shaft is in the radial direction of the valve body and the valve hole Extending in parallel and being arranged eccentrically from the center of the valve hole in the radial direction of the valve hole, and the seal surface being arranged eccentrically in the direction in which the axis of the valve body extends from the axis of the rotary shaft, By rotating the body about the axis of the rotation shaft, the seal surface is configured to be movable between a fully closed position where the seal surface is in surface contact with the seat surface and a fully open position where the seal surface is farthest from the seat surface. In the heavy eccentric valve, the valve seat or the valve body is the seat surface or the front Comprising a rubber seal portion sealing surface is formed, that the seat surface or groove in the sealing surface is formed in the rubber seal portion, characterized by.

  According to this aspect, the area of interference between the valve seat and the valve seat in the rubber seal portion can be reduced when the valve seat and the valve body are in contact. Therefore, it is possible to reduce the sliding resistance generated between the valve seat and the valve body while reducing the repulsive force of the rubber seal portion with respect to the valve body or the valve seat and ensuring the seal width between the valve seat and the valve body.

  In the above aspect, the valve body includes a first side portion and a second side portion with a virtual plane extending in parallel with a direction in which the axis of the valve body extends from the axis of the rotation shaft as a boundary, When the valve body rotates in the valve closing direction, the first side portion rotates from the inside of the valve hole to the outside, and the second side portion turns from the outside to the inside of the valve hole. The rubber seal portion is provided in the valve seat, the groove is formed over the entire circumferential direction of the valve seat, and the first side portion of the groove slides. The moving side portion is formed at a position on the inner side of the valve hole with respect to the direction of the central axis of the valve hole than the portion on the side where the second side portion of the groove slides. It is characterized by.

  According to this aspect, by changing the position of the groove in the circumferential direction of the valve seat, the tightening margin can be reduced when the valve body and the rubber seal portion of the valve seat start to contact during the valve closing operation. In this way, the sliding resistance generated between the valve seat and the valve body before the valve is fully closed before the valve is fully closed can be reduced. In addition, even during the opening operation of the valve, the sliding range between the valve seat and the valve body can be reduced to reduce the sliding resistance generated between the valve seat and the valve body.

  Another form of the present disclosure made in order to solve the above problems is a valve seat including a valve hole and an annular seat surface formed at an edge of the valve hole, and a disc shape, A valve body having a corresponding annular sealing surface formed on the outer periphery, and a rotating shaft for rotating the valve body, and the axis of the rotating shaft is in the radial direction of the valve body and the valve hole Extending in parallel and being arranged eccentrically from the center of the valve hole in the radial direction of the valve hole, and the seal surface being arranged eccentrically in the direction in which the axis of the valve body extends from the axis of the rotary shaft, By rotating the body about the axis of the rotation shaft, the seal surface is configured to be movable between a fully closed position where the seal surface is in surface contact with the seat surface and a fully open position where the seal surface is farthest from the seat surface. In the heavy eccentric valve, the valve body extends from the axis of the rotary shaft to the axis of the valve body. A first side portion and a second side portion with a virtual plane extending in parallel with the extending direction as a boundary, and when the valve body rotates in the valve closing direction, the first side portion of the valve hole The second side portion is turned from the outside to the inside of the valve hole, and the valve body has a rubber seal portion on which the seal surface is formed. And the second side portion of the rubber seal portion has a smaller amount of entering the valve hole when fully closed than the first side portion of the rubber seal portion. And

  According to this aspect, when the rubber seal portion is fully closed, the amount of the rubber seal portion that contacts the valve seat can be reduced by reducing the amount of the rubber seal portion entering the valve hole. Therefore, during the opening / closing operation of the valve, the sliding range between the valve seat and the valve body can be reduced, and the sliding resistance generated between the valve seat and the valve body can be reduced.

  In the above aspect, the rubber seal portion is attached at the outer peripheral portion in the radial direction of the valve body, with the central axis of the rubber seal portion being oblique to the axis of the valve body, and the rubber seal portion The second side portion of the rubber seal portion is formed at a position outside the valve hole when fully closed in the axial direction of the valve body relative to the first side portion portion of the rubber seal portion. It is characterized by that.

  In the above aspect, the rubber seal portion is attached at a radially outer periphery of the valve body such that a central axis of the rubber seal portion coincides with an axis of the valve body. The portion on the second side portion side has a smaller thickness in the central axis direction of the rubber seal portion than the portion on the first side portion side in the rubber seal portion.

  Another form of the present disclosure made in order to solve the above problems is a valve seat including a valve hole and an annular seat surface formed at an edge of the valve hole, and a disc shape, A valve body having a corresponding annular sealing surface formed on the outer periphery, and a rotating shaft for rotating the valve body, and the axis of the rotating shaft is in the radial direction of the valve body and the valve hole Extending in parallel and being arranged eccentrically from the center of the valve hole in the radial direction of the valve hole, and the seal surface being arranged eccentrically in the direction in which the axis of the valve body extends from the axis of the rotary shaft, By rotating the body about the axis of the rotation shaft, the seal surface is configured to be movable between a fully closed position where the seal surface is in surface contact with the seat surface and a fully open position where the seal surface is farthest from the seat surface. In the heavy eccentric valve, a recess is formed in at least one of the seat surface and the seal surface. Or the grooves are formed, characterized by.

