JP2008169976A - Control valve - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a control valve in which a diaphragm is hardly damaged. <P>SOLUTION: The control valve 1 is provided with a valve element 10; the diaphragm 30; and a housing 50. The valve element 10 opens/closes a refrigerant passage 70 in which the refrigerant flows. The diaphragm 30 is arranged such that its lower surface is abutted on the valve element 10, and moves the valve element 10. The housing 50 has a lid part 51 for fixing a peripheral edge of the diaphragm 30 and a receiving part 52. The receiving part 52 is formed so as to be opposed to a lower surface of the diaphragm 30 through a fine clearance. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a control valve for controlling the flow of circulating refrigerant, and more particularly to a control valve using a diaphragm.

2. Description of the Related Art Conventionally, a system that recovers exhaust heat from a vehicle to coolant of an engine cooling device using a refrigerant is known (see, for example, Patent Document 1).
Japanese Utility Model Publication No. 4-51808

  In the system of Patent Literature 1, if the exhaust heat of the vehicle is always recovered in the cooling water of the engine cooling device, the burden on the radiator increases. Therefore, it is necessary to use a control valve that controls the recovery of the waste heat by the refrigerant.

  When a control valve using a diaphragm is employed as such a control valve, there is a problem that the refrigerant freezes when the outside air temperature is low, such as in winter, and the diaphragm is damaged.

  The present invention has been made in view of the above problems, and an object thereof is to provide a control valve in which a diaphragm is hardly damaged.

In order to achieve the above object, the control valve of the present invention comprises:
A control valve for controlling the flow of circulating refrigerant,
A valve body for opening and closing a refrigerant passage through which the refrigerant flows;
One surface is disposed in contact with the valve body, and by warping to the one surface side or the other surface side due to the difference between the force acting on the one surface and the force acting on the other surface, A diaphragm for moving the valve body so as to open or close the refrigerant passage;
A housing for housing the diaphragm;
With
The housing has a flange portion that fixes a peripheral edge of the diaphragm,
The flange is formed so as to face one surface of the diaphragm with a minute gap therebetween.

The housing is formed with a protrusion that abuts against one surface of the diaphragm in a state where the valve body opens the refrigerant passage, and divides a space formed between the one surface of the diaphragm. And
It is preferable that the projecting portion is provided with a communicating portion that communicates the divided space.

The housing is preferably provided with an opening communicating with the refrigerant passage.
The opening is preferably provided in the vicinity of the communication portion.

  You may further provide the main-body part which accommodates the said valve body. In this case, a fluid passage is secured between the main body portion and the valve body.

  A spring means may be provided that is disposed on the opposite side of the valve body from the diaphragm and biases the valve body in the diaphragm direction. In this case, the valve body moves against the urging force of the spring means when the refrigerant between the valve body and the diaphragm freezes.

The diaphragm may be a laminated structure in which a plurality of diaphragms are laminated.
The control valve is, for example, a waste heat recovery control valve that controls the recovery of waste heat by the refrigerant.

  ADVANTAGE OF THE INVENTION According to this invention, the control valve which a diaphragm is hard to damage can be provided.

  A control valve according to an embodiment of the present invention will be described below with reference to the drawings. FIG. 1 is a sectional view showing a schematic configuration of a control valve 1 of the present invention.

  As shown in FIG. 1, the control valve 1 includes a valve body 10, a main body 20, a diaphragm 30, a coil spring 40, a housing 50, and a plate 53.

  The valve body 10 is accommodated in the main body 20. The valve body 10 is disposed so as to contact one surface of the diaphragm 30, for example, the lower surface. The valve body 10 is closed at one end contacting the lower surface of the diaphragm 30 and opened at the other end separated from the diaphragm 30. The valve body 10 is formed by, for example, stainless steel press molding.

