JP2017133529A - Flow rate adjusting valve - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a flow rate adjusting valve capable of suppressing a sliding wear between a valve seat and a valve body, with a comparatively simple structure and while saving a space.SOLUTION: In a flow rate adjusting valve 1, a rotary shaft 15 is equipped with an axis shaft 21, and a valve shaft 22, and has a first bearing eccentric plate 81. As a moving area of the valve shaft 22, a moving area where the first bearing eccentric plate 81 pushes the valve shaft 22 and the valve shaft 22 moves in a direction toward a valve seat 13 or separating from the valve seat 13 to make the valve body 14 contact with the valve seat 13 or make the valve body 14 separate from the valve seat 13; and a rotation area where while the valve seat 13 and the valve body 14 are separated from each other, the rotational force of the axis shaft 21 rotating about a center axis Ls acts on the valve shaft 22 to rotate the valve shaft 22 about the center axis Ls, are provided.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a flow rate adjusting valve, for example, a flow rate adjusting valve applied to air flow rate adjustment of an air system in a fuel cell system.

  With regard to the flow rate adjusting valve, Patent Document 1 discloses a butterfly valve that attempts to obtain complete sealing performance by strongly pressing a valve body against a closed position with a strong force by a screw mechanism.

Japanese Utility Model Publication No. 51-162328

  In the flow rate adjusting valve, if the valve body and the valve seat slide when the valve is opened, the valve body and the valve seat may be worn, and the sealing performance when fully closed may be deteriorated to increase the fluid leakage flow rate. Here, the butterfly valve disclosed in Patent Document 1 has a valve mechanism that is displaced by a predetermined distance toward the valve stem by a screw mechanism when the valve is opened, but the structure is complicated and the number of parts is also large. It will increase.

  Accordingly, the present invention has been made to solve the above-described problems, and provides a flow rate adjusting valve that can suppress sliding wear between a valve seat and a valve body with a relatively simple configuration and space saving. Objective.

  One form of this invention made | formed in order to solve the said subject is a valve seat, a valve body, the rotating shaft which is provided integrally with the said valve body, and rotates the said valve body, and the said rotating shaft integrally. And a driving force receiving portion that receives a driving force for rotating the rotating shaft in the valve opening direction, wherein the rotating shaft is provided integrally with the driving force receiving portion. A first shaft connected to an axial end of the first rotary shaft in a state of being provided integrally with the valve body and being relatively movable in the radial direction of the first rotary shaft with respect to the first rotary shaft; A second rotating shaft, and a bearing member that supports the second rotating shaft, and the second rotating shaft is pushed by the bearing member as a movable region of the second rotating shaft, and the first rotating shaft Relative to the radial direction of the first rotating shaft, the second rotating shaft is moved to the valve. Moving in a direction toward or away from the valve seat to bring the valve body into contact with the valve seat, or to move the valve body away from the valve seat, a valve seat orthogonal direction movement region, and the valve seat, A rotational region in which the second rotating shaft rotates about the axis by the rotational force of the first rotating shaft rotating about the axis acting on the second rotating shaft in a state where the valve body is separated; It is characterized by having.

  According to this aspect, at the time of valve opening, the valve body can be moved in a direction away from the valve seat, and then the valve body can be rotated about the axis while the valve seat and the valve body are separated from each other. Further, when the valve is closed, the valve body can be rotated about the shaft while the valve seat is separated from the valve body, and then the valve body can be moved in the direction toward the valve seat to contact the valve seat. Therefore, when the valve is opened or closed, sliding of the valve seat and the valve body due to the rotation of the valve body about the shaft center can be suppressed. Therefore, sliding wear between the valve seat and the valve body can be suppressed with a relatively simple configuration and space saving. Therefore, when the valve is fully closed, the sealing performance between the valve seat and the valve body is ensured, so that an increase in the amount of fluid leakage can be prevented.

  In the above aspect, the connecting structure of the first rotating shaft and the second rotating shaft is formed at the end of the first rotating shaft on the second rotating shaft side in the axial direction of the first rotating shaft. A groove-shaped slit portion formed in the radial direction of the first rotating shaft, and an end portion on the first rotating shaft side in the axial direction of the second rotating shaft in the second rotating shaft, It is preferable that there is provided a sliding portion that is inserted into the slit portion in a state in which the relative rotation with respect to the first rotating shaft is impossible and the first rotating shaft is slidable in the radial direction.

