WO2017154487A1 - Valve device - Google Patents

Valve device Download PDF

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Publication number
WO2017154487A1
WO2017154487A1 PCT/JP2017/005459 JP2017005459W WO2017154487A1 WO 2017154487 A1 WO2017154487 A1 WO 2017154487A1 JP 2017005459 W JP2017005459 W JP 2017005459W WO 2017154487 A1 WO2017154487 A1 WO 2017154487A1
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WO
WIPO (PCT)
Prior art keywords
seal ring
valve
joint
valve device
diameter
Prior art date
Application number
PCT/JP2017/005459
Other languages
French (fr)
Japanese (ja)
Inventor
晃 下山
将行 浜崎
祥平 鈴木
Original Assignee
大豊工業株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from JP2016045765A external-priority patent/JP6621346B2/en
Priority claimed from JP2016045766A external-priority patent/JP2017160990A/en
Priority claimed from JP2016045767A external-priority patent/JP2017160991A/en
Application filed by 大豊工業株式会社 filed Critical 大豊工業株式会社
Publication of WO2017154487A1 publication Critical patent/WO2017154487A1/en

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/18—Sealings between relatively-moving surfaces with stuffing-boxes for elastic or plastic packings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K1/00—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces
    • F16K1/16—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces with pivoted closure-members
    • F16K1/18—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces with pivoted closure-members with pivoted discs or flaps
    • F16K1/22—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces with pivoted closure-members with pivoted discs or flaps with axis of rotation crossing the valve member, e.g. butterfly valves
    • F16K1/226—Shaping or arrangements of the sealing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/65—Constructional details of EGR valves
    • F02M26/70—Flap valves; Rotary valves; Sliding valves; Resilient valves

