JP2011033088A - Three-way valve - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a three-way valve capable of accurately performing set proportional flow rate control even when a distance between abutting surfaces of a valve element and a valve seat is small, and capable of reducing the motor load for driving the valve element. <P>SOLUTION: A first valve element 4a and a second valve element 4b attached to a shaft 7a movable in the axial direction by driving of a motor are arranged in a linear channel 14a of the three-way valve. A first valve seat 18a abutted with the first valve element 4a and a second valve seat 19a abutted with the second valve element 4b are formed in the linear channel 14a. The abutting surfaces of the first valve element 4a and the first valve seat 18a and the abutting surfaces of the second valve element 4b and the second valve seat 19a are formed in a plane surface orthogonal to the axial direction of the shaft 7a. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present invention relates to a three-way valve, for example, a three-way valve used as a diversion valve or a mixing valve for a fluid such as water or hot water.

  Conventionally, as a three-way valve of this type, for example, a schematic configuration of a diversion valve has an input port at an intermediate position of a linear flow path, and a first port and a second port that serve as output ports at both ends of the linear flow path. Is forming. In the straight flow path, a first valve body that contacts or separates from the first valve seat on the first port side and a second valve body that contacts or separates from the second valve seat on the second port side are provided. It is arranged. The first valve body and the second valve body are attached to a shaft that moves in the axial direction by driving a motor, and the shaft positions are moved in the axial direction to set the valve positions of the first valve body and the second valve body. The flow control of the port and the second port is performed. In such a diversion, for example, when the flow rate flowing through the first port decreases proportionally, the flow rate flowing through the second port increases proportionally (see FIG. 11).

Japanese Patent Laid-Open No. 1-150076

  By the way, as for the conventional three-way valve currently disclosed by patent document 1, in order to improve the sealing performance of a valve seat and a valve body, the mutual contact surface of a valve seat and a valve body is formed in the taper shape. . Therefore, when the distance between the contact surfaces of the valve body and the valve seat is reduced, the flow rate of the fluid passing between the contact surfaces is increased, and the output port side is under negative pressure. As a result, the valve body is strongly pulled toward the valve closing side just before the valve body and the valve seat come into contact with each other.

  For example, even if the motor feed amount is set so that the distance between the contact surfaces of the first valve body and the first valve seat is kept small, the first valve body is strongly pulled into the first valve seat and the shaft is also motorized. The first valve body is seated on the first valve seat and closes as it moves against the feed amount, and as shown by the dotted line in FIG. 11, the flow rate of the first port becomes zero and the predetermined flow rate cannot be set. . Therefore, there is a problem that the set proportional flow rate control cannot be performed at a position where the distance between the contact surfaces of the valve body and the valve seat is small.

  In addition, when the valve body is pulled in strongly and closed, the valve body is strongly adhered to the valve seat by the wedge action on the tapered contact surface of the valve body and the valve seat, and the shaft is opened when the valve body is opened. A large load is applied to the motor that drives the motor.

  The present invention has been made in view of the above circumstances, and the object thereof is to accurately perform proportional flow rate control and drive the valve body even when the distance between the contact surface of the valve body and the valve seat is small. An object of the present invention is to provide a three-way valve that can reduce the motor load.

The three-way valve according to the present invention includes a first port and a second port communicating with a straight flow path, and a third port communicating between the first port and the second port in the straight flow path, A shaft that is movable in the axial direction by a motor drive and a first valve body and a second valve body that are attached to the shaft are disposed in the road, and the first valve that contacts or separates from the first valve body. A seat is formed between the first port and the third port of the linear flow path, and a second valve seat with which the second valve body abuts or separates is formed between the second port and the third port of the linear flow path. A three-way valve formed between
The mutual contact surfaces of the first valve body and the first valve seat and the mutual contact surfaces of the second valve body and the second valve seat are formed by a plane orthogonal to the axial direction of the shaft. Yes.