  The valve stem portion 11 of the valve body 10 is formed such that the outer diameter from the upper portion (from the diaphragm 30 side to the central portion) is smaller than the inner diameter of the main body portion 20. Moreover, the outer periphery of the upper part of the valve stem part 11 is formed in polygonal shape, for example, hexagonal shape. For this reason, the volume of the clearance channel between the outer peripheral surface of the valve stem portion 11 and the inner peripheral surface of the main body portion 20 can be increased. Moreover, the diameter of the valve stem part 11 is expanded at the center part.

  The valve body 10 is located between the outer peripheral surface of the lower valve stem portion 11 and the inner peripheral surface of the main body portion 20 expanded in accordance with the diameter expansion of the valve stem portion 11 from the center portion expanded in diameter. A refrigerant passage 70 through which the refrigerant flows is formed.

  The valve body 10 is provided with a flange 14 at a lower portion thereof, which abuts on the valve seat 22 of the main body 20 when the valve is closed. The flange 14 has a diameter larger than the inner diameter of the enlarged portion of the main body 20 described later, and the diameter of the main body 20 is increased in accordance with the movement of the main body 20 of the valve body 10 along the axial direction. The refrigerant passage 70 is opened and closed by contacting and separating from the valve seat 22 formed at the lower end of the portion.

  A coil spring 12 is disposed on the opposite side of the valve body 10 from the diaphragm 30, that is, on the lower side of the valve body 10. The coil spring 12 is biased in the direction of the diaphragm 30, that is, upward in the axial direction. One end of the coil spring 12 abuts on the upper end of the enlarged diameter portion of the valve body 10, and the other end abuts on the spring receiver 13. The spring receiver 13 is fixed to the inner peripheral surface of the lower end of the main body 20 that forms the outlet of the refrigerant passage 70.

  Here, when the refrigerant flowing between the valve stem portion 11 and the diaphragm 30 is frozen when the valve body 10 is closed, the volume of the refrigerant expands due to freezing and locally increases the pressure. At this time, the valve body 10 compresses the coil spring 12 downward in the axial direction and moves downward in the axial direction. Thereby, since the volume between the valve body 10 and the diaphragm 30 is expanded, the pressure increase by the volume expansion of a refrigerant | coolant can be relieve | moderated. For this reason, the diaphragm 30 can be made difficult to be damaged.

  The main body portion 20 is formed in a cylindrical shape in which one end side coupled to the housing 50 (receiving portion 52) and the other end side forming the outlet of the refrigerant passage 70 are opened. The main body 20 is formed, for example, by press molding of the same material as the valve body 10.

  The main body portion 20 is enlarged in diameter at the center portion corresponding to the shape of the valve body 10. A hole 21 communicating with the refrigerant passage 70 and the valve chamber 80 is formed on the outer peripheral surface of the enlarged diameter portion of the main body 20. The refrigerant flows from the valve chamber 80 into the refrigerant passage 70 through the hole 21.

  The lower end of the main body 20 is further expanded from the center. A groove 23 formed in the circumferential direction is formed on the upper edge of the enlarged diameter portion of the lower end. An O-ring 24 is disposed in the groove 23. The O-ring 24 ensures airtightness with the case 103 of the auxiliary heating system 100 described later.

  The main body 20 is press-fitted into the case 103 of the auxiliary heating system 100 and is fixed to the case 103 so as to be coaxial with the diaphragm 30 by a press-fitting member 25 disposed on the outer peripheral surface thereof.

  The diaphragm 30 is warped to the upper surface side or the lower surface side due to the difference between the force acting on one surface (lower surface) and the force acting on the other surface (upper surface), so that the refrigerant passage 70 is opened or closed. The valve body 10 is moved.

  The diaphragm 30 is accommodated in the housing 50 with the periphery thereof fixed to the housing 50. In the present embodiment, the outer peripheral portion is sandwiched between the flange portion of the housing 50, that is, the lid portion 51 and the receiving portion 52. For example, the outer edge is fixed to these by TIG welding, and is coaxial with the valve body 10. It is supported by.