  According to this aspect, the contact area between the valve seat and the valve body can be reduced, and the sliding resistance generated between the valve seat and the valve body can be reduced.

  In the above aspect, the valve seat or the valve body includes a rubber seal portion on which the seat surface or the seal surface is formed, and the valve seat and the valve body do not include the rubber seal portion. It is preferable that the unevenness or the groove is formed on the sheet surface or the seal surface.

  According to this aspect, when the valve seat or the valve body includes the rubber seal portion, the contact area between the valve seat and the valve body can be reduced, and the sliding resistance generated between the valve seat and the valve body can be reduced.

  In said aspect, it is preferable that the said unevenness | corrugation or the said groove | channel is formed more, so that the required value of the sliding resistance of the said valve body with respect to the said valve seat is low.

  According to this aspect, the sliding resistance generated between the valve seat and the valve body can be reduced by forming many irregularities or grooves to reduce the contact area between the valve seat and the valve body.

  In the above aspect, in the axial cross section of the valve seat and the valve body when the valve body is in the fully closed position, the valve seat and the valve seat in the sliding region of the valve body It is preferable to provide a region in line contact with the valve body.

  According to this aspect, in the fully closed state, the fluid is blocked in the region where the valve seat and the valve body are in line contact, so that fluid leakage can be suppressed.

  According to the double eccentric valve of the present disclosure, the sliding resistance generated between the valve seat and the valve body can be reduced.

It is a perspective view showing an example of a flow control valve provided with the double eccentric valve of this indication. It is the perspective view which fractured | ruptured and showed the valve | bulb part in a fully closed state. It is the perspective view which fractured | ruptured and showed the valve part in a fully open state. It is a side view which shows a valve seat, a valve body, and a rotating shaft when it is a valve closing state. It is AA sectional drawing of FIG. It is sectional drawing which shows the valve seat and valve body of a fully closed state. It is a top view which shows the valve seat and valve body of a fully closed state. It is a top view of the valve element of a 1st embodiment. It is BB sectional drawing of FIG. It is a figure which shows the interference with the valve seat in each valve position in 1st Embodiment. It is a top view of the valve body of 2nd Embodiment. It is a figure which shows the interference with the valve seat in each valve position in 2nd Embodiment. It is a figure which shows the example in which a valve body is provided with a rubber seal part. In the 1st example of a 3rd embodiment, it is a figure in the position of the CC section of Drawing 7, and the DD section. It is a figure which shows the change of the magnitude | size of the torque of a rotating shaft in 1st Example of 3rd Embodiment. In 2nd Example of 3rd Embodiment, it is the figure which showed changing the position of a groove | channel about the circumferential direction of a valve seat, and is the schematic when a valve seat is perspectively viewed. In the 2nd Example of 3rd Embodiment, it is a figure in the position of the CC cross section and DD cross section of FIG. It is a side view of the valve body in 4th Embodiment. It is sectional drawing of the valve body and valve seat at the time of full closure in 4th Embodiment. It is a side view of the valve body in 5th Embodiment. It is sectional drawing of the valve body and valve seat at the time of full closure in 5th Embodiment. In 1st Example of 6th Embodiment, it is sectional drawing in the position of CC cross section of FIG. 7 (a valve body is a figure shown as an external view). It is a figure which shows the peak torque when not performing shot blasting when shot blasting is performed. In 2nd Example of 6th Embodiment, it is sectional drawing in the position of CC section of FIG. 7 (a figure which shows a valve body as an external view). FIG. 10 is an enlarged cross-sectional view taken along the line CC in FIG. 7 in a third example of the sixth embodiment. It is a figure which shows the modification of 3rd Example of 6th Embodiment. It is a figure which shows the interference with the valve seat in each valve position in comparative embodiment.

  Hereinafter, an embodiment in which the double eccentric valve of the present disclosure is embodied as a flow control valve will be described in detail with reference to the drawings.

[First Embodiment]
First, the first embodiment will be described. As shown in FIG. 1, the flow control valve 1 includes a valve portion 2 constituted by a double eccentric valve, a motor portion 3 incorporating a motor, and a speed reduction mechanism portion 4 incorporating a plurality of gears. As shown in FIGS. 2 and 3, the valve portion 2 includes a metal pipe portion 12 having a flow path 11 through which a fluid flows. Inside the flow path 11, a valve seat 13, a valve body 14, and a rotation are provided. A shaft 15 is arranged. The inner shape of the flow path 11, the outer shape of the valve seat 13, and the outer shape of the valve element 14 are each circular or almost circular in plan view. The rotational force of the motor is transmitted to the rotating shaft 15 via a plurality of gears. In the present embodiment, the pipe portion 12 having the flow path 11 corresponds to a part of the housing 6, and the motor of the motor portion 3 and the plurality of gears of the speed reduction mechanism portion 4 are covered by the housing 6. The housing 6 is made of a metal such as aluminum.