  According to the above configuration, the fluid flowing from the third port to the first port or the second port changes the direction of flow to the direction perpendicular to the axial direction after colliding with the contact surface of the valve seat, and the valve body and the valve It passes between the contact surfaces of the seat. Thereby, the flow velocity of the fluid flowing between the contact surfaces of the valve body and the valve seat can be reduced. Furthermore, after the fluid flowing between the contact surfaces of the valve body and the valve seat collides with the contact surface of the valve seat, pressure acts on the contact surface of the valve body in a direction away from the contact surface of the valve seat. To do. Therefore, even when the distance between the contact surfaces is set to be small, the valve body is not strongly pulled into the valve seat due to the decrease in the flow velocity and the pressure of the fluid acting on the contact surface of the valve body. Therefore, even when the distance between the contact surface of the valve body and the valve seat is small, the distance between the contact surface of the valve body and the valve seat can be maintained at the set value by the accurate stroke of the shaft, and proportional flow rate control is accurate. It can be done.

  In addition, since each contact surface of the valve body and the valve seat is formed by a plane orthogonal to the axial direction of the shaft, when each contact surface contacts, a wedge action occurs like a conventional three-way valve. Adhesiveness can be suppressed compared with the case where taper-shaped contact surfaces are contacted. Therefore, the valve body that has been in contact with the valve seat can be easily separated from the valve seat, and the load on the motor that drives the shaft can be reduced. As a result, the life of the motor can be extended. .

Further, in the three-way valve of the present invention, the first valve body is formed with a tapered surface on the first port side with respect to the contact surface with the first valve seat, and the second valve body is connected to the second valve seat. It is preferable that a side surface including a tapered surface is formed on the second port side with respect to the contact surface.
Thereby, the change degree with respect to the axial movement amount of the flow path cross-sectional area of the gap formed between the tapered surface and the inner wall of the straight flow path can be set, and the change degree of the flow rate flowing through the first port The degree of change in the flow rate flowing through the second port can be set and controlled to a desired distribution ratio.

  Further, in the three-way valve of the present invention, the first valve body and the second valve body are joined in contact with each other and inserted through the shaft, and the shaft is supported by the support means for restricting movement in the axial direction. It is preferably fixed.

  For example, the first valve body and the second valve body may be connected to a shaft via a spring that urges the valve bodies in a direction that separates the valve bodies from each other, and a support unit that restricts movement in the axial direction due to the urging force of the springs. When the initial position of the valve body is set, the distance between the valve body and the valve seat is likely to vary due to an error in dimensional accuracy of each member.

  On the other hand, according to the above configuration, each valve body is directly joined and fixed to the shaft without interposing a spring, so that the fixed position of each valve body with respect to the shaft is always constant. Therefore, the position where the valve element hits the valve seat can always be fixed as the control start position, so that accurate flow rate control can be performed.

Furthermore, in the three-way valve of the present invention, it is preferable that the first valve body and the second valve body are formed with a plurality of guide portions that are always in contact with the inner wall of the linear flow path.
As a result, the valve body is not vibrated by the fluid, and generation of vibration noise can be prevented. Furthermore, even if the valve body moves in the axial direction, the valve body can be prevented from tilting, so that the flow path cross-sectional area can be kept constant, and variations in flow rate can be suppressed.

  As described above, according to the three-way valve of the present invention, even when the distance between the contact surfaces of the valve body and the valve seat is set small, the decrease in the flow velocity and the pressure of the fluid acting on the contact surface of the valve body Thus, the distance between the contact surfaces can be maintained at a set value by an accurate stroke of the shaft, and proportional flow rate control can be accurately performed. In addition, since the valve element that has been in contact with the valve seat can be easily separated from the valve seat, the load on the motor that drives the shaft can be reduced, and the life of the motor can be extended.