  According to this aspect, the second rotating shaft can be moved in the direction toward the valve seat or in the direction away from the valve seat while restricting the rotation of the second rotating shaft.

  In the above aspect, the bearing member includes a through hole into which the sliding portion is inserted, and the inner wall portion forming the through hole has a circular shape centering on the central axis of the first rotation shaft. Formed in the shape of a portion, and formed so as to protrude toward the inside of the circular shape, and an arc portion that supports the sliding portion when the second rotating shaft rotates about an axis, and the second rotating shaft is A convex part for pushing the sliding part when moving in the direction toward the valve seat and a concave part formed toward the outer side of the circular shape, and the sliding part pushed by the convex part are fitted. It is preferable to provide a recess.

  According to this aspect, the second rotating shaft can be moved in the direction toward the valve seat or in the direction away from the valve seat, or the second rotating shaft can be stably rotated about the axis by the bearing member.

  According to the flow regulating valve of the present invention, sliding wear between the valve seat and the valve body can be suppressed with a relatively simple configuration and space saving.

It is sectional drawing of the flow regulating valve of this embodiment. It is AA sectional drawing of FIG. It is an enlarged view of the slit part periphery of an axial shaft. It is an enlarged view around the 1st sliding part of a valve shaft. It is the schematic of the 1st bearing eccentric plate and 1st sliding part in the position of the BB cross section of FIG. 1 at the time of full closure. It is the schematic of the slit part and 1st sliding part in the position of CC cross section of FIG. 1 at the time of full closure. It is the schematic of the valve seat and valve body in the position of the DD cross section of FIG. 1 at the time of full closure. It is the schematic of the 1st bearing eccentric plate and the 1st sliding part in the position of the BB cross section of FIG. 1 at the time of valve opening. It is the schematic of the slit part and 1st sliding part in the position of CC cross section of FIG. 1 at the time of valve opening. It is the schematic of the valve seat and valve body in the position of the DD cross section of FIG. 1 at the time of valve opening. It is the schematic of the 1st bearing eccentric plate and the 1st sliding part in the position of the BB cross section of FIG. 1 at the time of full open. It is the schematic of the slit part and the 1st sliding part in the position of CC cross section of FIG. 1 at the time of full open. It is the schematic of the valve seat and valve body in the position of the DD cross section of FIG. 1 at the time of a full open. It is a schematic block diagram of the fuel cell system which has an integrated valve to which the flow regulating valve of this embodiment is applied.

  As shown in FIGS. 1 and 2, the flow rate adjusting valve 1 of the present embodiment includes a valve portion 2 and a drive mechanism portion 3. The valve section 2 includes a pipe section 12 having a flow path 11 through which a fluid flows. A valve seat 13, a valve body 14, and a rotary shaft 15 are disposed in the flow path 11. A driving force (rotational force) is transmitted from the drive mechanism unit 3 to the rotating shaft 15. The drive mechanism unit 3 includes a motor 32 and a speed reduction mechanism 33.

  The valve seat 13 has an annular shape and has a valve hole 16 in the center. An annular seat surface 17 is formed at the edge of the valve hole 16. The valve body 14 includes a disk-shaped portion, and an annular seal surface 18 corresponding to the seat surface 17 is formed on the outer periphery thereof.

  The valve body 14 is provided integrally with the rotary shaft 15 and rotates integrally with the rotary shaft 15. In the present embodiment, the valve body 14 is provided integrally with the valve shaft 22 constituting the rotating shaft 15.

  The valve body 14 is movable between a fully closed position and a fully open position by rotating about the central axis Ls of the rotating shaft 15. Here, the fully closed position refers to a valve when the sealing surface 18 of the valve body 14 is in contact with the seat surface 17 of the valve seat 13 over the entire circumference and the opening area of the valve hole 16 is “0”. This is the position of the body 14. The fully open position is the position of the valve body 14 when the opening area of the valve hole 16 is the largest.

  In the present embodiment, the time when the valve body 14 is in the fully closed position is referred to as “when fully closed”, and the time when the valve body 14 is in the fully open position is referred to as “when fully opened”. The time when the valve body 14 is in a position between the fully closed position and the fully open position and the valve body 14 is rotating from the fully closed position side toward the fully open position side is referred to as “when the valve is open”. . Furthermore, when the valve body 14 is in a position between the fully open position and the fully closed position and the valve body 14 is rotating from the fully open position side toward the fully closed position side, it is referred to as “when the valve is closed”. .