Definitions

  • the present invention relates to a technology of a valve device that controls a fluid flow by rotating a valve.
  • Patent Document 1 the technology of a valve device that controls the flow of fluid by rotating a valve is known. For example, as described in Patent Document 1.
  • a valve device (fluid control valve) described in Patent Document 1 includes a cylindrical sheet (a housing nozzle) in which a flow path is formed, a disk-shaped valve (butterfly valve) disposed in the flow path, A seal ring fitted to the outer periphery of the valve, a shaft for supporting the valve, an actuator for rotating the valve via the shaft, and the like are provided.
  • the valve device described in Patent Document 1 closes the flow path by rotating the valve so that the plate surface of the valve faces the axial direction of the seat by an actuator. At this time, the seal ring seals the gap between the seat and the valve. Further, the flow path is opened by rotating the valve closing the flow path.
  • Patent Document 1 the seat and the seal ring described in Patent Document 1 are disadvantageous in that they are easily worn by sliding when the valve rotates.
  • the present invention has been made in view of the above situation, and a problem to be solved is to provide a valve device capable of suppressing wear of a seat and a seal ring.
  • the valve device of the present invention includes a seat having a flow passage formed therethrough, a valve that is rotatably disposed in the flow passage, and that opens and closes the flow passage, and an outer periphery of the valve.
  • the seal ring includes a joint that is a cut portion, and the diameter expanding means expands the diameter of the seal ring by pushing and widening the joint.
  • the diameter expanding means pushes the joint together by entering the joint when the valve is rotated to a position where the flow path is closed.
  • the diameter expanding means is fixed to the seat.
  • the abutment is arranged at a position away from the rotation axis of the valve.
  • the diameter expanding means is constituted by a member different from the seat.
  • a tension in the direction of diameter reduction acts on the seal ring.
  • the valve device further includes a restricting means that is disposed inside the joint and restricts relative rotation of the seal ring with respect to the valve, and the diameter expanding means enters the joint and enters the joint.
  • the regulating means is provided with an accommodating portion that enters the inside when entering the joint.
  • the diameter expanding means is fixed to the seat.
  • the accommodating portion is open on the side of the diameter-expanding means that enters the joint, and is closed on the side opposite to the side that enters the joint.
  • the end surface of the housing portion opposite to the side entering the joint is formed in a shape that follows the shape of the restricting means.
  • the accommodating portion is formed so as to extend in a direction in which the diameter expanding means enters the joint.
  • the restricting means is constituted by a member different from the valve.
  • the seal ring includes a joint formed by abutting both end portions, and the diameter expanding means expands the seal ring by entering the joint and expanding the joint.
  • the seal ring further includes a guide portion that guides the diameter expanding means to enter the joint.
  • the guide portion is formed so as to gradually spread in the circumferential direction of the seal ring toward the receiving side of the diameter expanding means.
  • the guide portion is formed in a curved surface shape.
  • the seal ring includes a circumferential portion extending along a circumferential direction, and a projecting portion projecting in a direction in which the diameter expanding means enters the joint from an end portion of the circumferential portion. Furthermore, the said guide part is formed in the connection part of the said circumference part and the said protrusion part.
  • the valve has a narrow groove for fitting the circumferential portion, a width communicating with the narrow groove and wider than the width of the narrow groove, and the protruding portion is disposed. And a thick groove for carrying out.
  • the guide portion is formed on an end face of the seal ring.
  • the valve device of the present invention can suppress wear of the seat and the seal ring.
  • the valve device of the present invention can easily expand the diameter of the seal ring.
  • the valve device of the present invention can simplify the configuration of the diameter expanding means.
  • the valve device of the present invention can effectively suppress wear of the seat and the seal ring.
  • the valve device of the present invention can be easily provided with a diameter expanding means.
  • the valve device of the present invention can suppress the occurrence of malfunction.
  • the valve device of the present invention can improve the sealing performance.
  • the valve device of the present invention can make it difficult to break the restricting means and the diameter expanding means.
  • the valve device of the present invention can easily form the regulating means.
  • the valve device of the present invention can suppress wear of the seal ring.
  • the valve device of the present invention can effectively suppress the wear of the seal ring.
  • the front sectional view showing the valve device concerning a first embodiment of the present invention (A) The expanded side view which showed the valve
  • A The expanded side view which showed the valve
  • B A2-A2 cross-sectional view.
  • A The perspective view which showed the notch pin.
  • B Side surface sectional drawing which showed the accommodating part.
  • A The expanded side surface sectional view which showed a mode that a seal ring and a notch pin contact
  • B Similarly, an enlarged front sectional view.
  • A The expanded side surface sectional view which showed a mode that the joint opening was expanded.
  • B Similarly, an enlarged front sectional view.
  • Front sectional drawing which showed the state which obstruct
  • the front sectional view showing the valve device concerning a third embodiment of the present invention (A) The expanded side view which showed the valve
  • the valve device 10 is for controlling the flow of fluid.
  • the valve apparatus 10 which concerns on 1st embodiment shall be provided in an exhaust-gas recirculation (EGR) apparatus of an engine.
  • EGR exhaust-gas recirculation
  • the valve device 10 includes a seat 20, a valve 30, a seal ring 40, a shaft 50, a notch pin 60, and the like.
  • the sheet 20 forms a flow path of fluid (exhaust gas in the first embodiment).
  • the seat 20 is formed in a substantially cylindrical shape with its axial direction directed in the front-rear direction.
  • the seat 20 according to the first embodiment is provided in a passage that connects the intake passage and the exhaust passage of the engine.
  • the sheet 20 includes a flow path 21 and a support hole 22.
  • the flow path 21 is a passage through which fluid flows.
  • the channel 21 is formed in a substantially circular shape when viewed from the front, and penetrates the sheet 20 in the axial direction (front-rear direction).
  • the support hole 22 is a hole that supports a notch pin 60 described later.
  • the support hole 22 penetrates the sheet 20 in the radial direction from the outer peripheral surface to the inner peripheral surface.
  • the support hole 22 is formed at the right end portion of the sheet 20.
  • the valve 30 is a substantially disk-shaped member for opening and closing the flow path 21.
  • the valve 30 is formed so that its outer diameter is smaller than the inner diameter of the seat 20.
  • the valve 30 is rotatably supported by the seat 20 via a shaft 50 described later. As a result, the valve 30 is disposed in the flow path 21 with a gap between the seat 20 and the inner peripheral surface (wall surface of the flow path 21).
  • the valve 30 includes a seal ring groove 31.
  • the seal ring groove 31 is a groove formed on the outer peripheral surface of the valve 30.
  • the seal ring groove 31 is formed so as to extend in the circumferential direction of the valve 30, and is formed over the entire circumference of the valve 30.
  • the seal ring groove 31 is formed at the center in the thickness direction of the valve 30 and has side walls on the front and rear sides.
  • the valve 30 configured in this manner opens the flow path 21 when the state shown in FIG. 1, that is, when the plate surface faces a direction different from the axial direction of the seat 20. Further, the valve 30 completely opens the flow path 21 when the plate surface faces a direction (left-right direction) orthogonal to the axial direction of the seat 20. Further, the valve 30 completely closes the flow path 21 when the plate surface faces the axial direction of the seat 20 (see FIG. 6).
  • a position where the valve 30 completely closes the flow path 21 is referred to as a “fully closed position”.
  • the seal ring 40 shown in FIGS. 1 and 2 is for sealing the gap between the seat 20 and the valve 30.
  • the seal ring 40 is formed in a substantially C shape when viewed from the front, with its right end cut out.
  • the seal ring 40 is made of an elastic material.
  • the seal ring 40 is formed so that its outer diameter is larger than the outer diameter of the valve 30 and slightly smaller than the inner diameter of the seat 20.
  • the seal ring 40 includes a joint 41.
  • the joint 41 is a cut portion (gap along the circumferential direction of the seal ring 40) formed at the right end of the seal ring 40.
  • the seal ring 40 is fitted in the seal ring groove 31. Thereby, the outer peripheral surface of the seal ring 40 protrudes radially outward from the outer peripheral surface of the valve 30.
  • the seal ring 40 is supported by the side wall of the seal ring groove 31 so as to rotate integrally with the valve 30 and to restrict relative movement of the valve 30 in the thickness direction.
  • the tension in the direction of diameter reduction acts on the seal ring 40. That is, the seal ring 40 is constantly shrinking, and the inner peripheral surface thereof contacts the bottom surface of the seal ring groove 31 to press the valve 30 radially inward. According to this, the relative rotation of the seal ring 40 with respect to the valve 30 can be suppressed.
  • the shaft 50 is a substantially cylindrical member for supporting the valve 30 so as to be rotatable.
  • the shaft 50 is fixed to the rear surface of the valve 30 with the axial direction thereof being directed in the vertical direction.
  • the upper end of the shaft 50 protrudes from the seat 20 and is connected to a drive source such as a motor (not shown).
  • the shaft 50 receives power from the drive source and rotates relative to the seat 20. As a result, the shaft 50 rotates the valve 30 around the axis L1.
  • the notch pin 60 is a substantially cylindrical member for expanding the diameter of the seal ring 40.
  • the notch pin 60 is formed so that its outer diameter is larger than the distance along the vertical direction of the joint 41 of the seal ring 40.
  • the notch pin 60 is fixed to the sheet 20 by being press-fitted into the support hole 22 of the sheet 20. As a result, the notch pin 60 is arranged with the position in the circumferential direction of the seat 20 aligned with the joint 41 of the seal ring 40.
  • the left end of the notch pin 60 protrudes leftward from the inner peripheral surface of the sheet 20 (side wall of the flow path 21).
  • the protruding portion of the notch pin 60 protrudes from the seat 20 by a width corresponding to the distance along the radial direction from the outer peripheral surface of the valve 30 rotated to the fully closed position to the inner peripheral surface of the seat 20 (see FIG. 6). ).
  • the notch pin 60 is configured so as not to collide with the valve 30 even when the valve 30 is rotated to the fully closed position.
  • valve device 10 Next, the closing operation of the valve device 10 will be described with reference to FIGS.
  • the arrow shown in white in FIG. 3 and FIG. Further, the arrows shown in black in FIG. 5 indicate that the seal ring 40 is elastically deformed.
  • valve device 10 shown in FIGS. 1 and 2 transmits the power from the drive source to the shaft 50 to rotate the valve 30 and the seal ring 40 in the direction of the arrow shown in FIG. Thereby, the valve 30 is rotated so that the plate surface of the valve 30 faces the axial direction of the seat 20 (so that the opening degree becomes small). At this time, as shown in FIGS. 1 and 3, the joint 41 of the seal ring 40 approaches the notch pin 60.
  • the seal ring 40 rotates with a gap between the seal ring 40 and the inner peripheral surface of the sheet 20 (wall surface of the flow path 21). That is, the seal ring 40 does not slide with respect to the seat 20 even if it rotates from the state shown in FIG.
  • the joint 41 of the seal ring 40 tries to pass through the notch pin 60.
  • the outer diameter of the notch pin 60 is larger than the distance along the vertical direction of the joint 41. For this reason, the notch pin 60 comes into contact with the upper and lower end portions (both end portions in the circumferential direction of the seal ring 40) of the joint portion 41 so as to enter the joint portion 41.
  • the notch pin 60 enters the joint 41 until the axial center thereof is arranged at the front and rear central portions of the joint 41 of the seal ring 40. At this time, the top portion (upper end portion) and the bottom portion (lower end portion) of the notch pin 60 come into contact with both end surfaces of the seal ring 40.
  • the diameter of the seal ring 40 is increased by a length corresponding to the outer diameter of the notch pin 60, and the entire outer peripheral surface thereof is in close contact with the inner peripheral surface of the sheet 20 (the wall surface of the flow path 21).
  • the valve device 10 rotates the valve 30 in the direction opposite to the case where the flow path 21 is closed (the direction opposite to the arrow direction shown in FIG. 1). Accordingly, the joint 41 of the seal ring 40 moves rearward and is separated from the notch pin 60. At this time, the notch pin 60 comes out of the joint 41 immediately after the rotation of the valve 30 starts (when the valve 30 slightly rotates from the fully closed position). As a result, the seal ring 40 is reduced in diameter and does not adhere to the inner peripheral surface of the sheet 20. Thereafter, even if the valve 30 rotates until the flow path 21 is completely opened, the seal ring 40 does not slide with respect to the inner peripheral surface of the seat 20.
  • the valve device 10 when the valve 30 is in the rotational position that is very close to the fully closed position, the valve device 10 is slightly moved from just before the fully closed position to the fully closed position and slightly from the fully closed position.
  • the seal ring 40 is expanded in diameter by the notch pin 60 and is brought into close contact with the inner peripheral surface of the sheet 20 only until it is rotated. According to this, the seal ring 40 can be prevented from sliding with respect to the seat 20 unless the flow path 21 is completely closed or the completely closed flow path 21 is opened. For this reason, abrasion of the seat 20 and the seal ring 40 can be suppressed, and leakage of exhaust gas due to wear of the seat 20 and the seal ring 40 can be suppressed.
  • the valve device 10 includes the seat 20 through which the flow path 21 is formed and the flow path 21 so as to be rotatable, and the flow path 21 is configured to rotate.
  • a notch pin 60 (diameter expanding means) that seals the gap between the seat 20 and the seal ring 40.
  • the seal ring 40 includes a joint 41 which is a cut portion, and the notch pin 60 expands the diameter of the seal ring 40 by pushing and widening the joint 41.
  • the seal ring 40 is compared with the case where the diameter of the seal ring 40 is increased by pushing the inner peripheral surface of the seal ring 40 radially outward from the seal ring groove 31 as described later.
  • the diameter can be easily expanded.
  • the diameter of the seal ring 40 can be increased uniformly, the entire outer peripheral surface of the seal ring 40 can be easily adhered to the inner peripheral surface of the sheet 20. Thereby, sealing performance can be improved.
  • the notch pin 60 pushes the joint 41 by entering the joint 41 when rotated to the fully closed position.
  • Such a configuration makes it possible to easily expand the diameter of the seal ring 40 as compared with a case where compressed air or the like is sprayed onto the abutment 41 as described later to expand the diameter.
  • the notch pin 60 is fixed to the sheet 20.
  • the joint 41 is arranged at a position away from the rotation axis of the valve 30 (the axis L1 of the shaft 50). Note that the joint 41 according to the first embodiment is disposed at the right end of the valve 30, that is, the position farthest from the rotation axis of the valve 30.
  • the moving distance of the joint 41 with respect to the rotation angle of the valve 30 can be increased.
  • the notch pin 60 can be inserted into and withdrawn from the abutment 41 by slightly rotating the valve 30. Therefore, the diameter of the seal ring 40 is increased only when the valve 30 is in a rotational position very close to the fully closed position. It becomes possible to make it. According to this, the diameter of the seal ring 40 can be increased only when necessary, and the seal ring 40 can be prevented from sliding with respect to the seat 20 as much as possible. Therefore, wear of the seat 20 and the seal ring 40 can be effectively suppressed.
  • the notch pin 60 is constituted by a member different from the sheet 20.
  • the sheet 20 and the notch pin 60 can be formed by simple processing as compared with the case where the notch pin 60 is integrally formed on the sheet 20, and thus the notch pin 60 is simply provided on the sheet 20. be able to. Moreover, the notch pin 60 can be easily provided (retrofitted) on the existing valve device.
  • seal ring 40 is subjected to tension in the direction of diameter reduction.
  • notch pin 60 which concerns on 1st embodiment is one Embodiment of the diameter expansion means which concerns on this invention.
  • valve device 110 according to the second embodiment of the present invention.
  • members that are configured in the same manner as the valve device 10 according to the first embodiment are denoted by the same reference numerals as those in the first embodiment, and description thereof is omitted.
  • the valve device 110 includes a seat 20, a valve 130, a seal ring 140, a shaft 50, a non-rotating pin 160, a notch pin 170, and the like.
  • the valve 130 includes a seal ring groove 31 and a recess 132.
  • the recess 132 is a recess for supporting a rotation stopper pin 160 described later.
  • the recess 132 is formed at the right end of the valve 130.
  • the recess 132 is formed in a substantially circular shape when viewed from the side, and is formed so as to extend from the bottom surface of the seal ring groove 31 to the inside (left side) in the radial direction of the valve 130.
  • the abutment 141 is formed such that the distance along the circumferential direction is longer than the recess 132 of the valve 130.
  • the abutment 141 is arranged with the position in the circumferential direction aligned with the recess 132.
  • the rotation prevention pin 160 is a substantially columnar member for restricting relative rotation (relative movement in the circumferential direction) of the seal ring 140 with respect to the valve 130.
  • the anti-rotation pin 160 is formed so that the outer diameter thereof is substantially the same as the inner diameter of the recess 132 of the valve 130.
  • the anti-rotation pin 160 is formed such that its length (axial width) is longer than the depth of the recess 132.
  • the rotation prevention pin 160 is fixed to the right end portion of the valve 130 by being press-fitted into the recess 132 of the valve 130. Accordingly, the rotation prevention pin 160 is configured to be rotatable integrally with the valve 130, and a right portion thereof protrudes rightward from the bottom surface of the seal ring groove 31.
  • the protruding portion of the locking pin 160 is disposed inside the abutment 141 and protrudes from the outer peripheral surface of the valve 130 by the same length as the outer peripheral surface of the seal ring 140.
  • the notch pin 170 is formed so that its outer diameter is larger than the outer diameter of the non-rotating pin 160 and the distance along the vertical direction of the joint 141 of the seal ring 140.
  • the notch pin 170 is arranged with its axial direction facing the left-right direction.
  • the notch pin 170 includes a housing portion 171.
  • the accommodating portion 171 is for accommodating the detent pin 160 when the valve 130 is rotated.
  • the accommodating portion 171 is formed in a substantially U shape in side view as if the left rear end portion of the notch pin 170 is cut out. More specifically, the accommodating portion 171 is formed so as to extend in the forward direction from the rear end portion of the notch pin 170 to the front and rear central portion, and the extended end surface (a surface facing rearward, hereinafter referred to as “end surface 171a”). Is formed in a substantially circular arc shape when viewed from the side along the outer peripheral surface of the detent pin 160.
  • the accommodating part 171 is formed so that the vertical width thereof is narrower than the distance along the vertical direction of the joint 141 and wider than the vertical width (outer diameter) of the locking pin 160 (FIG. 11A). )reference).
  • the lateral width of the accommodating portion 171 is larger than the length of the portion of the locking pin 160 that protrudes from the outer peripheral surface of the valve 130 (the solid line portion of the locking pin 160 shown in FIG. 11B). It is formed.
  • the accommodating portion 171 is disposed so that the position in the circumferential direction of the seat 20 is aligned with the rotation prevention pin 160.
  • FIGS. 7, 8 and 10 to 13 the closing operation of the valve device 110 will be described with reference to FIGS. 7, 8 and 10 to 13.
  • the arrow shown in white in FIG.10 and FIG.11 (a) has shown the rotation direction of the valve
  • FIG. Also, the arrows shown in black in FIG. 12 indicate how the seal ring 140 is elastically deformed.
  • valve device 110 shown in FIGS. 7 and 8 transmits the power from the driving source to the shaft 50, thereby rotating the valve 130, the seal ring 140, and the rotation prevention pin 160 in the direction of the arrow shown in FIG. .
  • the abutment 141 and the rotation prevention pin 160 of the seal ring 140 approach the notch pin 170.
  • the detent pin 160 moves in the forward direction and enters the accommodating portion 171. Then, when the valve 130 rotates to the fully closed position shown in FIGS. 12 and 13, the rotation prevention pin 160 moves the housing portion 171 in the forward direction and contacts the end surface 171 a of the housing portion 171.
  • valve device 110 rotates the valve 130 in the direction opposite to the case where the flow path 21 is closed (the direction opposite to the arrow direction shown in FIG. 7).
  • the detent pin 160 moves out of the accommodating portion 171 by moving the accommodating portion 171 of the notch pin 170 rearward.
  • the rotation stop pin 160 is disposed inside the joint 141 so that when the seal ring 140 rotates relative to the valve 130, The upper end portion or the lower end portion can be brought into contact with the rotation prevention pin 160. According to this, since the relative rotation of the seal ring 140 with respect to the valve 130 can be kept at a constant amount, the notch pin 170 can be surely inserted inside the joint 141. Thereby, the diameter of the seal ring 140 can be expanded reliably. According to the above, it is possible to prevent the operation of expanding the diameter of the seal ring 140 from failing, and to suppress wear of the seat 20 and the seal ring 140 without causing an operation failure (seal failure).
  • the non-rotating pin 160 when the non-rotating pin 160 is disposed inside the joint 141, when the notch pin 170 enters the inside of the joint 141 (before the valve 130 is rotated to the fully closed position), the non-rotating pin 160 is notched. There is a risk that the robot 170 may come into contact (collision) with force from the rear. In this case, the rotation of the valve 130 may be stopped in the middle, or the locking pin 160 and the notch pin 170 may be damaged.
  • the notch pin 170 includes a housing portion 171. Accordingly, when the notch pin 170 enters the inside of the joint 141, the rotation prevention pin 160 can be inserted into the housing portion 171. According to this, the collision between the notch pin 170 and the rotation stopper pin 160 can be avoided. Thereby, the rotation of the valve 130 does not stop in the middle, and the notch pin 170 can enter the inside of the joint 141 and the diameter of the seal ring 140 can be reliably expanded. According to the above, it is possible to prevent the operation of expanding the diameter of the seal ring 140 from failing, and to suppress wear of the seat 20 and the seal ring 140 without causing a malfunction. Further, it is possible to make it difficult to damage the rotation prevention pin 160 and the notch pin 170.
  • the accommodating part 171 of the notch pin 170 which concerns on 2nd embodiment is formed ranging from the rear-end part of the notch pin 170 to the front-back center part.
  • the notch pin 170 can be sufficiently inserted inside the joint 141 (to the extent that the axial center of the notch pin 170 is disposed at the front and rear center portion of the joint 141).
  • the diameter of the seal ring 140 can be greatly expanded, and the outer peripheral surface of the seal ring 140 can be pressed against the inner peripheral surface of the seat 20 with a strong force. For this reason, sealing performance can be improved.
  • the valve device 110 further includes the rotation prevention pin 160 (regulating means) that is disposed inside the joint 141 and that regulates relative rotation of the seal ring 140 with respect to the valve 130.
  • the notch pin 170 (diameter expanding means) enters the inside of the joint 141 and pushes the joint 141.
  • the notch pin 160 has a receiving portion 171 into which the rotation prevention pin 160 enters. It has.
  • notch pin 170 is fixed to the sheet 20.
  • the seal ring 1 can be used without using a drive source or the like for moving a notch pin (notch pin 770 according to the fifth modification shown in FIG. 26) as will be described later. Since the diameter of 40 can be increased, the configuration for expanding the diameter of the seal ring 140 can be simplified.
  • the housing 171 is open on the rear side (the side entering the joint 141 of the notch pin 170) and closed on the front side (the side opposite to the side entering the joint 141).
  • end surface 171a of the housing portion 171 (the end surface on the side opposite to the side entering the abutment 141) is formed in a shape along the shape of the detent pin 160.
  • the end surface 171a of the accommodating portion 171 can be brought into contact with the anti-rotation pin 160 by a surface.
  • the rotation prevention pin 160 vigorously contacts (collises) with the end surface 171a of the accommodating portion 171 when the valve 130 is rotated due to an assembly error or the like, the rotation prevention pin 160 and the notch pin 170 are hardly damaged. Can do.
  • the accommodating portion 171 is formed to extend in the rearward direction (the direction in which the notch pin 170 enters the joint 141).
  • the rotation prevention pin 160 can be made difficult to collide with the accommodating portion 171 of the notch pin 170, so that the rotation prevention pin 160 and the notch pin 170 are hardly damaged. be able to. Further, the rotation prevention pin 160 can be deeply inserted into the housing portion 171. As a result, the notch pin 170 can sufficiently enter the inside of the joint 141. According to this, the diameter of the seal ring 140 can be further increased, and the sealing performance can be improved by pressing the outer peripheral surface of the seal ring 140 against the inner peripheral surface of the seat 20 with a strong force.
  • the detent pin 160 is constituted by a member different from the valve 130.
  • valve 130 and the rotation prevention pin 160 can be formed by simple processing as compared with the case where the rotation prevention pin 160 is formed integrally with the valve 130.
  • the valve 130 can be easily provided.
  • the anti-rotation pin 160 can be easily provided (retrofitted) on the existing valve device.
  • the rotation prevention pin 160 which concerns on 2nd embodiment is one Embodiment of the control means which concerns on this invention.
  • the notch pin 170 which concerns on 2nd embodiment is one Embodiment of the diameter expansion means which concerns on this invention.
  • the rear direction in the second embodiment corresponds to the direction in which the diameter expanding means according to the present invention enters the joint.
  • valve device 210 according to the third embodiment of the present invention will be described.
  • members that are configured in the same manner as the valve device 10 according to the first embodiment are denoted by the same reference numerals as those in the first embodiment, and description thereof is omitted.
  • the valve device 210 includes a seat 20, a valve 230, a seal ring 240, a shaft 50, a notch pin 260, and the like.
  • the valve 230 includes a seal ring groove 231.
  • the seal ring groove 231 includes a narrow groove 231a and a thick groove 231b.
  • the narrow groove 231a is a portion excluding the right end portion of the seal ring groove 231. That is, the narrow groove 231a is formed in a substantially C shape when viewed from the front.
  • the narrow groove 231a is formed so that its width (width in the thickness direction of the bulb 230) is narrower than the thickness of the bulb 230, and is formed in the center in the thickness direction of the bulb 230.
  • the narrow groove 231a has side walls on the front and rear sides.
  • the thick groove 231b is the right end of the seal ring groove 231.
  • the thick groove 231b communicates with the narrow groove 231a and is formed to have a width wider than that of the narrow groove 231a.
  • the thick groove 231b is formed so that the width thereof is the same as the thickness of the bulb 230. That is, the thick groove 231b does not have side walls on the front and rear sides.
  • the seal ring 240 shown in FIGS. 14 to 16 includes a circumferential portion 241, a projecting portion 242, a guide portion 243, and a joint 244.
  • the circumferential portion 241 is formed in a substantially C shape in front view as if the right end portion was cut away.
  • the circumferential portion 241 is formed so that its outer diameter is larger than the outer diameter of the valve 230 and slightly smaller than the inner diameter of the seat 20.
  • the protruding portion 242 is a portion protruding backward from the circumferential portion 241.
  • the protrusions 242 are formed at both ends of the circumferential portion 241 (the right end of the seal ring 240).
  • the protrusions 242 are arranged at intervals in the vertical direction.
  • the guide portion 243 includes a connecting portion between one end portion (upper end portion) of the circumferential portion 241 and the upper protruding portion 242 and a lower end portion protruding from the other end portion (lower end portion) of the circumferential portion 241. It is a curved surface formed in each connection part with the part 242.
  • the upper guide portion 243 is formed in a substantially arc shape in a side view so as to extend upward as it goes in the front direction.
  • the upper guide portion 243 is formed from the front side surface of the circumferential portion 241 to the lower side surface (surface facing downward) of the upper projection portion 242.
  • the lower guide portion 243 is formed in a substantially arc shape in a side view so as to extend downward as it goes forward.
  • the lower guide portion 243 is formed from the front side surface of the circumferential portion 241 to the upper side surface (surface facing upward) of the lower projection portion 242.
  • the upper and lower guide portions 243 are spaced apart from each other in the vertical direction, and are formed so as to expand in the circumferential direction of the circumferential portion 241 (the seal ring 240) toward the front direction.
  • the joint 244 is formed between the upper protrusion 242 and the lower protrusion 242.
  • the seal ring 240 is fitted in the seal ring groove 231. Specifically, the circumferential portion 241 of the seal ring 240 is fitted into the narrow groove 231 a of the seal ring groove 231. Thereby, the outer peripheral surface of the circumferential portion 241 protrudes radially outward from the outer peripheral surface of the valve 230.
  • the seal ring 240 is rotated integrally with the valve 230 and the relative movement in the thickness direction of the valve 230 is restricted by the circumferential portion 241 being supported by the side wall of the narrow groove 231a.
  • the right end portion of the seal ring 240 (both ends of the circumferential portion 241, the protruding portion 242, the guide portion 243, and the joint 244) is disposed in the thick groove 231 b.
  • the protrusion part 242 is arrange
  • the seal ring 240 according to the third embodiment is manufactured by bending a longitudinal member formed so as to extend in a predetermined direction.
  • the longitudinal member is prepared by performing a step of cutting a wire formed of a material having elasticity into a predetermined length.
  • the circumferential part 241 is formed by performing the process of bending the said longitudinal member in a substantially circular shape.
  • the protrusion part 242 and the guide part 243 are formed by performing the process of bending the both ends of the longitudinal member which formed the circumferential part 241 back.
  • the seal ring 240 is manufactured.
  • the guide part 243 can be formed only by bending the longitudinal member. For this reason, the seal ring 240 can be easily manufactured without chamfering.
  • the notch pin 260 is formed so that its outer diameter is larger than the distance along the vertical direction of the joint 244 (between the upper and lower protrusions 242).
  • the notch pin 260 is formed so that the outer diameter thereof is smaller than the distance along the vertical direction of the thick groove 231b of the seal ring groove 231.
  • the notch pin 260 is disposed so that the position in the circumferential direction of the sheet 20 is aligned with the thick groove 231 b of the seal ring groove 231 and the joint 244 of the seal ring 240.
  • the left end of the notch pin 260 protrudes leftward from the inner peripheral surface of the sheet 20 (side wall of the flow path 21).
  • the protruding portion of the notch pin 260 protrudes from the seat 20 by a width corresponding to the radial distance from the bottom surface of the thick groove 231b of the valve 230 rotated to the fully closed position to the inner peripheral surface of the seat 20 ( FIG. 20).
  • the notch pin 260 is configured not to collide with the valve 230 by entering the thick groove 231b when the valve 230 rotates to the fully closed position.
  • FIGS. 14, 15 and 17 to 20 the closing operation of the valve device 210 will be described with reference to FIGS. 14, 15 and 17 to 20.
  • the white arrows in FIG. 17 and FIG. 18A indicate the rotation direction of the valve 230.
  • the arrows shown in black in FIG. 18 indicate the direction of the load acting on the seal ring 240.
  • the arrows shown in black in FIG. 19 indicate that the seal ring 240 is elastically deformed.
  • valve device 210 shown in FIGS. 14 and 15 transmits the power from the drive source to the shaft 50, thereby rotating the valve 230 and the seal ring 240 in the direction of the arrow shown in FIG.
  • the right end of the seal ring 240 (both ends of the circumferential portion 241, the projecting portion 242, the guide portion 243, and the joint 244) approach the notch pin 260.
  • the notch pin 260 enters the thick groove 231 b of the seal ring groove 231.
  • the joint 244 of the seal ring 240 tends to pass through the notch pin 260.
  • the outer diameter of the notch pin 260 is larger than the distance along the vertical direction of the joint 244. For this reason, the notch pin 260 comes into contact with the guide portion 243 in an attempt to enter the joint 244. At this time, the notch pin 260 abuts from the left end portion to the left and right midway portion from the left end portion to the right end portion of the guide portion 243.
  • the notch pin 260 enters the joint 244 until the axial center thereof is disposed at the front and rear central portions of the circumferential portion 241 of the seal ring 240. At this time, the upper and rear lower portions of the notch pin 260 come into contact with the guide portion 243. Accordingly, the diameter of the seal ring 240 (circumferential portion 241) is increased by a length corresponding to the width of the abutment 244 expanded, and the entire outer peripheral surface thereof is the inner peripheral surface of the sheet 20 (the wall surface of the flow path 21). ). Thereby, when the valve 230 closes the flow path 21, the gap between the outer peripheral surface of the valve 230 and the inner peripheral surface of the seat 20 can be sealed with the seal ring 240.
  • the seal ring 240 guides the entry of the notch pin 260 by the guide portion 243, so that the general seal ring 1940 (projection portion 242 and guide portion 243 are formed) shown in FIG.
  • the wear caused by the notch pin 260 entering the joint 244 can be suppressed more than the seal ring that is not provided.
  • FIG. 32 an operation for expanding the diameter of a general seal ring 1940 will be briefly described with reference to FIG. Note that arrows shown in white in FIG. 32 indicate the rotation direction of the valve 230. Also, the arrows shown in black in FIG. 32 indicate the direction of the load acting on the seal ring 1940.
  • the notch pin 260 cannot expand the diameter of the seal ring 1940 unless a large load is applied to the seal ring 1940. For this reason, the seal ring 1940 receives a large load from the notch pin 260 and wears its corners. Depending on how the corners are worn, the notch pin 260 may not easily enter the joint 1944.
  • the guide part 243 having a substantially arc shape in a side view can be brought into contact with the notch pin 260.
  • the upper guide portion 243 can receive a load in the rear upper direction from the notch pin 260.
  • the lower guide portion 243 can receive a load in the rear lower direction from the notch pin 260.
  • the seal ring 240 can receive a load that is expanded from the notch pin 260 (the joint 244 is pushed and expanded).
  • the notch pin 260 can expand the diameter of the seal ring 240 with a small force. For this reason, the seal ring 240 can reduce the load received from the notch pin 260 and effectively suppress wear of the guide portion 243. According to this, since the notch pin 260 can be prevented from being caught by the guide portion 243, the notch pin 260 can be surely inserted into the joint 244. Therefore, it is possible to suppress wear of the seat 20 and the seal ring 240 (circumferential portion 241) without causing malfunction (seal failure). Further, wear of the notch pin 260 can be suppressed.
  • the seal ring 240 according to the third embodiment can bring the guide portion 243 having a substantially arc shape (curved surface) in a side view into contact with the notch pin 260. For this reason, the seal ring 240 according to the third embodiment can reduce wear due to contact with the notch pin 260 more than a general seal ring 1940.
  • the notch pin 260 enters the thick groove 231b of the seal ring groove 231 when the valve 230 rotates to the fully closed position. According to this, the notch pin 260 can contact from the left end portion of the guide portion 243 to the right end portion. Thereby, since the contact range of the notch pin 260 and the seal ring 240 can be widened, the notch pin 260 can be easily inserted into the joint 244 of the seal ring 240.
  • the seal ring 240 includes the abutment 244 formed by abutting both end portions, and the notch pin 260 (diameter expanding means) enters the abutment 244. Then, the diameter of the seal ring 240 is increased by pushing the joint 244 wide, and the seal ring 240 further includes a guide portion 243 for guiding the notch pin 260 to enter the joint 244.
  • the guide portion 243 is formed so as to gradually spread in the circumferential direction of the seal ring 240 toward the front side (receiving side of the notch pin 260).
  • the seal ring 240 can receive a load that is expanded from the notch pin 260. Thereby, abrasion of the seal ring 240 (guide part 243) can be suppressed.
  • the guide part 243 is formed in a curved surface shape.
  • the curved surface not the corner of the seal ring 240, can be brought into contact with the notch pin 260. Further, the notch pin 260 can be smoothly slid with respect to the guide portion 243. For this reason, abrasion of the seal ring 240 (guide part 243) can be suppressed.
  • the seal ring 240 includes a circumferential portion 241 extending along a circumferential direction, and a projecting portion 242 projecting rearward from the end portion of the circumferential portion 241 (a direction in which the notch pin 260 enters the joint 244).
  • the guide portion 243 is formed at a connection portion between the circumferential portion 241 and the protruding portion 242.
  • the seal ring 240 includes a projecting portion 242, so that guide portions 943 according to the seventh and eighth modifications shown in FIG.
  • the width in the front-rear direction of the guide portion 243 can be made wider than (see 1043).
  • diffusion condition to the circumferential direction of the guide part 243 can be made loose.
  • the notch pin 260 can be slid more smoothly with respect to the guide part 243, wear of the guide part 243 can be effectively reduced.
  • valve 230 has a narrow groove 231a for fitting the circumferential portion 241 and a width wider than the narrow groove 231a while communicating with the narrow groove 231a, and the protruding portion 242 is disposed. And a thick groove 231b.
  • the notch pin 260 which concerns on 3rd embodiment is one Embodiment of the diameter expansion means which concerns on this invention.
  • the rear direction in the third embodiment corresponds to the direction in which the diameter expanding means according to the present invention enters the joint.
  • valve devices 10, 110, and 210 are provided in the EGR device, but the application target of the valve devices 10, 110, and 210 is not limited thereto.
  • the fluid flowing through the flow path 21 is not limited to the exhaust gas, and may be, for example, compressed air.
  • circulates the flow path 21 is not limited to gas, For example, liquids, such as water, may be sufficient.
  • the diameter of the seal ring 40 is increased by expanding the joint 41, but it is not always necessary to expand the diameter of the seal ring 40 by expanding the joint 41.
  • the diameter of the seal ring 40 may be increased by pushing the inner peripheral surface of the seal ring 40 radially outward from the seal ring groove 31 with a shaft member capable of expanding the diameter, compressed air, or the like.
  • the notch pin 60 does not necessarily enter the abutment 41.
  • the abutment 41 may be expanded by spraying compressed air or the like onto the abutment 41.
  • the notch pin 60 according to the first embodiment is fixed to the sheet 20, but is not limited thereto, and may be supported by the sheet 20 so as to be relatively movable.
  • the notch pin 60 can be configured like the notch pin 360 of the valve device 310 according to the first modification shown in FIG.
  • the notch pin 360 according to the first modification is supported by the support hole 22 of the seat 20 so as to be movable in the left-right direction by a drive source. As shown in FIG. 21, the notch pin 360 is moved to the left after the valve 30 is rotated to the fully closed position, enters the joint 41, and widens the seal ring 40 by expanding the joint 41. Further, the notch pin 360 moves rightward and exits from the joint 41 when opening the flow path 21. Thereafter, the valve 30 is rotated. By comprising in this way, since it can prevent that the sheet
  • the valve device 310 according to the first modification may move the notch pin 360 in the left-right direction by a mechanism that is interlocked with the rotation of the valve 30.
  • the shaft centers of the notch pins 60 and 160 are arranged at the front and rear center portions of the joints 41 and 141.
  • the notch pins 60 and 160 are not limited thereto. is not.
  • the notch pins 60 and 160 are arranged such that, for example, when the valves 30 and 130 are rotated to the fully closed position, the axial centers thereof are arranged in front of the joints 41 and 141 (in front of the front and rear central portions). Also good. In such a case, the notch pins 60 and 160 may be in contact with the corner portions (the front upper end portion and the front lower end portion of the joints 41 and 141) instead of the both end faces of the seal rings 40 and 140.
  • notch pins 60, 160, and 260 are configured by members different from the sheet 20, the present invention is not limited thereto, and may be formed integrally with the sheet 20.
  • the member to which the notch pins 60, 160, and 260 are fixed is not limited to the sheet 20, and may be fixed to other members.
  • seal rings 40, 140, and 240 are assumed to be subjected to the radially inward tension, the seal rings 40, 140, and 240 are not limited thereto, and may be, for example, those that do not receive the tension.
  • the seal ring 40 according to the first embodiment does not matter whether or not the joint 41 is present.
  • the seal ring 40 may not be provided with the joint 41, that is, may be constituted by an elastic member such as an annular rubber.
  • the outer diameters of the seal rings 40, 140, and 240 are formed so as to be smaller than the inner diameter of the sheet 20.
  • the outer diameter is not limited to this, and is approximately the same as the inner diameter of the sheet 20. It may be formed as follows. In this case, since the seal rings 40, 140, and 240 come into contact with the sheet 20 with a weaker force than that at the time of diameter expansion before the diameter is expanded by the notch pins 60, 160, and 260, sliding with the sheet 20 occurs. Wear due to can be suppressed.
  • the joints 41, 141, and 244 are arranged at the right end of the valves 30, 130, and 230. However, the positions of the joints 41, 141, and 244 with respect to the valves 30, 130, and 230 are limited to this. It is not a thing.
  • the joints 41, 141, and 244 may be arranged at the left end of the valves 30, 130, and 230, for example. Even in such a case, the joints 41, 141, and 244 can be arranged at positions farthest from the rotation axis of the valves 30, 130, and 230.
  • the joints 41, 141, and 244 are not necessarily arranged at positions farthest from the rotation axis of the valves 30, 130, and 230.
  • the joints 41, 141, and 244 are arranged at positions separated from the rotation axis of the valves 30, 130, and 230 so that the notch pins 60, 160, and 260 are moved in and out during the rotation of the valves 30, 130, and 230. It only has to be.
  • the joints 41, 141, and 244 may be disposed, for example, in the lower left part, upper left part, lower right part, and upper right part of the valves 30, 130, and 230.
  • the positions at which the joints 41, 141, and 244 are arranged are included in “positions away from the rotation axis of the valve”.
  • valves 30, 130, and 230 close the flow path 21 by rotating in the arrow directions shown in FIGS. 1, 7, and 14, but the rotation direction of the valves 30, 130, and 230 is
  • the present invention is not limited to this.
  • the valves 30, 130, and 230 may close the flow path 21 by rotating in a direction opposite to the arrow direction shown in FIGS. 1, 7, and 14.
  • valve 30 is not limited to the first embodiment, and for example, a configuration like the valve 430 of the valve device 410 according to the second modification shown in FIGS. 22 and 23 may be employed. It is.
  • the valve 430 according to the second modification includes a seal ring groove 431 and a groove portion 432.
  • the seal ring groove 431 is formed over the entire outer peripheral surface of the valve 430 except for the right end portion of the valve 430.
  • Groove 432 is formed at the right end of valve 430 and communicates with seal ring groove 431.
  • the groove 432 is formed from the front side surface to the rear side surface of the valve 430.
  • An abutment 41 of the seal ring 40 is disposed inside the groove portion 432.
  • the notch pin 460 according to the second modification is formed such that its length (width in the axial direction) is longer by the depth of the groove portion 432 than the notch pin 60 according to the first embodiment. Is done.
  • the notch pin 460 can be inserted into the groove 432 of the valve 430 when the valve 430 is rotated, and the notch pin 460 can be abutted from the left end to the right end of the joint 41. It becomes. According to this, the contact range of the notch pin 460 and the seal ring 40 can be widened, and the notch pin 460 can be easily inserted into the joint 41 of the seal ring 40.
  • the shape of the rotation prevention pin 160 which concerns on 2nd embodiment shall be a substantially cylindrical shape, it is not limited to this, For example, a substantially rectangular parallelepiped shape, a substantially cylindrical shape, etc. may be sufficient. .
  • the detent pin 160 is configured by a member different from the valve 130, but is not limited thereto, and is formed integrally with the valve 130. May be.
  • the detent pin 160 according to the second embodiment may not be in contact with the end surface 171a of the notch pin 170. Thereby, the rotation prevention pin 160 and the notch pin 170 can be made more difficult to break.
  • the accommodating part 171 which concerns on 2nd embodiment shall be formed ranging from the rear-end part of the notch pin 170 to the front-back center part, it is not limited to this, For example, the 1st shown in FIG. It is also possible to make it the shape like the accommodating part 571 of the notch pin 570 which concerns on a 3rd modification.
  • the accommodating portion 571 according to the third modification is formed from the rear end portion of the notch pin 570 to the front end portion. That is, the accommodating portion 571 is formed so as to penetrate the notch pin 570 in the front-rear direction. According to this, since the accommodating part 571 can let the rotation prevention pin 160 pass in the front-back direction, it can prevent that the rotation prevention pin 160 contacts vigorously from back direction. For this reason, the rotation prevention pin 160 and the notch pin 570 can be made difficult to be damaged.
  • the single notch pin 170 having the accommodating portion 171 is provided.
  • the valve device 110 may include, for example, two notch pins 670 according to the fourth modification shown in FIG.
  • the notch pins 670 according to the fourth modification are arranged with a gap therebetween in the vertical direction.
  • the upper notch pin 670 is formed in a substantially semicircular shape when viewed from the side.
  • the lower notch pin 670 is formed in a substantially semicircular shape as viewed from the side that is convex downward.
  • a receiving portion 671 through which the detent pin 160 can pass in the front-rear direction is formed. Even in such a configuration, the anti-rotation pin 160 can be inserted into the housing portion 671, so that the collision between the anti-rotation pin 160 and the upper and lower notch pins 670 can be avoided.
  • the shape of the end surface 171a of the accommodating part 171 which concerns on 2nd embodiment shall be substantially circular arc shape by the side view, it is not limited to this, For example, it forms linearly by side view. It may be a thing.
  • the notch pin 170 according to the second embodiment is fixed to the sheet 20, but is not limited thereto, and may be supported by the sheet 20 so as to be relatively movable.
  • the notch pin 170 can be configured as a notch pin 770 of the valve device 710 according to the fifth modification shown in FIG. 26, for example.
  • the notch pin 770 according to the fifth modification is supported by the support hole 22 of the seat 20 so as to be movable in the left-right direction by a drive source.
  • the notch pin 770 includes a housing portion 771.
  • the accommodating portion 771 is formed to open on the left side surface of the notch pin 770 and extend in the right direction.
  • the accommodating portion 771 is formed in a substantially circular shape in a side view when the inner diameter is larger than the outer diameter of the rotation prevention pin 160.
  • the notch pin 770 moves to the left after the valve 130 has been rotated to the fully closed position, enters the inside of the joint 141, and pushes and widens the joint 141 to expand the diameter of the seal ring 140. At this time, the rotation prevention pin 160 enters the accommodating portion 771. Further, the notch pin 770 moves rightward and exits from the abutment 141 when opening the flow path 21. At this time, the rotation prevention pin 160 goes out of the housing portion 771. Thereafter, the valve 130 is rotated. With this configuration, it is possible to prevent the seat 20 and the seal ring 140 from sliding, and thus wear of the seat 20 and the seal ring 140 can be effectively suppressed.
  • the valve device 710 according to the fifth modification may move the notch pin 770 in the left-right direction by a mechanism that is interlocked with the rotation of the valve 130.
  • valve 130 is not limited to the second embodiment, and for example, a configuration like the valve 830 of the valve device 810 according to the sixth modification shown in FIGS. 27 and 28 may be employed. It is.
  • the valve 830 according to the sixth modification includes a seal ring groove 831, a groove part 832, and a recessed part 833.
  • the seal ring groove 831 is formed over the entire outer peripheral surface of the valve 830 except for the right end portion of the valve 830.
  • the groove 832 is formed at the right end of the valve 830 and communicates with the seal ring groove 831.
  • the groove 832 is formed from the front side surface to the rear side surface of the valve 830.
  • An abutment 141 of the seal ring 140 is disposed inside the groove portion 832.
  • the recess 833 is formed on the bottom surface of the groove 832. As shown in FIG.
  • the notch pin 870 according to the sixth modification is formed such that its length (width in the axial direction) is longer than the depth of the groove 832 than the notch pin 170 according to the second embodiment. Is done. Further, the accommodating portion 871 of the notch pin 870 is formed so that the width in the left-right direction is increased by the depth of the groove portion 832. With this configuration, the notch pin 870 can be inserted into the groove portion 832 of the valve 830 when the valve 830 is rotated, and the notch pin 870 can be brought into contact from the left end portion to the right end portion of the joint 141. It becomes. According to this, the contact range of the notch pin 870 and the seal ring 140 can be widened, and the notch pin 870 can easily enter the inside of the joint 141 of the seal ring 140.
  • the seal ring 240 is manufactured by bending the longitudinal member into a substantially circular shape and then bending both ends of the longitudinal member in the backward direction.
  • the seal ring 240 is manufactured.
  • the method to do is not limited to this.
  • the seal ring 240 may be manufactured by bending both ends of the longitudinal member in the backward direction and then bending the longitudinal member into a substantially circular shape.
  • the guide part 243 which concerns on 3rd embodiment shall be formed by bending the both ends of a longitudinal member, it is not limited to this, It can form by various processes.
  • the guide portion 243 may be formed by cutting out both end portions of the longitudinal member.
  • the guide part 243 may be formed by grind
  • the guide part 243 which concerns on 3rd embodiment shall be a curved surface of the substantially arc shape in side view, it is not limited to this, It spreads in the circumferential direction of the seal ring 240 toward the front direction. It may be a straight surface in a side view.
  • the seal ring 240 does not ask
  • the seal ring 240 may be configured as, for example, a seal ring 940 according to the seventh modification shown in FIG. 29 and a seal ring 1040 according to the eighth modification.
  • a seal ring 940 according to the seventh modification shown in FIG. 29A includes a circumferential portion 941 and a guide portion 943.
  • the circumferential part 941 is configured similarly to the circumferential part 241 according to the third embodiment.
  • the guide portion 943 is formed by notching the front end portion and the rear end portion on both end surfaces of the circumferential portion 941.
  • a seal ring 1040 according to an eighth modification shown in FIG. 29B includes a circumferential portion 1041 and a guide portion 1043.
  • the circumferential part 1041 is configured similarly to the circumferential part 241 according to the third embodiment.
  • the guide portion 1043 is formed by cutting out only the front end portions on both end faces of the circumferential portion 1041. Thereby, the curvature of the guide part 1043 according to the eighth modification can be made smaller than that of the guide part 943 according to the seventh modification. For this reason, since the notch pin 260 can be smoothly slid with respect to the guide part 1043, wear of the seal ring 1040 and the notch pin 260 can be effectively suppressed.
  • the seal rings 940 and 1040 according to the seventh modification and the eighth modification are manufactured by, for example, polishing the both end surfaces of the longitudinal member after performing a process of bending the longitudinal member into a substantially circular shape. According to this, since the total length of the longitudinal member can be shortened by the length of the protruding portion 242, the manufacturing cost can be reduced.
  • the guide portions 943 and 1043 according to the seventh and eighth modifications are formed on the end faces of the seal rings 940 and 1040.
  • the seal ring groove 231 has the presence or absence of the thick groove 231b. It doesn't matter.
  • the seal ring groove 231 may be configured like the seal ring groove 1131 of the valve 1130 according to the ninth modification shown in FIG.
  • the seal ring groove 1131 of the valve 1130 according to the ninth modification is a groove corresponding to the narrow groove 231a according to the third embodiment.
  • the seal ring groove 1131 is formed so as to extend in the circumferential direction of the valve 1130, and is formed over the entire circumference of the valve 1130.
  • the seal ring 940 according to the seventh modification is fitted into the seal ring groove 1131.
  • the seal ring groove 1131 can be formed over the entire circumference of the valve 1130, and the configuration of the valve 1130 can be simplified.
  • the notch pin 260 is fixed to the sheet 20, but is not limited to this, and may be supported by the sheet 20 so as to be relatively movable.
  • the valve 230, the seal ring 240, and the notch pin 260 are configured as, for example, the valve 1230, the seal ring 1240, and the notch pin 1260 of the valve device 1210 according to the tenth modification shown in FIG. It is also possible to do.
  • a valve 1230 according to the tenth modification includes a seal ring groove 1231 and a recess 1232.
  • the seal ring groove 1231 is configured similarly to the seal ring groove 1131 according to the ninth modification.
  • the recess 1232 is a recess formed at the right end of the seal ring groove 1231 and extending leftward from the bottom surface of the seal ring groove 1231.
  • a seal ring 1240 according to the tenth modification includes a circumferential portion 1241, a protruding portion 1242, a guide portion 1243, and a joint 1244.
  • the circumferential part 1241 is configured similarly to the circumferential part 241 according to the third embodiment.
  • the protrusions 1242 protrude from the both ends of the circumferential part 1241 to the left, and are disposed inside the recesses 1232.
  • the guide portion 1243 is formed between one end portion of the circumferential portion 1241 and the upper protruding portion 1242, and at a connection portion between the other end portion of the circumferential portion 1241 and the lower protruding portion 1242, and is substantially omitted in a front view. It is formed in an arc shape.
  • the joint 1244 is formed between the upper protrusion 1242 and the lower protrusion 1242.
  • the notch pin 1260 according to the tenth modification is supported by the support hole 22 of the seat 20 so as to be movable in the left-right direction by a drive source.
  • the notch pin 1260 moves to the left after the valve 1230 has been rotated to the fully closed position, enters the joint 1244, and widens the seal ring 1240 by expanding the joint 1244. At this time, the left end of the notch pin 1260 comes into contact with the guide portion 1243 and is guided by the guide portion 1243 to push the joint 1244 apart. In addition, the notch pin 1260 is moved to the right and exits from the joint 1244 when the channel 21 is opened. Thereafter, the valve 1230 is rotated. With this configuration, the seat 20 and the seal ring 1240 can be prevented from sliding, so that wear of the seat 20 and the seal ring 1240 (circumferential portion 1241) can be effectively suppressed. .
  • the valve device 1210 may move the notch pin 1260 in the left-right direction by a mechanism that is interlocked with the rotation of the valve 1230.
  • the notch pin 260 has its axial center disposed at the front and rear central portions of the circumferential portion 241 when the valve 230 rotates to the fully closed position, and thereafter the upper portion.
  • the abutment 244 is expanded at the lower rear portion, but the present invention is not limited to this.
  • the notch pin 260 may be disposed behind the state shown in FIG. 19 when the valve 230 rotates to the fully closed position. According to this, the joint 244 can be expanded at the top (upper end) and the bottom (lower end) of the notch pin 260. According to this, since the seal ring 240 can be expanded to the maximum extent and the seal ring 240 can be pressed against the seat 20 with a strong force, the sealing performance can be improved.
  • the present invention can be applied to a valve device that controls the flow of fluid by rotating the valve.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Lift Valve (AREA)

