JP2005003190A - Flow dividing valve and mixing valve - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a flow dividing valve and a mixing valve enabling a reduction in costs and space. <P>SOLUTION: In this flow dividing valve 10, a first valve element 15 and a second valve element 16 coming into contact with or apart from a first valve seat 41 and a second valve seat 51 are mounted between both ends of an E-ring 22 fixed to a shaft 20 driven by a motor 30 through a spring 19. Thus, since the shaft 20 is moved by a motor 30, the first valve element is brought into contact with/separated from the first valve seat 41 and the second valve element is brought into contact with/separated from the second valve seat 51. Since an input port 11 is allowed to communicate with or cut out from a first output port 12 or a second output port 13, the fluid flowing into an input port 11 is divided into the first output port 12 and the second output port 13. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

  The present invention relates to a motor-driven proportional valve. More specifically, the present invention relates to a diversion valve for distributing the flow rate of a fluid (gas, air, hot water, etc.) used in a fuel cell or the like into two systems, and a mixing valve for mixing fluid input from the two systems It is.

  Conventionally, in a fuel cell or the like, two flow rate adjustment valves are used to distribute the flow rates of fluids such as gas, air, and water into two systems. Also, when adjusting the fluid temperature by mixing two series of fluids having different temperatures, two flow rate adjusting valves are used. And as a flow regulating valve currently used for such a diversion or mixing, there is what is indicated by JP, 2000-97359, A, for example. As shown in FIG. 11, the flow rate adjusting valve includes a valve unit 108 that controls the flow rate of fluid, a driving unit that drives the valve unit 108, and a control unit that controls the driving unit. The DC motor 101 is driven at a high driving voltage at the beginning of at least one of the valve opening operation and the valve closing operation at 108, and is driven at a low voltage after a predetermined time has elapsed. That is, the direct current motor 101 drives the valve unit 108 to open and close the valve.

  When adjusting the fluid temperature by mixing two series of fluids with different temperatures, use two flow control valves as flow paths with one fixed and the other using a flow control valve. May be mixed.

JP 2000-97359 A (pages 4-5, FIG. 1)

  However, as described above, at present, a flow rate adjusting valve as disclosed in Japanese Patent Laid-Open No. 2000-97359 is used in order to distribute the flow rate of the fluid into two systems or to mix fluids input from the two systems. Because two were used, a dedicated controller was required for each. That is, not only the flow rate adjusting valve but also two controllers are required. For this reason, there were problems in terms of cost and exclusive space. This is because the flow dividing valve or the mixing valve used in the apparatus such as the fuel cell is required to reduce cost and save space.

  In addition, when the two series of fluids having different temperatures are mixed with only one flow rate adjusting valve, the above problem does not occur, but the fluid flowing through the fixed flow path always flows (the flow rate cannot be adjusted). Therefore, there is a problem that the adjustment range of the mixing ratio (that is, the temperature adjustment range) becomes small. This is a particularly serious problem when used in fuel cells. This is because a fuel cell needs to efficiently recover heat, and therefore requires a wide temperature adjustment range.

  Therefore, the present invention has been made to solve the above-described problems, and an object thereof is to provide a diversion valve and a mixing valve that can achieve cost reduction and space saving. Another object of the present invention is to reduce the cost and space of the mixing valve and to widen the adjustment range of the mixing ratio.

  A diversion valve according to the present invention made to solve the above problems is a diversion valve that diverts a fluid, and includes an input port, a first output port, a second output port, and the input port. And a first valve seat formed between the first output port, a second valve seat formed between the input port and the second output port, and the first valve. A first valve body that contacts and separates from the seat, a second valve body that contacts and separates from the second valve seat, and the first valve body and the second valve body are attached. And a motor for driving the shaft.

  In this diversion valve, the shaft on which the first valve body and the second valve body are attached is driven by a motor, whereby the first valve body comes into contact with and separates from the first valve seat. The second valve element comes into contact with and separates from the second valve seat. Thereby, the input port and the first output port or the second output port are communicated or blocked. That is, when the first valve body is in contact with the first valve seat, the second valve body is separated from the second valve seat, and the input port and the first output port are blocked, The input port communicates with the second output port. On the other hand, when the second valve body is in contact with the second valve seat, the first valve body is separated from the first valve seat, and the input port communicates with the first output port. The input port and the second output port are blocked. Thereby, the fluid flowing into the input port can be divided into the first output port and the second output port.

  Since the first valve body and the second valve body are fixed to the shaft driven by the motor, the first valve body and the second valve body are adjusted by adjusting the movement amount of the shaft. Can be stopped at any position. In other words, the opening between the first valve body and the first valve seat, or the opening between the second valve body and the second valve seat can be adjusted. Therefore, it is possible to freely change the flow rate flowing out from the first output port and the flow rate flowing out from the second output port (hereinafter, this flow rate ratio is referred to as “diversion ratio”).

  Such control of the diversion ratio can be performed by adjusting the driving amount of one motor, so that the diversion conventionally performed by two flow rate adjustment valves and two controllers is changed to one diversion valve. This can be done with one controller. Therefore, by using this diversion valve, it is possible to reduce the cost and the space of an apparatus such as a fuel cell.

  In the shunt valve according to the present invention, the spring for urging the first valve body and the second valve body in a direction to contact the first valve seat and the second valve seat, respectively, It is preferable that the first valve body and the second valve body are arranged with the spring sandwiched between both ends of the E-ring.

  By doing so, when the shaft is moved and the first valve body is brought into contact with the first valve seat, the shaft can further move in the direction of pressing the first valve body against the first valve seat. This is because the pressing force of the first valve body against the first valve seat by the force of the spring becomes stronger and the sealing performance can be improved. Similarly, when the shaft is moved to bring the second valve body into contact with the second valve seat, the shaft can further move in the direction of pressing the second valve body against the second valve seat. This is because the pressing force of the second valve body against the second valve seat by the force of the spring becomes stronger and the sealing performance can be improved. As described above, since the sealing performance can be improved, even if the fluid has a pressure of about 2 KPa, the flow can be accurately divided without causing leakage.

  In the flow dividing valve according to the present invention, it is preferable that at least one of the first valve body and the second valve body has a needle shape.

  This is because the accuracy of the flow rate adjustment can be improved. In particular, it is suitable for the case of diverting gas or air. In addition, if the valve body has a needle shape, the valve body will always be present in the valve seat, so even if the flow velocity of the fluid flowing through the valve increases, the valve body will not flow. This is because the valve seat can be reliably abutted and sealed.