  When the flow rate adjusting valve 1 is applied to an integrated valve 181 provided in a fuel cell system 101 (see FIG. 14) described later, a flow formed on the opposite side of the valve body 14 and the rotary shaft 15 with respect to the valve seat 13. The passage 11 is arranged on the fuel cell 111 side (upstream side of the air flow), and the flow path 11 formed on the valve body 14 and the rotary shaft 15 side with respect to the valve seat 13 is connected to the diluter 182 side (air flow direction). (Downstream). That is, air flows in the flow path 11 from the valve seat 13 side toward the valve body 14 (rotating shaft 15).

  The rotating shaft 15 includes a shaft shaft 21 (first rotating shaft), a valve shaft 22 (second rotating shaft), and a shaft shaft 23 (third rotating shaft). The shaft shaft 21, the valve shaft 22, and the shaft shaft 23 are arranged in order from the main gear 41 (driving force receiving portion) side to the third bearing 45 side in the direction of the central axis Ls of the rotary shaft 15.

  The shaft 21 is formed in a cylindrical shape. The central axis of the shaft shaft 21 coincides with the central axis Ls of the rotary shaft 15, and the shaft shaft 21 rotates about the central axis Ls, whereby the valve shaft 22 and the valve body 14 are centered on the central axis Ls. Rotate.

  The shaft 21 includes a proximal end portion 51, a slit portion 52, and the like.

  The base end 51 is formed at the end on the main gear 41 side in the direction of the central axis Ls. The base end portion 51 is provided integrally with the main gear 41 and transmits a driving force transmitted from the main gear 41 to the shaft shaft 21.

  The slit portion 52 is formed at the end of the shaft shaft 21 on the valve shaft 22 side in the direction of the central axis Ls (the central axis direction of the shaft shaft 21). As shown in FIG. 3, the slit portion 52 is formed in a groove shape formed in the radial direction of the shaft shaft 21 (vertical direction in FIG. 3). That is, the slit portion 52 has a groove shape recessed from the end surface 53 on the valve shaft 22 side in the central axis Ls direction of the shaft shaft 21 toward the base end portion 51 side, and penetrates in the radial direction of the shaft shaft 21. It is formed in the shape of a groove. Furthermore, in other words, the slit portion 52 is formed in a U-shape when viewed from the radial direction of the shaft shaft 21.

  In the slit portion 52, opposing side surfaces 52 a and side surfaces 52 b are formed in parallel to each other along the radial direction of the shaft shaft 21. A first sliding portion 62 of the valve shaft 22, which will be described later, is inserted into the slit portion 52 so as to be slidable on the side surface 52a and the side surface 52b. That is, the valve shaft 22 cannot rotate relative to the shaft shaft 21 and can move relative to the shaft shaft 21 in the radial direction of the shaft shaft 21 (slidable). It is connected to the end on the valve shaft 22 side in the Ls direction.

  The valve shaft 22 includes a main body portion 61, a first sliding portion 62, and a second sliding portion 63 (see FIGS. 1 and 2).

  The main body 61 is formed in a columnar shape. The valve body 14 is attached to the main body 61. That is, the valve shaft 22 is provided integrally with the valve body 14.

  The first sliding portion 62 is formed at the end of the valve shaft 22 on the shaft shaft 21 side in the direction of the central axis Lsb of the valve shaft 22. As shown in FIG. 4, the first sliding portion 62 is formed so as to protrude from the end surface 61 a on the shaft shaft 21 side in the central axis Lsb direction in the main body portion 61. And in this embodiment, the external shape of the 1st sliding part 62 seen from the central-axis Lsb direction is formed in the hexagon which the corner | angular part was formed in circular arc shape and the corner was made. And the 1st sliding part 62 is provided with the convex part 62a and the convex part 62b which are the corner | angular parts located on the diagonal in this hexagon.

  Such a first sliding portion 62 is inserted into the slit portion 52 of the shaft shaft 21 and the through hole 91 of the first bearing eccentric plate 81. The first sliding portion 62 is inserted into the slit portion 52 so as not to rotate relative to the shaft shaft 21 and to be slidable in the radial direction of the shaft shaft 21. Thereby, the shaft shaft 21 and the valve shaft 22 are connected.

  The second sliding portion 63 is formed at the end of the valve shaft 22 on the shaft shaft 23 side in the direction of the central axis Lsb, similarly to the first sliding portion 62. The second sliding portion 63 is inserted into the through hole 91 of the second bearing eccentric plate 82 and the slit portion 71 of the shaft shaft 23. The second sliding portion 63 is inserted into the slit portion 71 so as not to rotate relative to the shaft shaft 23 and to be slidable in the radial direction of the shaft shaft 23.