Abstract

Provided is a valve device wherein a seat and a seal ring can be prevented from wearing. Provided is a valve device comprising: a seat 20 having a flow passage 21 formed therein so as to extend therethrough; a valve 30 which is disposed in the flow passage 21 so as to be capable of pivoting and which pivots to open and close the flow passage 21; a seal ring 40 fitted to the outer periphery of the valve 30; and a notch pin 60 which, when the valve 30 pivots to a position where the valve 30 closes the flow passage 21, increases the diameter of the seal ring 40 to seal the gap between the seat 20 and the seal ring 40.

Description

バルブ装置Valve device
　本発明は、バルブを回動させて流体の流通を制御するバルブ装置の技術に関する。 The present invention relates to a technology of a valve device that controls a fluid flow by rotating a valve.
　従来、バルブを回動させて流体の流通を制御するバルブ装置の技術は公知となっている。例えば、特許文献１に記載の如くである。 Conventionally, the technology of a valve device that controls the flow of fluid by rotating a valve is known. For example, as described in Patent Document 1.
　特許文献１に記載されるバルブ装置（流体制御弁）は、流路が貫通形成された円筒状のシート（ハウジングのノズル）、流路に配置される円板状のバルブ（バタフライ型バルブ）、当該バルブの外周に嵌め合わされたシールリング、バルブを支持するシャフト及び当該シャフトを介してバルブを回動させるアクチュエータ等を具備する。 A valve device (fluid control valve) described in Patent Document 1 includes a cylindrical sheet (a housing nozzle) in which a flow path is formed, a disk-shaped valve (butterfly valve) disposed in the flow path, A seal ring fitted to the outer periphery of the valve, a shaft for supporting the valve, an actuator for rotating the valve via the shaft, and the like are provided.
　特許文献１に記載されるバルブ装置は、アクチュエータによってバルブの板面がシートの軸線方向を向くようにバルブを回動させることで、流路を閉塞する。このとき、シールリングは、シートとバルブとの隙間をシールする。また、流路を閉塞しているバルブを回動させることで、流路を開放する。 The valve device described in Patent Document 1 closes the flow path by rotating the valve so that the plate surface of the valve faces the axial direction of the seat by an actuator. At this time, the seal ring seals the gap between the seat and the valve. Further, the flow path is opened by rotating the valve closing the flow path.
　しかし、特許文献１に記載されるシート及びシールリングは、バルブの回動時に摺動することによって摩耗し易いという点で不利であった。 However, the seat and the seal ring described in Patent Document 1 are disadvantageous in that they are easily worn by sliding when the valve rotates.
特許第４７９３２９０号公報Japanese Patent No. 4793290
　本発明は、以上の如き状況を鑑みてなされたものであり、その解決しようとする課題は、シート及びシールリングの摩耗を抑制することが可能なバルブ装置を提供するものである。 The present invention has been made in view of the above situation, and a problem to be solved is to provide a valve device capable of suppressing wear of a seat and a seal ring.
　本発明の解決しようとする課題は以上の如くであり、次にこの課題を解決するための手段を説明する。 The problems to be solved by the present invention are as described above. Next, means for solving the problems will be described.
　本発明のバルブ装置は、流路が貫通形成されているシートと、前記流路に回動自在に配置されると共に、回動することで前記流路を開閉するバルブと、前記バルブの外周に嵌め合わされたシールリングと、前記バルブが前記流路を閉塞する位置まで回動したときに、前記シールリングを拡径させて前記シートと前記シールリングとの隙間をシールする拡径手段と、を具備するものである。 The valve device of the present invention includes a seat having a flow passage formed therethrough, a valve that is rotatably disposed in the flow passage, and that opens and closes the flow passage, and an outer periphery of the valve. A fitted seal ring, and a diameter expanding means for expanding the diameter of the seal ring to seal a gap between the seat and the seal ring when the valve is rotated to a position where the valve is closed. It has.
　本発明のバルブ装置においては、前記シールリングは、切れ目部分である合口を具備し、前記拡径手段は、前記合口を押し広げることで前記シールリングを拡径させるものである。 In the valve device of the present invention, the seal ring includes a joint that is a cut portion, and the diameter expanding means expands the diameter of the seal ring by pushing and widening the joint.
　本発明のバルブ装置においては、前記拡径手段は、前記バルブが前記流路を閉塞する位置まで回動したときに前記合口に入り込むことで、前記合口を押し広げるものである。 In the valve device of the present invention, the diameter expanding means pushes the joint together by entering the joint when the valve is rotated to a position where the flow path is closed.
　本発明のバルブ装置においては、前記拡径手段は、前記シートに固定されるものである。 In the valve device of the present invention, the diameter expanding means is fixed to the seat.
　本発明のバルブ装置においては、前記合口は、前記バルブの回動軸線に対して離れた位置に配置されるものである。 In the valve device of the present invention, the abutment is arranged at a position away from the rotation axis of the valve.
　本発明のバルブ装置においては、前記拡径手段は、前記シートとは異なる部材によって構成されるものである。 In the valve device of the present invention, the diameter expanding means is constituted by a member different from the seat.
　本発明のバルブ装置においては、前記シールリングには、縮径方向への張力が作用しているものである。 In the valve device of the present invention, a tension in the direction of diameter reduction acts on the seal ring.
　本発明のバルブ装置においては、前記合口の内側に配置され、前記シールリングの前記バルブに対する相対回転を規制する規制手段をさらに具備し、前記拡径手段は、前記合口の内側に入り込んで前記合口を押し広げるものであり、前記合口に入り込むときに、前記規制手段が内部に入り込む収容部を具備するものである。 In the valve device of the present invention, the valve device further includes a restricting means that is disposed inside the joint and restricts relative rotation of the seal ring with respect to the valve, and the diameter expanding means enters the joint and enters the joint. The regulating means is provided with an accommodating portion that enters the inside when entering the joint.
　本発明のバルブ装置においては、前記拡径手段は、前記シートに固定されるものである。 In the valve device of the present invention, the diameter expanding means is fixed to the seat.
　本発明のバルブ装置においては、前記収容部は、前記拡径手段の前記合口に入り込む側が開口すると共に、前記合口に入り込む側とは反対側が閉塞するものである。 In the valve device of the present invention, the accommodating portion is open on the side of the diameter-expanding means that enters the joint, and is closed on the side opposite to the side that enters the joint.
　本発明のバルブ装置においては、前記収容部の前記合口に入り込む側とは反対側の端面は、前記規制手段の形状に沿った形状に形成されるものである。 In the valve device of the present invention, the end surface of the housing portion opposite to the side entering the joint is formed in a shape that follows the shape of the restricting means.
　本発明のバルブ装置においては、前記収容部は、前記拡径手段が前記合口に入り込む方向に延びるように形成されるものである。 In the valve device of the present invention, the accommodating portion is formed so as to extend in a direction in which the diameter expanding means enters the joint.
　本発明のバルブ装置においては、前記規制手段は、前記バルブとは異なる部材によって構成されるものである。 In the valve device of the present invention, the restricting means is constituted by a member different from the valve.
　本発明のバルブ装置においては、前記シールリングは、両端部を突き合わせて形成されている合口を具備し、前記拡径手段は、前記合口に入り込んで前記合口を押し広げることで前記シールリングを拡径させ、前記シールリングは、前記拡径手段の前記合口への入り込みを案内する案内部をさらに具備するものである。 In the valve device of the present invention, the seal ring includes a joint formed by abutting both end portions, and the diameter expanding means expands the seal ring by entering the joint and expanding the joint. The seal ring further includes a guide portion that guides the diameter expanding means to enter the joint.
　本発明のバルブ装置においては、前記案内部は、前記拡径手段の受け入れ側に向かうにつれて徐々に前記シールリングの周方向に広がるように形成されるものである。 In the valve device of the present invention, the guide portion is formed so as to gradually spread in the circumferential direction of the seal ring toward the receiving side of the diameter expanding means.
　本発明のバルブ装置においては、前記案内部は、曲面状に形成される。 In the valve device of the present invention, the guide portion is formed in a curved surface shape.
　本発明のバルブ装置においては、前記シールリングは、周方向に沿って延びる円周部と、前記円周部の端部から前記拡径手段が前記合口に入り込む方向に突出する突出部と、をさらに具備し、前記案内部は、前記円周部と前記突出部との接続部分に形成されるものである。 In the valve device of the present invention, the seal ring includes a circumferential portion extending along a circumferential direction, and a projecting portion projecting in a direction in which the diameter expanding means enters the joint from an end portion of the circumferential portion. Furthermore, the said guide part is formed in the connection part of the said circumference part and the said protrusion part.
　本発明のバルブ装置においては、前記バルブは、前記円周部を嵌め合わせるための細溝と、前記細溝と連通すると共に前記細溝の幅よりも広い幅を有し、前記突出部を配置するための太溝と、を具備するものである。 In the valve device of the present invention, the valve has a narrow groove for fitting the circumferential portion, a width communicating with the narrow groove and wider than the width of the narrow groove, and the protruding portion is disposed. And a thick groove for carrying out.
　本発明のバルブ装置においては、前記案内部は、前記シールリングの端面に形成されているものである。 In the valve device according to the present invention, the guide portion is formed on an end face of the seal ring.
　本発明の効果として、以下に示すような効果を奏する。 As the effects of the present invention, the following effects are obtained.
　本発明のバルブ装置は、シート及びシールリングの摩耗を抑制することができる。 The valve device of the present invention can suppress wear of the seat and the seal ring.
　本発明のバルブ装置は、シールリングを簡単に拡径させることができる。 The valve device of the present invention can easily expand the diameter of the seal ring.
　本発明のバルブ装置は、拡径手段の構成を簡素化することができる。 The valve device of the present invention can simplify the configuration of the diameter expanding means.
　本発明のバルブ装置は、シート及びシールリングの摩耗を効果的に抑制することができる。 The valve device of the present invention can effectively suppress wear of the seat and the seal ring.
　本発明のバルブ装置は、拡径手段を簡単に設けることができる。 The valve device of the present invention can be easily provided with a diameter expanding means.
　本発明のバルブ装置は、動作不良の発生を抑制することができる。 The valve device of the present invention can suppress the occurrence of malfunction.
　本発明のバルブ装置は、シール性を向上させることができる。 The valve device of the present invention can improve the sealing performance.
　本発明のバルブ装置は、規制手段及び拡径手段を破損し難くすることができる。 The valve device of the present invention can make it difficult to break the restricting means and the diameter expanding means.
　本発明のバルブ装置は、規制手段を簡単に形成することができる。 The valve device of the present invention can easily form the regulating means.
　本発明のバルブ装置は、シールリングの摩耗を抑制することができる。 The valve device of the present invention can suppress wear of the seal ring.
　本発明のバルブ装置は、シールリングの摩耗を効果的に抑制することができる。 The valve device of the present invention can effectively suppress the wear of the seal ring.
本発明の第一実施形態に係るバルブ装置を示した正面断面図。The front sectional view showing the valve device concerning a first embodiment of the present invention. （ａ）バルブ及びシールリングを示した拡大側面図。（ｂ）Ａ１－Ａ１断面図。(A) The expanded side view which showed the valve | bulb and the seal ring. (B) A1-A1 sectional view. シールリングがノッチピンに接近する様子を示した拡大側面図。The enlarged side view which showed a mode that a seal ring approached a notch pin. （ａ）シールリングとノッチピンとが当接する様子を示した拡大側面図。（ｂ）同じく、拡大正面断面図。(A) The expanded side view which showed a mode that a seal ring and a notch pin contact | abut. (B) Similarly, an enlarged front sectional view. （ａ）合口を押し広げる様子を示した拡大側面図。（ｂ）同じく、拡大正面断面図。(A) The enlarged side view which showed a mode that an opening is expanded. (B) Similarly, an enlarged front sectional view. 流路を完全に閉塞した状態を示した正面断面図。Front sectional drawing which showed the state which obstruct | occluded the flow path completely. 本発明の第二実施形態に係るバルブ装置を示した正面断面図。Front sectional drawing which showed the valve apparatus which concerns on 2nd embodiment of this invention. （ａ）バルブ及びシールリングを示した拡大側面図。（ｂ）Ａ２－Ａ２断面図。(A) The expanded side view which showed the valve | bulb and the seal ring. (B) A2-A2 cross-sectional view. （ａ）ノッチピンを示した斜視図。（ｂ）収容部を示した側面断面図。(A) The perspective view which showed the notch pin. (B) Side surface sectional drawing which showed the accommodating part. シールリングがノッチピンに接近する様子を示した拡大側面断面図。The expanded side sectional view which showed a mode that a seal ring approached a notch pin. （ａ）シールリングとノッチピンとが当接する様子を示した拡大側面断面図。（ｂ）同じく、拡大正面断面図。(A) The expanded side surface sectional view which showed a mode that a seal ring and a notch pin contact | abut. (B) Similarly, an enlarged front sectional view. （ａ）合口を押し広げる様子を示した拡大側面断面図。（ｂ）同じく、拡大正面断面図。(A) The expanded side surface sectional view which showed a mode that the joint opening was expanded. (B) Similarly, an enlarged front sectional view. 流路を完全に閉塞した状態を示した正面断面図。Front sectional drawing which showed the state which obstruct | occluded the flow path completely. 本発明の第三実施形態に係るバルブ装置を示した正面断面図。The front sectional view showing the valve device concerning a third embodiment of the present invention. （ａ）バルブ及びシールリングを示した拡大側面図。（ｂ）Ａ３－Ａ３断面図。(A) The expanded side view which showed the valve | bulb and the seal ring. (B) A3-A3 sectional view. シールリングを示した斜視図。The perspective view which showed the seal ring. シールリングがノッチピンに接近する様子を示した拡大側面図。The enlarged side view which showed a mode that a seal ring approached a notch pin. （ａ）シールリングとノッチピンとが当接する様子を示した拡大側面図。（ｂ）同じく、拡大正面断面図。(A) The expanded side view which showed a mode that a seal ring and a notch pin contact | abut. (B) Similarly, an enlarged front sectional view. （ａ）合口を押し広げる様子を示した拡大側面図。（ｂ）同じく、拡大正面断面図。(A) The enlarged side view which showed a mode that an opening is expanded. (B) Similarly, an enlarged front sectional view. 流路を完全に閉塞した状態を示した正面断面図。Front sectional drawing which showed the state which obstruct | occluded the flow path completely. （ａ）第一変形例に係るバルブ装置を示した正面断面図。（ｂ）第一変形例に係るバルブ装置で流路を完全に閉塞した状態を示した正面断面図。(A) Front sectional drawing which showed the valve apparatus which concerns on a 1st modification. (B) Front sectional drawing which showed the state which closed the flow path completely with the valve apparatus which concerns on a 1st modification. （ａ）第二変形例に係るバルブ及びシールリングを示した拡大側面図。（ｂ）Ａ４－Ａ４断面図。(A) The expanded side view which showed the valve | bulb and seal ring which concern on a 2nd modification. (B) A4-A4 sectional view. （ａ）第二変形例に係るノッチピンによって合口を押し広げる様子を示した拡大側面図。（ｂ）同じく、拡大正面断面図。(A) The expanded side view which showed a mode that an opening was expanded with the notch pin which concerns on a 2nd modification. (B) Similarly, an enlarged front sectional view. （ａ）第三変形例に係るノッチピンを示した斜視図。（ｂ）収容部を示した側面断面図。(A) The perspective view which showed the notch pin which concerns on a 3rd modification. (B) Side surface sectional drawing which showed the accommodating part. 第四変形例に係るノッチピンを示した斜視図。The perspective view which showed the notch pin which concerns on a 4th modification. （ａ）第五変形例に係るバルブ装置を示した正面断面図。（ｂ）ノッチピンを示した正面図。（ｃ）収容部を示した側面断面図。(A) Front sectional drawing which showed the valve apparatus which concerns on a 5th modification. (B) The front view which showed the notch pin. (C) Side surface sectional drawing which showed the accommodating part. （ａ）第六変形例に係るバルブ及びシールリングを示した拡大側面図。（ｂ）Ａ５－Ａ５断面図。(A) The expanded side view which showed the valve | bulb and seal ring which concern on a 6th modification. (B) A5-A5 sectional view. （ａ）第六変形例に係るノッチピンによって合口を押し広げる様子を示した拡大側面断面図。（ｂ）同じく、拡大正面断面図。(A) The expanded side surface sectional view which showed a mode that an opening was expanded with the notch pin which concerns on a 6th modification. (B) Similarly, an enlarged front sectional view. （ａ）第七変形例に係るシールリングを示した拡大側面図。（ｂ）第八変形例に係るシールリングを示した拡大側面図。(A) The expanded side view which showed the seal ring which concerns on a 7th modification. (B) The expanded side view which showed the seal ring which concerns on an 8th modification. （ａ）第九変形例に係るバルブ及びシールリングを示した拡大側面図。（ｂ）Ａ６－Ａ６断面図。(A) The expanded side view which showed the valve | bulb and seal ring which concern on a 9th modification. (B) A6-A6 sectional view. （ａ）第十変形例に係るバルブ装置を示した正面断面図。（ｂ）第十変形例に係るバルブ装置で流路を完全に閉塞した状態を示した正面断面図。(A) Front sectional drawing which showed the valve apparatus which concerns on a 10th modification. (B) Front sectional drawing which showed the state which closed the flow path completely with the valve apparatus which concerns on a 10th modification. 一般的なシールリングとノッチピンとが当接する様子を示した拡大側面図。The expanded side view which showed a mode that the general seal ring and the notch pin contact | abutted.
　以下では、図中の矢印Ｕ、矢印Ｄ、矢印Ｆ、矢印Ｂ、矢印Ｌ及び矢印Ｒで示した方向を、それぞれ上方向、下方向、前方向、後方向、左方向及び右方向と定義して説明を行う。 In the following, the directions indicated by arrow U, arrow D, arrow F, arrow B, arrow L and arrow R in the figure are defined as upward, downward, forward, backward, leftward and rightward, respectively. To explain.
　以下では、図１及び図２を参照して、本発明の第一実施形態に係るバルブ装置１０の構成について説明する。なお、本明細書に添付した図面においては、バルブ装置１０等の構成や動作をわかり易くするために、各部材の寸法や部材間の隙間等を誇張して記載している。 Hereinafter, the configuration of the valve device 10 according to the first embodiment of the present invention will be described with reference to FIGS. 1 and 2. In the drawings attached to the present specification, in order to make the configuration and operation of the valve device 10 and the like easier to understand, the dimensions of each member, the gaps between the members, and the like are exaggerated.
　バルブ装置１０は、流体の流通を制御するためのものである。なお、第一実施形態に係るバルブ装置１０は、エンジンの排気ガス再循環（ＥＧＲ）装置に設けられるものとする。図１に示すように、バルブ装置１０は、シート２０、バルブ３０、シールリング４０、シャフト５０及びノッチピン６０等を具備する。 The valve device 10 is for controlling the flow of fluid. In addition, the valve apparatus 10 which concerns on 1st embodiment shall be provided in an exhaust-gas recirculation (EGR) apparatus of an engine. As shown in FIG. 1, the valve device 10 includes a seat 20, a valve 30, a seal ring 40, a shaft 50, a notch pin 60, and the like.
　シート２０は、流体（第一実施形態では排気ガス）の流路を形成するものである。シート２０は、その軸線方向を前後方向に向けた略筒状に形成される。第一実施形態に係るシート２０は、エンジンの吸気通路と排気通路とを連通する通路に設けられる。シート２０は、流路２１及び支持孔２２を具備する。 The sheet 20 forms a flow path of fluid (exhaust gas in the first embodiment). The seat 20 is formed in a substantially cylindrical shape with its axial direction directed in the front-rear direction. The seat 20 according to the first embodiment is provided in a passage that connects the intake passage and the exhaust passage of the engine. The sheet 20 includes a flow path 21 and a support hole 22.
　流路２１は、流体が流通する通路である。流路２１は、正面視略円状に形成され、シート２０を軸線方向（前後方向）に貫通する。 The flow path 21 is a passage through which fluid flows. The channel 21 is formed in a substantially circular shape when viewed from the front, and penetrates the sheet 20 in the axial direction (front-rear direction).
　支持孔２２は、後述するノッチピン６０を支持する孔である。支持孔２２は、シート２０を外周面から内周面まで径方向に貫通する。支持孔２２は、シート２０の右端部に形成される。 The support hole 22 is a hole that supports a notch pin 60 described later. The support hole 22 penetrates the sheet 20 in the radial direction from the outer peripheral surface to the inner peripheral surface. The support hole 22 is formed at the right end portion of the sheet 20.
　バルブ３０は、流路２１を開閉するための略円板状の部材である。バルブ３０は、その外径がシート２０の内径よりも小さくなるように形成される。バルブ３０は、後述するシャフト５０を介してシート２０に回動自在に支持される。これにより、バルブ３０は、シート２０の内周面（流路２１の壁面）との間に隙間を空けた状態で流路２１に配置される。図２に示すように、バルブ３０は、シールリング溝３１を具備する。 The valve 30 is a substantially disk-shaped member for opening and closing the flow path 21. The valve 30 is formed so that its outer diameter is smaller than the inner diameter of the seat 20. The valve 30 is rotatably supported by the seat 20 via a shaft 50 described later. As a result, the valve 30 is disposed in the flow path 21 with a gap between the seat 20 and the inner peripheral surface (wall surface of the flow path 21). As shown in FIG. 2, the valve 30 includes a seal ring groove 31.
　シールリング溝３１は、バルブ３０の外周面に形成される溝である。シールリング溝３１は、バルブ３０の周方向に延びるように形成され、バルブ３０の全周に亘って形成される。シールリング溝３１は、バルブ３０の厚み方向における中央部に形成され、前後に側壁を有する。 The seal ring groove 31 is a groove formed on the outer peripheral surface of the valve 30. The seal ring groove 31 is formed so as to extend in the circumferential direction of the valve 30, and is formed over the entire circumference of the valve 30. The seal ring groove 31 is formed at the center in the thickness direction of the valve 30 and has side walls on the front and rear sides.
　このように構成されるバルブ３０は、図１に示す状態、すなわちその板面がシート２０の軸線方向とは異なる方向を向いたときに、流路２１を開放する。また、バルブ３０は、その板面がシート２０の軸線方向に対して直交する方向（左右方向）を向いたときに、流路２１を完全に開放する。また、バルブ３０は、その板面がシート２０の軸線方向を向いたときに、流路２１を完全に閉塞する（図６参照）。以下においては、このようなバルブ３０が流路２１を完全に閉塞する位置（図６に示す位置）を「全閉位置」と称する。 The valve 30 configured in this manner opens the flow path 21 when the state shown in FIG. 1, that is, when the plate surface faces a direction different from the axial direction of the seat 20. Further, the valve 30 completely opens the flow path 21 when the plate surface faces a direction (left-right direction) orthogonal to the axial direction of the seat 20. Further, the valve 30 completely closes the flow path 21 when the plate surface faces the axial direction of the seat 20 (see FIG. 6). Hereinafter, such a position where the valve 30 completely closes the flow path 21 (position shown in FIG. 6) is referred to as a “fully closed position”.
　図１及び図２に示すシールリング４０は、シート２０とバルブ３０との隙間をシールするためのものである。シールリング４０は、その右端部が切り欠かれたような正面視略Ｃ字状に形成される。シールリング４０は、弾性を有する材料によって構成される。シールリング４０は、その外径がバルブ３０の外径よりも大きく、かつシート２０の内径よりも僅かに小さくなるように形成される。シールリング４０は、合口４１を具備する。 The seal ring 40 shown in FIGS. 1 and 2 is for sealing the gap between the seat 20 and the valve 30. The seal ring 40 is formed in a substantially C shape when viewed from the front, with its right end cut out. The seal ring 40 is made of an elastic material. The seal ring 40 is formed so that its outer diameter is larger than the outer diameter of the valve 30 and slightly smaller than the inner diameter of the seat 20. The seal ring 40 includes a joint 41.
　合口４１は、シールリング４０の右端部に形成される切れ目部分（シールリング４０の周方向に沿った隙間）である。 The joint 41 is a cut portion (gap along the circumferential direction of the seal ring 40) formed at the right end of the seal ring 40.
　シールリング４０は、シールリング溝３１に嵌め合わされる。これにより、シールリング４０は、その外周面がバルブ３０の外周面から径方向外側に突出する。シールリング４０は、シールリング溝３１の側壁に支持されることによって、バルブ３０と一体的に回動すると共にバルブ３０の厚み方向への相対移動が規制される。 The seal ring 40 is fitted in the seal ring groove 31. Thereby, the outer peripheral surface of the seal ring 40 protrudes radially outward from the outer peripheral surface of the valve 30. The seal ring 40 is supported by the side wall of the seal ring groove 31 so as to rotate integrally with the valve 30 and to restrict relative movement of the valve 30 in the thickness direction.
　シールリング４０には、縮径方向への張力が作用している。すなわち、シールリング４０は、常に収縮しようとしており、その内周面がシールリング溝３１の底面と接触してバルブ３０を径方向内側に押圧している。これによれば、シールリング４０のバルブ３０に対する相対回転を抑制することができる。 The tension in the direction of diameter reduction acts on the seal ring 40. That is, the seal ring 40 is constantly shrinking, and the inner peripheral surface thereof contacts the bottom surface of the seal ring groove 31 to press the valve 30 radially inward. According to this, the relative rotation of the seal ring 40 with respect to the valve 30 can be suppressed.