It is sectional drawing which shows an example of the state by which the 3rd port and 2nd port of the shunt valve (three-way valve) which concern on Embodiment 1 of this invention were interrupted | blocked. It is sectional drawing which shows an example of the state which the 1st port and 2nd port of the flow dividing valve (three-way valve) which concern on Embodiment 1 of this invention are connecting with the 3rd port. It is a perspective view of the 1st valve body used for a diversion valve (three-way valve) concerning Embodiment 1 of the present invention, and is a perspective view seen from the 1st umbrella part side. It is the perspective view which looked at the 1st valve body shown in FIG. 3 from the end surface on the opposite side. It is a perspective view of the 2nd valve body used for a diversion valve (three-way valve) concerning Embodiment 1 of the present invention, and is a perspective view seen from the 2nd umbrella part side. It is the perspective view which looked at the 2nd valve body shown in FIG. 5 from the end surface on the opposite side. It is sectional drawing which shows an example of the state by which the 3rd port and 2nd port of the shunt valve (three-way valve) which concern on Embodiment 2 of this invention were interrupted | blocked. It is sectional drawing which shows an example of the state which the 1st port and 2nd port of the shunt valve (three-way valve) which concern on Embodiment 2 of this invention are connecting with the 3rd port. It is the perspective view of the valve body used for the diversion valve (three-way valve) which concerns on Embodiment 2 of this invention, Comprising: It is the perspective view seen from the collar part side. It is the perspective view which looked at the valve body shown in FIG. 9 from the end surface on the opposite side. It is a graph which shows the relationship between the flow volume of the fluid which flows through a 1st port and a 2nd port, and the feed amount of the motor which drives a shaft.

(Embodiment 1)
Embodiment 1 of the present invention will be described below with reference to the accompanying drawings.
1 and 2 show a diversion valve as an embodiment of a three-way valve according to the present invention. The shunt valve according to the first embodiment includes a casing 1a having first and second ports 11a and 12a serving as output ports and a third port 13a serving as an input port.

  The casing 1a has a cylindrical main body 2a having a first port 11a, a second port 12a and a third port 13a on its side surface, and is inserted into a cylinder of the main body 2a via a packing 61a. The shaft guide member 3a is formed with an internal passage communicating with the port 13a.

  In the casing 1a, a linear flow path 14a is formed by the main body 2a and the shaft guide member 3a. A first flow path 15a is formed by the shaft guide member 3a in a direction perpendicular to the straight flow path 14a. A second flow path 16a and a third flow path 17a are formed in a direction perpendicular to the path 14a. The first channel 15a communicates with the first port 11a, the second channel 16a communicates with the second port 12a, and the third channel 17a communicates with the third port 13a.

  In the straight flow path 14a, a first valve body 4a and a second valve body 4b attached to a shaft 7a that can be moved in the axial direction by driving a motor are disposed. And the end surface arrange | positioned in the main body 2a of the shaft guide member 3a is made into the 1st valve seat 18a to which the 1st valve body 4a contact | abuts or spaces apart. Further, a step portion 21a having a small channel cross-sectional area is formed on the second flow passage 16a side in the straight flow passage 14a, and the second valve seat 4b abuts or separates from the step portion 21a. 19a. In the first embodiment, the mutual contact surfaces of the first valve body 4a and the first valve seat 18a and the mutual contact surfaces of the second valve body 4b and the second valve seat 19a are formed on the shaft 7a. It is formed by a plane orthogonal to the axial direction.

  Further, the first valve body 4a and the second valve body 4b have different shapes. 1-4, the 1st valve body 4a is integrally formed in the end of this 1st cylinder part 42a and the 1st cylinder part 42a which has the 1st insertion hole 41a in which the shaft 7a is penetrated. A first umbrella portion 43a and a first step portion 44a formed at the other end of the first tube portion 42a. The 1st step part 44a is formed in the inner peripheral surface side, and is fitted with the 2nd step part 44b formed in the 2nd cylinder part 42b of the 2nd valve body 4b. Furthermore, the 1st collar part 45a extended in the direction orthogonal to the axial direction of the shaft 7a is formed in the outer periphery of the 1st umbrella part 43a. The surface of the first flange 45a opposite to the first step portion 44a is formed in a plane perpendicular to the axial direction, and this plane abuts against the first valve seat 18a in a surface contact state. It becomes the tangent surface.