  That is, the diaphragm 30 can be warped (inverted) upward in the axial direction so as to allow the valve body 10 to move in the valve closing direction, and can be warped downward in the axial direction so as to move the valve body 10 in the valve opening direction ( The outer peripheral portion is secured to the housing 50 by welding so that a possible effective portion is secured at a predetermined distance from the welded portion of the outer peripheral portion to the inside thereof.

  In addition to TIG welding, welding methods such as gas arc welding, laser welding, and resistance welding are used for welding the diaphragm 30.

  A coil spring 40 is disposed on the other surface of the diaphragm 30. The coil spring 40 is arranged so that one end abuts on the adjustment screw 42 and the other end abuts on the upper surface of the spring receiver 41. The coil spring 40 urges the diaphragm 30 downward in the axial direction, that is, in the valve opening direction of the valve body 10 via the spring receiver 41.

  The spring receiver 41 is formed in a cylindrical shape with one end opened. The spring receiver 41 is disposed such that the bottom surface is in contact with the other surface of the diaphragm 30 and the side surface is in contact with the inner peripheral surface of the lid portion 51 of the housing 50. The spring receiver 41 moves upward in the axial direction of the diaphragm 30 because the coil spring 40 is compressed when the diaphragm 30 reverses in the valve closing direction (returns upward). At this time, when the open end of the spring receiver 41 comes into contact with a restricting portion (projecting portion 512) formed on the inner peripheral surface of the lid 51, the movement of the diaphragm 30 is restricted via the spring receiver 41.

  The adjusting screw 42 is disposed so as to be screwed into a screw groove formed on the inner peripheral surface of the lid portion 51 of the housing 50. The adjustment screw 42 is moved upward or downward in the axial direction of the diaphragm 30 as necessary to adjust the spring load of the coil spring 40. Thereby, the reversal pressure at the time of reversal of the diaphragm 30 and the return pressure at the time of return can be finely adjusted.

  The housing 50 includes a lid part 51 and a receiving part 52. The housing 50 is disposed coaxially with the valve body 10 and the diaphragm 30.

  The lid 51 is formed in a cylindrical shape. A flange 511 is formed at one end of the lid 51. In the present embodiment, the flange 511 and the receiving portion 52 constitute a flange portion that fixes the periphery of the diaphragm 30.

  The outer peripheral portion of the flange 511 of the lid portion 51 sandwiches the outer periphery of the diaphragm 30 together with the outer peripheral portion of the receiving portion 52. The outer peripheral portion of the flange 511 is formed corresponding to the outer peripheral shape of the diaphragm 30. The outer edge of the flange 511 is welded to the outer edge of the diaphragm 30 together with the outer edge of the receiving portion 52.

  The receiving part 52 is formed in a dish shape whose center is opened. The central portion of the receiving portion 52 is formed flat and protrudes upward in the axial direction of the housing 50. Here, the shape of the receiving portion 52 is configured to face the diaphragm 30 with a minute gap. Thus, since the shape of the receiving part 52 is formed, the pressure increase by volume expansion at the time of freezing of a refrigerant | coolant can be relieve | moderated. For this reason, the diaphragm 30 can be made difficult to be damaged.

  A projection 521 that includes a central opening and projects upward in the axial direction of the housing 50 is formed at the center of the receiving portion 52. The protrusion 521 is formed at a height at which the diaphragm 30 warps downward and comes into contact with the lower surface of the diaphragm 30 in a valve open state. Therefore, when the valve is opened, the diaphragm 30 moves downward in the axial direction and comes into contact with the protruding portion 521 of the receiving portion 52, so that the space defined by the receiving portion 52 and the diaphragm 30 is formed by the protruding portion 521. It is divided into a space on the outer peripheral side and a space on the inner peripheral side of the diaphragm.