  In the shunt valve according to the present invention, at least one of the first valve body and the second valve body is always in contact with the inner peripheral surface of the first valve seat or the second valve seat. It is desirable that a guide portion is formed.

  Thereby, even when the flow velocity of the fluid flowing in the valve is increased, the guide portion provided on at least one of the first valve body or the second valve body always has the first valve seat or the second valve seat. Since the first valve body and the second valve body are not flowed, the first valve body and the second valve seat are securely brought into contact with each other and sealed. Because you can.

  The mixing valve according to the present invention, which has been made in order to solve the above problems, is obtained by reversing the input / output relationship in the above-described diversion valve. That is, a mixing valve that mixes fluids, and is formed between a first input port, a second input port, an output port, and the first input port and the output port. A valve seat, a second valve seat formed between the second input port and the output port, a first valve body abutting and separating from the first valve seat, and the first A second valve body that contacts and separates from the second valve seat, a shaft to which the first valve body and the second valve body are attached, and a motor that drives the shaft. It is characterized by being.

  In this mixing valve, the shaft on which the first valve body and the second valve body are attached is driven by a motor, so that the first valve body comes into contact with and separates from the first valve seat. The second valve element comes into contact with and separates from the second valve seat. As a result, the first input port and the output port are communicated or blocked, and the second input port and the output port are communicated or blocked. That is, when the first valve body is in contact with the first valve seat, the second valve body is separated from the second valve seat, and the first input port and the output port are blocked, The second input port communicates with the output port. On the other hand, when the second valve body is in contact with the second valve seat, the first valve body is separated from the first valve seat, and the first input port and the output port communicate with each other. The second input port and the output port are blocked.

  Since the first valve body and the second valve body are fixed to the shaft driven by the motor, the first valve body and the second valve body are adjusted by adjusting the movement amount of the shaft. Can be stopped at any position. In other words, the opening between the first valve body and the first valve seat, or the opening between the second valve body and the second valve seat can be adjusted. As a result, the flow rate of the fluid supplied from the first input port to the output port and the flow rate of the fluid supplied from the second input port to the output port (hereinafter, this flow rate ratio is referred to as “mixing ratio”) can be freely set. Can be changed. Therefore, the adjustment range of the mixing ratio can be widened.

  Further, since the control of the mixing ratio can be performed by adjusting the driving amount of one motor, conventionally, in order to widen the adjustment range of the mixing ratio, two flow rate adjusting valves and two controllers are used. The mixing performed in step 1 can be performed by one shunt valve and one controller. Therefore, by using this mixing valve, it is possible to reduce the cost and space of an apparatus such as a fuel cell while widening the adjustment range of the mixing ratio.

  In the mixing valve according to the present invention, the spring for urging the first valve body and the second valve body in a direction to contact the first valve seat and the second valve seat, respectively, It is preferable that the first valve body and the second valve body are arranged with the spring sandwiched between both ends of the E-ring.

  By doing so, when the shaft is moved and the first valve body is brought into contact with the first valve seat, the shaft can further move in the direction of pressing the first valve body against the first valve seat. This is because the pressing force of the first valve body against the first valve seat by the force of the spring becomes stronger and the sealing performance can be improved. Similarly, when the shaft is moved to bring the second valve body into contact with the second valve seat, the shaft can further move in the direction of pressing the second valve body against the second valve seat. This is because the pressing force of the second valve body against the second valve seat by the force of the spring becomes stronger and the sealing performance can be improved. Thus, since the sealing performance can be improved, even if the fluid has a pressure of about 2 KPa, it can be accurately mixed without causing leakage.

  In the mixing valve according to the present invention, it is preferable that at least one of the first valve body and the second valve body has a needle shape.

  This is because the accuracy of the flow rate adjustment can be improved. In particular, it is suitable when gas or air is mixed. In addition, if the valve body has a needle shape, the valve body will always be present in the valve seat, so even if the flow velocity of the fluid flowing through the valve increases, the valve body will not flow. This is because the valve seat can be reliably abutted and sealed.

  In the mixing valve according to the present invention, at least one of the first valve body and the second valve body is always in contact with the inner peripheral surface of the first valve seat or the second valve seat. It is desirable that a guide portion is formed.

  Thereby, even when the flow velocity of the fluid flowing in the valve is increased, the guide portion provided on at least one of the first valve body or the second valve body always has the first valve seat or the second valve seat. Since the first valve body and the second valve body are not flowed, the first valve body and the second valve seat are securely brought into contact with each other and sealed. Because you can.

  According to the flow dividing valve which concerns on this invention, cost reduction and space saving can be achieved. Moreover, according to the mixing valve which concerns on this invention, cost reduction and space saving can be achieved, making the adjustment range of a mixing ratio wide.

  Hereinafter, a most preferred embodiment in which the diversion valve of the present invention is embodied will be described in detail based on the drawings. The diversion valve and the mixing valve according to the present embodiment are suitable for use in a fuel cell system.

(First embodiment)
First, the first embodiment will be described. In the first embodiment, a shunt valve will be described. Accordingly, FIG. 1 shows a schematic configuration of the flow dividing valve according to the first embodiment. FIG. 1 is a cross-sectional view showing a schematic configuration of the diversion valve 10. As shown in FIG. 1, the diversion valve 10 includes an input port 11, a first output port 12, a second output port 13, a valve chamber 14, a first valve body 15, and a second valve body 16. And a spring 19, a shaft 20, a shaft guide 21, an E-ring 22, a DC motor 30, and the like. The diversion valve 10 distributes the fluid flowing into the input port 11 to the first output port 12 and the second output port 13 at an arbitrary diversion ratio and causes the fluid to flow out.

  Here, a part of the valve chamber 14 and a first valve seat 41 are formed in the first body 40 in which the input port 11 and the first output port are formed. A part of the valve chamber 14 is opened on the lower surface of the first body 40 and is connected to a part of the valve chamber 14 formed in the second body 50 described later so that the valve chamber 14 is formed. It has become. Further, a first valve seat 41 is formed at a communication portion between the first output port 12 and the valve chamber 14. When the first valve body 15 (more precisely, a first valve seat 15a described later) abuts against the first valve seat 41, the input port 11 and the first output port 12 are shut off, and the first valve seat 41 When the first valve body 15 (more precisely, the first valve seat 15a) is separated from the input port 11, the input port 11 and the first output port 12 communicate with each other.