  Further, the side surface of the first umbrella portion 43a of the first valve body 4a is formed with a first tapered surface 46a that extends from one end side of the first tube portion 42a toward the other end side where the first step portion 44a is formed. Yes. Four first guide portions 47a are formed on the first tapered surface 46a at equal intervals in the circumferential direction. The first guide portion 47a extends in the axial direction and is formed so as to protrude outward in the radial direction, and is always in contact with the inner wall of the linear flow path 14a of the shaft guide member 3a. In the first embodiment, a flow path is formed by the wall surface of the first guide portion 47a and the first tapered surface 46a.

  As shown in FIGS. 1, 2, 5, and 6, the second valve body 4b includes a second cylinder portion 42b having a second insertion hole 41b through which the shaft 7a is inserted, and the second cylinder portion 42b. A second umbrella portion 43b formed integrally at one end and a second stepped portion 44b formed at the other end of the second tube portion 42b are provided. The 2nd step part 44b is formed in the outer peripheral surface side, and is fitted with the 1st step part 44a of the 1st valve body 4a. Furthermore, the 2nd collar part 45b extended in the direction orthogonal to the axial direction of the shaft 7a is formed in the outer periphery of the 2nd umbrella part 43b. The surface of the second flange 45b opposite to the second step portion 44b is formed in a plane perpendicular to the axial direction, and this plane abuts against the second valve seat 19a in a surface contact state. It becomes the tangent surface.

  Furthermore, the side surface of the second umbrella portion 43b of the second valve body 4b is continuous with the circumferential surface 48b formed at the end portion on the opposite side to the second step portion 44b in the axial direction, and the circumferential surface 48b. A second tapered surface 46b is formed so as to expand from the circumferential surface 48b toward the second stepped portion 44b. Four second guide portions 47b are formed at equal intervals in the circumferential direction on the circumferential surface 48b and the second tapered surface 46b. The second guide portion 47b extends in the axial direction and extends outward in the radial direction, and always comes into contact with the inner wall of the linear channel 14a having a small diameter near the step portion 21a. ing. In the first embodiment, a flow path is formed by the wall surface of the second guide portion 47b, the circumferential surface 48b, and the second tapered surface 46b.

  The first step portion 44a of the first valve body 4a and the second step portion 44b of the second valve body 4b are fitted in a close contact state so that the valve bodies 4a and 4b cannot rotate individually. Further, the first valve body 4a and the second valve body 4b are the distance between the first flange 45a and the second flange 45b in a state where the first step 44a and the second step 44b are fitted together. The lengths of the first cylinder part 42a and the second cylinder part 42b are set so that is larger than the inner diameter of the third port 17a.

  In the first embodiment, the first taper surface 46a of the first valve body 4a and the second taper surface 46b of the second valve body 4b have different taper angles. The first taper surface 46a is set so that the taper angle is smaller than that of the second taper surface 46b. Further, the axial length of the first tapered surface 46a is longer than that of the second tapered surface 46b. Thus, by changing the taper angle and the axial length of the first taper surface 46a and the second taper surface 46b, the change degree (gradient) of the flow rate from the third port 13a to the first port 11a can be changed. The flow rate change degree (gradient) from the third port 13a to the second port 12a can be set and controlled to achieve a desired distribution ratio. The taper angles of the tapered surfaces of the first valve body 4a and the second valve body 4b may be the same angle.