  As shown in FIG. 2, a pressure relief groove 522 is formed on the contact surface of the protrusion 521 with the diaphragm 30. The pressure relief groove 522 communicates the space on the outer peripheral side and the inner peripheral side of the diaphragm 30. That is, the pressure relief groove 522 improves the pressure equalization between the space on the outer peripheral side of the diaphragm 30 and the space on the inner peripheral side of the diaphragm 30. Further, the pressure relief groove 522 prevents the surface adhesion of the diaphragm 30 and the pressure rise when the refrigerant is frozen. For this reason, when the refrigerant freezes, the volume expansion due to freezing can be released, and the pressure increase due to the volume expansion of the refrigerant can be mitigated. Therefore, the diaphragm 30 can be further prevented from being damaged.

  A plurality of pressure equalizing holes 523 are formed in the flat portion of the receiving portion 52. The pressure equalizing hole 523 communicates with the valve chamber 80 through the through hole 54 of the plate 53. Thereby, the responsiveness of the refrigerant pressure is improved, and the volume expansion due to freezing can be released when the refrigerant freezes, so that the diaphragm 30 can be more reliably prevented from being damaged. In this case, it is effective that the pressure equalizing hole 523 is formed in the vicinity of the pressure relief groove 522 of the protruding portion 521.

  The plate 53 is a support plate that supports the main body 20 and the housing 50. A through hole 54 is formed in the plate 53 at a position corresponding to the pressure equalizing hole 523 of the receiving portion 52.

  The plate 53 forms a valve chamber 80 by the main body 20 and a case 103 of the auxiliary heating system 100 described later. The plate 53 is formed so that the center protrudes upward. As described above, since the diameter of the central portion of the main body portion 20 is increased, that is, the upper end is reduced in diameter, the volume of the valve chamber 80 is increased. Thereby, the volume expansion by freezing of a refrigerant | coolant can further be relieve | moderated or prevented.

  The plate 53 is coupled to the receiving portion 52 of the main body 20 and the housing 50 and the respective connecting portions thereof, for example, by brazing in the furnace. Thereby, airtightness and pressure | voltage resistance can be ensured.

  Next, the operation of the control valve 1 will be described. FIG. 3 shows the relationship between the valve lift and the pressure. In addition, the inversion characteristic of the diaphragm 30 alone is indicated by a broken line, and the spring characteristic of the coil spring 40 is indicated by a one-dot chain line.

As shown in FIG. 3, the load (first load) generated by the diaphragm 30 changes as the valve lift changes.
Initially, the first load increases as the valve lift increases until the diaphragm 30 reverses. After the reversal of the diaphragm 30, the first load decreases as opposed to increasing the valve lift. However, when the valve lift further increases, the first load increases in accordance with the valve lift. That is, the diaphragm 30 generates a first load that is different between when it is reversed and when it is returned.

  On the other hand, the coil spring 40 generates a spring load (second load) that linearly increases in accordance with the valve lift (compression amount).

  As described above, since the diaphragm 30 is urged by the coil spring 40, the relationship between the pressure (load) and the valve lift that actually acts on the valve body 10 via the diaphragm 30 is the reverse characteristic of the diaphragm 30. It is determined by the spring characteristics of the coil spring 40. That is, as shown by a solid line in FIG. 3, the valve body 10 is acted on the valve body 10 by superposing the first load generated by the diaphragm 30 and the second load applied by the coil spring 40 via the diaphragm 30. To do.

  Therefore, as shown in FIG. 3, when the refrigerant pressure is in the range of zero to point A, the valve body 10 is moved to a position corresponding to the valve lift corresponding to the pressure. 70 is open. When the refrigerant pressure increases to the pressure at the point A, the diaphragm 30 reverses upward in the axial direction to allow the valve body to move, so that the valve body 10 starts moving. The valve body 10 moves in the valve closing direction against the pressure acting via the diaphragm 30 to the position corresponding to the valve lift at the point B, and closes the refrigerant passage 70. That is, the valve closing pressure is set to the pressure at point A.