  The second body 50 is disposed below the first body 40. In the second body 50, the second output port 13 and a part of the valve chamber 14 are formed. A second valve seat 51 is formed at the communication portion between the second output port 13 and the valve chamber 14. That is, the second valve seat 51 is disposed so as to face the first valve seat 41. When the second valve body 16 (more precisely, a second valve seat 16a described later) comes into contact with the second valve seat 51, the input port 11 and the second output port 13 are blocked, and the second valve seat 51 When the second valve body 16 (more precisely, the second valve seat 16a) is separated from the input port 11, the input port 11 and the second output port 13 communicate with each other.

  And the 1st valve body 15 and the 2nd valve body 16 are arrange | positioned in the valve chamber 14 formed when the 1st body 40 and the 2nd body 50 connect. A first valve seat 15 a is attached to the outer periphery of the first valve body 15. When the first valve seat 15a comes into contact with or separates from the first valve seat 41, the input port 11 and the first output port 12 are blocked or communicated. A first spring retainer 17 is attached to the inner periphery of the first valve body 15. On the other hand, a second valve seat 16 a is attached to the outer periphery of the second valve body 16. When the second valve seat 16a comes into contact with or separates from the second valve seat 51, the input port 11 and the second output port 13 are blocked or communicated. A second spring retainer 18 is attached to the inner periphery of the second valve body 16.

  The first valve body 15 and the second valve body 16 are connected to the motor 30 attached to the upper portion of the first body 40 via the conversion mechanism 77, penetrate the first body 40, and have the other end. Is attached to the shaft 20 located at the top of the second body 50. Specifically, the first valve body 15 and the first valve body 15 are connected to both ends of the E ring 22 fixed to the lower portion of the shaft via springs 19 provided between the first spring holder 17 and the second spring holder 18. A two-valve body 16 is arranged. Therefore, the first valve body 15 and the second valve body 16 are respectively pressed against the E ring 22 side (the first valve seat 41 side and the second valve seat 51 side) by the biasing force of the spring 19. 20 is attached.

  The shaft 20 to which the first valve body 15 and the second valve body 16 are attached is slidably supported by the shaft guide 21 disposed on the upper portion of the first body 40, and as described above, the conversion mechanism 77. It is connected to the motor 30 via.

  Here, the conversion mechanism 77 will be described with reference to FIG. FIG. 2 is an exploded perspective view of the conversion mechanism. The conversion mechanism 77 includes a rotating member 78, a guide member 79, and the like. The guide member 79 is formed by molding a plastic material into a substantially cylindrical shape by injection molding. The guide member 79 is clamped at the lower end between the shaft guide 21 and the fastening plate 73, and is restricted from moving in the rotational direction. The guide member 79 has a pair of long holes 80 formed in the outer peripheral surface so as to be long in the axial direction. The shaft 20 has an upper end inserted into the guide member 79, and the engagement pin 81 is penetrated and fixed so as to pass through the long hole 80 of the guide member 79.

  On the other hand, the rotating member 78 is formed by injection molding of a plastic material into a bag shape, and is mounted so as to cover the distal end portion of the guide member 79. A pair of feed screws 82 are formed in a female thread shape on the inner peripheral surface of the rotating member 78, and both end portions of the engagement pins 81 are slidably fitted to the feed screw 22. The rotating member 78 is configured such that the convex portion 83 is uniquely positioned and engaged with the output shaft of the motor 30 and rotates with the rotation of the motor 30. Therefore, when the motor 30 rotates the rotating member 78, the engaging pin 81 is moved along the long hole 80 of the guide member 79 by the feed screw 82, and the shaft 20 is slid in the axial direction. Therefore, if the driving amount of the motor 30 is controlled, the moving amount of the shaft 20 can be adjusted. Thereby, the movement amount of the 1st valve body 15 and the 2nd valve body 16 to which the shaft 20 is being fixed can be adjusted.

  In this way, the shaft 20 moves in the vertical direction in the figure according to the drive amount of the motor 30. Since the first valve body 15 and the second valve body 16 are attached to the shaft 20, the first valve body 15 and the second valve body 16 also move in conjunction with the movement of the shaft 20. For this reason, the 1st valve body 15 and the 2nd valve body 16 can be stopped in arbitrary positions by stopping the shaft 20 in arbitrary positions. In this manner, in the diversion valve 10, the opening and closing of the valve and the flow rate adjustment are performed by driving the motor 30.

  Next, the operation of the flow dividing valve 10 having the above configuration will be described. First, a state where the diversion ratio is “OUT1 (flow rate of the first output port 12): OUT2 (flow rate of the second output port 13) = 10: 0” will be described with reference to FIG. In this state, the shaft 20 is lowered by driving the motor 30, and the second valve seat 16 a comes into contact with the second valve seat 51. Here, since the first valve body 15 and the second valve body 16 are disposed between both ends of the E-ring 22 via the spring 19, the second valve seat 16a comes into contact with the second valve seat 51. However, the shaft 20 is further lowered by about 1 mm and then stopped. Thereby, the force which presses the 2nd valve body sheet | seat 16a by the spring 19 against the 2nd valve seat 51 becomes large. For this reason, the sealing performance superior to the case where the second valve seat 16a is simply brought into contact with the second valve seat 51 is obtained. As a result, the input port 11 and the second output port 13 are completely blocked. On the other hand, the first valve body 16 is moved downward by the E-ring 22 when the shaft 20 is lowered. Therefore, the first valve seat 15a is separated from the first valve seat 41, and the input port 11 and the first output port 12 communicate with each other. Therefore, all the fluid that has flowed into the input port 11 flows out from the first output port 12.

  Next, the operation of the diversion valve 10 when the shaft 20 is raised by reversing the driving direction of the motor 30 from the state shown in FIG. 1 will be described with reference to FIGS. 3 and 4. 3 shows a state where the shunt ratio is “OUT1: OUT2 = 5: 5”, and FIG. 4 shows a state where the shunt ratio is “OUT1: OUT2 = 0: 10”.

  When the drive direction of the motor 30 is reversed and the shaft 20 is raised, the E-ring 22 contacts the second valve body 16. At this time, the first valve body 15 is also in contact with the E-ring 22 by the force of the spring 19. Thereafter, while maintaining this state, the first valve body 15 and the second valve body 16 rise together with the shaft 20. For this reason, the second valve seat 16 a is separated from the second valve seat 51. As a result, the input port 11 and the second output port 13 communicate with each other. That is, both the input port 11 and the first output port 12 and the second output port 13 communicate with each other.