  The shaft shaft 23 is formed in a cylindrical shape. The shaft shaft 23 includes a slit portion 71. The slit portion 71 is formed at the end of the shaft shaft 23 on the valve shaft 22 side in the direction of the central axis Ls. The slit portion 71 is formed in the same manner as the slit portion 52 of the shaft shaft 21. A second sliding portion 63 of the valve shaft 22 is inserted into the slit portion 71. Thereby, the valve shaft 22 and the shaft shaft 23 are connected.

  In the present embodiment, the flow rate adjusting valve 1 further includes a first bearing eccentric plate 81 and a second bearing eccentric plate 82 as two bearing members.

  The first bearing eccentric plate 81 is disposed at a position between the shaft shaft 21 and the main body 61 of the valve shaft 22 in the direction of the central axis Ls. As shown in FIG. 5, the first bearing eccentric plate 81 is formed in a plate shape and includes a through hole 91. A first sliding portion 62 of the valve shaft 22 is inserted into the through hole 91 of the first bearing eccentric plate 81.

  The inner wall portion that forms the through hole 91 includes an arc portion 91a, a convex portion 91b, and a concave portion 91c. The arc portion 91a is a portion formed in a circular shape centered on the central axis Ls, and supports the first sliding portion 62 when the valve shaft 22 rotates about the central axis Ls. . The convex portion 91b is a portion formed so as to protrude toward the inner side of the circular shape that forms the arc portion 91a, and is first when the valve shaft 22 moves in the direction toward the valve seat 13 as will be described later. The sliding part 62 is pushed. The concave portion 91c is a portion formed so as to be recessed toward the inside of the circular shape forming the arc portion 91a, and the first sliding portion 62 pushed by the convex portion 91b is fitted therein as will be described later.

  The second bearing eccentric plate 82 is disposed at a position between the main body portion 61 of the valve shaft 22 and the shaft shaft 23 in the direction of the central axis Ls. The second bearing eccentric plate 82 is formed in the same shape as the first bearing eccentric plate 81. A second sliding portion 63 of the valve shaft 22 is inserted into the through hole 91 of the second bearing eccentric plate 82.

  The rotating shaft 15 is supported in a rotatable state by the first bearing 37, the second bearing 38, and the third bearing 45. Specifically, the shaft shaft 21 is rotatably supported with respect to the valve housing 35 via a first bearing 37 and a second bearing 38 which are two bearings arranged apart from each other. The shaft shaft 23 is rotatably supported with respect to the valve housing 35 via a third bearing 45. The first bearing 37, the second bearing 38, and the third bearing 45 are all constituted by ball bearings.

  The end frame 36 made of metal or synthetic resin closes the open end of the valve housing 35. A main gear 41 is fixed to the proximal end portion 51 of the shaft shaft 21. A return spring 40 is provided between the valve housing 35 and the main gear 41. The main gear 41 is provided integrally with the shaft 21 of the rotating shaft 15 and receives a driving force generated by the motor 32.

  As shown in FIG. 2, the motor 32 is housed and fixed in a housing recess 35 a formed in the valve housing 35. The motor 32 generates a driving force that rotates the rotating shaft 15 in the valve opening and closing directions. The motor 32 is coupled so that the driving force is transmitted to the rotary shaft 15 via the speed reduction mechanism 33 in order to open and close the valve body 14. That is, the motor gear 43 is fixed to the output shaft of the motor 32. The motor gear 43 is coupled so that a driving force is transmitted to the main gear 41 via the intermediate gear 42.

  When the flow rate adjusting valve 1 configured as described above is energized to the motor 32, the driving force of the motor 32 is transmitted to the main gear 41 via the motor gear 43 and the intermediate gear 42, and against the urging force of the return spring 40, The rotating shaft 15 rotates around the central axis Ls. Then, the valve body 14 is rotated, the valve hole 16 is opened, and the flow path 11 is opened, whereby the flow rate adjusting valve 1 is opened.

  Therefore, the operation between the shaft shaft 21 and the valve shaft 22 when the flow rate adjusting valve 1 is opened will be described. Since the operation between the shaft shaft 23 and the valve shaft 22 is the same as the operation between the shaft shaft 21 and the valve shaft 22, here, mainly between the shaft shaft 21 and the valve shaft 22. The operation between the two will be described.