  The shaft 7a is inserted through the shaft guide member 3a and supported by the bearing portion 33a of the shaft guide member 3a via the seal member 62a. The shaft 7a has a first small diameter portion 71a to which the first valve body 4a and the second valve body 4b are attached on one end side, and a second small diameter portion 72a to which the drive gear 8a is attached on the other end side. A large diameter portion 73a is formed between the first small diameter portion 71a and the second small diameter portion 72a. A stepped portion 76a is formed by the large diameter portion 73a and the first small diameter portion 71a. A projection 77a is formed on the first small diameter portion 71a continuously to a part of the stepped portion 76a, and a recess 48a into which the projection 77a is fitted at the end of the first insertion hole 41a of the first valve body 4a. Is formed. Then, the combined first valve body 4a and second valve body 4b are inserted through the first small-diameter portion 71a, the recess 48a is fitted into the projection 77a, and then the ring-shaped push nut 78a is attached to the second valve body 4b. By press-contacting, the movement of the first valve body 4a and the second valve body 4b in the axial direction is restricted by the stepped portion 76a and the push nut 78a, and is fixed to the shaft 7a. Further, by fitting the recess 48a to the protrusion 77a, the rotation of the combined first valve body 4a and second valve body 4b with respect to the shaft 7a is prevented.

  The drive gear 8a inserted through the second small diameter portion 72a of the shaft 7a has a through hole 81a having substantially the same diameter as the second small diameter portion 72a of the shaft 7a, and the outer peripheral surface of the gear support portion 31a of the shaft guide member 3a. A male screw portion 82a that is screwed into the female screw portion 32a and a tooth portion 83a that is adjacent to the male screw portion 82a in the axial direction and meshes with the transmission gear 91 connected to the motor 9 are formed.

  One end of the drive gear 8a in the axial direction is received by a coil spring 5a inserted through the large diameter portion 73a of the shaft 7a via a washer 74a. One end of the coil spring 5a is received by a part of the shaft guide member 3a. A washer 74a for receiving the coil spring 5a can be brought into contact with a stepped end surface of the large diameter portion 73a. The other axial end of the drive gear 8a is received by an E-ring 75a fixed to the second small diameter portion 72a via another washer 74a. The drive gear 8a is attached to the shaft 7a while being pressed against the E ring 75a by the urging force of the coil spring 5a.

  Further, when the drive gear 8a is rotated by the drive of the motor 9, the male screw portion 82a is screwed with the female screw portion 32a of the shaft guide member 3a, so that the drive gear 8a moves in the axial direction. As the drive gear 8a moves, the shaft 7a also moves in the axial direction. The coil spring 5a is provided to prevent backlash in the axial direction of the drive gear 8a.

  And according to the flow dividing valve which concerns on this Embodiment 1, the fluid which flows in into the linear flow path 14a from the 3rd port 13a by driving the motor 9 and advancing / retracting the shaft 7a is made into 1st port 11a and 2nd. The flow is divided into an arbitrary diversion ratio with the port 12a.

  For example, as shown in FIG. 1, the second flange 45b of the second valve body 4b is brought into contact with the second valve seat 19a to shut off the second port 12a, and the fluid is allowed to flow out only from the first port 11a. Can do. From the state of FIG. 1, as shown in FIG. 2, the motor 9 is driven to move the shaft 7a to the first port 11a side, and the opening degree of the first valve body 4a relative to the first valve seat 18a and the second When the opening degree of the second valve body 4b with respect to the valve seat 19a is adjusted, the diversion ratio of the fluid flowing to the first port 11a and the second port 12a can be adjusted. Furthermore, the 1st valve body 4a can be made to contact | abut to the 1st valve seat 18a, and the 1st port 11a can also be interrupted | blocked.

  In the shunt valve of the first embodiment, when the fluid flowing into the linear flow path 14a from the third port 13a flows in the axial direction and flows between the valve body and the valve seat, the first valve seat 18a or the second valve It collides with the contact surface of the seat 19a. The fluid that collides with the contact surface changes the flow direction to a direction orthogonal to the axial direction, and flows along the first tapered surface 46a or the second tapered surface 46b. Therefore, the fluid flows between the first flange 45a of the first valve body 4a and the first valve seat 18a, or between the second flange 45b of the second valve body 4b and the second valve seat 19a. In this case, the flow rate decreases.