  A step portion 10 is formed in the flow path 11, and a valve seat 13 is incorporated in the step portion 10. The valve seat 13 has an annular shape and has a circular or substantially circular valve hole 16 in the center. An annular seat surface 17 is formed at the edge of the valve hole 16. In the present embodiment, the valve seat 13 includes a rubber seal portion 13a, and a seat surface 17 is formed on the rubber seal portion 13a. The valve body 14 has a disc shape, and an annular seal surface 18 corresponding to the seat surface 17 is formed on the outer periphery thereof. The valve body 14 is fixed to the rotating shaft 15 and rotates integrally with the rotating shaft 15.

  As shown in FIGS. 5 to 7, the axis L <b> 1 of the rotating shaft 15 extends parallel to the radial direction of the valve body 14 and the valve hole 16, and is decentered from the center P <b> 1 of the valve hole 16 to the radial direction of the valve hole 16. At the same time, the sealing surface 18 of the valve body 14 is arranged eccentrically in the direction in which the axis L2 of the valve body 14 extends from the axis L1 of the rotating shaft 15. Further, by rotating the valve body 14 about the axis L1 of the rotary shaft 15, a fully closed position (see FIG. 2) where the seal surface 18 of the valve body 14 is in surface contact with the seat surface 17 of the valve seat 13. It is configured to be movable between a fully open position (see FIG. 3) farthest from the seat surface 17.

  In the present embodiment, in FIG. 5, the valve body 14 starts to rotate in the valve opening direction (the direction of the arrow F <b> 1 shown in FIG. 5, that is, the clockwise direction in FIG. 5) from the fully closed position. The surface 18 starts to move away from the seat surface 17 of the valve seat 13 and starts to move along the rotation trajectories T1 and T2 about the axis L1 of the rotation shaft 15.

  As shown in FIGS. 6 and 7, the valve body 14 has a virtual plane V1 extending in parallel with the direction in which the central axis L3 of the valve hole 16 (the axis L2 of the valve body 14) extends from the axis L1 of the rotating shaft 15. Divided into a first side portion 21 (a portion shown by shading in FIGS. 6 and 7) and a second side portion 22 (a portion not shaded in FIGS. 6 and 7). . When the valve body 14 rotates in the valve opening direction indicated by the arrow F1 from the fully closed position shown in FIG. 6, the first side portion 21 rotates toward the valve hole 16, and the second side The portion 22 is configured to rotate toward the outside of the valve hole 16. Further, when the valve is turned in the valve closing direction (the direction opposite to the direction indicated by the arrow F1) from the valve opening position (see FIG. 3) toward the fully closed position shown in FIG. The second side portion 22 is configured to rotate from the outside to the inside of the valve hole 16.

  As shown in FIGS. 4 to 7, the valve body 14 includes a mountain-shaped fixing portion 14 b that protrudes from the upper plate surface 14 a and is fixed to the rotating shaft 15. The fixing portion 14b is fixed to the rotating shaft 15 via a pin 15a protruding from the tip of the rotating shaft 15 at a position shifted from the axis L1 of the rotating shaft 15 in the radial direction of the rotating shaft 15. 5-7, the fixing | fixed part 14b is arrange | positioned on the axis line L2 of the valve body 14, and the valve body 14 containing the fixing | fixed part 14b is a left-right symmetric shape centering on the axis line L2 of the valve body 14. As shown in FIG. Is formed.

  In the present embodiment, the end face of the valve body 14 is cut (cut). That is, as shown in FIGS. 8 and 9, the valve body 14 has an end portion in the radial direction of the valve body 14 and parallel to the direction in which the axis L <b> 1 of the rotating shaft 15 extends (end portion in the rotating shaft direction). The cut portion 31 (notch portion) is provided at the position (valve position PO5). In this way, both end faces of the valve body 14 in the direction of the axis L1 of the rotating shaft 15 (the vertical direction in FIG. 8) are cut. That is, the valve body 14 is formed in a shape in which both ends in the radial direction are cut in a part of a perfect circle. As an example, when the diameter of the valve body 14 is 30 mm, the maximum width in the radial direction of the valve body 14 cut by the cut portion 31 on one side is set to 0.05 mm.

  In this way, the tightening margin TM (hereinafter simply referred to as “tightening margin TM”) between the valve seat 13 (specifically, the rubber seal portion 13a) and the valve body 14 is minimized at the valve position PO5. That is, as shown in FIG. 10, the tightening allowance TM at the valve position PO5 (shown by a dotted line in FIG. 10) is the tightening allowance TM at the valve positions PO1, PO2, PO3, PO4 (see FIG. 8) (in FIG. 10). Smaller than that shown by the solid line).