  First, when the motor 32 that is not energized is not driven, the seal surface 18 of the valve body 14 contacts the seat surface 17 of the valve seat 13 over the entire circumference as shown in FIG. The opening area of the valve hole 16 is “0”. That is, when the motor 32 is not driven, the valve body 14 is in the fully closed position.

  In such a fully closed state, as shown in FIG. 5, the convex portion 62a of the first sliding portion 62 of the valve shaft 22 is pushed by the convex portion 91b of the first bearing eccentric plate 81, and the first sliding portion. The convex portion 62 b of 62 is fitted in the concave portion 91 c of the first bearing eccentric plate 81. As a result, as shown in FIG. 6, the position of the central axis Lsb of the valve shaft 22 deviates from the position of the central axis Ls of the rotating shaft 15, and the valve shaft 22 moves to the valve seat 13 side (upper side in FIG. 6). Yes. In this way, as shown in FIG. 7, when fully closed, the valve body 14 is pressed against the valve seat 13, so that the sealing performance between the valve seat 13 and the valve body 14 is ensured.

  Next, the flow control valve 1 is opened by energizing the motor 32 to drive the motor 32. Then, when the shaft shaft 21 starts to rotate, as shown in FIG. 8, the valve shaft 22 starts to rotate, so that the convex portion 62 a of the first sliding portion 62 extends from the convex portion 91 b of the first bearing eccentric plate 81. Leave. On the other hand, the convex part 62 b of the first sliding part 62 moves away from the concave part 91 c of the first bearing eccentric plate 81 and is pushed by the arc part 91 a of the through hole 91. As a result, as shown in FIG. 9, the first sliding portion 62 moves relative to the shaft shaft 21 in the radial direction of the shaft shaft 21. Then, as shown in FIG. 10, the valve shaft 22 moves to the side away from the valve seat 13, and eventually the position of the central axis Lsb of the valve shaft 22 coincides with the position of the central axis Ls of the rotating shaft 15.

  As a result, the valve body 14 moves in the direction of the central axis Lh of the valve hole 16 and leaves the valve seat 13. Thus, when the valve is opened, the valve shaft 22 is separated from the valve seat 13 by the first sliding portion 62 of the valve shaft 22 being pushed by the arc portion 91a of the through hole 91 of the first bearing eccentric plate 81. The valve body 14 is moved away from the valve seat 13. Thus, the movable region of the valve shaft 22 has a valve seat orthogonal direction moving region (counter valve seat direction moving region) in which the valve shaft 22 moves in a direction away from the valve seat 13.

  Next, the flow rate adjustment valve 1 is further opened by further driving the motor 32. Then, as shown in FIGS. 11 and 12, the first sliding portion 62 of the valve shaft 22 receives the rotational force from the shaft shaft 21, thereby causing the arc portion 91 a of the through hole 91 of the first bearing eccentric plate 81 to move. While being supported, the valve shaft 22 rotates around the central axis Ls. At this time, as shown in FIG. 13, the valve body 14 rotates integrally with the valve shaft 22, but the valve body 14 rotates around the central axis Ls in a state where the valve body 14 is separated from the valve seat 13. . Thus, as the movable region of the valve shaft 22, the rotational force of the shaft shaft 21 that rotates about the central axis Ls acts on the valve shaft 22 in a state where the valve seat 13 and the valve body 14 are separated from each other. The shaft 22 has a rotation region that rotates about the central axis Ls. Thereafter, the valve body 14 reaches the fully open position. As described above, the valve opening operation of the flow rate adjusting valve 1 is performed.

  When the flow regulating valve 1 is closed, the valve shaft 22 rotates in the direction toward the valve seat 13 after the valve shaft 22 rotates about the central axis Ls in a state where the valve seat 13 and the valve body 14 are separated from each other. The valve body 14 is brought into contact with the valve seat 13 by moving. As described above, when the flow rate adjustment valve 1 is closed, as a movable region of the valve shaft 22, a rotation region in which the valve shaft 22 rotates about the central axis Ls in a state where the valve seat 13 and the valve body 14 are separated from each other, The valve shaft 22 has a valve seat orthogonal direction movement region (valve seat direction movement region) in which the valve shaft 22 moves in a direction toward the valve seat 13.