　図１に示すように、シャフト５０は、バルブ３０を回動可能に支持するための略円柱状の部材である。シャフト５０は、その軸線方向を上下方向に向けた状態で、バルブ３０の後面に固定される。シャフト５０は、その上端部がシート２０から突出すると共にモータ等の駆動源と連結される（不図示）。シャフト５０は、前記駆動源から動力が伝達されてシート２０に対して相対的に回動する。これによって、シャフト５０は、その軸線Ｌ１を中心としてバルブ３０を回動させる。 As shown in FIG. 1, the shaft 50 is a substantially cylindrical member for supporting the valve 30 so as to be rotatable. The shaft 50 is fixed to the rear surface of the valve 30 with the axial direction thereof being directed in the vertical direction. The upper end of the shaft 50 protrudes from the seat 20 and is connected to a drive source such as a motor (not shown). The shaft 50 receives power from the drive source and rotates relative to the seat 20. As a result, the shaft 50 rotates the valve 30 around the axis L1.
　ノッチピン６０は、シールリング４０を拡径させるための略円柱状の部材である。ノッチピン６０は、その外径がシールリング４０の合口４１の上下方向に沿った距離よりも大きくなるように形成される。 The notch pin 60 is a substantially cylindrical member for expanding the diameter of the seal ring 40. The notch pin 60 is formed so that its outer diameter is larger than the distance along the vertical direction of the joint 41 of the seal ring 40.
　ノッチピン６０は、シート２０の支持孔２２に圧入されることでシート２０に固定される。これによって、ノッチピン６０は、シールリング４０の合口４１に対してシート２０の周方向における位置を合わせて配置される。ノッチピン６０は、その左端部がシート２０の内周面（流路２１の側壁）から左方向に突出する。当該ノッチピン６０の突出部分は、全閉位置まで回動したバルブ３０の外周面からシート２０の内周面までの径方向に沿った距離に対応する幅だけシート２０から突出している（図６参照）。これにより、ノッチピン６０は、バルブ３０が全閉位置まで回動してもバルブ３０と衝突しないように構成される。 The notch pin 60 is fixed to the sheet 20 by being press-fitted into the support hole 22 of the sheet 20. As a result, the notch pin 60 is arranged with the position in the circumferential direction of the seat 20 aligned with the joint 41 of the seal ring 40. The left end of the notch pin 60 protrudes leftward from the inner peripheral surface of the sheet 20 (side wall of the flow path 21). The protruding portion of the notch pin 60 protrudes from the seat 20 by a width corresponding to the distance along the radial direction from the outer peripheral surface of the valve 30 rotated to the fully closed position to the inner peripheral surface of the seat 20 (see FIG. 6). ). Thereby, the notch pin 60 is configured so as not to collide with the valve 30 even when the valve 30 is rotated to the fully closed position.
　次に、図１から図６までを参照してバルブ装置１０の閉塞動作について説明する。なお、図３及び図４（ａ）に白塗りで示す矢印は、バルブ３０の回動方向を示している。また、図５に黒塗りで示す矢印は、シールリング４０が弾性変形する様子を示している。 Next, the closing operation of the valve device 10 will be described with reference to FIGS. In addition, the arrow shown in white in FIG. 3 and FIG. Further, the arrows shown in black in FIG. 5 indicate that the seal ring 40 is elastically deformed.
　まず、図１及び図２に示すバルブ装置１０は、前記駆動源からシャフト５０に動力を伝達することで、図１に示す矢印方向にバルブ３０及びシールリング４０を回動させる。これによって、バルブ３０の板面がシート２０の軸線方向を向くように（開度が小さくなるように）バルブ３０を回動させる。このとき、図１及び図３に示すように、シールリング４０の合口４１は、ノッチピン６０に接近する。 First, the valve device 10 shown in FIGS. 1 and 2 transmits the power from the drive source to the shaft 50 to rotate the valve 30 and the seal ring 40 in the direction of the arrow shown in FIG. Thereby, the valve 30 is rotated so that the plate surface of the valve 30 faces the axial direction of the seat 20 (so that the opening degree becomes small). At this time, as shown in FIGS. 1 and 3, the joint 41 of the seal ring 40 approaches the notch pin 60.
　前述の如く、シールリング４０は、その外径がシート２０の内径よりも小さいため、シート２０の内周面（流路２１の壁面）との間に隙間を空けた状態で回動する。すなわち、シールリング４０は、図１に示す状態から回動してもシート２０に対して摺動しない。 As described above, since the outer diameter of the seal ring 40 is smaller than the inner diameter of the sheet 20, the seal ring 40 rotates with a gap between the seal ring 40 and the inner peripheral surface of the sheet 20 (wall surface of the flow path 21). That is, the seal ring 40 does not slide with respect to the seat 20 even if it rotates from the state shown in FIG.
　図４に示すように、全閉位置の直前までバルブ３０が回動すると、シールリング４０の合口４１は、ノッチピン６０を通過しようとする。前述の如く、ノッチピン６０は、その外径が合口４１の上下方向に沿った距離よりも大きい。このため、ノッチピン６０は、合口４１に入り込もうとして当該合口４１の上下両端部（シールリング４０の周方向における両端部）と当接する。 As shown in FIG. 4, when the valve 30 rotates just before the fully closed position, the joint 41 of the seal ring 40 tries to pass through the notch pin 60. As described above, the outer diameter of the notch pin 60 is larger than the distance along the vertical direction of the joint 41. For this reason, the notch pin 60 comes into contact with the upper and lower end portions (both end portions in the circumferential direction of the seal ring 40) of the joint portion 41 so as to enter the joint portion 41.
　図５及び図６に示すように、シールリング４０とノッチピン６０とが当接した状態からさらにバルブ３０が回動すると、ノッチピン６０は、シールリング４０の合口４１を押し広げながら合口４１に入り込む。これによって、ノッチピン６０は、シールリング４０を均一に拡径させる。 As shown in FIGS. 5 and 6, when the valve 30 further rotates from the state in which the seal ring 40 and the notch pin 60 are in contact, the notch pin 60 enters the joint 41 while pushing the joint 41 of the seal ring 40 wide. As a result, the notch pin 60 uniformly expands the diameter of the seal ring 40.
　図５及び図６に示す全閉位置までバルブ３０が回動すると、ノッチピン６０は、その軸心がシールリング４０の合口４１の前後中央部に配置されるまで合口４１に入り込む。このとき、ノッチピン６０は、その頂部（上端部）及び底部（下端部）がシールリング４０の両端面と当接する。これによって、シールリング４０は、ノッチピン６０の外径に応じた長さだけ拡径され、その外周面の全域がシート２０の内周面（流路２１の壁面）に密着する。これにより、バルブ３０が流路２１を閉塞したときに、バルブ３０の外周面とシート２０の内周面との隙間をシールリング４０でシールすることができる。 When the valve 30 is rotated to the fully closed position shown in FIGS. 5 and 6, the notch pin 60 enters the joint 41 until the axial center thereof is arranged at the front and rear central portions of the joint 41 of the seal ring 40. At this time, the top portion (upper end portion) and the bottom portion (lower end portion) of the notch pin 60 come into contact with both end surfaces of the seal ring 40. Thus, the diameter of the seal ring 40 is increased by a length corresponding to the outer diameter of the notch pin 60, and the entire outer peripheral surface thereof is in close contact with the inner peripheral surface of the sheet 20 (the wall surface of the flow path 21). Thereby, when the valve 30 closes the flow path 21, the gap between the outer peripheral surface of the valve 30 and the inner peripheral surface of the seat 20 can be sealed with the seal ring 40.
　バルブ装置１０は、流路２１を開放するとき、流路２１を閉塞した場合とは反対方向（図１に示す矢印方向とは反対方向）にバルブ３０を回動させる。これによって、シールリング４０の合口４１は、後方向に移動してノッチピン６０から離間する。このとき、ノッチピン６０は、バルブ３０の回動が始まった直後に（全閉位置からバルブ３０が僅かに回動したときに）合口４１から出て行くこととなる。これにより、シールリング４０は、縮径してシート２０の内周面に密着しなくなる。その後、流路２１を完全に開放するまでバルブ３０が回動しても、シールリング４０は、シート２０の内周面に対して摺動することはない。 When the flow path 21 is opened, the valve device 10 rotates the valve 30 in the direction opposite to the case where the flow path 21 is closed (the direction opposite to the arrow direction shown in FIG. 1). Accordingly, the joint 41 of the seal ring 40 moves rearward and is separated from the notch pin 60. At this time, the notch pin 60 comes out of the joint 41 immediately after the rotation of the valve 30 starts (when the valve 30 slightly rotates from the fully closed position). As a result, the seal ring 40 is reduced in diameter and does not adhere to the inner peripheral surface of the sheet 20. Thereafter, even if the valve 30 rotates until the flow path 21 is completely opened, the seal ring 40 does not slide with respect to the inner peripheral surface of the seat 20.
　以上のように、バルブ装置１０は、バルブ３０が全閉位置にごく近い回動位置にある場合（全閉位置の直前から全閉位置となるまでの間及び全閉位置から僅かにバルブ３０を回動させるまでの間）だけ、ノッチピン６０によってシールリング４０を拡径させてシート２０の内周面に密着させている。これによれば、流路２１を完全に閉塞したり完全に閉塞した流路２１を開放しない限り、シールリング４０をシート２０に対して摺動しないようにすることができる。このため、シート２０及びシールリング４０の摩耗を抑制することができ、シート２０及びシールリング４０の摩耗に起因する排気ガスの漏れを抑制することができる。 As described above, when the valve 30 is in the rotational position that is very close to the fully closed position, the valve device 10 is slightly moved from just before the fully closed position to the fully closed position and slightly from the fully closed position. The seal ring 40 is expanded in diameter by the notch pin 60 and is brought into close contact with the inner peripheral surface of the sheet 20 only until it is rotated. According to this, the seal ring 40 can be prevented from sliding with respect to the seat 20 unless the flow path 21 is completely closed or the completely closed flow path 21 is opened. For this reason, abrasion of the seat 20 and the seal ring 40 can be suppressed, and leakage of exhaust gas due to wear of the seat 20 and the seal ring 40 can be suppressed.
　以上の如く、第一実施形態に係るバルブ装置１０は、流路２１が貫通形成されているシート２０と、前記流路２１に回動自在に配置されると共に、回動することで前記流路２１を開閉するバルブ３０と、前記バルブ３０の外周に嵌め合わされたシールリング４０と、全閉位置（前記バルブ３０が前記流路２１を閉塞する位置）まで回動したときに、前記シールリング４０を拡径させて前記シート２０と前記シールリング４０との隙間をシールするノッチピン６０（拡径手段）と、を具備するものである。 As described above, the valve device 10 according to the first embodiment includes the seat 20 through which the flow path 21 is formed and the flow path 21 so as to be rotatable, and the flow path 21 is configured to rotate. A valve 30 for opening and closing the valve 21, a seal ring 40 fitted to the outer periphery of the valve 30, and the seal ring 40 when rotated to a fully closed position (position where the valve 30 closes the flow path 21). And a notch pin 60 (diameter expanding means) that seals the gap between the seat 20 and the seal ring 40.
　このように構成することにより、シート２０及びシールリング４０の摩耗を抑制することができる。 With this configuration, wear of the seat 20 and the seal ring 40 can be suppressed.
　また、前記シールリング４０は、切れ目部分である合口４１を具備し、前記ノッチピン６０は、前記合口４１を押し広げることで前記シールリング４０を拡径させるものである。 Further, the seal ring 40 includes a joint 41 which is a cut portion, and the notch pin 60 expands the diameter of the seal ring 40 by pushing and widening the joint 41.
　このように構成することにより、後述するようなシールリング溝３１から径方向外側にシールリング４０の内周面を押し出すことでシールリング４０を拡径させる場合等と比較して、シールリング４０を簡単に拡径させることができる。
　また、シールリング４０を均一に拡径させることができるため、シールリング４０の外周面の全域をシート２０の内周面に密着させ易くすることができる。これによって、シール性を向上させることができる。 By configuring in this way, the seal ring 40 is compared with the case where the diameter of the seal ring 40 is increased by pushing the inner peripheral surface of the seal ring 40 radially outward from the seal ring groove 31 as described later. The diameter can be easily expanded.
In addition, since the diameter of the seal ring 40 can be increased uniformly, the entire outer peripheral surface of the seal ring 40 can be easily adhered to the inner peripheral surface of the sheet 20. Thereby, sealing performance can be improved.
　また、前記ノッチピン６０は、前記全閉位置まで回動したときに前記合口４１に入り込むことで、前記合口４１を押し広げるものである。 Also, the notch pin 60 pushes the joint 41 by entering the joint 41 when rotated to the fully closed position.
　このように構成することにより、後述するような合口４１に圧縮空気等を噴き付けて拡径させる場合等と比較して、シールリング４０を簡単に拡径させることができる。 Such a configuration makes it possible to easily expand the diameter of the seal ring 40 as compared with a case where compressed air or the like is sprayed onto the abutment 41 as described later to expand the diameter.
　また、前記ノッチピン６０は、前記シート２０に固定されるものである。 The notch pin 60 is fixed to the sheet 20.
　このように構成することにより、後述するようなノッチピン（図２１に示す第一変形例に係るノッチピン３６０）を移動させるための駆動源等を用いることなくシールリング４０を拡径させることが可能となるため、シールリング４０を拡径させる構成を簡素化することができる。 With this configuration, it is possible to increase the diameter of the seal ring 40 without using a drive source or the like for moving a notch pin (notch pin 360 according to the first modification shown in FIG. 21) as will be described later. Therefore, the configuration for expanding the diameter of the seal ring 40 can be simplified.
　また、前記合口４１は、前記バルブ３０の回動軸線（シャフト５０の軸線Ｌ１）に対して離れた位置に配置されるものである。
　なお、第一実施形態に係る合口４１は、バルブ３０の右端部、すなわちバルブ３０の回動軸線に対して最も離れた位置に配置されている。 Further, the joint 41 is arranged at a position away from the rotation axis of the valve 30 (the axis L1 of the shaft 50).
Note that the joint 41 according to the first embodiment is disposed at the right end of the valve 30, that is, the position farthest from the rotation axis of the valve 30.
　このように構成することにより、バルブ３０の回動角度に対する合口４１の移動距離を長くすることができる。これにより、バルブ３０を僅かに回動させるだけでノッチピン６０を合口４１に対して出し入れすることができるため、バルブ３０が全閉位置にごく近い回動位置にある場合だけシールリング４０を拡径させることが可能となる。これによれば、必要なときだけシールリング４０を拡径させることができ、シールリング４０をシート２０に対して極力摺動しないようにすることができる。従って、シート２０及びシールリング４０の摩耗を効果的に抑制することができる。 With this configuration, the moving distance of the joint 41 with respect to the rotation angle of the valve 30 can be increased. As a result, the notch pin 60 can be inserted into and withdrawn from the abutment 41 by slightly rotating the valve 30. Therefore, the diameter of the seal ring 40 is increased only when the valve 30 is in a rotational position very close to the fully closed position. It becomes possible to make it. According to this, the diameter of the seal ring 40 can be increased only when necessary, and the seal ring 40 can be prevented from sliding with respect to the seat 20 as much as possible. Therefore, wear of the seat 20 and the seal ring 40 can be effectively suppressed.
　また、前記ノッチピン６０は、前記シート２０とは異なる部材によって構成されるものである。 Further, the notch pin 60 is constituted by a member different from the sheet 20.
　このように構成することにより、シート２０にノッチピン６０を一体的に形成する場合と比較して簡単な加工でシート２０及びノッチピン６０を形成することができるため、ノッチピン６０をシート２０に簡単に設けることができる。
　また、既存のバルブ装置に簡単にノッチピン６０を設ける（後付けする）ことができる。 With this configuration, the sheet 20 and the notch pin 60 can be formed by simple processing as compared with the case where the notch pin 60 is integrally formed on the sheet 20, and thus the notch pin 60 is simply provided on the sheet 20. be able to.
Moreover, the notch pin 60 can be easily provided (retrofitted) on the existing valve device.
　また、前記シールリング４０には、縮径方向への張力が作用しているものである。 Further, the seal ring 40 is subjected to tension in the direction of diameter reduction.
　このように構成することにより、シールリング４０のバルブ３０に対する相対回転を抑制することができる。これによれば、合口４１がノッチピン６０に対してシールリング４０の周方向にずれることを抑制できるため、合口４１にノッチピン６０を入り込ませ易くすることができる。これによって、シールリング４０のバルブ３０に対する相対回転に起因する動作不良の発生を抑制できる。 With this configuration, relative rotation of the seal ring 40 with respect to the valve 30 can be suppressed. According to this, since it can suppress that the abutment 41 slip | deviates to the circumferential direction of the seal ring 40 with respect to the notch pin 60, it can make it easy to enter the notch pin 60 in the abutment 41. Thereby, it is possible to suppress the occurrence of malfunction due to the relative rotation of the seal ring 40 with respect to the valve 30.
　なお、第一実施形態に係るノッチピン６０は、本発明に係る拡径手段の実施の一形態である。 In addition, the notch pin 60 which concerns on 1st embodiment is one Embodiment of the diameter expansion means which concerns on this invention.
　次に、本発明の第二実施形態に係るバルブ装置１１０の構成について説明する。なお、以下においては、第一実施形態に係るバルブ装置１０と同様に構成される部材については、第一実施形態と同一の符号を付し、その説明を省略する。 Next, the configuration of the valve device 110 according to the second embodiment of the present invention will be described. In the following, members that are configured in the same manner as the valve device 10 according to the first embodiment are denoted by the same reference numerals as those in the first embodiment, and description thereof is omitted.
　図７に示すように、バルブ装置１１０は、シート２０、バルブ１３０、シールリング１４０、シャフト５０、回り止めピン１６０及びノッチピン１７０等を具備する。 As shown in FIG. 7, the valve device 110 includes a seat 20, a valve 130, a seal ring 140, a shaft 50, a non-rotating pin 160, a notch pin 170, and the like.
　図８に示すように、バルブ１３０は、シールリング溝３１及び凹部１３２を具備する。凹部１３２は、後述する回り止めピン１６０を支持するための窪みである。凹部１３２は、バルブ１３０の右端部に形成される。凹部１３２は、側面視略円状に形成されると共に、シールリング溝３１の底面からバルブ１３０の径方向内側（左側）に延びるように形成される。 As shown in FIG. 8, the valve 130 includes a seal ring groove 31 and a recess 132. The recess 132 is a recess for supporting a rotation stopper pin 160 described later. The recess 132 is formed at the right end of the valve 130. The recess 132 is formed in a substantially circular shape when viewed from the side, and is formed so as to extend from the bottom surface of the seal ring groove 31 to the inside (left side) in the radial direction of the valve 130.
　図７及び図８に示すシールリング１４０は、合口１４１を具備する。合口１４１は、バルブ１３０の凹部１３２よりも周方向に沿った距離が長くなるように形成される。合口１４１は、凹部１３２に対して周方向における位置を合わせて配置される。 The seal ring 140 shown in FIG. 7 and FIG. The abutment 141 is formed such that the distance along the circumferential direction is longer than the recess 132 of the valve 130. The abutment 141 is arranged with the position in the circumferential direction aligned with the recess 132.
　回り止めピン１６０は、シールリング１４０のバルブ１３０に対する相対回転（周方向への相対移動）を規制するための略円柱状の部材である。回り止めピン１６０は、その外径がバルブ１３０の凹部１３２の内径と略同一の大きさとなるように形成される。回り止めピン１６０は、その長さ（軸線方向幅）が凹部１３２の深さよりも長くなるように形成される。 The rotation prevention pin 160 is a substantially columnar member for restricting relative rotation (relative movement in the circumferential direction) of the seal ring 140 with respect to the valve 130. The anti-rotation pin 160 is formed so that the outer diameter thereof is substantially the same as the inner diameter of the recess 132 of the valve 130. The anti-rotation pin 160 is formed such that its length (axial width) is longer than the depth of the recess 132.
　回り止めピン１６０は、バルブ１３０の凹部１３２に圧入されることでバルブ１３０の右端部に固定される。これによって、回り止めピン１６０は、バルブ１３０と一体的に回動可能に構成されると共に、その右部がシールリング溝３１の底面から右方向に突出する。当該回り止めピン１６０の突出部分は、合口１４１の内側に配置されると共に、シールリング１４０の外周面と同程度の長さだけバルブ１３０の外周面から突出する。 The rotation prevention pin 160 is fixed to the right end portion of the valve 130 by being press-fitted into the recess 132 of the valve 130. Accordingly, the rotation prevention pin 160 is configured to be rotatable integrally with the valve 130, and a right portion thereof protrudes rightward from the bottom surface of the seal ring groove 31. The protruding portion of the locking pin 160 is disposed inside the abutment 141 and protrudes from the outer peripheral surface of the valve 130 by the same length as the outer peripheral surface of the seal ring 140.
　図７及び図９に示すように、ノッチピン１７０は、その外径が回り止めピン１６０の外径及びシールリング１４０の合口１４１の上下方向に沿った距離よりも大きくなるように形成される。ノッチピン１７０は、その軸線方向を左右方向に向けて配置される。ノッチピン１７０は、収容部１７１を具備する。 7 and 9, the notch pin 170 is formed so that its outer diameter is larger than the outer diameter of the non-rotating pin 160 and the distance along the vertical direction of the joint 141 of the seal ring 140. The notch pin 170 is arranged with its axial direction facing the left-right direction. The notch pin 170 includes a housing portion 171.
　収容部１７１は、バルブ１３０の回動時に回り止めピン１６０を収容するためのものである。収容部１７１は、ノッチピン１７０の左後端部を切り欠いたような側面視略Ｕ字状に形成される。より詳細には、収容部１７１は、ノッチピン１７０の後端部から前後中央部まで前方向に延びるように形成されると共に、当該延びた端面（後方向を向いた面、以下「端面１７１ａ」と称する）が回り止めピン１６０の外周面に沿うような側面視略円弧状に形成される。収容部１７１は、その上下方向幅が合口１４１の上下方向に沿った距離よりも狭く、かつ回り止めピン１６０の上下方向幅（外径）よりも広くなるように形成される（図１１（ａ）参照）。収容部１７１の左右方向幅は、回り止めピン１６０のうち、バルブ１３０の外周面から突出している部分（図１１（ｂ）に示す回り止めピン１６０の実線部分）の長さよりも広くなるように形成される。収容部１７１は、回り止めピン１６０に対してシート２０の周方向における位置を合わせて配置される。 The accommodating portion 171 is for accommodating the detent pin 160 when the valve 130 is rotated. The accommodating portion 171 is formed in a substantially U shape in side view as if the left rear end portion of the notch pin 170 is cut out. More specifically, the accommodating portion 171 is formed so as to extend in the forward direction from the rear end portion of the notch pin 170 to the front and rear central portion, and the extended end surface (a surface facing rearward, hereinafter referred to as “end surface 171a”). Is formed in a substantially circular arc shape when viewed from the side along the outer peripheral surface of the detent pin 160. The accommodating part 171 is formed so that the vertical width thereof is narrower than the distance along the vertical direction of the joint 141 and wider than the vertical width (outer diameter) of the locking pin 160 (FIG. 11A). )reference). The lateral width of the accommodating portion 171 is larger than the length of the portion of the locking pin 160 that protrudes from the outer peripheral surface of the valve 130 (the solid line portion of the locking pin 160 shown in FIG. 11B). It is formed. The accommodating portion 171 is disposed so that the position in the circumferential direction of the seat 20 is aligned with the rotation prevention pin 160.
　次に、図７、図８、図１０から図１３までを参照してバルブ装置１１０の閉塞動作について説明する。なお、図１０及び図１１（ａ）に白塗りで示す矢印は、バルブ１３０の回動方向を示している。また、図１２に黒塗りで示す矢印は、シールリング１４０が弾性変形する様子を示している。 Next, the closing operation of the valve device 110 will be described with reference to FIGS. 7, 8 and 10 to 13. In addition, the arrow shown in white in FIG.10 and FIG.11 (a) has shown the rotation direction of the valve | bulb 130. FIG. Also, the arrows shown in black in FIG. 12 indicate how the seal ring 140 is elastically deformed.
　まず、図７及び図８に示すバルブ装置１１０は、前記駆動源からシャフト５０に動力を伝達することで、図７に示す矢印方向にバルブ１３０、シールリング１４０及び回り止めピン１６０を回動させる。このとき、図７及び図１０に示すように、シールリング１４０の合口１４１及び回り止めピン１６０は、ノッチピン１７０に接近する。 First, the valve device 110 shown in FIGS. 7 and 8 transmits the power from the driving source to the shaft 50, thereby rotating the valve 130, the seal ring 140, and the rotation prevention pin 160 in the direction of the arrow shown in FIG. . At this time, as shown in FIGS. 7 and 10, the abutment 141 and the rotation prevention pin 160 of the seal ring 140 approach the notch pin 170.
　図１１に示すように、全閉位置の直前までバルブ１３０が回動すると、ノッチピン１７０の外周面は、合口１４１の内側に入り込もうとして当該合口１４１の上下両端部（シールリング１４０の周方向における両端部）と当接する。このとき、回り止めピン１６０は、収容部１７１の後方に配置される。 As shown in FIG. 11, when the valve 130 rotates just before the fully closed position, the outer peripheral surface of the notch pin 170 tries to enter the inside of the joint 141 (upper and lower ends of the joint 141 in the circumferential direction of the seal ring 140). (Both ends) At this time, the locking pin 160 is disposed behind the housing portion 171.
　また、回り止めピン１６０は、図１１に示すシールリング１４０とノッチピン１７０とが当接した状態からさらにバルブ１３０が回動すると、前方向に移動して収容部１７１に入り込む。そして、図１２及び図１３に示す全閉位置までバルブ１３０が回動すると、回り止めピン１６０は、収容部１７１を前方向に移動して、収容部１７１の端面１７１ａと接触する。 Further, when the valve 130 is further rotated from the state in which the seal ring 140 and the notch pin 170 shown in FIG. 11 are in contact with each other, the detent pin 160 moves in the forward direction and enters the accommodating portion 171. Then, when the valve 130 rotates to the fully closed position shown in FIGS. 12 and 13, the rotation prevention pin 160 moves the housing portion 171 in the forward direction and contacts the end surface 171 a of the housing portion 171.