  Here, as shown in FIG. 8, the valve position PO1 is the position of the end of the valve body 14 in the direction orthogonal to the direction in which the axis L1 of the rotary shaft 15 extends in the radial direction of the valve body 14. Further, the valve position PO5 is a position of an end portion in a direction parallel to the direction in which the axis L1 of the rotating shaft 15 extends in the radial direction of the valve body 14 in the valve body 14. The valve positions PO2, PO3, and PO4 are positions shifted in the circumferential direction of the valve body 14 between the valve position PO1 and the valve position PO5.

  Thus, in this embodiment, since the valve body 14 includes the cut portion 31, the portion where the valve body 14 and the valve seat 13 are in contact with each other at the time of opening and closing the valve (the rotation axis of the valve body 14). At the position of the direction end (valve position PO5), the tightening margin TM can be reduced to reduce the contact range between the valve seat 13 and the valve body 14 during the valve opening / closing operation. Therefore, the sliding range between the valve seat 13 and the valve body 14 can be reduced, and the sliding resistance generated between the valve seat 13 and the valve body 14 can be reduced.

  Further, as shown in FIG. 22, in the comparative embodiment in which the valve body 14 does not include the cut portion 31, the tightening margin TM at the valve position PO5 is large, so that the opening degree of the entire circumference increases. However, as shown in FIG. 10, in the present embodiment, the tightening margin TM at the valve position PO5 is smaller than in this comparative example, so that the opening degree of the entire circumference is small. The all-round opening is the opening when the tightening margin TM becomes 0 without the valve element 14 contacting the valve seat 13 over the entire circumference.

[Second Embodiment]
Hereinafter, although 2-6th embodiment is described, about the component equivalent to 1st Embodiment, the same code | symbol is attached | subjected and description is abbreviate | omitted and it describes focusing on a different point. Therefore, a second embodiment will be described next.

  In the present embodiment, as shown in FIG. 11, the valve body 14 is formed in an elliptical shape having a direction parallel to the direction in which the axis L <b> 1 of the rotating shaft 15 extends as a minor axis direction.

  In this way, as shown in FIG. 12, the tightening allowance TM is gradually reduced in the order of the valve positions PO1, PO2, PO3, PO4 and PO5. The tightening allowance TM is minimum at the valve position PO5. As an example, when fully closed (when the opening degree is 0), the allowance TM at the valve position PO5 is 0.05 mm smaller than when the valve body 14 is formed in a perfect circle shape. .

  Thus, in the present embodiment, the tightening margin TM is gradually reduced from the valve position PO2 to the valve position PO5 as it goes from the valve position PO1 toward the valve position PO5 along the circumferential direction of the valve body 14. Thus, the contact range between the valve seat 13 and the valve body 14 during the opening / closing operation of the valve can be reduced. Therefore, the sliding range between the valve seat 13 and the valve body 14 can be further reduced, and the sliding resistance generated between the valve seat 13 and the valve body 14 can be reduced.

  Also, as shown in FIG. 12, in this embodiment, the tightening margin TM at the valve positions PO1, PO2, PO3, PO4, and PO5 is smaller than in the comparative example shown in FIG. It becomes even smaller.

  In addition, as shown in FIG. 13, the valve body 14 may be provided with the rubber seal part 14c instead of the valve seat 13 being provided with the rubber seal part 13a. At this time, a seal surface 18 is formed on the rubber seal portion 14c. Thereby, the pipe part 12 (body) and the valve seat 13 can be integrally molded. Therefore, there is no need to press-fit and attach the valve seat 13 to the pipe portion 12 (step portion 10), thereby eliminating the trouble of positioning the valve seat 13 and reducing the cost. Further, there is no fear of occurrence of fluid leakage at the portion where the valve seat 13 is press-fitted and attached.

  In the present embodiment, as a modification, the valve body 14 may further include a notch portion similar to the cut portion 31 of the first embodiment.

[Third Embodiment]
Next, a third embodiment will be described.

(First embodiment)
First, a first example of the third embodiment will be described. In the present embodiment, a groove 32 is added to an interference portion with the valve body 14 in the rubber seal portion 13a of the valve seat 13. That is, as shown in FIG. 14, a groove 32 is formed in the seat surface 17 in the rubber seal portion 13 a of the valve seat 13. In addition, the groove | channel 32 of a present Example is formed over the whole circumferential direction of the valve seat 13, and the position of the center hole L3 direction of the valve hole 16 about the groove | channel 32 is the same over the whole circumferential direction of the valve seat 13. Formed in position.

  Thereby, the interference area S (refer FIG. 14) with the valve body 14 in the rubber seal part 13a of the valve seat 13 at the time of contact of the valve seat 13 and the valve body 14 can be reduced. Therefore, the repulsive force of the rubber seal part 13a of the valve seat 13 with respect to the valve body 14 can be reduced, and the sliding resistance generated between the valve seat 13 and the valve body 14 can be reduced. This reduces the peak torque (maximum torque) PT of the rotating shaft 15 during the opening operation of the valve shown in FIG. Can reduce the sliding resistance. Further, a seal width δ between the valve seat 13 and the valve body 14 can be secured.