  Even when the refrigerant pressure decreases when the valve is closed, the valve body 10 is held in the closed position by the diaphragm 30 until the pressure at the point C is reached. When the refrigerant pressure decreases to the pressure at point C, the diaphragm 30 returns to the lower side in the axial direction, whereby the valve body 10 starts moving in the valve opening direction. The valve body 10 moves in the valve opening direction and opens the refrigerant passage 70 by a load acting via the diaphragm 30 to a position corresponding to the valve lift at the point D. That is, the valve opening pressure is set to the pressure at point C.

  Here, the valve closing pressure can be adjusted by changing the position of the protruding portion 512 of the lid portion 51 of the housing 50. For example, when the valve lift at point C is E, by changing the position of the protruding portion 512 downward in the axial direction, when the valve lift reaches F, the protruding portion 512 causes the spring receiver 41 to be interposed. Since the movement of the diaphragm 30 and the valve body 10 is restricted, the position corresponding to the valve lift at point F is the valve closing position. Then, as shown in FIG. 3, when the refrigerant pressure increases to the pressure at point A, the valve body 10 starts to move and moves in the valve closing direction to a position corresponding to the valve lift at point B ′. The passage 70 is closed. When the refrigerant pressure decreases to a pressure at point C ′ that is lower than the pressure at point C, the valve body 10 starts moving and moves in the valve opening direction of the diaphragm 30 to a position corresponding to the valve lift at point D ′. Then, the refrigerant passage 70 is opened. That is, the valve opening pressure is changed to the pressure at the point C ′.

  The valve opening pressure and the valve closing pressure can be finely adjusted by adjusting the spring load of the coil spring 40 with the adjusting screw 42 as described above.

  Next, the case where the control valve 1 of the present invention is used in the auxiliary heating system 100 shown in FIG. 4 will be described. In the auxiliary heating system 100, the control valve 1 is used as a control valve for recovering waste heat.

  As shown in FIG. 4, the auxiliary heating system 100 includes a heater 101, a cooler 102, and a control valve 1.

  For example, the heater 101 heats the refrigerant circulating through the control valve 1 using the exhaust heat of the exhaust gas of the engine as a heat source, and raises the temperature of the cooling water in the cooler 102. Here, the refrigerant is preferably composed of pure water sealed after the piping of the auxiliary heating system 100 is evacuated.

  The cooler 102 condenses the refrigerant heated and boiled by the heater 101 with cooling water.

  As described above, the control valve 1 is accommodated in the case 103 of the auxiliary heating system 100 by securing the airtightness with the case 103 by arranging the O-ring 24 in the groove 23 of the main body 20. .

  When the control valve 1 is opened, the refrigerant heated by the heater 101 is condensed by the cooler 102 and flows into the valve chamber 80 from the opening of the case 103. The refrigerant that has flowed in flows into the refrigerant passage 70 through the hole 21 of the main body portion 20, passes between the valve stem portion 11 and the valve seat 22, and flows out through the control valve 1. Therefore, the cooling water in the cooler 102 is heated and warmed.

  On the other hand, when the cooling water in the cooler 102 is too warm, the temperature difference between the refrigerant flowing toward the cooler 102 and the cooling water in the cooler 102 relatively decreases, so that the temperature of the refrigerant condensed in the cooler 102 is reduced. Rise relatively. Specifically, as shown in FIG. 5, when the temperature of the refrigerant flowing from the cooler 102 to the control valve 1 rises to 140 ° C. and the pressure rises to 0.4 MPa, the valve body 10 of the control valve 1 is The valve is closed so that the refrigerant circulating in the auxiliary heating system 100 does not flow.