　バルブ装置１１０は、流路２１を開放するとき、流路２１を閉塞した場合とは反対方向（図７に示す矢印方向とは反対方向）にバルブ１３０を回動させる。これによって、回り止めピン１６０は、ノッチピン１７０の収容部１７１を後方向に移動して収容部１７１から出て行く。 When the flow path 21 is opened, the valve device 110 rotates the valve 130 in the direction opposite to the case where the flow path 21 is closed (the direction opposite to the arrow direction shown in FIG. 7). As a result, the detent pin 160 moves out of the accommodating portion 171 by moving the accommodating portion 171 of the notch pin 170 rearward.
　以上のように動作する第二実施形態に係るバルブ装置１１０は、合口１４１の内側に回り止めピン１６０を配置することにより、シールリング１４０がバルブ１３０に対して相対回転したときに、合口１４１の上端部又は下端部を回り止めピン１６０に当接させることができる。これによれば、シールリング１４０のバルブ１３０に対する相対回転を一定量に留めることができるため、ノッチピン１７０を合口１４１の内側に確実に入り込ませることができる。これによって、シールリング１４０を確実に拡径させることができる。以上によれば、シールリング１４０を拡径させる動作が失敗することを防止でき、動作不良（シール不良）が発生することなくシート２０及びシールリング１４０の摩耗抑制を実現することができる。 In the valve device 110 according to the second embodiment that operates as described above, the rotation stop pin 160 is disposed inside the joint 141 so that when the seal ring 140 rotates relative to the valve 130, The upper end portion or the lower end portion can be brought into contact with the rotation prevention pin 160. According to this, since the relative rotation of the seal ring 140 with respect to the valve 130 can be kept at a constant amount, the notch pin 170 can be surely inserted inside the joint 141. Thereby, the diameter of the seal ring 140 can be expanded reliably. According to the above, it is possible to prevent the operation of expanding the diameter of the seal ring 140 from failing, and to suppress wear of the seat 20 and the seal ring 140 without causing an operation failure (seal failure).
　ここで、合口１４１の内側に回り止めピン１６０が配置されると、ノッチピン１７０が合口１４１の内側に入り込むときに（バルブ１３０が全閉位置まで回動する前に）、回り止めピン１６０がノッチピン１７０に対して後方向から勢い良く接触（衝突）してしまうおそれがある。この場合、バルブ１３０の回動が途中で止まってしまったり、回り止めピン１６０及びノッチピン１７０が破損してしまうおそれがある。 Here, when the non-rotating pin 160 is disposed inside the joint 141, when the notch pin 170 enters the inside of the joint 141 (before the valve 130 is rotated to the fully closed position), the non-rotating pin 160 is notched. There is a risk that the robot 170 may come into contact (collision) with force from the rear. In this case, the rotation of the valve 130 may be stopped in the middle, or the locking pin 160 and the notch pin 170 may be damaged.
　そこで、第二実施形態に係るノッチピン１７０は、収容部１７１を具備している。これによって、ノッチピン１７０が合口１４１の内側に入り込むときに、収容部１７１に回り止めピン１６０を入り込ませることができる。これによれば、ノッチピン１７０と回り止めピン１６０との衝突を回避することができる。これにより、バルブ１３０の回動が途中で止まることなく、ノッチピン１７０を合口１４１の内側に入り込ませてシールリング１４０を確実に拡径させることができる。以上によれば、シールリング１４０を拡径させる動作が失敗することを防止でき、動作不良が発生することなくシート２０及びシールリング１４０の摩耗抑制を実現することができる。また、回り止めピン１６０及びノッチピン１７０を破損し難くすることができる。 Therefore, the notch pin 170 according to the second embodiment includes a housing portion 171. Accordingly, when the notch pin 170 enters the inside of the joint 141, the rotation prevention pin 160 can be inserted into the housing portion 171. According to this, the collision between the notch pin 170 and the rotation stopper pin 160 can be avoided. Thereby, the rotation of the valve 130 does not stop in the middle, and the notch pin 170 can enter the inside of the joint 141 and the diameter of the seal ring 140 can be reliably expanded. According to the above, it is possible to prevent the operation of expanding the diameter of the seal ring 140 from failing, and to suppress wear of the seat 20 and the seal ring 140 without causing a malfunction. Further, it is possible to make it difficult to damage the rotation prevention pin 160 and the notch pin 170.
　また、第二実施形態に係るノッチピン１７０の収容部１７１は、ノッチピン１７０の後端部から前後中央部に亘って形成されている。これによれば、ノッチピン１７０を合口１４１の内側に十分に（ノッチピン１７０の軸心が合口１４１の前後中央部に配置される程度に）入り込ませることができる。これにより、シールリング１４０を大きく拡径させてシールリング１４０の外周面をシート２０の内周面に強い力で押し付けることができる。このため、シール性を向上させることができる。 Moreover, the accommodating part 171 of the notch pin 170 which concerns on 2nd embodiment is formed ranging from the rear-end part of the notch pin 170 to the front-back center part. According to this, the notch pin 170 can be sufficiently inserted inside the joint 141 (to the extent that the axial center of the notch pin 170 is disposed at the front and rear center portion of the joint 141). Thereby, the diameter of the seal ring 140 can be greatly expanded, and the outer peripheral surface of the seal ring 140 can be pressed against the inner peripheral surface of the seat 20 with a strong force. For this reason, sealing performance can be improved.
　以上の如く、第二実施形態に係るバルブ装置１１０は、前記合口１４１の内側に配置され、前記シールリング１４０の前記バルブ１３０に対する相対回転を規制する回り止めピン１６０（規制手段）をさらに具備し、前記ノッチピン１７０（拡径手段）は、前記合口１４１の内側に入り込んで前記合口１４１を押し広げるものであり、前記合口１４１に入り込むときに、前記回り止めピン１６０が内部に入り込む収容部１７１を具備するものである。 As described above, the valve device 110 according to the second embodiment further includes the rotation prevention pin 160 (regulating means) that is disposed inside the joint 141 and that regulates relative rotation of the seal ring 140 with respect to the valve 130. The notch pin 170 (diameter expanding means) enters the inside of the joint 141 and pushes the joint 141. When the notch pin 170 enters the joint 141, the notch pin 160 has a receiving portion 171 into which the rotation prevention pin 160 enters. It has.
　このように構成することにより、シート２０及びシールリング１４０の摩耗を抑制することができる。
　また、回り止めピン１６０によってシールリング１４０のバルブ１３０に対する相対回転を一定量に留めることができる。
　また、収容部１７１によって回り止めピン１６０とノッチピン１７０との衝突を回避することができるため、ノッチピン１７０を合口１４１の内側に入り込ませてシールリング１４０を確実に拡径させることができる。 By comprising in this way, abrasion of the sheet | seat 20 and the seal ring 140 can be suppressed.
Further, the rotation of the seal ring 140 with respect to the valve 130 can be kept constant by the rotation prevention pin 160.
Moreover, since the collision between the locking pin 160 and the notch pin 170 can be avoided by the accommodating portion 171, the notch pin 170 can enter the inside of the joint 141 and the diameter of the seal ring 140 can be reliably expanded.
　また、前記ノッチピン１７０は、前記シート２０に固定されるものである。 Further, the notch pin 170 is fixed to the sheet 20.
　このように構成することにより、後述するようなノッチピン（図２６に示す第五変形例に係るノッチピン７７０）を移動させるための駆動源等を用いることなくシールリング１
４０を拡径させることが可能となるため、シールリング１４０を拡径させる構成を簡素化することができる。 With this configuration, the seal ring 1 can be used without using a drive source or the like for moving a notch pin (notch pin 770 according to the fifth modification shown in FIG. 26) as will be described later.
Since the diameter of 40 can be increased, the configuration for expanding the diameter of the seal ring 140 can be simplified.
　また、前記収容部１７１は、後側（前記ノッチピン１７０の前記合口１４１に入り込む側）が開口すると共に、前側（前記合口１４１に入り込む側とは反対側）が閉塞するものである。 The housing 171 is open on the rear side (the side entering the joint 141 of the notch pin 170) and closed on the front side (the side opposite to the side entering the joint 141).
　このように構成することにより、全閉位置までバルブ１３０が回動したときに、収容部１７１と回り止めピン１６０との隙間から流体が下流側に流通する（漏れる）ことを防止できる。これによって、シール性を向上させることができる。 With this configuration, when the valve 130 is rotated to the fully closed position, fluid can be prevented from flowing (leaking) downstream from the gap between the accommodating portion 171 and the rotation prevention pin 160. Thereby, sealing performance can be improved.
　また、前記収容部１７１の端面１７１ａ（前記合口１４１に入り込む側とは反対側の端面）は、前記回り止めピン１６０の形状に沿った形状に形成されるものである。 Further, the end surface 171a of the housing portion 171 (the end surface on the side opposite to the side entering the abutment 141) is formed in a shape along the shape of the detent pin 160.
　このように構成することにより、収容部１７１の端面１７１ａを回り止めピン１６０に対して面で接触させることが可能となる。これにより、組み付け誤差等の影響でバルブ１３０の回動時に回り止めピン１６０が収容部１７１の端面１７１ａに勢い良く接触（衝突）した場合でも、回り止めピン１６０及びノッチピン１７０を破損し難くすることができる。 With this configuration, the end surface 171a of the accommodating portion 171 can be brought into contact with the anti-rotation pin 160 by a surface. As a result, even if the rotation prevention pin 160 vigorously contacts (collises) with the end surface 171a of the accommodating portion 171 when the valve 130 is rotated due to an assembly error or the like, the rotation prevention pin 160 and the notch pin 170 are hardly damaged. Can do.
　また、前記収容部１７１は、後方向（前記ノッチピン１７０が前記合口１４１に入り込む方向）に延びるように形成されるものである。 Further, the accommodating portion 171 is formed to extend in the rearward direction (the direction in which the notch pin 170 enters the joint 141).
　このように構成することにより、組み付け誤差等があった場合でも、回り止めピン１６０がノッチピン１７０の収容部１７１に衝突し難くすることができるため、回り止めピン１６０及びノッチピン１７０を破損し難くすることができる。
　また、回り止めピン１６０を収容部１７１に深く入り込ませることができる。これにより、ノッチピン１７０を合口１４１の内側に十分に入り込ませることができる。これによれば、シールリング１４０をより大きく拡径させることができ、シールリング１４０の外周面をシート２０の内周面に強い力で押し付けてシール性を向上させることができる。 With this configuration, even when there is an assembly error or the like, the rotation prevention pin 160 can be made difficult to collide with the accommodating portion 171 of the notch pin 170, so that the rotation prevention pin 160 and the notch pin 170 are hardly damaged. be able to.
Further, the rotation prevention pin 160 can be deeply inserted into the housing portion 171. As a result, the notch pin 170 can sufficiently enter the inside of the joint 141. According to this, the diameter of the seal ring 140 can be further increased, and the sealing performance can be improved by pressing the outer peripheral surface of the seal ring 140 against the inner peripheral surface of the seat 20 with a strong force.
　また、前記回り止めピン１６０は、前記バルブ１３０とは異なる部材によって構成されるものである。 Further, the detent pin 160 is constituted by a member different from the valve 130.
　このように構成することにより、バルブ１３０に回り止めピン１６０を一体的に形成する場合と比較して簡単な加工でバルブ１３０及び回り止めピン１６０を形成することができるため、回り止めピン１６０をバルブ１３０に簡単に設けることができる。
　また、既存のバルブ装置に簡単に回り止めピン１６０を設ける（後付けする）ことができる。 By configuring in this way, the valve 130 and the rotation prevention pin 160 can be formed by simple processing as compared with the case where the rotation prevention pin 160 is formed integrally with the valve 130. The valve 130 can be easily provided.
In addition, the anti-rotation pin 160 can be easily provided (retrofitted) on the existing valve device.
　なお、第二実施形態に係る回り止めピン１６０は、本発明に係る規制手段の実施の一形態である。
　また、第二実施形態に係るノッチピン１７０は、本発明に係る拡径手段の実施の一形態である。
　第二実施形態における後方向は、本発明に係る拡径手段が合口に入り込む方向に対応する。 In addition, the rotation prevention pin 160 which concerns on 2nd embodiment is one Embodiment of the control means which concerns on this invention.
Moreover, the notch pin 170 which concerns on 2nd embodiment is one Embodiment of the diameter expansion means which concerns on this invention.
The rear direction in the second embodiment corresponds to the direction in which the diameter expanding means according to the present invention enters the joint.
　次に、本発明の第三実施形態に係るバルブ装置２１０の構成について説明する。なお、以下においては、第一実施形態に係るバルブ装置１０と同様に構成される部材については、第一実施形態と同一の符号を付し、その説明を省略する。 Next, the configuration of the valve device 210 according to the third embodiment of the present invention will be described. In the following, members that are configured in the same manner as the valve device 10 according to the first embodiment are denoted by the same reference numerals as those in the first embodiment, and description thereof is omitted.
　図１４及び図１５に示すように、バルブ装置２１０は、シート２０、バルブ２３０、シールリング２４０、シャフト５０及びノッチピン２６０等を具備する。 14 and 15, the valve device 210 includes a seat 20, a valve 230, a seal ring 240, a shaft 50, a notch pin 260, and the like.
　バルブ２３０は、シールリング溝２３１を具備する。シールリング溝２３１は、細溝２３１ａ及び太溝２３１ｂを具備する。 The valve 230 includes a seal ring groove 231. The seal ring groove 231 includes a narrow groove 231a and a thick groove 231b.
　細溝２３１ａは、シールリング溝２３１のうち、右端部を除く部分である。すなわち、細溝２３１ａは、正面視略Ｃ字状に形成される。細溝２３１ａは、その幅（バルブ２３０の厚み方向幅）がバルブ２３０の厚みよりも狭くなるように形成されると共に、バルブ２３０の厚み方向における中央部に形成される。細溝２３１ａは、前後に側壁を有する。 The narrow groove 231a is a portion excluding the right end portion of the seal ring groove 231. That is, the narrow groove 231a is formed in a substantially C shape when viewed from the front. The narrow groove 231a is formed so that its width (width in the thickness direction of the bulb 230) is narrower than the thickness of the bulb 230, and is formed in the center in the thickness direction of the bulb 230. The narrow groove 231a has side walls on the front and rear sides.
　太溝２３１ｂは、シールリング溝２３１の右端部である。太溝２３１ｂは、細溝２３１ａと連通し、細溝２３１ａよりもその幅が広くなるように形成される。また、太溝２３１ｂは、その幅がバルブ２３０の厚みと同一の幅となるように形成される。すなわち、太溝２３１ｂは、前後に側壁を有していない。 The thick groove 231b is the right end of the seal ring groove 231. The thick groove 231b communicates with the narrow groove 231a and is formed to have a width wider than that of the narrow groove 231a. The thick groove 231b is formed so that the width thereof is the same as the thickness of the bulb 230. That is, the thick groove 231b does not have side walls on the front and rear sides.
　図１４から図１６までに示すシールリング２４０は、円周部２４１、突出部２４２、案内部２４３及び合口２４４を具備する。 The seal ring 240 shown in FIGS. 14 to 16 includes a circumferential portion 241, a projecting portion 242, a guide portion 243, and a joint 244.
　円周部２４１は、その右端部が切り欠かれたような正面視略Ｃ字状に形成される。円周部２４１は、その外径がバルブ２３０の外径よりも大きく、かつシート２０の内径よりも僅かに小さくなるように形成される。 The circumferential portion 241 is formed in a substantially C shape in front view as if the right end portion was cut away. The circumferential portion 241 is formed so that its outer diameter is larger than the outer diameter of the valve 230 and slightly smaller than the inner diameter of the seat 20.
　突出部２４２は、円周部２４１から後方向に突出する部分である。突出部２４２は、円周部２４１の両端部（シールリング２４０の右端部）にそれぞれ形成される。突出部２４２は、互いに上下方向に間隔を空けて配置される。 The protruding portion 242 is a portion protruding backward from the circumferential portion 241. The protrusions 242 are formed at both ends of the circumferential portion 241 (the right end of the seal ring 240). The protrusions 242 are arranged at intervals in the vertical direction.
　案内部２４３は、円周部２４１の一端部（上側の端部）と上側の突出部２４２との接続部分、並びに円周部２４１の他端部（下側の端部）と下側の突出部２４２との接続部分にそれぞれ形成される曲面である。上側の案内部２４３は、前方向に向かうにつれて上方向に延びるような側面視略円弧状に形成される。上側の案内部２４３は、円周部２４１の前側面から上側の突出部２４２の下側面（下方向を向いた面）に亘って形成される。下側の案内部２４３は、前方向に向かうにつれて下方向に延びるような側面視略円弧状に形成される。下側の案内部２４３は、円周部２４１の前側面から下側の突出部２４２の上側面（上方向を向いた面）に亘って形成される。上下の案内部２４３は、互いに上下方向に間隔を空けて配置され、前方向に向かうにつれて円周部２４１（シールリング２４０）の周方向に広がるように形成される。 The guide portion 243 includes a connecting portion between one end portion (upper end portion) of the circumferential portion 241 and the upper protruding portion 242 and a lower end portion protruding from the other end portion (lower end portion) of the circumferential portion 241. It is a curved surface formed in each connection part with the part 242. The upper guide portion 243 is formed in a substantially arc shape in a side view so as to extend upward as it goes in the front direction. The upper guide portion 243 is formed from the front side surface of the circumferential portion 241 to the lower side surface (surface facing downward) of the upper projection portion 242. The lower guide portion 243 is formed in a substantially arc shape in a side view so as to extend downward as it goes forward. The lower guide portion 243 is formed from the front side surface of the circumferential portion 241 to the upper side surface (surface facing upward) of the lower projection portion 242. The upper and lower guide portions 243 are spaced apart from each other in the vertical direction, and are formed so as to expand in the circumferential direction of the circumferential portion 241 (the seal ring 240) toward the front direction.
　合口２４４は、上側の突出部２４２と下側の突出部２４２との間に形成される。 The joint 244 is formed between the upper protrusion 242 and the lower protrusion 242.
　シールリング２４０は、シールリング溝２３１に嵌め合わされる。具体的には、シールリング２４０の円周部２４１は、シールリング溝２３１の細溝２３１ａに嵌め合わされる。これにより、円周部２４１は、その外周面がバルブ２３０の外周面から径方向外側に突出する。シールリング２４０は、円周部２４１が細溝２３１ａの側壁に支持されることによって、バルブ２３０と一体的に回動すると共にバルブ２３０の厚み方向への相対移動が規制される。シールリング２４０の右端部（円周部２４１の両端部、突出部２４２、案内部２４３及び合口２４４）は、太溝２３１ｂに配置される。また、突出部２４２は、細溝２３１ａと太溝２３１ｂとの段差部分（図１５に示す符号Ａ参照）に対して間隔を空けて配置される。 The seal ring 240 is fitted in the seal ring groove 231. Specifically, the circumferential portion 241 of the seal ring 240 is fitted into the narrow groove 231 a of the seal ring groove 231. Thereby, the outer peripheral surface of the circumferential portion 241 protrudes radially outward from the outer peripheral surface of the valve 230. The seal ring 240 is rotated integrally with the valve 230 and the relative movement in the thickness direction of the valve 230 is restricted by the circumferential portion 241 being supported by the side wall of the narrow groove 231a. The right end portion of the seal ring 240 (both ends of the circumferential portion 241, the protruding portion 242, the guide portion 243, and the joint 244) is disposed in the thick groove 231 b. Moreover, the protrusion part 242 is arrange | positioned at intervals with respect to the level | step-difference part (refer code | symbol A shown in FIG. 15) of the narrow groove 231a and the thick groove 231b.
　第三実施形態に係るシールリング２４０は、所定の方向に延びるように形成された長手部材を曲げることで製造される。具体的には、弾性を有する材料で形成された線材を所定の長さに切断する工程を行うことで、前記長手部材を準備する。そして、当該長手部材を略円状に曲げる工程を行うことで、円周部２４１を形成する。その後、円周部２４１を形成した長手部材の両端部を後方向に曲げる工程を行うことで、突出部２４２及び案内部２４３を形成する。以上によって、シールリング２４０は製造される。これによれば、長手部材を曲げるだけで案内部２４３を形成することができる。このため、面取り加工等を施すことなく、シールリング２４０を簡単に製造することができる。 The seal ring 240 according to the third embodiment is manufactured by bending a longitudinal member formed so as to extend in a predetermined direction. Specifically, the longitudinal member is prepared by performing a step of cutting a wire formed of a material having elasticity into a predetermined length. And the circumferential part 241 is formed by performing the process of bending the said longitudinal member in a substantially circular shape. Then, the protrusion part 242 and the guide part 243 are formed by performing the process of bending the both ends of the longitudinal member which formed the circumferential part 241 back. Thus, the seal ring 240 is manufactured. According to this, the guide part 243 can be formed only by bending the longitudinal member. For this reason, the seal ring 240 can be easily manufactured without chamfering.
　ノッチピン２６０は、その外径が合口２４４（上側及び下側の突出部２４２の間）の上下方向に沿った距離よりも大きくなるように形成される。また、ノッチピン２６０は、その外径がシールリング溝２３１の太溝２３１ｂの上下方向に沿った距離よりも小さくなるように形成される。 The notch pin 260 is formed so that its outer diameter is larger than the distance along the vertical direction of the joint 244 (between the upper and lower protrusions 242). The notch pin 260 is formed so that the outer diameter thereof is smaller than the distance along the vertical direction of the thick groove 231b of the seal ring groove 231.
　ノッチピン２６０は、シールリング溝２３１の太溝２３１ｂ及びシールリング２４０の合口２４４に対してシート２０の周方向における位置を合わせて配置される。ノッチピン２６０は、その左端部がシート２０の内周面（流路２１の側壁）から左方向に突出する。当該ノッチピン２６０の突出部分は、全閉位置まで回動したバルブ２３０の太溝２３１ｂの底面からシート２０の内周面までの径方向に沿った距離に対応する幅だけシート２０から突出している（図２０参照）。ノッチピン２６０は、バルブ２３０が全閉位置まで回動するときに太溝２３１ｂに入り込むことで、バルブ２３０と衝突しないように構成される。 The notch pin 260 is disposed so that the position in the circumferential direction of the sheet 20 is aligned with the thick groove 231 b of the seal ring groove 231 and the joint 244 of the seal ring 240. The left end of the notch pin 260 protrudes leftward from the inner peripheral surface of the sheet 20 (side wall of the flow path 21). The protruding portion of the notch pin 260 protrudes from the seat 20 by a width corresponding to the radial distance from the bottom surface of the thick groove 231b of the valve 230 rotated to the fully closed position to the inner peripheral surface of the seat 20 ( FIG. 20). The notch pin 260 is configured not to collide with the valve 230 by entering the thick groove 231b when the valve 230 rotates to the fully closed position.
　次に、図１４、図１５、図１７から図２０までを参照してバルブ装置２１０の閉塞動作について説明する。なお、図１７及び図１８（ａ）に白塗りで示す矢印は、バルブ２３０の回動方向を示している。また、図１８に黒塗りで示す矢印は、シールリング２４０に作用する荷重の方向を示している。また、図１９に黒塗りで示す矢印は、シールリング２４０が弾性変形する様子を示している。 Next, the closing operation of the valve device 210 will be described with reference to FIGS. 14, 15 and 17 to 20. Note that the white arrows in FIG. 17 and FIG. 18A indicate the rotation direction of the valve 230. Further, the arrows shown in black in FIG. 18 indicate the direction of the load acting on the seal ring 240. Further, the arrows shown in black in FIG. 19 indicate that the seal ring 240 is elastically deformed.
　まず、図１４及び図１５に示すバルブ装置２１０は、前記駆動源からシャフト５０に動力を伝達することで、図１４に示す矢印方向にバルブ２３０及びシールリング２４０を回動させる。このとき、図１４及び図１７に示すように、シールリング２４０の右端部（円周部２４１の両端部、突出部２４２、案内部２４３及び合口２４４）は、ノッチピン２６０に接近する。 First, the valve device 210 shown in FIGS. 14 and 15 transmits the power from the drive source to the shaft 50, thereby rotating the valve 230 and the seal ring 240 in the direction of the arrow shown in FIG. At this time, as shown in FIGS. 14 and 17, the right end of the seal ring 240 (both ends of the circumferential portion 241, the projecting portion 242, the guide portion 243, and the joint 244) approach the notch pin 260.
　図１８に示すように、全閉位置の直前までバルブ２３０が回動すると、ノッチピン２６０は、シールリング溝２３１の太溝２３１ｂに入り込む。このとき、シールリング２４０の合口２４４は、ノッチピン２６０を通過しようとする。前述の如く、ノッチピン２６０は、その外径が合口２４４の上下方向に沿った距離よりも大きい。このため、ノッチピン２６０は、合口２４４に入り込もうとして案内部２４３と当接する。このとき、ノッチピン２６０は、その左端部から左右中途部までが、案内部２４３の左端部から右端部までに亘って当接する。 As shown in FIG. 18, when the valve 230 rotates just before the fully closed position, the notch pin 260 enters the thick groove 231 b of the seal ring groove 231. At this time, the joint 244 of the seal ring 240 tends to pass through the notch pin 260. As described above, the outer diameter of the notch pin 260 is larger than the distance along the vertical direction of the joint 244. For this reason, the notch pin 260 comes into contact with the guide portion 243 in an attempt to enter the joint 244. At this time, the notch pin 260 abuts from the left end portion to the left and right midway portion from the left end portion to the right end portion of the guide portion 243.
　図１９及び図２０に示すように、シールリング２４０の案内部２４３とノッチピン２６０とが当接した状態からさらにバルブ２３０が回動すると、ノッチピン２６０は、案内部２４３に対して後方向に滑らかに摺動しながら、前方から後方に向かって合口２４４に入り込む。これによって、ノッチピン２６０は、案内部２４３に案内されながら合口２４４を押し広げ、シールリング２４０を均一に拡径させる。 As shown in FIGS. 19 and 20, when the valve 230 further rotates from the state where the guide portion 243 of the seal ring 240 and the notch pin 260 are in contact with each other, the notch pin 260 is smoothly moved backward with respect to the guide portion 243. While sliding, it enters the joint 244 from the front to the rear. As a result, the notch pin 260 pushes and widens the joint 244 while being guided by the guide portion 243, thereby expanding the diameter of the seal ring 240 uniformly.