  Instead of the valve seat 13 including the rubber seal portion 13a, the valve body 14 may include a rubber seal portion, and the groove 32 may be formed in the seal surface 18 of the rubber seal portion of the valve body 14. Further, the groove 32 may be formed only in a part of the valve seat 13 or the valve body 14 in the circumferential direction. Further, as shown in FIG. 24 described later, a flat portion 34 may be provided in the sliding area SA of the valve seat 13 and the valve body 14.

(Second embodiment)
Next, a second example of the third embodiment will be described. In the present embodiment, the position of the groove 32 is changed in the circumferential direction of the valve seat 13. That is, as shown in FIGS. 16 and 17, the groove 32 is formed over the entire circumferential direction of the valve seat 13. The first portion 32a on the side where the first side portion 21 of the valve body 14 slides in the groove 32 is the second portion 32b on the side where the second side portion 22 of the valve body 14 in the groove 32 slides. More in the direction of the central axis L3 of the valve hole 16 than in the position indicated by the alternate long and short dash line in FIG. 17 (the lower side of FIG. 17, the side away from the rotary shaft 15). Is formed.

  In this way, by changing the position of the groove 32 in the circumferential direction of the valve seat 13, the valve body 14 moves in the direction of the arrow F <b> 2 during the valve closing operation, and the rubber seal portion 13 a between the valve body 14 and the valve seat 13. The tightening allowance TM can be reduced when and start to contact. That is, as shown by a solid line in FIG. 17, when the valve body 14 and the rubber seal portion 13a start to contact, the rubber seal portion 13a and the valve body 14 do not contact at the first portion 32a of the groove 32. The cost TM can be reduced. After that, as shown by a two-dot chain line in FIG. 17, a necessary tightening allowance TM can be obtained when fully closed. In this manner, sliding resistance generated between the valve seat 13 and the valve body 14 before the valve is fully closed before the valve is fully closed can be reduced. Further, even during the opening operation of the valve, the sliding range between the valve seat 13 and the valve body 14 can be reduced, and the sliding resistance generated between the valve seat 13 and the valve body 14 can be reduced.

  Also in this embodiment, similarly to the first embodiment, the sliding torque generated between the valve seat 13 and the valve body 14 can be reduced by reducing the peak torque of the rotating shaft 15.

[Fourth Embodiment]
Next, a fourth embodiment will be described. In the present embodiment, as shown in FIG. 18, the valve body 14 includes a rubber seal portion 14 d at the outer peripheral portion in the radial direction of the valve body 14. A seal surface 18 is formed on the rubber seal portion 14d. The rubber seal portion 14d is attached to the valve body 14 at an angle. That is, the rubber seal portion 14d is attached at the outer peripheral portion in the radial direction of the valve body 14 with the central axis L4 of the rubber seal portion 14d inclined (tilted) with respect to the axis L2 of the valve body 14. The thickness of the rubber seal portion 14d is constant in the circumferential direction of the rubber seal portion 14d. Further, as shown in FIG. 19, the second portion 14db on the second side portion 22 side of the valve body 14 in the rubber seal portion 14d is the first portion on the first side portion 21 side of the valve body 14 in the rubber seal portion 14d. It is formed at a position that is outside of the valve hole 16 (upper side in FIG. 19) when fully closed with respect to the direction of the axis L2 of the valve body 14 than 14da.

  In this way, as shown in FIG. 19, the second portion 14db in the rubber seal portion 14d has a smaller amount of entering the valve hole 16 when fully closed than the first portion 14da in the rubber seal portion 14d. Sometimes the amount of contact with the valve seat 13 is small. Therefore, during the opening / closing operation of the valve, the sliding range between the valve seat 13 and the valve body 14 (particularly, the sliding range between the valve seat 13 and the second portion 14db of the rubber seal portion 14d) can be reduced. Therefore, the sliding resistance generated between the valve seat 13 and the valve body 14 can be reduced.

[Fifth Embodiment]
Next, a fifth embodiment will be described. In the present embodiment, as shown in FIG. 20, the valve body 14 includes a rubber seal portion 14 e at the outer peripheral portion in the radial direction of the valve body 14. Note that a seal surface 18 is formed in the rubber seal portion 14e. The rubber seal portion 14e is attached to the outer peripheral portion of the valve body 14 in the radial direction so that the central axis L5 of the rubber seal portion 14e coincides with the axis L2 of the valve body 14. The rubber seal portion 14e is formed such that one is thin and the other is thick. That is, the portion 14eb on the second side portion 22 side of the rubber seal portion 14e has a smaller thickness in the direction of the central axis L5 of the rubber seal portion 14e than the portion 14ea on the first side portion 21 side of the rubber seal portion 14e.