  At this time, the ratio between the flow rate of the fluid flowing out from the first output port 12 and the flow rate of the fluid flowing out from the second output port 13, that is, the diversion ratio, is the opening area of the first output port 12 and the opening area of the second output port 13. It is determined by the ratio. Here, the opening area of the first output port 12 is determined by the distance between the first valve seat 41 and the first valve body 15, and the opening area of the second output port 13 is the second valve seat 51 and the second valve body. It is determined by the distance to 16. Since the positions of the first valve seat 41 and the second valve seat 51 are fixed, the diversion ratio is determined by the positions of the first valve body 15 and the second valve body 16. In other words, in a state where both the input port 11 and the first output port 12 and the second output port 13 are in communication, the diversion ratio can be adjusted depending on the positions of the first valve body 15 and the second valve body 16. Therefore, in the diversion valve 10, the first valve body 15 and the second valve body are both attached to the shaft 20, and the shaft 20 moves up and down according to the drive amount of the motor 30, so that the drive amount of the motor 30 is adjusted. Thus, the flow rate can be adjusted.

  The state shown in FIG. 3 is that the diversion ratio is “OUT1: OUT2 = 5: 5”. In order to achieve this state, the shaft 20 is raised by the motor 30 to a position where the distance between the first valve seat 41 and the first valve body 15 and the distance between the second valve seat 51 and the second valve body 16 are equal. You can do that.

  Further, when the shaft 20 is raised, the first valve seat 15 a comes into contact with the first valve seat 41. Here, since the first valve body 15 and the second valve body 16 are disposed between both ends of the E-ring 22 via the spring 19, the first valve seat 15 a comes into contact with the first valve seat 41. However, as shown in FIG. 4, the shaft 20 is further raised by about 1 mm and then stopped. Thereby, the force which presses the 1st valve seat 15a by the spring 19 against the 1st valve seat 41 becomes large. For this reason, the sealing performance superior to the case where the first valve seat 15a is simply brought into contact with the first valve seat 41 is obtained. As a result, the input port 11 and the first output port 12 are completely blocked. For this reason, all the fluid that has flowed into the input port 11 flows out from the second output port 13.

  As described above, the flow dividing valve 10 distributes the fluid flowing into the input port 11 to the first output port 12 and the second output port 13 at an arbitrary flow dividing ratio by providing only one controller for driving the motor 30. be able to. That is, the diversion valve 10 can perform diversion, which conventionally requires two flow rate adjustment valves and two controllers, with one diversion valve and one controller. Therefore, by using the diversion valve 10 in a device such as a fuel cell, it is possible to reduce costs and save space.

  Here, a modified example of the flow dividing valve 10 will be described with reference to FIG. FIG. 5 is a cross-sectional view showing a configuration of a diversion valve 10a which is a modified example. This diversion valve 10a has substantially the same configuration as the diversion valve 10 described above, but differs in that a guide is provided in the second valve body 16. For this reason, in the following description, it demonstrates centering around difference, attaches | subjects the same code | symbol about a common point, and abbreviate | omits description suitably.

  As shown in FIG. 5, a guide 16b is formed at the distal end (second valve seat 51 side) of the second valve body 16 in the diversion valve 10a. The guide 16b is formed along the inner peripheral surface of the second valve seat 51. Even when the second valve seat 16a is separated from the second valve seat 51, the guide 16b is formed on the inner peripheral surface of the second valve seat 51. It touches. That is, the second valve body 16 contacts and separates from the second valve seat 51 while maintaining the state where the guide 16b is in contact with the inner peripheral surface of the second valve seat 51. Thereby, even when the flow velocity of the fluid flowing in from the input port 11 is large, the guide 16b formed in the second valve body 16 is always present in the second valve seat 51, so that the shaft 20 is firmly supported by the shaft guide 21 and the guide 16b at the upper and lower ends. Therefore, even if the flow velocity of the fluid flowing in from the input port 11 is large, the first valve body 15 and the second valve body 16 are not flown. The first valve seat 41 and the second valve seat 51 can be reliably brought into contact with each other.

  As described above, in the flow dividing valve 10 according to the first embodiment as described in detail, the shaft 20 on which the first valve body 15 and the second valve body 16 are fixed by the motor 30 is driven. The first valve seat 15 a contacts and separates from the first valve seat 41, and the second valve seat 16 a contacts and separates from the second valve seat 51. As a result, the input port 11 and the first output port 12 or the second output port 13 are communicated or blocked, so that the fluid flowing into the input port 11 is divided into the first output port 12 and the second output port 13. Can do.

  Since the first valve body 15 and the second valve body 16 are fixed to the shaft 20 driven by the motor 30, the first valve body 15 and the second valve body 15 are adjusted by adjusting the amount of movement of the shaft 20. The valve body 16 can be stopped at a desired position. That is, the opening degree between the first valve body 15 and the first valve seat 41 or the opening degree between the second valve body 16 and the second valve seat 51 can be adjusted. Therefore, the diversion ratio can be freely changed.

  Such control of the diversion ratio can be performed by adjusting the driving amount of one motor 30 in the diversion valve 10, and therefore, the diversion conventionally performed by two flow rate adjustment valves and two controllers. Can be performed by one shunt valve and one controller. Therefore, by using this diversion valve 10, it is possible to reduce the cost and space of an apparatus such as a fuel cell.

  Further, in the diversion valve 10, the first valve body 15 and the second valve body 16 are arranged with the springs 19 sandwiched between both ends of the E ring 22 fixed to the shaft 20. When the first valve seat 15a is brought into contact with the first valve seat 41 by being moved, the shaft 20 can further move in the direction of pressing the first valve body 15 against the first valve seat 41. The pressing force of the first valve body 15 against the first valve seat 41 due to the force is increased, and the sealing performance is improved. Similarly, when the shaft 20 is moved and the second valve seat 16 a is brought into contact with the second valve seat 51, the shaft 20 may further move in the direction of pressing the second valve body 16 against the second valve seat 51. Therefore, the pressing force of the second valve seat 16a against the second valve seat 51 by the force of the spring 19 is increased, and the sealing performance is improved. In this way, the flow dividing valve 10 improves the sealing performance, so that the flow can be accurately divided without causing leakage.