  Furthermore, after the collision with the first valve seat 18a or the second valve seat 19a, fluid that enters between the valve seat 18a or 19a and the flange 45a or 45b causes the flange 45a or 45b to enter the flange 45a or 45b from the valve seat 18a or 19a. Pressure is applied in the direction of leaving. Accordingly, when the gap between the contact surfaces of the valve seat 18a or 19a and the flange 45a or 45b is set small, the valve body 4a or the valve body 4a or the liquid due to the decrease in the flow velocity and the pressure of the fluid acting on the flange 45a or 45b. The gap between the contact surfaces can be maintained at the set value without 4b being pulled in the closing direction. As a result, even when the distance between the contact surfaces of the valve body 4a or 4b and the valve seat 18a or 19a is small, by setting the feed amount of the motor 9 and accurately controlling the stroke of the shaft 7a, the solid line in FIG. As shown in the figure, proportional flow control can always be performed accurately. Furthermore, even when the gap between the contact surfaces of the valve body 4a or 4b and the valve seat 18a or 19a is set small, the valve body 4a or 4b is not pulled in the closing direction by the fluid, so that the shaft 7a is driven. The load on the motor 9 can also be reduced.

  In addition, each contact surface of the valve body 4a or 4b and the valve seat 18a or 19a is formed by a plane orthogonal to the axial direction of the shaft 7a, so when the contact surfaces contact each other, the conventional three-way Adhesiveness can be suppressed as compared with the case where the tapered contact surfaces where the wedge action occurs such as a valve (Patent Document 1) are brought into contact with each other. As a result, the first valve body 4a or the second valve body 4b that has been in contact with the first valve seat 18a or the second valve seat 19a can be easily separated. Therefore, the load on the motor 9 that drives the shaft 7a can be reduced, and the life of the motor 9 can be extended.

  Moreover, in this Embodiment 1, the 1st valve body 4a and the 2nd valve body 4b are penetrated by the shaft 7a in the state which fitted and couple | bonded the 1st step part 44a and the 2nd step part 44b, and are a support means. The movement in the axial direction is restricted by a certain stepped portion 76a and the push nut 78a and is fixed to the shaft 7a. Thereby, the fixed position of the 1st valve body 4a and the 2nd valve body 4b with respect to the shaft 7a becomes always constant. As a result, between the first flange 45a and the first valve seat 18a of the first valve body 4a at the start of control, and between the second flange 45b and the second valve seat 19a of the second valve body 4b. Therefore, accurate flow rate control can be performed.

  In addition, the first tapered surface 46a of the first valve body 4a and the second tapered surface 46b of the second valve body 4b are cross-shaped first guide portions 47a that are always in contact with the inner peripheral surface of the linear flow path 14a. In addition, since the second guide portion 47b is formed, even if the first valve body 4a and the second valve body 4b are moved with the movement of the shaft 7a, the first valve body 4a and the second valve body 4b are not moved. There is no backlash. Therefore, no vibration noise is produced or tilted during use, and accurate flow rate control can be performed. The first guide portion 47a and the second guide portion 47b are formed in a cross shape in the first embodiment, but three guide portions may be provided at equal intervals in the circumferential direction.