  In this way, as shown in FIG. 21, the second portion 14eb in the rubber seal portion 14e has a smaller amount of entering the valve hole 16 when fully closed than the first portion 14ea in the rubber seal portion 14e. Sometimes the amount of contact with the valve seat 13 is small. Therefore, during the opening / closing operation of the valve, the sliding range between the valve seat 13 and the valve body 14 (particularly, the sliding range between the valve seat 13 and the second portion 14eb of the rubber seal portion 14e) can be reduced. Therefore, the sliding resistance generated between the valve seat 13 and the valve body 14 can be reduced.

[Sixth Embodiment]
Next, a sixth embodiment will be described.

(First embodiment)
First, a first example of the sixth embodiment will be described. In this embodiment, as shown in FIG. 22, when the valve seat 13 is provided with a rubber seal portion 13a, a plurality of seal surfaces 18 of a metal (for example, stainless steel) valve body 14 not provided with a rubber seal portion are provided. Concavities and convexities formed of (innumerable) concave portions 33 are formed. The unevenness (recess 33) is formed by, for example, performing shot blasting on the outer peripheral surface of the valve body 14. Thereby, the contact area of the valve seat 13 and the valve body 14 in a fully closed state can be reduced.

  As an analysis result regarding this example, as shown in FIG. 23, when shot blasting is performed on the outer peripheral surface of the valve body 14 (in the case of “shot blasting”), shot blasting is performed on the outer peripheral surface of the valve body 14. The result that peak torque PT fell rather than the case where it did not do (in the case of "shot blast non-execution") was obtained. In this manner, shot blasting is performed on the outer peripheral surface of the valve body 14 to form irregularities on the seal surface 18, thereby reducing the peak torque PT and the sliding generated between the valve seat 13 and the valve body 14. Dynamic resistance can be reduced.

  As described above, according to the present embodiment, when the valve seat 13 includes the rubber seal portion 13a, the unevenness is formed on the seal surface 18 of the metal valve body 14 that does not include the rubber seal portion.

  Accordingly, the sliding resistance generated between the valve seat 13 and the valve body 14 can be reduced by reducing the contact area between the valve seat 13 and the valve body 14 without changing the seal width δ and the tightening allowance TM. .

  Further, as the required value of the sliding resistance of the valve body 14 with respect to the valve seat 13 is lower (that is, as the requirement for suppressing the sliding resistance is more severe), more unevenness may be formed. In this way, sliding resistance generated between the valve seat 13 and the valve body 14 can be reduced by forming many irregularities and reducing the contact area between the valve seat 13 and the valve body 14.

  As a modified example, when the valve body 14 includes a rubber seal portion, irregularities may be formed on the seat surface 17 of the valve seat 13 made of metal (for example, aluminum) that does not include the rubber seal portion. . Further, in the valve seat 13 or the valve body 14, unevenness may be formed only on the seat surface 17 or the seal surface 18 instead of the entire outer peripheral surface of the valve seat 13 or the valve body 14.

(Second embodiment)
Next, a second example of the sixth embodiment will be described, but differences from the first example of the sixth embodiment will be described. In the present embodiment, when unevenness is formed on the seal surface 18 of the valve body 14, a flat portion 34 is formed on a part of the seal surface 18 as shown in FIG. 24. In this way, when the valve body 14 is in the fully closed position (when in the fully closed state), the valve seat 13 and the valve body 14 in the axial cross section (cross section formed along the axial direction) A flat portion 34 is provided as a region where the valve seat 13 and the valve body 14 are in line contact with each other in the sliding area SA of the valve body 13 and the valve body 14. The flat portion 34 is formed over the entire circumferential direction of the valve body 14. Thereby, the sealing performance can be maintained by the flat portion 34 in the fully closed state. As a modification, when the seat surface 17 of the valve seat 13 is uneven, the flat portion 34 may be formed on a part of the seat surface 17.

  As described above, according to the present embodiment, the valve seat 13 and the valve body 14 are in the sliding area SA in the axial cross section of the valve seat 13 and the valve body 14 in the fully closed state. A flat portion 34 is provided as a region where the valve body 14 is in line contact. Thereby, in a fully closed state, since the fluid is interrupted | blocked by the plane part 34, the leakage of the fluid can be suppressed.

(Third embodiment)
Next, a third example of the sixth embodiment will be described. In the present embodiment, as shown in FIG. 25, when the valve seat 13 includes a rubber seal portion 13a, two grooves 35 are formed on the seal surface 18 of the metal valve body 14 that does not include the rubber seal portion. ing. The groove 35 is formed over the entire circumferential direction of the valve body 14.

  In this way, when the two grooves 35 are formed on the seal surface 18, the repulsive force of the rubber seal portion 13 a is lower than when the groove 35 is not formed on the seal surface 18.

  The number of grooves 35 is not particularly limited. For example, as a modification, four grooves 35 may be formed on the seal surface 18 as shown in FIG. Thereby, the contact area of the valve seat 13 and the valve body 14 can be reduced as compared with the case where the two grooves 35 are formed in the seal surface 18. Therefore, for example, when emphasizing ensuring the sealing performance in the fully closed state, two grooves 35 are formed on the seal surface 18 while reducing the sliding resistance generated between the valve seat 13 and the valve body 14. If importance is attached, four grooves 35 may be formed on the seal surface 18. That is, as the required value of the sliding resistance of the valve body 14 with respect to the valve seat 13 is lower, more grooves 35 may be formed.