(Second Embodiment)
Next, a second embodiment will be described. The shunt valve will be described also in the second embodiment. The shunt valve according to the second embodiment has substantially the same configuration as the shunt valve 10 according to the first embodiment, but the shapes of the first valve body and the second valve body are different. For this reason, in the following description, it demonstrates centering around difference, attaches | subjects the same code | symbol about a common point, and abbreviate | omits description suitably. Accordingly, FIG. 6 shows a schematic configuration of the flow dividing valve according to the second embodiment. FIG. 6 is a cross-sectional view showing a schematic configuration of the diversion valve 60.

  Also in the diversion valve 60, the first valve body 65 and the second valve body 66 are connected to the motor 30 attached to the upper portion of the first body 40, penetrate the first body 40, and the other end is the second. It is attached to the shaft 20 located in the upper part of the body 50. Specifically, the first valve body 65 is connected to both ends of the E-ring 22 fixed to the lower portion of the shaft 20 via springs 19 provided between the first spring retainer 17 and the second spring retainer 18. A second valve body 66 is disposed. For this reason, the first valve body 65 and the second valve body 66 are pressed against the E ring 22 side (the first valve seat 41 side and the second valve seat 51 side) by the biasing force of the spring 19, respectively. 20 is attached.

  The shaft 20 to which the first valve body 65 and the second valve body 66 are attached is slidably supported by the shaft guide 21 disposed on the upper portion of the first body 40, and is mounted on the motor 30 as described above. It is connected. As a result, the shaft 20 moves in the vertical direction in the figure according to the drive amount of the motor 30. Since the first valve body 65 and the second valve body 66 are attached to the shaft 20, the first valve body 65 and the second valve body 66 also move in conjunction with the movement of the shaft 20. For this reason, the 1st valve body 65 and the 2nd valve body 66 can be stopped in arbitrary positions by stopping the shaft 20 in arbitrary positions. In this way, in the diversion valve 60, the opening and closing of the valve and the flow rate adjustment are performed by driving the motor 30.

  And since both the 1st valve body 65 and the 2nd valve body 66 have comprised the needle shape, it can adjust finely the flow volume when it spaces apart from the 1st valve seat 41 and the 2nd valve seat 51, respectively. It has become. In addition, since the first valve body 65 and the second valve body 66 are always present in the first valve seat 41 and the second valve seat 51, even when the flow velocity of the fluid flowing into the input port 11 is high, The first valve body 65 and the second valve body 66 are prevented from flowing.

  Next, the operation of the flow dividing valve 60 having the above configuration will be described. First, the state where the diversion ratio is “OUT1 (flow rate of the first output port 12): OUT2 (flow rate of the second output port 13) = 10: 0” will be described with reference to FIG. In this state, the shaft 20 is lowered by driving the motor 30, and the second valve seat 16 a comes into contact with the second valve seat 51. Here, since the first valve body 65 and the second valve body 66 are disposed between both ends of the E-ring 22 via the spring 19, the second valve seat 16a comes into contact with the second valve seat 51. However, the shaft 20 is further lowered by about 1 mm and then stopped. Thereby, the force which presses the 2nd valve body sheet | seat 16a by the spring 19 against the 2nd valve seat 51 becomes large. For this reason, the sealing performance superior to the case where the second valve seat 16a is simply brought into contact with the second valve seat 51 is obtained. At this time, since the first valve body 65 and the second valve body 66 are always present in the first valve seat 41 and the second valve seat 51, even when the flow velocity of the fluid flowing into the input port 11 is high. The first valve body 65 and the second valve body 66 are not flowed. Therefore, the input port 11 and the second output port 13 are completely blocked.

  On the other hand, the first valve body 66 is moved downward by the E-ring 22 when the shaft 20 is lowered. Therefore, the first valve seat 15a is separated from the first valve seat 41, and the input port 11 and the first output port 12 communicate with each other. Therefore, all the fluid that has flowed into the input port 11 flows out from the first output port 12.

  Next, the operation of the flow dividing valve 60 when the shaft 20 is raised by reversing the driving direction of the motor 30 from the state shown in FIG. 6 will be described with reference to FIGS. 7 and 8. 7 shows a state where the shunt ratio is “OUT1: OUT2 = 5: 5”, and FIG. 8 shows a state where the shunt ratio is “OUT1: OUT2 = 0: 10”.

  When the drive direction of the motor 30 is reversed to raise the shaft 20, the E-ring 22 comes into contact with the second valve body 66. At this time, the first valve body 65 is also in contact with the E-ring 22 by the force of the spring 19. Thereafter, while maintaining this state, the first valve body 65 and the second valve body 66 rise together with the shaft 20. For this reason, the second valve seat 16 a is separated from the second valve seat 51. As a result, the input port 11 and the second output port 13 communicate with each other. That is, both the input port 11 and the first output port 12 and the second output port 13 communicate with each other.

  At this time, the ratio between the flow rate of the fluid flowing out from the first output port 12 and the flow rate of the fluid flowing out from the second output port 13, that is, the diversion ratio, is the opening area of the first output port 12 and the opening area of the second output port 13 It is determined by the ratio. Here, the opening area of the first output port 12 is determined by the distance between the first valve seat 41 and the first valve body 65, and the opening area of the second output port 13 is the second valve seat 51 and the second valve body. 66 is determined by the distance to 66. Since the positions of the first valve seat 41 and the second valve seat 51 are fixed, the diversion ratio is determined by the positions of the first valve body 65 and the second valve body 66. That is, in the state where both the input port 11 and the first output port 12 and the second output port 13 communicate with each other, the flow dividing ratio can be adjusted by the positions of the first valve body 65 and the second valve body 66. Therefore, in the diversion valve 60, the first valve body 65 and the second valve body 66 are both attached to the shaft 20, and the shaft 20 moves up and down according to the drive amount of the motor 30, so the drive amount of the motor 30 is adjusted. Thus, the flow rate can be adjusted.

  Here, since the first valve body 65 and the second valve body 66 have a needle shape in the diversion valve 60, the amount of change in the opening area of the first output port 12 and the opening area of the second output port 13 can be determined. Fine adjustments can be made. Therefore, the amount of fluid flowing out from the first output port 12 and the second output port 13 can be controlled with very high accuracy.