　図１９及び図２０に示す全閉位置までバルブ２３０が回動すると、ノッチピン２６０は、その軸心がシールリング２４０の円周部２４１の前後中央部に配置されるまで合口２４４に入り込む。このとき、ノッチピン２６０は、その後上部及び後下部が案内部２４３と当接する。これによって、シールリング２４０（円周部２４１）は、合口２４４が押し広げられた幅に応じた長さだけ拡径され、その外周面の全域がシート２０の内周面（流路２１の壁面）に密着する。これにより、バルブ２３０が流路２１を閉塞したときに、バルブ２３０の外周面とシート２０の内周面との隙間をシールリング２４０でシールすることができる。 19 and FIG. 20, when the valve 230 is rotated to the fully closed position, the notch pin 260 enters the joint 244 until the axial center thereof is disposed at the front and rear central portions of the circumferential portion 241 of the seal ring 240. At this time, the upper and rear lower portions of the notch pin 260 come into contact with the guide portion 243. Accordingly, the diameter of the seal ring 240 (circumferential portion 241) is increased by a length corresponding to the width of the abutment 244 expanded, and the entire outer peripheral surface thereof is the inner peripheral surface of the sheet 20 (the wall surface of the flow path 21). ). Thereby, when the valve 230 closes the flow path 21, the gap between the outer peripheral surface of the valve 230 and the inner peripheral surface of the seat 20 can be sealed with the seal ring 240.
　以上のように、第三実施形態に係るシールリング２４０は、案内部２４３によってノッチピン２６０の入り込みを案内することで、図３２に示す一般的なシールリング１９４０（突出部２４２及び案内部２４３が形成されていないシールリング）よりも、ノッチピン２６０が合口２４４に入り込むことによって生じる摩耗を抑制することができる。以下では、一般的なシールリング１９４０を拡径させる場合の動作について図３２を参照して簡単に説明する。なお、図３２に白塗りで示す矢印は、バルブ２３０の回動方向を示している。また、図３２に黒塗りで示す矢印は、シールリング１９４０に作用する荷重の方向を示している。 As described above, the seal ring 240 according to the third embodiment guides the entry of the notch pin 260 by the guide portion 243, so that the general seal ring 1940 (projection portion 242 and guide portion 243 are formed) shown in FIG. The wear caused by the notch pin 260 entering the joint 244 can be suppressed more than the seal ring that is not provided. Hereinafter, an operation for expanding the diameter of a general seal ring 1940 will be briefly described with reference to FIG. Note that arrows shown in white in FIG. 32 indicate the rotation direction of the valve 230. Also, the arrows shown in black in FIG. 32 indicate the direction of the load acting on the seal ring 1940.
　一般的なシールリング１９４０をノッチピン２６０で拡径させる場合、シールリング１９４０の角部（合口１９４４の前上端部及び前下端部）とノッチピン２６０とが当接し、シールリング１９４０に対して概ね後方向への荷重が作用することとなる。このため、シールリング１９４０は、その両端部が後方向に曲げられるような荷重を受けることとなる。 When the diameter of the general seal ring 1940 is expanded by the notch pin 260, the corners of the seal ring 1940 (the front upper end portion and the front lower end portion of the joint 1944) are in contact with the notch pin 260, and generally in the backward direction with respect to the seal ring 1940. The load on will act. For this reason, the seal ring 1940 receives a load such that both ends thereof are bent backward.
　この場合、ノッチピン２６０は、シールリング１９４０に対して大きな荷重を作用させなければシールリング１９４０を拡径させることができない。このため、シールリング１９４０は、ノッチピン２６０から受ける荷重が大きくなってその角部が摩耗してしまう。当該角部の摩耗の仕方によってはノッチピン２６０が合口１９４４に入り難くなるおそれがある。 In this case, the notch pin 260 cannot expand the diameter of the seal ring 1940 unless a large load is applied to the seal ring 1940. For this reason, the seal ring 1940 receives a large load from the notch pin 260 and wears its corners. Depending on how the corners are worn, the notch pin 260 may not easily enter the joint 1944.
　これに対して、第三実施形態に係るシールリング２４０は、ノッチピン２６０で拡径されるときに、側面視略円弧状の案内部２４３をノッチピン２６０に当接させることができる。これによれば、図１８に示すように、上側の案内部２４３は、ノッチピン２６０から後上方向への荷重を受けることができる。また、下側の案内部２４３は、ノッチピン２６０から後下方向への荷重を受けることができる。以上によれば、シールリング２４０は、ノッチピン２６０から拡径される（合口２４４が押し広げられる）ような荷重を受けることができる。 In contrast, when the diameter of the seal ring 240 according to the third embodiment is increased by the notch pin 260, the guide part 243 having a substantially arc shape in a side view can be brought into contact with the notch pin 260. According to this, as shown in FIG. 18, the upper guide portion 243 can receive a load in the rear upper direction from the notch pin 260. Further, the lower guide portion 243 can receive a load in the rear lower direction from the notch pin 260. According to the above, the seal ring 240 can receive a load that is expanded from the notch pin 260 (the joint 244 is pushed and expanded).
　これにより、ノッチピン２６０は、小さい力でシールリング２４０を拡径させることができる。このため、シールリング２４０は、ノッチピン２６０から受ける荷重が小さくなって案内部２４３の摩耗を効果的に抑制することができる。これによれば、ノッチピン２６０が案内部２４３に引っかかることを抑制できるため、ノッチピン２６０を合口２４４に確実に入り込ませることができる。従って、動作不良（シール不良）が発生することなく、シート２０及びシールリング２４０（円周部２４１）の摩耗抑制を実現することができる。また、ノッチピン２６０の摩耗を抑制することができる。 Thereby, the notch pin 260 can expand the diameter of the seal ring 240 with a small force. For this reason, the seal ring 240 can reduce the load received from the notch pin 260 and effectively suppress wear of the guide portion 243. According to this, since the notch pin 260 can be prevented from being caught by the guide portion 243, the notch pin 260 can be surely inserted into the joint 244. Therefore, it is possible to suppress wear of the seat 20 and the seal ring 240 (circumferential portion 241) without causing malfunction (seal failure). Further, wear of the notch pin 260 can be suppressed.
　また、図３２に示す一般的なシールリング１９４０は、ノッチピン２６０で拡径されるときに、その角部がノッチピン２６０に対して接触する。これに対して、第三実施形態に係るシールリング２４０は、図１８に示すように、側面視略円弧状（曲面状）の案内部２４３をノッチピン２６０に対して接触させることができる。このため、第三実施形態に係るシールリング２４０は、一般的なシールリング１９４０よりもノッチピン２６０との接触による摩耗を低減することができる。 32, when the diameter of the general seal ring 1940 shown in FIG. 32 is expanded by the notch pin 260, the corner portion thereof contacts the notch pin 260. On the other hand, as shown in FIG. 18, the seal ring 240 according to the third embodiment can bring the guide portion 243 having a substantially arc shape (curved surface) in a side view into contact with the notch pin 260. For this reason, the seal ring 240 according to the third embodiment can reduce wear due to contact with the notch pin 260 more than a general seal ring 1940.
　また、第三実施形態に係るノッチピン２６０は、バルブ２３０が全閉位置まで回動するときに、シールリング溝２３１の太溝２３１ｂに入り込むようにしている。これによれば、ノッチピン２６０は、案内部２４３の左端部から右端部までに亘って当接可能となる。これにより、ノッチピン２６０とシールリング２４０との当接範囲を広くすることができるため、ノッチピン２６０をシールリング２４０の合口２４４に入り込ませ易くすることができる。 In addition, the notch pin 260 according to the third embodiment enters the thick groove 231b of the seal ring groove 231 when the valve 230 rotates to the fully closed position. According to this, the notch pin 260 can contact from the left end portion of the guide portion 243 to the right end portion. Thereby, since the contact range of the notch pin 260 and the seal ring 240 can be widened, the notch pin 260 can be easily inserted into the joint 244 of the seal ring 240.
　以上の如く、第三実施形態に係るバルブ装置２１０において、前記シールリング２４０は、両端部を突き合わせて形成されている合口２４４を具備し、ノッチピン２６０（拡径手段）は、前記合口２４４に入り込んで前記合口２４４を押し広げることで前記シールリング２４０を拡径させ、前記シールリング２４０は、前記ノッチピン２６０の前記合口２４４への入り込みを案内する案内部２４３をさらに具備するものである。 As described above, in the valve device 210 according to the third embodiment, the seal ring 240 includes the abutment 244 formed by abutting both end portions, and the notch pin 260 (diameter expanding means) enters the abutment 244. Then, the diameter of the seal ring 240 is increased by pushing the joint 244 wide, and the seal ring 240 further includes a guide portion 243 for guiding the notch pin 260 to enter the joint 244.
　このように構成することにより、シート２０とシールリング２４０とが摺動することによって生じるシート２０及びシールリング２４０（円周部２４１）の摩耗を抑制することができる。
　また、拡径によって生じる案内部２４３の摩耗を抑制することができる。 By comprising in this way, abrasion of the sheet | seat 20 and the seal ring 240 (circumferential part 241) which arises when the sheet | seat 20 and the seal ring 240 slide can be suppressed.
Further, wear of the guide portion 243 caused by the diameter expansion can be suppressed.
　また、前記案内部２４３は、前側（前記ノッチピン２６０の受け入れ側）に向かうにつれて徐々に前記シールリング２４０の周方向に広がるように形成されるものである。 The guide portion 243 is formed so as to gradually spread in the circumferential direction of the seal ring 240 toward the front side (receiving side of the notch pin 260).
　このように構成することにより、シールリング２４０は、ノッチピン２６０から拡径されるような荷重を受けることができる。これにより、シールリング２４０（案内部２４３）の摩耗を抑制することができる。 With this configuration, the seal ring 240 can receive a load that is expanded from the notch pin 260. Thereby, abrasion of the seal ring 240 (guide part 243) can be suppressed.
　また、前記案内部２４３は、曲面状に形成される。 Further, the guide part 243 is formed in a curved surface shape.
　このように構成することにより、シールリング２４０の角部ではなく、曲面をノッチピン２６０に対して接触させることができる。また、ノッチピン２６０を案内部２４３に対して滑らかに摺動させることができる。このため、シールリング２４０（案内部２４３）の摩耗を抑制することができる。 With this configuration, the curved surface, not the corner of the seal ring 240, can be brought into contact with the notch pin 260. Further, the notch pin 260 can be smoothly slid with respect to the guide portion 243. For this reason, abrasion of the seal ring 240 (guide part 243) can be suppressed.
　また、前記シールリング２４０は、周方向に沿って延びる円周部２４１と、前記円周部２４１の端部から後方向（前記ノッチピン２６０が前記合口２４４に入り込む方向）に突出する突出部２４２と、をさらに具備し、前記案内部２４３は、前記円周部２４１と前記突出部２４２との接続部分に形成されるものである。 The seal ring 240 includes a circumferential portion 241 extending along a circumferential direction, and a projecting portion 242 projecting rearward from the end portion of the circumferential portion 241 (a direction in which the notch pin 260 enters the joint 244). The guide portion 243 is formed at a connection portion between the circumferential portion 241 and the protruding portion 242.
　このように構成することにより、シールリング２４０（案内部２４３）の摩耗を効果的に抑制することができる。具体的には、シールリング２４０は、突出部２４２を具備することで、後述するような両端面を切り欠いた案内部（図２９に示す第七変形例及び第八変形例に係る案内部９４３・１０４３参照）よりも、案内部２４３の前後方向幅を広くすることができる。これにより、案内部２４３の周方向への広がり具合を緩やかなものにすることができる。これによれば、ノッチピン２６０を案内部２４３に対してより滑らかに摺動させることができるため、案内部２４３の摩耗を効果的に低減することができる。 With this configuration, wear of the seal ring 240 (guide portion 243) can be effectively suppressed. Specifically, the seal ring 240 includes a projecting portion 242, so that guide portions 943 according to the seventh and eighth modifications shown in FIG. The width in the front-rear direction of the guide portion 243 can be made wider than (see 1043). Thereby, the spreading | diffusion condition to the circumferential direction of the guide part 243 can be made loose. According to this, since the notch pin 260 can be slid more smoothly with respect to the guide part 243, wear of the guide part 243 can be effectively reduced.
　また、前記バルブ２３０は、前記円周部２４１を嵌め合わせるための細溝２３１ａと、前記細溝２３１ａと連通すると共に前記細溝２３１ａの幅よりも広い幅を有し、前記突出部２４２を配置するための太溝２３１ｂと、を具備するものである。 In addition, the valve 230 has a narrow groove 231a for fitting the circumferential portion 241 and a width wider than the narrow groove 231a while communicating with the narrow groove 231a, and the protruding portion 242 is disposed. And a thick groove 231b.
　このように構成することにより、動作不良の発生を抑制することができる。具体的には、シールリング２４０がバルブ２３０に対して相対回転したときに、細溝２３１ａと太溝２３１ｂとの段差部分（図１５（ａ）に示す符号Ａ参照）に突出部２４２を当接させることができる。これにより、シールリング２４０のバルブ２３０に対する相対回転を一定量に留めることができるため、ノッチピン２６０を合口２４４の内側に確実に入り込ませることができる。これによって、シールリング２４０を確実に拡径させることができるため、シールリング２４０のバルブ２３０に対する相対回転に起因する動作不良（シール不良）の発生を抑制できる。
　また、シールリング２４０のバルブ２３０に対する相対回転を規制するための部材（例えば、合口２４４の内側に配置される軸状部材）を設ける必要がなくなるため、部品点数を減らしてコストを低減することができる。 With this configuration, it is possible to suppress the occurrence of malfunction. Specifically, when the seal ring 240 rotates relative to the valve 230, the projecting portion 242 comes into contact with the step portion (see reference numeral A shown in FIG. 15A) between the narrow groove 231a and the thick groove 231b. Can be made. As a result, the relative rotation of the seal ring 240 with respect to the valve 230 can be kept at a constant amount, so that the notch pin 260 can surely enter inside the joint 244. As a result, the diameter of the seal ring 240 can be surely increased, so that the occurrence of malfunction (seal failure) due to relative rotation of the seal ring 240 with respect to the valve 230 can be suppressed.
Further, since it is not necessary to provide a member for regulating the relative rotation of the seal ring 240 with respect to the valve 230 (for example, a shaft-like member disposed inside the joint 244), the number of parts can be reduced and the cost can be reduced. it can.
　なお、第三実施形態に係るノッチピン２６０は、本発明に係る拡径手段の実施の一形態である。
　第三実施形態における後方向は、本発明に係る拡径手段が合口に入り込む方向に対応する。 In addition, the notch pin 260 which concerns on 3rd embodiment is one Embodiment of the diameter expansion means which concerns on this invention.
The rear direction in the third embodiment corresponds to the direction in which the diameter expanding means according to the present invention enters the joint.
　以上、本発明の実施形態を説明したが、本発明は上記構成に限定されるものではなく、特許請求の範囲に記載された発明の範囲内で種々の変更が可能である。 As mentioned above, although embodiment of this invention was described, this invention is not limited to the said structure, A various change is possible within the range of the invention described in the claim.
　例えば、バルブ装置１０・１１０・２１０は、ＥＧＲ装置に設けられるものとしたが、バルブ装置１０・１１０・２１０の適用対象は、これに限定されるものではない。 For example, the valve devices 10, 110, and 210 are provided in the EGR device, but the application target of the valve devices 10, 110, and 210 is not limited thereto.
　また、流路２１には、排気ガスが流通するものとしたが、流路２１を流通する流体は、排気ガスに限定されるものではなく、例えば、圧縮空気等であってもよい。また、流路２１を流通する流体は、気体に限定されるものではなく、例えば、水等の液体であってもよい。 In addition, although the exhaust gas is assumed to flow through the flow path 21, the fluid flowing through the flow path 21 is not limited to the exhaust gas, and may be, for example, compressed air. Moreover, the fluid which distribute | circulates the flow path 21 is not limited to gas, For example, liquids, such as water, may be sufficient.
　また、第一実施形態においては、合口４１を押し広げることでシールリング４０を拡径させるものとしたが、必ずしも合口４１を押し広げてシールリング４０を拡径させる必要はない。例えば、拡径可能な軸部材や圧縮空気等によってシールリング溝３１から径方向外側にシールリング４０の内周面を押し出すことでシールリング４０を拡径させてもよい。 In the first embodiment, the diameter of the seal ring 40 is increased by expanding the joint 41, but it is not always necessary to expand the diameter of the seal ring 40 by expanding the joint 41. For example, the diameter of the seal ring 40 may be increased by pushing the inner peripheral surface of the seal ring 40 radially outward from the seal ring groove 31 with a shaft member capable of expanding the diameter, compressed air, or the like.
　また、必ずしもノッチピン６０を合口４１に入り込ませる必要はなく、例えば、合口４１に圧縮空気等を噴き付けることによって合口４１を押し広げてもよい。 Further, the notch pin 60 does not necessarily enter the abutment 41. For example, the abutment 41 may be expanded by spraying compressed air or the like onto the abutment 41.
　また、第一実施形態に係るノッチピン６０は、シート２０に固定されるものとしたが、これに限定されるものではなく、シート２０に相対移動可能に支持されていてもよい。このような場合において、ノッチピン６０は、例えば、図２１（ａ）に示す第一変形例に係るバルブ装置３１０のノッチピン３６０のような構成とすることも可能である。 Further, the notch pin 60 according to the first embodiment is fixed to the sheet 20, but is not limited thereto, and may be supported by the sheet 20 so as to be relatively movable. In such a case, for example, the notch pin 60 can be configured like the notch pin 360 of the valve device 310 according to the first modification shown in FIG.
　第一変形例に係るノッチピン３６０は、駆動源によって左右方向に移動自在にシート２０の支持孔２２に支持される。図２１に示すように、ノッチピン３６０は、バルブ３０が全閉位置まで回動した後で、左方に移動されて合口４１に入り込み、合口４１を押し広げてシールリング４０を拡径させる。また、ノッチピン３６０は、流路２１を開放するときに、右方向に移動されて合口４１から出て行く。その後、バルブ３０は回動される。このように構成することで、シート２０とシールリング４０とが摺動しないようにすることができるため、シート２０及びシールリング４０の摩耗を効果的に抑制することができる。
　このような第一変形例に係るバルブ装置３１０は、バルブ３０の回動に連動する機構によってノッチピン３６０を左右方向に移動させてもよい。 The notch pin 360 according to the first modification is supported by the support hole 22 of the seat 20 so as to be movable in the left-right direction by a drive source. As shown in FIG. 21, the notch pin 360 is moved to the left after the valve 30 is rotated to the fully closed position, enters the joint 41, and widens the seal ring 40 by expanding the joint 41. Further, the notch pin 360 moves rightward and exits from the joint 41 when opening the flow path 21. Thereafter, the valve 30 is rotated. By comprising in this way, since it can prevent that the sheet | seat 20 and the seal ring 40 slide, the abrasion of the sheet | seat 20 and the seal ring 40 can be suppressed effectively.
The valve device 310 according to the first modification may move the notch pin 360 in the left-right direction by a mechanism that is interlocked with the rotation of the valve 30.
　また、ノッチピン６０・１６０は、バルブ３０・１３０が全閉位置まで回動したときに、その軸心が合口４１・１４１の前後中央部に配置されるものとしたが、これに限定されるものではない。ノッチピン６０・１６０は、例えば、バルブ３０・１３０が全閉位置まで回動したときに、その軸心が合口４１・１４１の前部（前後中央部よりも前方）に配置されるものであってもよい。このような場合において、ノッチピン６０・１６０は、シールリング４０・１４０の両端面ではなく、角部（合口４１・１４１の前上端部及び前下端部）と当接していてもよい。 In addition, when the valves 30 and 130 are rotated to the fully closed position, the shaft centers of the notch pins 60 and 160 are arranged at the front and rear center portions of the joints 41 and 141. However, the notch pins 60 and 160 are not limited thereto. is not. The notch pins 60 and 160 are arranged such that, for example, when the valves 30 and 130 are rotated to the fully closed position, the axial centers thereof are arranged in front of the joints 41 and 141 (in front of the front and rear central portions). Also good. In such a case, the notch pins 60 and 160 may be in contact with the corner portions (the front upper end portion and the front lower end portion of the joints 41 and 141) instead of the both end faces of the seal rings 40 and 140.
　また、ノッチピン６０・１６０・２６０は、シート２０とは異なる部材によって構成されるものとしたが、これに限定されるものではなく、シート２０と一体的に形成されるものであってもよい。 Further, although the notch pins 60, 160, and 260 are configured by members different from the sheet 20, the present invention is not limited thereto, and may be formed integrally with the sheet 20.
　また、ノッチピン６０・１６０・２６０が固定される部材は、シート２０に限定されるものではなく、他の部材に固定されていてもよい。 Further, the member to which the notch pins 60, 160, and 260 are fixed is not limited to the sheet 20, and may be fixed to other members.
　また、シールリング４０・１４０・２４０は、径方向内側への張力が作用するものとしたが、これに限定されるものではなく、例えば、張力が作用しないものであってもよい。 Further, although the seal rings 40, 140, and 240 are assumed to be subjected to the radially inward tension, the seal rings 40, 140, and 240 are not limited thereto, and may be, for example, those that do not receive the tension.
　また、第一実施形態に係るシールリング４０は、合口４１の有無を問わない。シールリング４０は、例えば、合口４１を具備しないもの、すなわち円環状のゴム等の弾性部材によって構成されるものであってもよい。 Moreover, the seal ring 40 according to the first embodiment does not matter whether or not the joint 41 is present. For example, the seal ring 40 may not be provided with the joint 41, that is, may be constituted by an elastic member such as an annular rubber.
　また、シールリング４０・１４０・２４０の外径は、シート２０の内径よりも小さくなるように形成されるものとしたが、これに限定されるものではなく、シート２０の内径と略同一の大きさとなるように形成されていてもよい。この場合、シールリング４０・１４０・２４０は、ノッチピン６０・１６０・２６０による拡径前の状態において、拡径時よりも弱い力でシート２０と接触することになるため、シート２０との摺動による摩耗を抑制することができる。 Further, the outer diameters of the seal rings 40, 140, and 240 are formed so as to be smaller than the inner diameter of the sheet 20. However, the outer diameter is not limited to this, and is approximately the same as the inner diameter of the sheet 20. It may be formed as follows. In this case, since the seal rings 40, 140, and 240 come into contact with the sheet 20 with a weaker force than that at the time of diameter expansion before the diameter is expanded by the notch pins 60, 160, and 260, sliding with the sheet 20 occurs. Wear due to can be suppressed.
　また、合口４１・１４１・２４４は、バルブ３０・１３０・２３０の右端部に配置されるものとしたが、合口４１・１４１・２４４のバルブ３０・１３０・２３０に対する位置は、これに限定されるものではない。合口４１・１４１・２４４は、例えば、バルブ３０・１３０・２３０の左端部に配置されるものであってもよい。このような場合においても、合口４１・１４１・２４４をバルブ３０・１３０・２３０の回動軸線に対して最も離れた位置に配置することができる。 The joints 41, 141, and 244 are arranged at the right end of the valves 30, 130, and 230. However, the positions of the joints 41, 141, and 244 with respect to the valves 30, 130, and 230 are limited to this. It is not a thing. The joints 41, 141, and 244 may be arranged at the left end of the valves 30, 130, and 230, for example. Even in such a case, the joints 41, 141, and 244 can be arranged at positions farthest from the rotation axis of the valves 30, 130, and 230.
　また、合口４１・１４１・２４４は、必ずしもバルブ３０・１３０・２３０の回動軸線に対して最も離れた位置に配置する必要はない。合口４１・１４１・２４４は、バルブ３０・１３０・２３０の回動途中でノッチピン６０・１６０・２６０が出入りする程度に、バルブ３０・１３０・２３０の回動軸線に対して離れた位置に配置されていればよい。合口４１・１４１・２４４は、例えば、バルブ３０・１３０・２３０の左下部、左上部、右下部及び右上部等に配置されていてもよい。このような合口４１・１４１・２４４が配置される位置は、「バルブの回動軸線に対して離れた位置」に含まれる。 Further, the joints 41, 141, and 244 are not necessarily arranged at positions farthest from the rotation axis of the valves 30, 130, and 230. The joints 41, 141, and 244 are arranged at positions separated from the rotation axis of the valves 30, 130, and 230 so that the notch pins 60, 160, and 260 are moved in and out during the rotation of the valves 30, 130, and 230. It only has to be. The joints 41, 141, and 244 may be disposed, for example, in the lower left part, upper left part, lower right part, and upper right part of the valves 30, 130, and 230. The positions at which the joints 41, 141, and 244 are arranged are included in “positions away from the rotation axis of the valve”.
　また、バルブ３０・１３０・２３０は、図１、図７及び図１４に示す矢印方向に回動することで流路２１を閉塞するものとしたが、バルブ３０・１３０・２３０の回動方向は、これに限定されるものではない。バルブ３０・１３０・２３０は、例えば、図１、図７及び図１４に示す矢印方向とは反対方向に回動することで流路２１を閉塞してもよい。 In addition, the valves 30, 130, and 230 close the flow path 21 by rotating in the arrow directions shown in FIGS. 1, 7, and 14, but the rotation direction of the valves 30, 130, and 230 is However, the present invention is not limited to this. For example, the valves 30, 130, and 230 may close the flow path 21 by rotating in a direction opposite to the arrow direction shown in FIGS. 1, 7, and 14.
　また、バルブ３０の構成は、第一実施形態に限定されるものではなく、例えば、図２２及び図２３に示す第二変形例に係るバルブ装置４１０のバルブ４３０のような構成とすることも可能である。 Further, the configuration of the valve 30 is not limited to the first embodiment, and for example, a configuration like the valve 430 of the valve device 410 according to the second modification shown in FIGS. 22 and 23 may be employed. It is.
　第二変形例に係るバルブ４３０は、シールリング溝４３１及び溝部４３２を具備する。シールリング溝４３１は、バルブ４３０の右端部を除いてバルブ４３０の外周面の全域に亘って形成される。溝部４３２は、バルブ４３０の右端部に形成され、シールリング溝４３１と連通する。溝部４３２は、バルブ４３０の前側面から後側面に亘って形成される。溝部４３２の内側には、シールリング４０の合口４１が配置される。また、図２３に示すように、第二変形例に係るノッチピン４６０は、第一実施形態に係るノッチピン６０よりも、その長さ（軸線方向幅）が溝部４３２の深さだけ長くなるように形成される。