  In the flow rate adjusting valve 1 of the present embodiment as described above, the valve shaft 22 is pushed by the convex portion 91b of the first bearing eccentric plate 81 and the convex portion 91b of the second bearing eccentric plate 82 as the movable region of the valve shaft 22. Accordingly, the valve shaft 22 moves in the direction toward the valve seat 13 or in the direction away from the valve seat 13 by relatively moving in the radial direction of the shaft shaft 21 with respect to the shaft shaft 21. The rotational force of the shaft shaft 21 that rotates around the central axis Ls in a state where the valve seat 14 is moved away from the valve seat 13 and the valve seat orthogonal direction moving region is in contact with the valve seat 14 Acts on the valve shaft 22 so that the valve shaft 22 has a rotation region that rotates about the central axis Ls.

  Thus, in this embodiment, when the valve body 14 is in the vicinity of the valve seat 13, the valve body 14 moves in a direction toward the valve seat 13 or away from the valve seat 13, and the valve body 14 is separated from the valve seat 13. When in this position, the valve body 14 rotates about the central axis Ls. Thus, when the valve is opened, the valve body 14 is moved in a direction away from the valve seat 13, and then the valve body 14 is rotated around the central axis Ls in a state where the valve seat 13 and the valve body 14 are separated from each other. it can. Further, when the valve is closed, the valve body 14 is rotated about the central axis Ls in a state where the valve seat 13 and the valve body 14 are separated from each other, and then the valve body 14 is moved in a direction toward the valve seat 13 to thereby move the valve seat. 13 can be contacted. Therefore, sliding of the valve seat 13 and the valve body 14 due to the rotation of the valve body 14 can be suppressed when the valve is opened or closed. Therefore, sliding wear between the valve seat 13 and the valve body 14 can be suppressed with a relatively simple configuration and space saving. Therefore, since the sealing performance between the valve seat 13 and the valve body 14 is maintained, an increase in the amount of fluid leakage when fully closed can be prevented.

  Further, when fully closed, the valve shaft 22 is pushed in the direction toward the valve seat 13 by the convex portion 91b of the first bearing eccentric plate 81 and the convex portion 91b of the second bearing eccentric plate 82, and the valve body 14 is moved to the valve seat. 13 is in contact. Therefore, the sealing performance between the valve seat 13 and the valve body 14 is improved when fully closed.

  Further, as a connecting structure of the shaft shaft 21 and the valve shaft 22, a slit portion 52 provided in the shaft shaft 21 and a first sliding portion 62 provided in the valve shaft 22 are provided. The slit portion 52 is formed in a groove shape formed in the radial direction of the shaft shaft 21 at the end of the shaft shaft 21 on the valve shaft 22 side in the axial direction of the shaft shaft 21. The first sliding portion 62 is not rotatable relative to the shaft shaft 21 and is slidable in the radial direction of the shaft shaft 21 at the end of the valve shaft 22 on the shaft shaft 21 side in the axial direction of the valve shaft 22. In this state, it is inserted into the slit portion 52. Thereby, the valve shaft 22 can be moved in the direction toward the valve seat 13 or in the direction away from the valve seat 13 while restricting the rotation of the valve shaft 22 about the axis. As a connection structure between the shaft shaft 23 and the valve shaft 22, a slit portion 72 provided in the shaft shaft 23 and a second sliding portion 63 provided in the valve shaft 22 are provided.

  The first bearing eccentric plate 81 includes a through hole 91 into which the first sliding portion 62 is inserted, and the second bearing eccentric plate 82 includes a through hole 91 into which the second sliding portion 63 is inserted. The inner wall portion that forms 91 includes an arc portion 91a, a convex portion 91b, and a concave portion 91c. The first bearing eccentric plate 81 and the second bearing eccentric plate 82 move the valve shaft 22 in the direction toward the valve seat 13 or away from the valve seat 13 or stabilize the valve shaft 22 around the axis. And can be rotated.

  The flow rate adjusting valve 1 of the present embodiment is applied to, for example, an integrated valve 181 of an air system 113 in a fuel cell system 101 as described below.

  Therefore, the fuel cell system 101 will be described. The fuel cell system 101 is mounted on an electric automobile and used to supply electric power to a drive motor (not shown). As shown in FIG. 14, the fuel cell system 101 includes a fuel cell (FC stack) 111, a hydrogen system 112, and an air system 113.

  The fuel cell 111 generates power by receiving supply of fuel gas and supply of oxidant gas. In the present embodiment, the fuel gas is hydrogen gas, and the oxidant gas is air. That is, the fuel cell 111 generates power by receiving supply of hydrogen gas from the hydrogen system 112 and supply of air from the air system 113. The electric power generated by the fuel cell 111 is supplied to a drive motor (not shown) via an inverter (not shown).