  The state shown in FIG. 7 is that the diversion ratio is “OUT1: OUT2 = 5: 5”. In order to achieve this state, the shaft 20 is raised by the motor 30 to a position where the distance between the first valve seat 41 and the first valve body 65 and the distance between the second valve seat 51 and the second valve body 66 are equal. You can do that.

  Further, when the shaft 20 is raised, the first valve seat 15 a comes into contact with the first valve seat 41. Here, since the first valve body 65 and the second valve body 66 are disposed between both ends of the E-ring 22 via the spring 19, the first valve seat 15a comes into contact with the first valve seat 41. However, as shown in FIG. 8, the shaft 20 is further raised by about 1 mm and then stopped. Thereby, the force which presses the 1st valve seat 15a by the spring 19 against the 1st valve seat 41 becomes large. For this reason, the sealing performance superior to the case where the first valve seat 15a is simply brought into contact with the first valve seat 41 is obtained. As a result, the input port 11 and the first output port 12 are completely blocked. Therefore, all the fluid that has flowed into the input port 11 flows out from the second output port 12.

  As described above, the flow dividing valve 60 distributes the fluid flowing into the input port 11 to the first output port 12 and the second output port 13 at an arbitrary flow dividing ratio by providing only one controller for driving the motor 30. be able to. That is, the diversion valve 10 can perform diversion, which conventionally requires two flow rate adjustment valves and two controllers, with one diversion valve and one controller. Therefore, by using the diversion valve 60 in a device such as a fuel cell, cost reduction and space saving can be achieved. In addition, since the first valve body 65 and the second valve body 66 are needle-shaped, the accuracy of flow rate adjustment can be improved and the flow rate of the fluid flowing into the input port 11 is increased. In addition, the first valve body 65 and the second valve body 66 can be reliably brought into contact with the first valve seat 41 and the second valve seat 51 without being flowed.

  As described above, in the flow dividing valve 60 according to the second embodiment as described in detail, the shaft 20 to which the first valve body 65 and the second valve body 66 are fixed by the motor 30 is driven. The first valve seat 15 a contacts and separates from the first valve seat 41, and the second valve seat 16 a contacts and separates from the second valve seat 51. As a result, the input port 11 and the first output port 12 or the second output port 13 are communicated or blocked, so that the fluid flowing into the input port 11 is divided into the first output port 12 and the second output port 13. Can do.

  Since the first valve body 65 and the second valve body 66 are fixed to the shaft 20 driven by the motor 30, the first valve body 15 and the second valve body 65 are adjusted by adjusting the movement amount of the shaft 20. The valve body 16 can be stopped at a desired position. That is, the opening degree between the first valve body 65 and the first valve seat 41 or the opening degree between the second valve body 66 and the second valve seat 51 can be adjusted. Further, since the first valve body 65 and the second valve body 66 have a needle shape, the opening degree between the first valve body 65 and the first valve seat 41 or the second valve body 66 and the second valve seat. The opening degree with 51 can be finely adjusted. For this reason, since the accuracy of the flow rate adjustment can be improved, the diversion ratio can be controlled with high accuracy.

  Such control of the diversion ratio can also be performed in the diversion valve 60 by adjusting the driving amount of one motor 30. Therefore, the diversion that has been conventionally performed by two flow rate adjustment valves and two controllers. Can be performed by one shunt valve and one controller. Therefore, by using this diversion valve 60, it is possible to achieve cost reduction and space saving of a device such as a fuel cell.

  In addition, since the first valve body 65 and the second valve body 66 have a needle shape, the first valve body 65 and the second valve body 66 are always in the first valve seat 41 and the second valve seat 51. Therefore, even when the flow velocity of the fluid flowing into the input port 11 is high, the first valve body 65 and the second valve body 66 are not flowed.

  Furthermore, in the diversion valve 60, the first valve body 65 and the second valve body 66 are disposed with the spring 19 sandwiched between both ends of the E-ring 22 fixed to the shaft 20, so that the shaft 20 is When the first valve seat 15a is brought into contact with the first valve seat 41 by being moved, the shaft 20 can further move in the direction of pressing the first valve body 15 against the first valve seat 41. The pressing force of the first valve body 65 against the first valve seat 41 due to the force is increased, and the sealing performance is improved. Similarly, when the shaft 20 is moved and the second valve seat 16 a is brought into contact with the second valve seat 51, the shaft 20 may further move in the direction of pressing the second valve body 16 against the second valve seat 51. Therefore, the pressing force of the second valve seat 16a against the second valve seat 51 by the force of the spring 19 is increased, and the sealing performance is improved. In this way, since the sealing performance is improved also in the diversion valve 60, the diversion can be performed accurately without causing leakage.

(Third embodiment)
Finally, a third embodiment will be described. In the third embodiment, a mixing valve will be described. The mixing valve according to the third embodiment has substantially the same configuration as that of the flow dividing valve 10 according to the first embodiment, but the method of use is different. That is, the input port 11 in the diversion valve 10 is used as an output port, and the output ports 12 and 13 in the diversion valve 10 are used as two series of input ports. Another difference is that a stepping motor is used instead of the DC motor. For this reason, in the following description, it demonstrates centering around difference, attaches | subjects the same code | symbol about a common point, and abbreviate | omits description suitably. FIG. 9 shows a schematic configuration of the mixing valve according to the third embodiment. FIG. 9 is a cross-sectional view showing a schematic configuration of the mixing valve 110.

  As shown in FIG. 9, the mixing valve 110 includes a first input port 112, a second input port 113, an output port 111, a valve chamber 14, a first valve body 15, and a guide 16b. A two-valve body 16, a spring 19, a shaft 20, a shaft guide 21, an E-ring 22, a stepping motor 30a, and the like are provided. The mixing valve 110 supplies the fluid flowing into the first input port 112 and the second input port 113 to the output port 111 at an arbitrary ratio and mixes them. Note that the first valve body 15 and the second valve body 16 may have a needle shape as exemplified in the second embodiment.

  An adapter 72 having a hollow hole is fixed to the first body 40 with a bolt 74 via a fastening plate 73, and the upper end portion of the shaft 20 protrudes from the first body 40 to the adapter 72 via the fastening plate 73. ing. The stepping motor 30a is fixed to the adapter 72, and the drive shaft 76 protrudes downward into the adapter 72 and is connected to the shaft 20 via the conversion mechanism 77a. Thereby, the rotational motion of the stepping motor 30a is converted into a linear motion in the vertical direction of the shaft 20, and the shaft 20 moves in the vertical direction according to the amount of rotation of the stepping motor 30a.