  As described above, according to this embodiment, when the valve seat 13 includes the rubber seal portion 13a, the groove 35 is formed in the seal surface 18 of the metal valve body 14 that does not include the rubber seal portion.

  Accordingly, the sliding resistance generated between the valve seat 13 and the valve body 14 can be reduced by reducing the contact area between the valve seat 13 and the valve body 14 without changing the seal width δ and the tightening allowance TM. . Further, in the case where the groove is formed in the rubber seal portion, the groove forming accuracy may be a problem. However, in this embodiment, the groove 35 is formed on the seal surface 18 of the metal valve body 14, and therefore the groove 35 is formed. Accuracy can be improved.

  Moreover, the groove | channel 35 may be formed more, so that the required value of the sliding resistance of the valve body 14 with respect to the valve seat 13 is low. In this way, the sliding resistance generated between the valve seat 13 and the valve body 14 can be reduced by forming many grooves 35 and reducing the contact area between the valve seat 13 and the valve body 14.

  As a modification, when the valve body 14 includes a rubber seal portion, a groove 35 may be formed in the seat surface 17 of the metal valve seat 13 that does not include the rubber seal portion. Further, the groove 35 may be formed only in a part of the valve seat 13 or the valve body 14 in the circumferential direction. Further, a flat portion 34 (see FIG. 24) may be provided in the sliding area SA between the valve seat 13 and the valve body 14.

  It should be noted that the above-described embodiment is merely an example, and does not limit the present disclosure in any way, and various improvements and modifications can be made without departing from the scope of the present invention.

  For example, grooves may be formed on both the seat surface 17 of the valve seat 13 and the seal surface 18 of the valve body 14. Moreover, both the valve body 14 and the valve seat 13 may be provided with the rubber seal part. Further, both the valve body 14 and the valve seat 13 may not include the rubber seal portion. Moreover, both the unevenness | corrugation and the groove | channel 35 may be formed in the sheet | seat surface 17 or the sealing surface 18 in the metal valve seat 13 or the valve body 14 which is not provided with the rubber seal part.

DESCRIPTION OF SYMBOLS 1 Flow control valve 2 Valve part 3 Motor part 13 Valve seat 13a Rubber seal part 14 Valve body 14c Rubber seal part 14d Rubber seal part 14da First part 14db Second part 14e Rubber seal part 14ea First part 14eb Second part 15 Rotating shaft 15a Pin 16 Valve hole 17 Seat surface 18 Seal surface 21 First side portion 22 Second side portion 31 Cut portion 32 Groove 32a First portion 32b Second portion 33 Recess 34 Flat portion 35 Groove L1 (Rotating shaft) axis L2 (Valve) Body axis L3 (Valve hole) Center axis L4 (Rubber seal part) Center axis L5 (Rubber seal part) Center axis V1 Virtual plane PO1, PO2, PO3, PO4, PO5 Valve position TM Tightening margin S Interference area PT Peak Torque δ Seal width SA Sliding area

Claims (12)