　このように構成することで、バルブ４３０の回動時にノッチピン４６０をバルブ４３０の溝部４３２に入り込ませることができ、ノッチピン４６０を合口４１の左端部から右端部までに亘って当接させることが可能となる。これによれば、ノッチピン４６０とシールリング４０との当接範囲を広くすることができ、ノッチピン４６０をシールリング４０の合口４１に入り込ませ易くすることができる。 The valve 430 according to the second modification includes a seal ring groove 431 and a groove portion 432. The seal ring groove 431 is formed over the entire outer peripheral surface of the valve 430 except for the right end portion of the valve 430. Groove 432 is formed at the right end of valve 430 and communicates with seal ring groove 431. The groove 432 is formed from the front side surface to the rear side surface of the valve 430. An abutment 41 of the seal ring 40 is disposed inside the groove portion 432. Further, as shown in FIG. 23, the notch pin 460 according to the second modification is formed such that its length (width in the axial direction) is longer by the depth of the groove portion 432 than the notch pin 60 according to the first embodiment. Is done.
With this configuration, the notch pin 460 can be inserted into the groove 432 of the valve 430 when the valve 430 is rotated, and the notch pin 460 can be abutted from the left end to the right end of the joint 41. It becomes. According to this, the contact range of the notch pin 460 and the seal ring 40 can be widened, and the notch pin 460 can be easily inserted into the joint 41 of the seal ring 40.
　また、第二実施形態に係る回り止めピン１６０の形状は、略円柱状であるものとしたが、これに限定されるものではなく、例えば、略直方体状や略円筒状等であってもよい。 Moreover, although the shape of the rotation prevention pin 160 which concerns on 2nd embodiment shall be a substantially cylindrical shape, it is not limited to this, For example, a substantially rectangular parallelepiped shape, a substantially cylindrical shape, etc. may be sufficient. .
　また、第二実施形態に係る回り止めピン１６０は、バルブ１３０とは異なる部材によって構成されるものとしたが、これに限定されるものではなく、バルブ１３０と一体的に形成されるものであってもよい。 In addition, the detent pin 160 according to the second embodiment is configured by a member different from the valve 130, but is not limited thereto, and is formed integrally with the valve 130. May be.
　また、第二実施形態に係る回り止めピン１６０は、ノッチピン１７０の端面１７１ａと接触しないものであってもよい。これによって、回り止めピン１６０及びノッチピン１７０をより破損し難くすることができる。 Further, the detent pin 160 according to the second embodiment may not be in contact with the end surface 171a of the notch pin 170. Thereby, the rotation prevention pin 160 and the notch pin 170 can be made more difficult to break.
　また、第二実施形態に係る収容部１７１は、ノッチピン１７０の後端部から前後中央部に亘って形成されるものとしたが、これに限定されるものではなく、例えば、図２４に示す第三変形例に係るノッチピン５７０の収容部５７１のような形状とすることも可能である。第三変形例に係る収容部５７１は、ノッチピン５７０の後端部から前端部に亘って形成される。すなわち、収容部５７１は、ノッチピン５７０を前後に貫通するように形成される。これによれば、収容部５７１は、回り止めピン１６０を前後方向に通過させることができるため、後方向から回り止めピン１６０が勢い良く接触することを防止できる。このため、回り止めピン１６０及びノッチピン５７０を破損し難くすることができる。 Moreover, although the accommodating part 171 which concerns on 2nd embodiment shall be formed ranging from the rear-end part of the notch pin 170 to the front-back center part, it is not limited to this, For example, the 1st shown in FIG. It is also possible to make it the shape like the accommodating part 571 of the notch pin 570 which concerns on a 3rd modification. The accommodating portion 571 according to the third modification is formed from the rear end portion of the notch pin 570 to the front end portion. That is, the accommodating portion 571 is formed so as to penetrate the notch pin 570 in the front-rear direction. According to this, since the accommodating part 571 can let the rotation prevention pin 160 pass in the front-back direction, it can prevent that the rotation prevention pin 160 contacts vigorously from back direction. For this reason, the rotation prevention pin 160 and the notch pin 570 can be made difficult to be damaged.
　また、第二実施形態においては、収容部１７１が形成された一本のノッチピン１７０を具備するものとしたが、バルブ装置１１０が具備するノッチピン１７０の本数は、一本に限定されるものではない。バルブ装置１１０は、例えば、図２５に示す第四変形例に係る二本のノッチピン６７０を具備していてもよい。第四変形例に係るノッチピン６７０は、互いに上下に隙間を空けて配置される。上側のノッチピン６７０は、上に凸の側面視略半円状に形成される。下側のノッチピン６７０は、下に凸の側面視略半円状に形成される。上下のノッチピン６７０の間には、回り止めピン１６０が前後方向に通過可能な収容部６７１が形成される。このような構成においても、回り止めピン１６０を収容部６７１に入り込ませることができるため、回り止めピン１６０と上下のノッチピン６７０との衝突を回避することができる。 Further, in the second embodiment, the single notch pin 170 having the accommodating portion 171 is provided. However, the number of the notch pins 170 provided in the valve device 110 is not limited to one. . The valve device 110 may include, for example, two notch pins 670 according to the fourth modification shown in FIG. The notch pins 670 according to the fourth modification are arranged with a gap therebetween in the vertical direction. The upper notch pin 670 is formed in a substantially semicircular shape when viewed from the side. The lower notch pin 670 is formed in a substantially semicircular shape as viewed from the side that is convex downward. Between the upper and lower notch pins 670, a receiving portion 671 through which the detent pin 160 can pass in the front-rear direction is formed. Even in such a configuration, the anti-rotation pin 160 can be inserted into the housing portion 671, so that the collision between the anti-rotation pin 160 and the upper and lower notch pins 670 can be avoided.
　また、第二実施形態に係る収容部１７１の端面１７１ａの形状は、側面視略円弧状であるものとしたが、これに限定されるものではなく、例えば、側面視で直線状に形成されるものであってもよい。 Moreover, although the shape of the end surface 171a of the accommodating part 171 which concerns on 2nd embodiment shall be substantially circular arc shape by the side view, it is not limited to this, For example, it forms linearly by side view. It may be a thing.
　また、第二実施形態に係るノッチピン１７０は、シート２０に固定されるものとしたが、これに限定されるものではなく、シート２０に相対移動可能に支持されていてもよい。このような場合において、ノッチピン１７０は、例えば、図２６に示す第五変形例に係るバルブ装置７１０のノッチピン７７０のような構成とすることも可能である。 In addition, the notch pin 170 according to the second embodiment is fixed to the sheet 20, but is not limited thereto, and may be supported by the sheet 20 so as to be relatively movable. In such a case, the notch pin 170 can be configured as a notch pin 770 of the valve device 710 according to the fifth modification shown in FIG. 26, for example.
　第五変形例に係るノッチピン７７０は、駆動源によって左右方向に移動自在にシート２０の支持孔２２に支持される。ノッチピン７７０は、収容部７７１を具備する。収容部７７１は、ノッチピン７７０の左側面で開口し、右方向に延びるように形成される。収容部７７１は、その内径が回り止めピン１６０の外径よりも大きな側面視略円状に形成される。 The notch pin 770 according to the fifth modification is supported by the support hole 22 of the seat 20 so as to be movable in the left-right direction by a drive source. The notch pin 770 includes a housing portion 771. The accommodating portion 771 is formed to open on the left side surface of the notch pin 770 and extend in the right direction. The accommodating portion 771 is formed in a substantially circular shape in a side view when the inner diameter is larger than the outer diameter of the rotation prevention pin 160.
　ノッチピン７７０は、バルブ１３０が全閉位置まで回動した後で、左方に移動されて合口１４１の内側に入り込み、合口１４１を押し広げてシールリング１４０を拡径させる。このとき、回り止めピン１６０は、収容部７７１に入り込む。また、ノッチピン７７０は、流路２１を開放するときに、右方向に移動されて合口１４１から出て行く。このとき、回り止めピン１６０は、収容部７７１から出て行くこととなる。その後、バルブ１３０は回動される。このように構成することで、シート２０とシールリング１４０とが摺動しないようにすることができるため、シート２０及びシールリング１４０の摩耗を効果的に抑制することができる。
　このような第五変形例に係るバルブ装置７１０は、バルブ１３０の回動に連動する機構によってノッチピン７７０を左右方向に移動させてもよい。 The notch pin 770 moves to the left after the valve 130 has been rotated to the fully closed position, enters the inside of the joint 141, and pushes and widens the joint 141 to expand the diameter of the seal ring 140. At this time, the rotation prevention pin 160 enters the accommodating portion 771. Further, the notch pin 770 moves rightward and exits from the abutment 141 when opening the flow path 21. At this time, the rotation prevention pin 160 goes out of the housing portion 771. Thereafter, the valve 130 is rotated. With this configuration, it is possible to prevent the seat 20 and the seal ring 140 from sliding, and thus wear of the seat 20 and the seal ring 140 can be effectively suppressed.
The valve device 710 according to the fifth modification may move the notch pin 770 in the left-right direction by a mechanism that is interlocked with the rotation of the valve 130.
　また、バルブ１３０の構成は、第二実施形態に限定されるものではなく、例えば、図２７及び図２８に示す第六変形例に係るバルブ装置８１０のバルブ８３０のような構成とすることも可能である。 Further, the configuration of the valve 130 is not limited to the second embodiment, and for example, a configuration like the valve 830 of the valve device 810 according to the sixth modification shown in FIGS. 27 and 28 may be employed. It is.
　第六変形例に係るバルブ８３０は、シールリング溝８３１、溝部８３２及び凹部８３３を具備する。シールリング溝８３１は、バルブ８３０の右端部を除いてバルブ８３０の外周面の全域に亘って形成される。溝部８３２は、バルブ８３０の右端部に形成され、シールリング溝８３１と連通する。溝部８３２は、バルブ８３０の前側面から後側面に亘って形成される。溝部８３２の内側には、シールリング１４０の合口１４１が配置される。凹部８３３は、溝部８３２の底面に形成される。また、図２８に示すように、第六変形例に係るノッチピン８７０は、第二実施形態に係るノッチピン１７０よりも、その長さ（軸線方向幅）が溝部８３２の深さだけ長くなるように形成される。また、ノッチピン８７０の収容部８７１は、その左右方向幅が溝部８３２の深さだけ広くなるように形成される。
　このように構成することで、バルブ８３０の回動時にノッチピン８７０をバルブ８３０の溝部８３２に入り込ませることができ、ノッチピン８７０を合口１４１の左端部から右端部までに亘って当接させることが可能となる。これによれば、ノッチピン８７０とシールリング１４０との当接範囲を広くすることができ、ノッチピン８７０をシールリング１４０の合口１４１の内側に入り込ませ易くすることができる。 The valve 830 according to the sixth modification includes a seal ring groove 831, a groove part 832, and a recessed part 833. The seal ring groove 831 is formed over the entire outer peripheral surface of the valve 830 except for the right end portion of the valve 830. The groove 832 is formed at the right end of the valve 830 and communicates with the seal ring groove 831. The groove 832 is formed from the front side surface to the rear side surface of the valve 830. An abutment 141 of the seal ring 140 is disposed inside the groove portion 832. The recess 833 is formed on the bottom surface of the groove 832. As shown in FIG. 28, the notch pin 870 according to the sixth modification is formed such that its length (width in the axial direction) is longer than the depth of the groove 832 than the notch pin 170 according to the second embodiment. Is done. Further, the accommodating portion 871 of the notch pin 870 is formed so that the width in the left-right direction is increased by the depth of the groove portion 832.
With this configuration, the notch pin 870 can be inserted into the groove portion 832 of the valve 830 when the valve 830 is rotated, and the notch pin 870 can be brought into contact from the left end portion to the right end portion of the joint 141. It becomes. According to this, the contact range of the notch pin 870 and the seal ring 140 can be widened, and the notch pin 870 can easily enter the inside of the joint 141 of the seal ring 140.
　また、第三実施形態においては、長手部材を略円状に曲げた後で、当該長手部材の両端部を後方向に曲げることでシールリング２４０を製造するものとしたが、シールリング２４０を製造する方法は、これに限定されるものではない。例えば、長手部材の両端部を後方向に曲げた後で、当該長手部材を略円状に曲げることでシールリング２４０を製造してもよい。 In the third embodiment, the seal ring 240 is manufactured by bending the longitudinal member into a substantially circular shape and then bending both ends of the longitudinal member in the backward direction. However, the seal ring 240 is manufactured. The method to do is not limited to this. For example, the seal ring 240 may be manufactured by bending both ends of the longitudinal member in the backward direction and then bending the longitudinal member into a substantially circular shape.
　また、第三実施形態に係る案内部２４３は、長手部材の両端部を曲げることで形成されるものとしたが、これに限定されるものではなく、種々の加工によって形成することができる。案内部２４３は、例えば、長手部材の両端部を切り欠くことで形成されていてもよい。また、案内部２４３は、長手部材の両端部を研磨することで形成されていてもよい。 Moreover, although the guide part 243 which concerns on 3rd embodiment shall be formed by bending the both ends of a longitudinal member, it is not limited to this, It can form by various processes. For example, the guide portion 243 may be formed by cutting out both end portions of the longitudinal member. Moreover, the guide part 243 may be formed by grind | polishing the both ends of a longitudinal member.
　また、第三実施形態に係る案内部２４３は、側面視略円弧状の曲面であるものとしたが、これに限定されるものではなく、前方向に向かうにつれてシールリング２４０の周方向に広がるような側面視直線状の面であってもよい。 Moreover, although the guide part 243 which concerns on 3rd embodiment shall be a curved surface of the substantially arc shape in side view, it is not limited to this, It spreads in the circumferential direction of the seal ring 240 toward the front direction. It may be a straight surface in a side view.
　また、シールリング２４０は、突出部２４２の有無を問わない。このような場合において、シールリング２４０は、例えば、図２９に示す第七変形例に係るシールリング９４０及び第八変形例に係るシールリング１０４０のような構成とすることも可能である。 Moreover, the seal ring 240 does not ask | require the presence or absence of the protrusion part 242. In such a case, the seal ring 240 may be configured as, for example, a seal ring 940 according to the seventh modification shown in FIG. 29 and a seal ring 1040 according to the eighth modification.
　図２９（ａ）に示す第七変形例に係るシールリング９４０は、円周部９４１及び案内部９４３を具備する。円周部９４１は、第三実施形態に係る円周部２４１と同様に構成される。案内部９４３は、円周部９４１の両端面における前端部及び後端部をそれぞれ切り欠くことによって形成される。 A seal ring 940 according to the seventh modification shown in FIG. 29A includes a circumferential portion 941 and a guide portion 943. The circumferential part 941 is configured similarly to the circumferential part 241 according to the third embodiment. The guide portion 943 is formed by notching the front end portion and the rear end portion on both end surfaces of the circumferential portion 941.
　図２９（ｂ）に示す第八変形例に係るシールリング１０４０は、円周部１０４１及び案内部１０４３を具備する。円周部１０４１は、第三実施形態に係る円周部２４１と同様に構成される。案内部１０４３は、円周部１０４１の両端面における前端部だけを切り欠くことによって形成される。これによって、第八変形例に係る案内部１０４３は、第七変形例に係る案内部９４３よりもその曲率を小さくすることができる。このため、ノッチピン２６０を案内部１０４３に対して滑らかに摺動させることができるため、シールリング１０４０及びノッチピン２６０の摩耗を効果的に抑制することができる。 A seal ring 1040 according to an eighth modification shown in FIG. 29B includes a circumferential portion 1041 and a guide portion 1043. The circumferential part 1041 is configured similarly to the circumferential part 241 according to the third embodiment. The guide portion 1043 is formed by cutting out only the front end portions on both end faces of the circumferential portion 1041. Thereby, the curvature of the guide part 1043 according to the eighth modification can be made smaller than that of the guide part 943 according to the seventh modification. For this reason, since the notch pin 260 can be smoothly slid with respect to the guide part 1043, wear of the seal ring 1040 and the notch pin 260 can be effectively suppressed.
　第七変形例及び第八変形例に係るシールリング９４０・１０４０は、例えば、長手部材を略円状に曲げる工程を行った後で、当該長手部材の両端面を研磨することで製造される。これによれば、突出部２４２の長さだけ長手部材の全長を短くすることができるため、製造コストを低減することができる。 The seal rings 940 and 1040 according to the seventh modification and the eighth modification are manufactured by, for example, polishing the both end surfaces of the longitudinal member after performing a process of bending the longitudinal member into a substantially circular shape. According to this, since the total length of the longitudinal member can be shortened by the length of the protruding portion 242, the manufacturing cost can be reduced.
　以上の如く、第七変形例及び第八変形例に係る案内部９４３・１０４３は、前記シールリング９４０・１０４０の端面に形成されているものである。 As described above, the guide portions 943 and 1043 according to the seventh and eighth modifications are formed on the end faces of the seal rings 940 and 1040.
　このように構成することにより、シールリング９４０・１０４０の摩耗を抑制することができる。 By configuring in this way, wear of the seal rings 940 and 1040 can be suppressed.
　また、シールリング２４０が突出部２４２を具備しない構成（例えば、第七変形例又は第八変形例に係るシールリング９４０・１０４０のような構成）において、シールリング溝２３１は、太溝２３１ｂの有無を問わない。シールリング溝２３１は、例えば、図３０に示す第九変形例に係るバルブ１１３０のシールリング溝１１３１のような構成とすることも可能である。 In the configuration in which the seal ring 240 does not include the protruding portion 242 (for example, the configuration of the seal rings 940 and 1040 according to the seventh modified example or the eighth modified example), the seal ring groove 231 has the presence or absence of the thick groove 231b. It doesn't matter. For example, the seal ring groove 231 may be configured like the seal ring groove 1131 of the valve 1130 according to the ninth modification shown in FIG.
　第九変形例に係るバルブ１１３０のシールリング溝１１３１は、第三実施形態に係る細溝２３１ａに相当する溝である。シールリング溝１１３１は、バルブ１１３０の周方向に延びるように形成され、バルブ１１３０の全周に亘って形成される。シールリング溝１１３１には、第七変形例に係るシールリング９４０が嵌め合わされる。このように、第九変形例においては、太溝２３１ｂを形成する必要がないため、シールリング溝１１３１をバルブ１１３０の全周に亘って形成でき、バルブ１１３０の構成を簡素化することができる。 The seal ring groove 1131 of the valve 1130 according to the ninth modification is a groove corresponding to the narrow groove 231a according to the third embodiment. The seal ring groove 1131 is formed so as to extend in the circumferential direction of the valve 1130, and is formed over the entire circumference of the valve 1130. The seal ring 940 according to the seventh modification is fitted into the seal ring groove 1131. Thus, in the ninth modified example, since it is not necessary to form the thick groove 231b, the seal ring groove 1131 can be formed over the entire circumference of the valve 1130, and the configuration of the valve 1130 can be simplified.
　また、第三実施形態に係るノッチピン２６０は、シート２０に固定されるものとしたが、これに限定されるものではなく、シート２０に相対移動可能に支持されていてもよい。このような場合において、バルブ２３０、シールリング２４０及びノッチピン２６０は、例えば、図３１（ａ）に示す第十変形例に係るバルブ装置１２１０のバルブ１２３０、シールリング１２４０及びノッチピン１２６０のような構成とすることも可能である。 Further, the notch pin 260 according to the third embodiment is fixed to the sheet 20, but is not limited to this, and may be supported by the sheet 20 so as to be relatively movable. In such a case, the valve 230, the seal ring 240, and the notch pin 260 are configured as, for example, the valve 1230, the seal ring 1240, and the notch pin 1260 of the valve device 1210 according to the tenth modification shown in FIG. It is also possible to do.
　第十変形例に係るバルブ１２３０は、シールリング溝１２３１及び凹部１２３２を具備する。シールリング溝１２３１は、第九変形例に係るシールリング溝１１３１と同様に構成される。凹部１２３２は、シールリング溝１２３１の右端部に形成されると共に、シールリング溝１２３１の底面から左方向に延びるように形成される窪みである。
　第十変形例に係るシールリング１２４０は、円周部１２４１、突出部１２４２、案内部１２４３及び合口１２４４を具備する。円周部１２４１は、第三実施形態に係る円周部２４１と同様に構成される。突出部１２４２は、円周部１２４１の両端部からそれぞれ左方向に突出し、凹部１２３２の内側に配置される。案内部１２４３は、円周部１２４１の一端部と上側の突出部１２４２との間、並びに円周部１２４１の他端部と下側の突出部１２４２との接続部分にそれぞれ形成され、正面視略円弧状に形成される。合口１２４４は、上側の突出部１２４２と下側の突出部１２４２との間に形成される。
　第十変形例に係るノッチピン１２６０は、駆動源によって左右方向に移動自在にシート２０の支持孔２２に支持される。 A valve 1230 according to the tenth modification includes a seal ring groove 1231 and a recess 1232. The seal ring groove 1231 is configured similarly to the seal ring groove 1131 according to the ninth modification. The recess 1232 is a recess formed at the right end of the seal ring groove 1231 and extending leftward from the bottom surface of the seal ring groove 1231.
A seal ring 1240 according to the tenth modification includes a circumferential portion 1241, a protruding portion 1242, a guide portion 1243, and a joint 1244. The circumferential part 1241 is configured similarly to the circumferential part 241 according to the third embodiment. The protrusions 1242 protrude from the both ends of the circumferential part 1241 to the left, and are disposed inside the recesses 1232. The guide portion 1243 is formed between one end portion of the circumferential portion 1241 and the upper protruding portion 1242, and at a connection portion between the other end portion of the circumferential portion 1241 and the lower protruding portion 1242, and is substantially omitted in a front view. It is formed in an arc shape. The joint 1244 is formed between the upper protrusion 1242 and the lower protrusion 1242.
The notch pin 1260 according to the tenth modification is supported by the support hole 22 of the seat 20 so as to be movable in the left-right direction by a drive source.
　図３１に示すように、ノッチピン１２６０は、バルブ１２３０が全閉位置まで回動した後で、左方に移動されて合口１２４４に入り込み、合口１２４４を押し広げてシールリング１２４０を拡径させる。このとき、ノッチピン１２６０は、その左端部が案内部１２４３と当接し、案内部１２４３に案内されて合口１２４４を押し広げる。また、ノッチピン１２６０は、流路２１を開放するときに、右方向に移動されて合口１２４４から出て行く。その後、バルブ１２３０は回動される。このように構成することで、シート２０とシールリング１２４０とが摺動しないようにすることができるため、シート２０及びシールリング１２４０（円周部１２４１）の摩耗を効果的に抑制することができる。
　このような第十変形例に係るバルブ装置１２１０は、バルブ１２３０の回動に連動する機構によってノッチピン１２６０を左右方向に移動させてもよい。 As shown in FIG. 31, the notch pin 1260 moves to the left after the valve 1230 has been rotated to the fully closed position, enters the joint 1244, and widens the seal ring 1240 by expanding the joint 1244. At this time, the left end of the notch pin 1260 comes into contact with the guide portion 1243 and is guided by the guide portion 1243 to push the joint 1244 apart. In addition, the notch pin 1260 is moved to the right and exits from the joint 1244 when the channel 21 is opened. Thereafter, the valve 1230 is rotated. With this configuration, the seat 20 and the seal ring 1240 can be prevented from sliding, so that wear of the seat 20 and the seal ring 1240 (circumferential portion 1241) can be effectively suppressed. .
The valve device 1210 according to the tenth modification may move the notch pin 1260 in the left-right direction by a mechanism that is interlocked with the rotation of the valve 1230.
　また、第三実施形態に係るノッチピン２６０は、図１９に示すように、バルブ２３０が全閉位置まで回動したときに、その軸心が円周部２４１の前後中央部に配置され、その後上部及び後下部で合口２４４を押し広げるものとしたが、これに限定されるものではない。ノッチピン２６０は、例えば、バルブ２３０が全閉位置まで回動したときに、図１９に示す状態よりも後方に配置されるものであってもよい。これによれば、ノッチピン２６０の頂部（上端部）及び底部（下端部）で合口２４４を押し広げることができる。これによれば、シールリング２４０を最大限に拡径させてシールリング２４０をシート２０に強い力で押し付けることができるため、シール性を向上させることができる。 In addition, as shown in FIG. 19, the notch pin 260 according to the third embodiment has its axial center disposed at the front and rear central portions of the circumferential portion 241 when the valve 230 rotates to the fully closed position, and thereafter the upper portion. In addition, the abutment 244 is expanded at the lower rear portion, but the present invention is not limited to this. For example, the notch pin 260 may be disposed behind the state shown in FIG. 19 when the valve 230 rotates to the fully closed position. According to this, the joint 244 can be expanded at the top (upper end) and the bottom (lower end) of the notch pin 260. According to this, since the seal ring 240 can be expanded to the maximum extent and the seal ring 240 can be pressed against the seat 20 with a strong force, the sealing performance can be improved.
　本発明は、バルブを回動させて流体の流通を制御するバルブ装置に適用することができる。 The present invention can be applied to a valve device that controls the flow of fluid by rotating the valve.
　１０　バルブ装置
　２０　シート
　２１　流路
　３０　バルブ
　４０　シールリング
　６０　ノッチピン（拡径手段） DESCRIPTION OF SYMBOLS 10 Valve apparatus 20 Seat 21 Flow path 30 Valve 40 Seal ring 60 Notch pin (diameter expansion means)