  Here, the conversion mechanism 77a will be described with reference to FIG. FIG. 10 is an exploded perspective view of the conversion mechanism. The conversion mechanism 77 a includes a drive shaft 76, a rotating member 78, a guide member 79, and the like, and is accommodated in the adapter 72. The guide member 79 is formed by molding a plastic material into a substantially cylindrical shape by injection molding. The guide member 79 is disposed so that the tip end protrudes from the fastening plate 73 to the adapter 72, and the lower end portion is held between the shaft guide 21 and the fastening plate 73, so that the movement in the rotational direction is restricted. ing. The guide member 79 has a pair of long holes 80 formed in the outer peripheral surface so as to be long in the axial direction. The shaft 20 has an upper end inserted into the guide member 79, and the engagement pin 81 is penetrated and fixed so as to pass through the long hole 80 of the guide member 79.

  On the other hand, the rotating member 78 is formed by injection molding of a plastic material into a bag shape, and is mounted so as to cover the distal end portion of the guide member 79. A pair of feed screws 82 are formed in a female thread shape on the inner peripheral surface of the rotating member 78, and both end portions of the engagement pins 81 are slidably fitted to the feed screw 22. The rotating member 78 is configured such that the convex portion 83 is uniquely positioned and engaged with the concave portion 84 of the drive shaft 76 and rotates integrally with the drive shaft 76. Accordingly, when the stepping motor 30a rotates the rotating member 78 via the drive shaft 76, the engaging pin 81 is moved along the long hole 80 of the guide member 79 by the feed screw 82, and the shaft 20 is slid in the axial direction. Let Therefore, the amount of movement of the shaft 20 can be adjusted by controlling the rotation of the stepping motor 30a. Thereby, the movement amount of the 1st valve body 15 and the 2nd valve body 16 to which the shaft 20 is being fixed can be adjusted. That is, the fluid supplied from the first input port 112 and the fluid supplied from the second input port 113 can be mixed at an arbitrary ratio and allowed to flow out from the output port 111.

  Next, the operation of the mixing valve 110 having the above configuration will be described. A state where the mixing ratio is “IN1 (flow rate of the first input port 112): IN2 (flow rate of the second input port 113) = 10: 0” will be described. In this state, the shaft 20 is lowered by the driving of the stepping motor 30 a, and the second valve seat 16 a comes into contact with the second valve seat 51. Here, since the first valve body 15 and the second valve body 16 are disposed between both ends of the E-ring 22 via the spring 19, the second valve seat 16a comes into contact with the second valve seat 51. However, the shaft 20 is further lowered by about 1 mm and then stopped. Thereby, the force which presses the 2nd valve body sheet | seat 16a by the spring 19 against the 2nd valve seat 51 becomes large. For this reason, the sealing performance superior to the case where the second valve seat 16a is simply brought into contact with the second valve seat 51 is obtained. As a result, the second input port 113 and the output port 111 are completely blocked. On the other hand, the first valve body 16 is moved downward by the E-ring 22 when the shaft 20 is lowered. For this reason, the first valve seat 15a is separated from the first valve seat 41, and the first input port 112 and the output port 111 communicate with each other. For this reason, the fluid supplied to the first input port 112 flows out from the output port 11.

  Subsequently, when the shaft 20 is raised by reversing the drive direction of the stepping motor 30 a, the E ring 22 contacts the second valve body 16. At this time, the first valve body 15 is also in contact with the E-ring 22 by the force of the spring 19. Thereafter, while maintaining this state, the first valve body 15 and the second valve body 16 rise together with the shaft 20. For this reason, the second valve seat 16 a is separated from the second valve seat 51. As a result, the second input port 113 and the output port 111 communicate with each other. That is, both the first input port 112 and the second input port 113 communicate with the output port 111.

  At this time, the ratio of the flow rate of the fluid flowing out from the first input port 112 and the flow rate of the fluid flowing out from the second input port 113, that is, the mixing ratio, is the opening area of the first input port 112 and the opening area of the second input port 113. It is determined by the ratio. Here, the opening area of the first input port 112 is determined by the distance between the first valve seat 41 and the first valve body 15, and the opening area of the second input port 113 is the second valve seat 51 and the second valve body. It is determined by the distance to 16. Since the positions of the first valve seat 41 and the second valve seat 51 are fixed, the mixing ratio is determined by the positions of the first valve body 15 and the second valve body 16. That is, in a state where both the first input port 112 and the second input port 113 communicate with the output port 111, the mixing ratio can be adjusted by the positions of the first valve body 15 and the second valve body 16. it can. Therefore, in the mixing valve 110, the first valve body 15 and the second valve body are both attached to the shaft 20, and the shaft 20 moves up and down according to the driving amount of the stepping motor 30a. By adjusting, fluid can be mixed at an arbitrary ratio within a wide adjustment range.

  When the shaft 20 continues to rise, the first valve seat 15a comes into contact with the first valve seat 41. Here, since the first valve body 15 and the second valve body 16 are disposed between both ends of the E-ring 22 via the spring 19, the first valve seat 15 a comes into contact with the first valve seat 41. However, the shaft 20 is further raised by about 1 mm and then stopped. Thereby, the force which presses the 1st valve seat 15a by the spring 19 against the 1st valve seat 41 becomes large. For this reason, the sealing performance superior to the case where the first valve seat 15a is simply brought into contact with the first valve seat 41 is obtained. As a result, the first input port 112 and the output port 111 are completely blocked. For this reason, the fluid supplied to the second input port 113 flows out from the output port 111.

  As described above, the mixing valve 110 is provided with only one controller for driving the stepping motor 30a, and the fluid supplied to the first input port 112 and the second input port 113 can be mixed at an arbitrary mixing ratio. From the output port 111. In other words, the mixing valve 110 can perform mixing, which conventionally requires two flow control valves and two controllers, with one mixing valve and one controller. Moreover, the adjustment range of the mixing ratio is wide. Therefore, by using the mixing valve 110 in an apparatus such as a fuel cell, it is possible to reduce the cost and save space while widening the adjustment range of the mixing ratio.