  The hydrogen system 112 is provided on the anode side of the fuel cell 111. The hydrogen system 112 includes a hydrogen supply passage 121, a hydrogen discharge passage 122, and a filling passage 123. The hydrogen supply passage 121 is a passage for supplying hydrogen gas from the hydrogen tank 131 to the fuel cell 111. The hydrogen discharge passage 122 is a passage for discharging hydrogen gas discharged from the fuel cell 111 (hereinafter referred to as “hydrogen off-gas” as appropriate). The filling passage 123 is a passage for filling the hydrogen tank 131 with hydrogen gas from the filling port 151.

  The hydrogen system 112 includes a main stop valve 132, a high pressure regulator 133, an intermediate pressure relief valve 134, a pressure sensor 135, an injector unit 136, a low pressure relief valve 137, and a pressure sensor 138 in order from the hydrogen tank 131 side in the hydrogen supply passage 121. I have. The main stop valve 132 is a valve that switches between supply and shutoff of hydrogen gas from the hydrogen tank 131 to the hydrogen supply passage 121. The high pressure regulator 133 is a pressure adjustment valve for reducing the pressure of hydrogen gas. The intermediate pressure relief valve 134 is a valve that opens when the pressure between the high pressure regulator 133 and the injector unit 136 in the hydrogen supply passage 121 exceeds a predetermined pressure, and adjusts the pressure below the predetermined pressure. The pressure sensor 135 is a sensor that detects the pressure between the high-pressure regulator 133 and the injector unit 136 in the hydrogen supply passage 121. The injector unit 136 is a mechanism that adjusts the flow rate of hydrogen gas. The low-pressure relief valve 137 is a valve that opens when the pressure between the injector section 136 and the fuel cell 111 in the hydrogen supply passage 121 is equal to or higher than a predetermined pressure, and adjusts the pressure to be lower than the predetermined pressure. The pressure sensor 138 is a sensor that detects the pressure between the injector 136 and the fuel cell 111 in the hydrogen supply passage 121.

  In the hydrogen system 112, a gas-liquid separator 141 and an exhaust drain valve 142 are arranged in this order from the fuel cell 111 side in the hydrogen discharge passage 122. The gas-liquid separator 141 is a device that separates moisture in the hydrogen off-gas. The exhaust / drain valve 142 is a valve that switches between discharging and shutting off hydrogen off-gas and moisture from the gas-liquid separator 141 to the diluter 182 of the air system 113.

  The air system 113 is provided on the cathode side of the fuel cell 111. The air system 113 includes an air supply passage 161, an air discharge passage 162, and a bypass passage 163. The air supply passage 161 is a passage for supplying air from the outside of the fuel cell system 101 to the fuel cell 111. The air discharge passage 162 is a passage for discharging air discharged from the fuel cell 111 (hereinafter, appropriately referred to as “air off gas”). The bypass passage 163 is a passage through which air flows from the air supply passage 161 to the air discharge passage 162 without passing through the fuel cell 111.

  The air system 113 includes an air pump 172, an intercooler 173, and a sealing valve 174 in order from the air cleaner 171 side in the air supply passage 161. The air cleaner 171 is a device that cleans the air taken from the outside of the fuel cell system 101. The air pump 172 is a device that adjusts the flow rate of air. The intercooler 173 is a device that cools air. The sealing valve 174 is a valve that switches between supplying and shutting off air to the fuel cell 111.

  In the air system 113, an integrated valve 181 and a diluter 182 are arranged in order from the fuel cell 111 side in the air discharge passage 162.

  The integrated valve 181 is a valve (a valve having an air sealing function) that switches between discharging and shutting off the air off gas from the fuel cell 111 and a valve that controls the amount of air off gas discharged from the fuel cell 111 (control of the flow rate). Valve with function). And in this embodiment, the flow regulating valve 1 of this invention is applied as the integrated valve 181. FIG.

  The diluter 182 is a device that dilutes the hydrogen off gas discharged from the hydrogen discharge passage 122 by the air off gas and the air flowing through the bypass passage 163.

  The air system 113 includes a bypass valve 191 in the bypass passage 163. The bypass valve 191 is a valve that controls the flow rate of air in the bypass passage 163.

  The fuel cell system 101 includes a controller 201 that controls the system. The controller 201 controls each device provided in the fuel cell system 101. The fuel cell system 101 also has a cooling system (not shown) that cools the fuel cell 111.