Claims (19)

  1. 　流路が貫通形成されているシートと、
    　前記流路に回動自在に配置されると共に、回動することで前記流路を開閉するバルブと、
    　前記バルブの外周に嵌め合わされたシールリングと、
    　前記バルブが前記流路を閉塞する位置まで回動したときに、前記シールリングを拡径させて前記シートと前記シールリングとの隙間をシールする拡径手段と、
    　を具備する、
    　バルブ装置。     A sheet having a flow passage formed therethrough;
    A valve that is rotatably arranged in the flow path, and that opens and closes the flow path by rotating,
    A seal ring fitted to the outer periphery of the valve;
    A diameter expanding means for expanding the diameter of the seal ring and sealing a gap between the seat and the seal ring when the valve rotates to a position closing the flow path;
    Comprising
    Valve device.
  2. 　前記シールリングは、切れ目部分である合口を具備し、
    　前記拡径手段は、前記合口を押し広げることで前記シールリングを拡径させる、
    　請求項１に記載のバルブ装置。     The seal ring has a joint that is a cut portion,
    The diameter-expanding means expands the diameter of the seal ring by expanding the joint.
    The valve device according to claim 1.
  3. 　前記拡径手段は、前記バルブが前記流路を閉塞する位置まで回動したときに前記合口に入り込むことで、前記合口を押し広げる、
    　請求項２に記載のバルブ装置。     The diameter-expanding means pushes the abutment by entering the abutment when the valve rotates to a position to close the flow path,
    The valve device according to claim 2.
  4. 　前記拡径手段は、前記シートに固定される、
    　請求項２又は請求項３に記載のバルブ装置。     The diameter expanding means is fixed to the sheet,
    The valve device according to claim 2 or 3.
  5. 　前記合口は、前記バルブの回動軸線に対して離れた位置に配置される、
    　請求項２から請求項４までのいずれか一項に記載のバルブ装置。     The joint is disposed at a position away from the rotation axis of the valve.
    The valve device according to any one of claims 2 to 4.
  6. 　前記拡径手段は、前記シートとは異なる部材によって構成される、
    　請求項１から請求項５までのいずれか一項に記載のバルブ装置。     The diameter expanding means is constituted by a member different from the sheet,
    The valve device according to any one of claims 1 to 5.
  7. 　前記シールリングには、縮径方向への張力が作用している、
    　請求項１から請求項６までのいずれか一項に記載のバルブ装置。     A tension in the direction of diameter reduction is acting on the seal ring.
    The valve device according to any one of claims 1 to 6.
  8. 　前記合口の内側に配置され、前記シールリングの前記バルブに対する相対回転を規制する規制手段をさらに具備し、
    　前記拡径手段は、
    　前記合口の内側に入り込んで前記合口を押し広げるものであり、前記合口に入り込むときに、前記規制手段が内部に入り込む収容部を具備する、
    　請求項２に記載のバルブ装置。     Further comprising a restricting means disposed inside the joint and restricting relative rotation of the seal ring with respect to the valve;
    The diameter expanding means is
    It enters the inside of the joint and pushes the joint, and when entering the joint, the restricting means includes an accommodating part that enters the inside.
    The valve device according to claim 2.
  9. 　前記拡径手段は、前記シートに固定される、
    　請求項８に記載のバルブ装置。     The diameter expanding means is fixed to the sheet,
    The valve device according to claim 8.
  10. 　前記収容部は、前記拡径手段の前記合口に入り込む側が開口すると共に、前記合口に入り込む側とは反対側が閉塞する、
    　請求項９に記載のバルブ装置。     The accommodating portion is opened on the side of the diameter expanding means that enters the joint, and the side opposite to the side that enters the joint is closed.
    The valve device according to claim 9.
  11. 　前記収容部の前記合口に入り込む側とは反対側の端面は、前記規制手段の形状に沿った形状に形成される、
    　請求項１０に記載のバルブ装置。     An end surface of the housing portion opposite to the side entering the joint is formed in a shape along the shape of the restricting means.
    The valve device according to claim 10.
  12. 　前記収容部は、前記拡径手段が前記合口に入り込む方向に延びるように形成される、
    　請求項８から請求項１１までのいずれか一項に記載のバルブ装置。     The accommodating portion is formed to extend in a direction in which the diameter expanding means enters the joint.
    The valve device according to any one of claims 8 to 11.
  13. 　前記規制手段は、前記バルブとは異なる部材によって構成される、
    　請求項８から請求項１２までのいずれか一項に記載のバルブ装置。     The restricting means is constituted by a member different from the valve.
    The valve device according to any one of claims 8 to 12.
  14. 　前記シールリングは、両端部を突き合わせて形成されている合口を具備し、
    　前記拡径手段は、前記合口に入り込んで前記合口を押し広げることで前記シールリングを拡径させ、
    　前記シールリングは、
    　前記拡径手段の前記合口への入り込みを案内する案内部をさらに具備する、
    　請求項１に記載のバルブ装置。     The seal ring includes a joint formed by abutting both ends,
    The diameter expanding means expands the diameter of the seal ring by entering the joint and expanding the joint.
    The seal ring is
    A guide portion for guiding the diameter expansion means to enter the joint;
    The valve device according to claim 1.
  15. 　前記案内部は、
    　前記拡径手段の受け入れ側に向かうにつれて徐々に前記シールリングの周方向に広がるように形成される、
    　請求項１４に記載のバルブ装置。     The guide part is
    Formed so as to gradually spread in the circumferential direction of the seal ring toward the receiving side of the diameter expanding means,
    The valve device according to claim 14.
  16. 　前記案内部は、
    　曲面状に形成される、
    　請求項１５に記載のバルブ装置。     The guide part is
    Formed in a curved shape,
    The valve device according to claim 15.
  17. 　前記シールリングは、
    　周方向に沿って延びる円周部と、
    　前記円周部の端部から前記拡径手段が前記合口に入り込む方向に突出する突出部と、
    　をさらに具備し、
    　前記案内部は、
    　前記円周部と前記突出部との接続部分に形成される、
    　請求項１４から請求項１６までのいずれか一項に記載のバルブ装置。     The seal ring is
    A circumferential portion extending along the circumferential direction;
    A projecting portion projecting in a direction in which the diameter expanding means enters the joint from an end of the circumferential portion;
    Further comprising
    The guide part is
    Formed at a connection portion between the circumferential portion and the protruding portion;
    The valve device according to any one of claims 14 to 16.
  18. 　前記バルブは、
    　前記円周部を嵌め合わせるための細溝と、
    　前記細溝と連通すると共に前記細溝の幅よりも広い幅を有し、前記突出部を配置するための太溝と、
    　を具備する、
    　請求項１７に記載のバルブ装置。     The valve is
    A narrow groove for fitting the circumferential portion;
    A wide groove communicating with the narrow groove and having a width wider than that of the narrow groove, and for arranging the protruding portion;
    Comprising
    The valve device according to claim 17.
  19. 　前記案内部は、
    　前記シールリングの端面に形成されている、
    　請求項１４から請求項１６までのいずれか一項に記載のバルブ装置。     The guide part is
    Formed on the end face of the seal ring,
    The valve device according to any one of claims 14 to 16.
PCT/JP2017/005459 2016-03-09 2017-02-15 Valve device WO2017154487A1 (en)

Applications Claiming Priority (6)

Application Number Priority Date Filing Date Title
JP2016-045767 2016-03-09
JP2016-045765 2016-03-09
JP2016045765A JP6621346B2 (en) 2016-03-09 2016-03-09 Valve device
JP2016045766A JP2017160990A (en) 2016-03-09 2016-03-09 Valve device
JP2016-045766 2016-03-09
JP2016045767A JP2017160991A (en) 2016-03-09 2016-03-09 Valve device

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Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE866284C (en) * 1943-06-24 1953-02-09 Ruhrchemie Ag throttle
JPS53121528U (en) * 1977-03-05 1978-09-27
JPH1026235A (en) * 1996-07-12 1998-01-27 Kubota Corp Butterfly valve

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE866284C (en) * 1943-06-24 1953-02-09 Ruhrchemie Ag throttle
JPS53121528U (en) * 1977-03-05 1978-09-27
JPH1026235A (en) * 1996-07-12 1998-01-27 Kubota Corp Butterfly valve

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