(Embodiment 2)
Next, Embodiment 2 of the present invention will be described with reference to the accompanying drawings.
7 and 8 show a diversion valve according to the second embodiment. Similar to the first embodiment, a first port 11b, a second port 12b, and a third port 13b are formed in the casing 1b, and include a first valve body 40a and a second valve body 40b. The casing 1b includes a main body 2b and a shaft guide member 3b. Furthermore, a straight flow path 14b, a first flow path 15b, a second flow path 16b, and a third flow path 17b are formed in the casing 1b. The shaft guide member 3b includes a gear support portion 31b formed with a female screw portion 32b and a bearing portion 33b. The shaft 7b has a first small diameter portion 71b, a second small diameter portion 72b, and a large diameter portion 73b, and is supported by the bearing portion 33b via a seal member 62b. Two packings 61b are interposed between the outer peripheral surface of the shaft guide member 3b and the inner surface of the main body 2b, and the flow path formed in the casing 1b is sealed from the outside. Similarly to the first embodiment, the drive gear 8 b includes a through hole 81 b, a male screw portion 82 b, and a tooth portion 83 b that meshes with the transmission gear 91 connected to the motor 9. One end of the drive gear 8ba in the axial direction is received by the shaft guide member 3b via a coil spring 5a inserted through the shaft 7b. The coil spring 5a is provided to prevent backlash in the axial direction of the drive gear 8b. In the second embodiment, a coil spring 5b is provided between the first valve body 40a and the second valve body 40b attached to the shaft 7b to urge the valve bodies 40a and 40b in a direction in which they are separated from each other. . The coil spring 5b is also inserted through the shaft 7b.

  Both the first valve body 40a and the second valve body 40b have the same shape. 7 to 10, the first valve body 40a and the second valve body 40b have an insertion hole 49 through which the shaft 7b is inserted. The insertion hole 49 includes a first insertion portion 49a having an inner diameter substantially the same as the first small diameter portion 71b of the shaft 7b, and a first insertion portion 49a adjacent to the first insertion portion 49a and having a larger diameter than the inner diameter of the first insertion portion 49a. A second insertion portion 49b and a third insertion portion 49c adjacent to the second insertion portion 49b and having a diameter larger than the inner diameter of the second insertion portion 49b are formed.

  A ring-shaped seal member 63b is disposed in the second insertion portion 49b, and the shaft 7b and the valve bodies 40a and 40b are sealed by the seal member 63b. Furthermore, a ring plate-shaped receiving member 51b that receives the end of the coil spring 5b is disposed in the third insertion portion 49c. The third insertion portion 49c is formed in a size that allows the coil spring 5b to be inserted. A flange portion 50a is formed at the end of the first valve body 40a and the second valve body 40b on the third insertion portion 49c side, and the end surface of the flange portion 50a on the first insertion portion 49a side is a plane orthogonal to the axial direction. The first valve seat 18b formed on the end surface of the shaft guide member 3b or the second valve seat 19b formed on the stepped portion 21b of the main body 2b is brought into contact with each other in a surface contact state.

  Furthermore, the side surfaces of the first valve body 40a and the second valve body 40b are formed with tapered surfaces 50b that taper from the third insertion portion 49c side toward the first insertion portion 49a side. Similar to the first embodiment, four guide portions 50c are formed on the tapered surface 50b at equal intervals in the circumferential direction.

  The tapered surfaces 50b of the first valve body 40a and the second valve body 40b have the same taper angle in the second embodiment, but the degree of change (inclination) of the flow rate from the third port 13b to the first port 11b. ) And the change degree (inclination) of the flow rate from the third port 13b to the second port 12b, the taper surfaces 50b of the valve bodies 40a and 40b have different taper angles. . In this way, by changing the taper angle, the degree of change in the flow rate to the first port 11b and the second port 12b can be set.

  As in the first embodiment, the shaft 7b has a stepped portion 76b formed by the large diameter portion 73b and the first small diameter portion 71b, and a ring-shaped washer 74b is inserted so as to contact the stepped portion 76b. Next, the first valve body 40a is inserted through the first small diameter portion 71b, and the coil spring 5b is inserted through the first small diameter portion 71b, and then the second valve body 40b is inserted through the first small diameter portion 71b, With one ring-shaped washer 74b in contact with the second valve body 40b, the E-ring 75b is fitted into an annular groove formed in the first small diameter portion 71b.