  When the valve is closed, the refrigerant does not circulate through the auxiliary heating system 100. Therefore, since the refrigerant in the cooler 102 is cooled by the cooling water, the refrigerant between the cooler 102 and the control valve 1 is also cooled, and the temperature of the refrigerant relatively decreases, and the refrigerant in the control valve 1 The pressure drops. Specifically, as shown in FIG. 5, when the temperature of the refrigerant in the control valve 1 decreases to 70 ° C. and the pressure decreases to 0.03 MPa, the valve body 10 of the control valve 1 opens, and the refrigerant Is circulated to the auxiliary heating system 100.

  As described above, according to the present embodiment, since the shape of the receiving portion 52 is formed so as to face the diaphragm 30 with a minute gap, the pressure increase due to the volume expansion of the refrigerant is prevented. Can be relaxed. For this reason, the diaphragm 30 can be made difficult to be damaged.

  According to the present embodiment, the protruding portion 521 that protrudes upward in the axial direction of the housing 50 is formed at the center of the receiving portion 52, and the pressure relief groove 522 is formed in the protruding portion 521, so that the refrigerant is frozen. In this case, the volume expansion due to freezing can be released, and the pressure increase due to the volume expansion of the refrigerant can be mitigated. Therefore, the diaphragm 30 can be further prevented from being damaged.

  In addition, according to the present embodiment, the diaphragm 30 generates a first load that is different between when the diaphragm 30 is reversed and when the diaphragm 30 returns and acts on the valve body 10, and the second load is applied to the valve body 10 via the diaphragm 30 by the coil spring 40. Acts on the body 10. When the valve body 10 is closed, the valve body 10 moves in the valve closing direction for closing the refrigerant passage 70 against the first load and the second load. On the other hand, when the valve body 10 is opened, the valve body 10 moves in the valve opening direction for opening the refrigerant passage 70 by the first load and the second load. Here, as described above, since the first load is different between the reverse time and the return time, the valve body 10 is operated with different refrigerant pressures in the valve opening direction and the valve closing direction. That is, the control valve 1 controls the flow of the refrigerant so that the pressure when the valve body 10 opens the refrigerant passage 70 and the pressure when the valve body 10 closes the refrigerant passage 70 are different. be able to.

  The present invention is not limited to the above-described embodiment, and its application and modification are arbitrary. For example, the diaphragm 30 may be a laminated structure in which a plurality of diaphragms are laminated. In this case, the stress applied to the diaphragm 30 can be relaxed, and the diaphragm 30 can be further prevented from being damaged.

  In the above embodiment, the other end of the coil spring 12 of the valve body 10 abuts against the spring receiver 13. However, as shown in FIG. 6, an adjustment screw 15 that is screwed onto the inner peripheral surface of the lower end of the main body 20 is disposed, and the amount of compression of the coil spring 12 with which the other end abuts is changed by the adjustment screw 15. The spring load may be adjusted.

  In the above embodiment, the control valve 1 is supported by the case 103 of the auxiliary heating system 100 by the plate 53. However, the case 103 is omitted, and instead of the plate 53, as shown in FIG. 6, an auxiliary heating system using a flange portion 60 having a valve chamber 61 inside and a thread groove 62 formed on the outer periphery is provided. You may make it directly screw in 100 piping.

  Further, as shown in FIGS. 7A and 7B, a screw portion 55 for screwing may be formed on the plate 53 and directly screwed to the case 103 of the auxiliary heating system 100. In this case, in order to prevent leakage between the plate 53 and the auxiliary heating system 100 side, the packing 56 and the O-ring seal 57 may be used.

  In the above embodiment, the coil spring 12 of the valve body 10 abuts on the valve stem portion 11 and the spring receiver 13 fixed to the main body portion 20 to urge the valve stem portion 11 upward in the axial direction. However, as shown in FIG. 8, the upper end of the valve stem portion 11 may be fixed to the other surface of the diaphragm 30 by welding, and the coil spring 10 and the spring receiver 13 may be omitted.

  Further, instead of welding and fixing the valve body 10 and the diaphragm 30, the valve body 10 may be fixed by a bolt 16 as shown in FIG. The bolt 16 is screwed into the corresponding screw hole 17 of the valve body 10. A washer 18 may be interposed between the head of the bolt 16 and the diaphragm 30.