A valve seat including a valve hole and an annular seat surface formed at an edge of the valve hole;
A disc having a disc shape and an annular sealing surface corresponding to the seat surface formed on the outer periphery;
A rotating shaft for rotating the valve body,
The axis of the rotary shaft extends parallel to the radial direction of the valve body and the valve hole, and is arranged eccentrically from the center of the valve hole in the radial direction of the valve hole, and the seal surface is the axis of the rotary shaft. The valve body is arranged eccentrically in the direction in which the axis of the valve body extends, and the valve body is rotated about the axis of the rotary shaft, whereby the seal surface is in surface contact with the seat surface and the seat In the double eccentric valve configured to be movable between the fully open position furthest away from the surface,
The valve seat or the valve body includes a rubber seal portion on which the seat surface or the seal surface is formed,
The tightening allowance between the valve seat and the valve body is minimized at the position of the end of the rotary shaft in the radial direction of the valve body in the direction parallel to the direction in which the axis of the rotary shaft extends. That
Double eccentric valve characterized by The double eccentric valve of claim 1,
The valve seat includes a rubber seal portion on which the seat surface is formed,
The valve body has a notch at the position of the end in the rotational axis direction;
Double eccentric valve characterized by The double eccentric valve according to claim 1 or 2,
The valve body is formed in an elliptical shape having a direction parallel to a direction in which the axis of the rotation axis extends as a minor axis direction;
Double eccentric valve characterized by A valve seat including a valve hole and an annular seat surface formed at an edge of the valve hole;
A disc having a disc shape and an annular sealing surface corresponding to the seat surface formed on the outer periphery;
A rotating shaft for rotating the valve body,
The axis of the rotary shaft extends parallel to the radial direction of the valve body and the valve hole, and is arranged eccentrically from the center of the valve hole in the radial direction of the valve hole, and the seal surface is the axis of the rotary shaft. The valve body is arranged eccentrically in the direction in which the axis of the valve body extends, and the valve body is rotated about the axis of the rotary shaft, whereby the seal surface is in surface contact with the seat surface and the seat In the double eccentric valve configured to be movable between the fully open position furthest away from the surface,
The valve seat or the valve body includes a rubber seal portion on which the seat surface or the seal surface is formed,
Grooves are formed in the sheet surface or the seal surface in the rubber seal portion,
Double eccentric valve characterized by The double eccentric valve of claim 4,
The valve body includes a first side and a second side with a virtual plane extending in parallel with a direction in which the axis of the valve extends from the axis of the rotation shaft as a boundary,
When the valve body rotates in the valve closing direction, the first side portion rotates from the inside of the valve hole to the outside, and the second side portion faces from the outside to the inside of the valve hole. And rotate,
The rubber seal portion is provided in the valve seat,
The groove is formed throughout the circumferential direction of the valve seat,
The portion of the groove on the side where the first side portion slides is more in the direction of the central axis of the valve hole than the portion of the groove on the side where the second side portion slides. Being formed in the middle position,
Double eccentric valve characterized by A valve seat including a valve hole and an annular seat surface formed at an edge of the valve hole;
A disc having a disc shape and an annular sealing surface corresponding to the seat surface formed on the outer periphery;
A rotating shaft for rotating the valve body,
The axis of the rotary shaft extends parallel to the radial direction of the valve body and the valve hole, and is arranged eccentrically from the center of the valve hole in the radial direction of the valve hole, and the seal surface is the axis of the rotary shaft. The valve body is arranged eccentrically in the direction in which the axis of the valve body extends, and the valve body is rotated about the axis of the rotary shaft, whereby the seal surface is in surface contact with the seat surface and the seat In the double eccentric valve configured to be movable between the fully open position furthest away from the surface,
The valve body includes a first side and a second side with a virtual plane extending in parallel with a direction in which the axis of the valve extends from the axis of the rotation shaft as a boundary,
When the valve body rotates in the valve closing direction, the first side portion rotates from the inside of the valve hole to the outside, and the second side portion faces from the outside to the inside of the valve hole. And rotate,
The valve body includes a rubber seal portion on which the seal surface is formed,
The second side portion of the rubber seal portion has a smaller amount of entering the valve hole when fully closed than the first side portion of the rubber seal portion.
Double eccentric valve characterized by The double eccentric valve of claim 6,
The rubber seal portion is attached at the outer peripheral portion in the radial direction of the valve body, with the central axis of the rubber seal portion being oblique to the axis of the valve body,
The portion on the second side portion side of the rubber seal portion is positioned outside the valve hole when fully closed in the axial direction of the valve body, compared to the portion on the first side portion side of the rubber seal portion. Being formed,
Double eccentric valve characterized by The double eccentric valve of claim 6,
The rubber seal portion is attached at the outer peripheral portion in the radial direction of the valve body such that the central axis of the rubber seal portion coincides with the axis of the valve body,
The second side portion side portion of the rubber seal portion has a smaller thickness in the central axis direction of the rubber seal portion than the first side portion portion of the rubber seal portion.
Double eccentric valve characterized by A valve seat including a valve hole and an annular seat surface formed at an edge of the valve hole;
A disc having a disc shape and an annular sealing surface corresponding to the seat surface formed on the outer periphery;
A rotating shaft for rotating the valve body,
The axis of the rotary shaft extends parallel to the radial direction of the valve body and the valve hole, and is arranged eccentrically from the center of the valve hole in the radial direction of the valve hole, and the seal surface is the axis of the rotary shaft. The valve body is arranged eccentrically in the direction in which the axis of the valve body extends, and the valve body is rotated about the axis of the rotary shaft, whereby the seal surface is in surface contact with the seat surface and the seat In the double eccentric valve configured to be movable between the fully open position furthest away from the surface,
Concavities and convexities or grooves are formed on at least one of the sheet surface and the seal surface,
Double eccentric valve characterized by The double eccentric valve of claim 9,
The valve seat or the valve body includes a rubber seal portion on which the seat surface or the seal surface is formed,
The unevenness or the groove is formed on the seat surface or the seal surface of the valve seat and the valve body that does not include the rubber seal portion,
Double eccentric valve characterized by A double eccentric valve according to claim 4 or 5 or 9 or 10
As the required value of the sliding resistance of the valve body with respect to the valve seat is lower, the unevenness or the groove is more formed,
Double eccentric valve characterized by A double eccentric valve according to claim 4 or 5 or 9 or 10 or 11
In the axial cross section of the valve seat and the valve body when the valve body is in the fully closed position, the valve seat and the valve body are lined in a sliding region of the valve seat and the valve body. Providing a contact area;
Double eccentric valve characterized by

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