  One end of the coil spring 5b provided between the first valve body 40a and the second valve body 40b is accommodated in the third insertion portion 49c of the first valve body 40a and received by the receiving member 51b, and the other end is second. It is accommodated in the third insertion part 49c of the valve body 40b and received by the receiving member 51b. The first valve body 40a and the second valve body 40b are fixed by being restricted from moving in the axial direction by the stepped portion 76b of the shaft 7b and the E-ring 75b in a state of being biased away from each other by the coil spring 5b. The

In the second embodiment, the axial length of the space formed between the first valve body 40a and the second valve body 40b is a length obtained by adding the diameter of the third port 13b and the maximum moving length of the shaft 7b. The first valve body 40a and the second valve body 40b are closed when the first valve body 40a or the second valve body 40b contacts the first valve seat 18b or the second valve seat 19b. Sometimes it is arranged so as not to face the third port 13b. Thereby, even if the 1st valve body 40a and the 2nd valve body 40b move the inside of the straight flow path 14b to an axial direction, the 1st valve body 40a and the 2nd valve body 40b do not oppose the 3rd port 13b. Can be. Therefore, the fluid flowing into the straight flow path 14b from the third port 13b does not collide with the first valve body 40a or the second valve body 40b from the side, and the valve bodies 40a, 40b and the straight flow path 14b The pressure flow can be reduced as much as possible by flowing from the gap formed between the inner wall and the first port 11b or the second port 12b. As a result, the overall flow rate of the fluid flowing from the third port 13b to the first port 11b and the second port 12b can be increased.
In the second embodiment described above, the same effects as those of the first embodiment can be obtained.

  The present invention is not limited to the above embodiment. In the above embodiment, the configuration in the case where the three-way valve is used as the flow dividing valve has been described. However, the first port and the second port serve as the two systems of fluid inlets, and the fluid outlet obtained by mixing the two systems of fluids serves as the fluid outlet. It can also be used as a mixing valve as the third port.

4a 1st valve body 4b 2nd valve body 5a, 5b Coil springs 7a, 7b Shaft 11a, 11b 1st port 12a, 12b 2nd port 13a, 13b 3rd port 14a, 14b Linear flow path 18a, 18b 1st valve seat 19a , 19b Second valve seat 45a First flange portion 46a First tapered surface 47a First guide portion 45b Second flange portion 46b Second tapered surface 47b Second guide portion 40a First valve body 40b Second valve body 50a flange 50b Tapered surface 50c guide part

Claims (4)

A first port and a second port communicating with the linear flow path; and a third port communicating between the first port and the second port in the linear flow path, and a shaft driven by a motor is driven in the linear flow path. A shaft that is movable in the direction and a first valve body and a second valve body that are attached to the shaft are disposed, and a first valve seat that contacts or separates from the first valve body is provided in the first flow path. A three-way valve formed between the 1st port and the 3rd port, and the 2nd valve seat which the 2nd valve body contacts or separates is formed between the 2nd port and the 3rd port of the above-mentioned straight flow path. There,
The mutual contact surfaces of the first valve body and the first valve seat and the mutual contact surfaces of the second valve body and the second valve seat are formed by a plane orthogonal to the axial direction of the shaft. There is a three-way valve. The three-way valve according to claim 1,
The first valve body is formed with a tapered surface on the first port side with respect to the contact surface with the first valve seat, and the second valve body is on the second port side with respect to the contact surface with the second valve seat. A three-way valve with a tapered side. In the three-way valve according to claim 1 or 2,
The first valve body and the second valve body are joined in contact with each other, inserted through the shaft, and fixed to the shaft by support means for restricting movement in the axial direction. In the three-way valve in any one of Claim 1 to 3,
A three-way valve in which a plurality of guide portions that are always in contact with the inner wall of the linear flow path are formed in the first valve body and the second valve body.