In this case, for example, by changing the diameters of the valve body 10 and the washer 18, the diameter (contact diameter) of the portion where the diaphragm 30 contacts the valve body 10 and the washer 18 is changed between when the diaphragm 30 is reversed and when the diaphragm 30 is returned. Is done. Further, for example, by changing the length of the flat part of the cover part 51 and the receiving part 52 of the housing 50, the diameter (fulcrum diameter) of the part where the diaphragm 30 is supported by the cover part 51 and the receiving part 52 is also reversed. It changes with time and return time. That is, since the area (diameter) of the effective portion is relatively large at the time of reversal and relatively small at the time of return, the reversal pressure and the return pressure can be changed to appropriately set the above reversal characteristics. .
The modifications shown in FIGS. 6 to 9 can be combined with the above-described embodiment and other modifications.

It is a figure which shows schematic structure of the control valve which concerns on embodiment of this invention. It is a figure which shows the receiving part of a housing. It is a figure which shows the relationship between a valve lift and a pressure (load). It is a figure which shows schematic structure of the auxiliary heating system to which the control valve of this invention was applied. It is a figure which shows the relationship between the temperature of the refrigerant | coolant circulated through the auxiliary heating system of FIG. 4, and a pressure. It is a figure which shows the modification of the control valve of this invention. It is a figure which shows the coupling | bond part with the auxiliary | assistant heating system of the control valve of FIG. It is a figure which shows the other modification of the control valve of this invention. It is a figure which shows the other modification of the control valve of this invention.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Control valve 10 Valve body 11 Valve stem part 12 Coil spring 20 Main body part 23 Groove 24 O-ring 30 Diaphragm 40 Coil spring 41 Spring receiver 42 Adjustment screw 50 Housing 51 Cover part 512 Protrusion part 52 Receiving part 521 Protrusion part 522 Pressure relief Groove 523 Pressure equalizing hole 53 Plate 70 Refrigerant passage 80 Valve chamber 100 Auxiliary heating system 101 Heater 102 Cooler 103 Case

Claims (8)

A control valve for controlling the flow of circulating refrigerant,
A valve body for opening and closing a refrigerant passage through which the refrigerant flows;
One surface is disposed in contact with the valve body, and by warping to the one surface side or the other surface side due to the difference between the force acting on the one surface and the force acting on the other surface, A diaphragm for moving the valve body so as to open or close the refrigerant passage;
A housing for housing the diaphragm;
With
The housing has a flange portion that fixes a peripheral edge of the diaphragm,
2. The control valve according to claim 1, wherein the flange portion is formed so as to face one surface of the diaphragm through a minute gap. The housing is formed with a protrusion that abuts against one surface of the diaphragm in a state where the valve body opens the refrigerant passage, and divides a space formed between the one surface of the diaphragm. And
The control valve according to claim 1, wherein the projecting portion is provided with a communication portion that communicates the divided space.   The control valve according to claim 1, wherein the housing is provided with an opening communicating with the refrigerant passage.   The control valve according to claim 3, wherein the opening is provided in the vicinity of the communication portion. Further comprising a main body for accommodating the valve body;
The control valve according to claim 1, wherein a fluid passage is secured between the main body and the valve body. A spring means that is disposed on the opposite side of the valve body from the diaphragm and biases the valve body in the diaphragm direction;
The said valve body moves against the urging | biasing force of the said spring means, if the refrigerant | coolant between the said valve body and the said diaphragm freezes, The any one of Claim 1 thru | or 5 characterized by the above-mentioned. Control valve.   The control valve according to any one of claims 1 to 6, wherein the diaphragm is a laminated structure in which a plurality of diaphragms are laminated.   The control valve according to claim 1, wherein the control valve is a waste heat recovery control valve that controls recovery of waste heat by the refrigerant.

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