  In the fuel cell system 101 configured as described above, the hydrogen gas supplied from the hydrogen supply passage 121 to the fuel cell 111 is used for power generation in the fuel cell 111, and then the hydrogen discharge passage from the fuel cell 111 as hydrogen off-gas. It is discharged to the outside of the fuel cell system 101 through 122 and the diluter 182. In addition, the air supplied from the air supply passage 161 to the fuel cell 111 is used for power generation in the fuel cell 111, and then the fuel cell system passes through the air discharge passage 162 and the diluter 182 as air off gas from the fuel cell 111. 101 is discharged to the outside.

  In such a fuel cell system 101, the flow rate adjustment valve 1 of this embodiment is applied to the integrated valve 181 in the air system 113. Thereby, the integrated valve 181 can suppress sliding wear of the valve seat 13 and the valve body 14 with a relatively simple configuration and space saving. Therefore, the integrated valve 181 can prevent an increase in the air leakage flow rate when fully closed. Therefore, for example, when the power generation of the fuel cell 111 is stopped, the hydrogen discharge passage 122 is blocked by the integrated valve 181 so that air is not easily sucked into the fuel cell 111. Therefore, the reaction does not easily occur in the fuel cell 111, and deterioration due to oxidation in the fuel cell 111 can be suppressed.

  The flow rate adjusting valve 1 of the present embodiment can also be applied to valves other than the integrated valve 181 in the fuel cell system 101, for example, the sealing valve 174 and the bypass valve 191 in the air system 113.

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

DESCRIPTION OF SYMBOLS 1 Flow control valve 13 Valve seat 14 Valve body 15 Rotary shaft 16 Valve hole 21 Shaft shaft 22 Valve shaft 23 Shaft shaft 51 Base end portion 52 Slit portion 52a Side surface 52b Side surface 61 Main body portion 62 First sliding portion 62a Convex portion 62b Convex Part 63 second sliding part 71 slit part 81 first bearing eccentric plate 91 through hole 91a arc part 91b convex part 91c concave part 82 second bearing eccentric plate 101 fuel cell system 174 sealing valve 181 integrated valve 191 bypass valve Ls (rotation) Center axis Lsb (Valve shaft) Center axis Lh (Valve hole) Center axis

Claims (3)

A valve seat, a valve body, a rotation shaft provided integrally with the valve body and rotating the valve body, and a driving force provided integrally with the rotation shaft and rotating the rotation shaft in a valve opening direction; A flow rate adjusting valve having a driving force receiving portion for receiving,
The rotation shaft is provided with a first rotation shaft provided integrally with the driving force receiving portion, and is moved integrally with the valve body in the radial direction of the first rotation shaft with respect to the first rotation shaft. A second rotating shaft coupled to the axial end of the first rotating shaft in a possible state,
A bearing member for supporting the second rotating shaft;
As the movable region of the second rotating shaft,
The second rotating shaft is pushed by the bearing member and relatively moves in the radial direction of the first rotating shaft with respect to the first rotating shaft, so that the second rotating shaft moves toward the valve seat or the Moving in a direction away from the valve seat to bring the valve body into contact with the valve seat, or to move the valve body away from the valve seat;
When the valve seat and the valve body are separated from each other, the rotational force of the first rotating shaft that rotates about the shaft acts on the second rotating shaft, whereby the second rotating shaft rotates about the shaft. Having an area,
A flow control valve characterized by The flow regulating valve according to claim 1,
As a connection structure of the first rotating shaft and the second rotating shaft,
A groove-shaped slit formed at the end of the first rotating shaft on the second rotating shaft side in the axial direction of the first rotating shaft, and formed in the radial direction of the first rotating shaft;
The second rotation shaft is formed at an end portion on the first rotation shaft side in the axial direction of the second rotation shaft, cannot be relatively rotated with respect to the first rotation shaft, and is in a radial direction of the first rotation shaft. A sliding part to be inserted into the slit part in a slidable state is provided;
A flow control valve characterized by The flow regulating valve according to claim 2,
The bearing member includes a through hole into which the sliding portion is inserted,
The inner wall forming the through hole is
An arc part formed in a part of a circular shape centering on the central axis of the first rotation axis, and supporting the sliding part when the second rotation axis rotates about the axis;
A convex portion for pushing the sliding portion when the second rotation shaft moves in a direction toward the valve seat;
A concave portion formed to be recessed toward the outer side of the circular shape and into which the sliding portion pressed by the convex portion is fitted,
A flow control valve characterized by

Images