  As described above, in the mixing valve 110 according to the third embodiment as described in detail, the shaft 20 to which the first valve body 15 and the second valve body 16 are fixed is driven by the stepping motor 30a. The first valve seat 15a contacts and separates from the first valve seat 41, and the second valve seat 16a contacts and separates from the second valve seat 51. As a result, the output port 111 and the first input port 112 or the second input port 113 are communicated or blocked. Therefore, the fluid supplied to the first input port 112 and the second input port 113 is mixed and the output port is mixed. 111 can flow out.

  Since the first valve body 15 and the second valve body 16 are fixed to the shaft 20 driven by the stepping motor 30a, the first valve body 15 and the second valve body 16 are adjusted by adjusting the movement amount of the shaft 20. The two-valve body 16 can be stopped at a desired position. That is, the opening degree between the first valve body 15 and the first valve seat 41 or the opening degree between the second valve body 16 and the second valve seat 51 can be adjusted. Therefore, the mixing ratio can be freely changed.

  Such mixing ratio control can be performed in the mixing valve 110 by adjusting the driving amount of one motor 30a. Therefore, mixing that has been conventionally performed by two flow rate adjusting valves and two controllers is performed. Can be performed with one mixing valve and one controller. Therefore, by using the mixing valve 110, it is possible to reduce the cost and the space of an apparatus such as a fuel cell.

  Further, in the mixing valve 110, the first valve body 15 and the second valve body 16 are arranged with the spring 19 sandwiched between both ends of the E ring 22 fixed to the shaft 20, so that the shaft 20 is When the first valve seat 15a is brought into contact with the first valve seat 41 by being moved, the shaft 20 can further move in the direction of pressing the first valve body 15 against the first valve seat 41. The pressing force of the first valve body 15 against the first valve seat 41 due to the force is increased, and the sealing performance is improved. Similarly, when the shaft 20 is moved and the second valve seat 16 a is brought into contact with the second valve seat 51, the shaft 20 may further move in the direction of pressing the second valve body 16 against the second valve seat 51. Therefore, the pressing force of the second valve seat 16a against the second valve seat 51 by the force of the spring 19 is increased, and the sealing performance is improved. In this way, the flow dividing valve 10 improves the sealing performance, so that fluid can be accurately mixed without causing leakage.

  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. For example, as a modification of the first embodiment described above, the second valve body 16 is formed with the guide 16b, but of course the guide may be formed on the first valve body 15. However, since the shaft 20 can be supported at the lower end by forming the guide on the second valve body 16, the guide is formed on the second valve body 16 rather than forming the guide on the first valve body 15. Is preferred.

  In the third embodiment, a stepping motor is used, but a DC motor can also be used. On the contrary, in the first and second embodiments, a DC motor is used, but a stepping motor can also be used.

It is sectional drawing which shows schematic structure of the shunt valve which concerns on 1st Embodiment, and is a figure which shows the state of shunt ratio 10: 0. It is a disassembled perspective view which shows schematic structure of a conversion mechanism. It is sectional drawing which shows schematic structure of the shunt valve which concerns on 1st Embodiment, and is a figure which shows the state of a shunt valve in a shunt ratio of 5: 5. It is sectional drawing which shows schematic structure of the shunt valve which concerns on 1st Embodiment, and is a figure which shows the state of a shunt valve in a state where a shunt ratio is 0:10. It is sectional drawing which shows schematic structure of the shunt valve which concerns on the modification of 1st Embodiment. It is sectional drawing which shows schematic structure of the shunt valve which concerns on 2nd Embodiment, and is a figure which shows the state whose shunt ratio is 10: 0. It is sectional drawing which shows schematic structure of the shunt valve which concerns on 2nd Embodiment, and is a figure which shows the state of a shunt valve in a shunt ratio of 5: 5. It is sectional drawing which shows schematic structure of the shunt valve which concerns on 2nd Embodiment, and is a figure which shows the state of a shunt valve in a state where a shunt ratio is 0:10. It is sectional drawing which shows schematic structure of the mixing valve which concerns on 3rd Embodiment. It is a disassembled perspective view which shows schematic structure of a conversion mechanism. It is sectional drawing which shows schematic structure of the flow control valve conventionally used in order to perform a flow or mixing.

Explanation of symbols

DESCRIPTION OF SYMBOLS 10 Valve flow valve 11 Input port 12 1st output port 13 2nd output port 14 Valve chamber 15 1st valve body 16 2nd valve body 19 Spring 20 Shaft 30 DC motor 30a Stepping motor 22 E ring 41 1st valve seat 51 1st valve seat 51 Two valve seat 110 Mixing valve 111 Output port 112 First input port 113 Second input port

Claims (8)

A diversion valve for diverting a fluid,
An input port;
A first output port;
A second output port;
A first valve seat formed between the input port and the first output port;
A second valve seat formed between the input port and the second output port;
A first valve body that contacts and separates from the first valve seat;
A second valve body that contacts and separates from the second valve seat;
A shaft to which the first valve body and the second valve body are attached;
A motor for driving the shaft;
A diverter valve, characterized by comprising: The shunt valve according to claim 1,
A spring that urges the first valve body and the second valve body in a direction to abut against the first valve seat and the second valve seat, respectively;
An E-ring attached to the shaft;
The first valve body and the second valve body are arranged with the spring sandwiched between both ends of the E-ring. In the shunt valve according to claim 1 or 2,
At least one of the first valve body or the second valve body has a needle shape. In the shunt valve according to claim 1 or 2,
At least one of the first valve body or the second valve body is formed with a guide portion that is always in contact with the inner peripheral surface of the first valve seat or the second valve seat. Characteristic shunt valve. A mixing valve for mixing fluids,
A first input port;
A second input port;
An output port;
A first valve seat formed between the first input port and the output port;
A second valve seat formed between the second input port and the output port;
A first valve body that contacts and separates from the first valve seat;
A second valve body that contacts and separates from the second valve seat;
A shaft to which the first valve body and the second valve body are attached;
A motor for driving the shaft;
A mixing valve characterized by having. The mixing valve according to claim 5,
A spring that urges the first valve body and the second valve body in a direction to abut against the first valve seat and the second valve seat, respectively;
An E-ring attached to the shaft;
The mixing valve, wherein the first valve body and the second valve body are arranged with the spring sandwiched between both ends of the E-ring. In the mixing valve according to claim 5 or 6,
At least one of the first valve body or the second valve body has a needle shape. In the mixing valve according to claim 5 or 6,
At least one of the first valve body or the second valve body is formed with a guide portion that is always in contact with the inner peripheral surface of the first valve seat or the second valve seat. Feature mixing valve.

Images