JP2017026191A - Temperature expansion valve and refrigeration cycle - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a temperature expansion valve capable of suppressing vibration of a valve member 2 to prevent a needle valve 21 from repeatedly colliding with a valve port 13 or prevent noise, and provide a refrigeration cycle.SOLUTION: A valve member 2 is arranged oppositely to a valve port 13 and a valve seat 13a. A temperature expansion valve causes a diaphragm device 6 to drive the valve member 2 through an operational shaft 4, to open/close the valve port 13. At least a part of the valve member 2 is arranged on a downstream side with respect to a throttle part of the valve port 13 and valve member 2. The temperature expansion valve includes energization means of energizing the valve member 2 to one side with respect to axial line L by force of fluid flowing from the valve port 12. The energization means is a flange part 22 having a D cut surface 221 of the valve member 2. On the D cut surface 221 side of the valve member 2, a flow rate of refrigerant is increased.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a temperature expansion valve connected between a condenser and an evaporator of a heat pump refrigeration cycle and a refrigeration cycle.

  Conventionally, as a temperature expansion valve, for example, there is one disclosed in JP-A-11-270929 (Patent Document 1). This temperature expansion valve is provided between the condenser and the evaporator in the refrigeration cycle of an air conditioner such as an air conditioner. The temperature expansion valve includes a temperature sensing cylinder that senses the outlet temperature of the evaporator, and displaces the diaphragm according to the temperature sensed by the temperature sensing cylinder. The movement of the diaphragm is transmitted to the valve member via the operating shaft, and the opening degree of the valve port is controlled by the valve member. Thereby, the flow rate of the refrigerant (fluid) circulating through the refrigeration cycle is controlled according to the outlet temperature of the evaporator.

JP 11-270929 A

  In the temperature expansion valve, the refrigerant is throttled at the throttle part between the valve port and the valve member. Cavitation occurs in the refrigerant after passing through the throttle part, and the valve member slightly vibrates due to the burst of this cavitation. However, this vibration may be transmitted to the operating shaft or the like to generate abnormal noise. In particular, when the valve member is a needle valve, this fine vibration may cause the needle valve to repeatedly collide with the valve port and wear the valve port (valve seat). Such vibration of the valve member is also caused by the flow of the refrigerant.

  It is an object of the present invention to provide a temperature expansion valve and a refrigeration cycle that can suppress vibration of a valve member and prevent the valve member from repeatedly colliding with a valve port and generating abnormal noise.

  The temperature expansion valve according to claim 1 is a temperature expansion valve that controls the circulation flow rate of the fluid in the refrigeration cycle in response to the temperature of the outlet side piping of the evaporator of the refrigeration cycle, and opens and closes the valve port through which the fluid flows At least a portion of the valve member that is positioned downstream of the throttle portion between the valve port and the valve member, and the valve member is moved with respect to the axis of the valve port by the force of fluid flowing from the valve port. An urging means for urging to one side is provided.

  The temperature expansion valve according to claim 2 is the temperature expansion valve according to claim 1, wherein the biasing means is configured by an asymmetric shape portion that is non-rotationally symmetric about the axis of the valve member. Features.

  The temperature expansion valve according to claim 3 is the temperature expansion valve according to claim 1, wherein the biasing means is a non-rotationally symmetric asymmetric shape formed around a valve seat formed around the valve port. It is comprised by the part.

  The temperature expansion valve according to claim 4 is the temperature expansion valve according to claim 2, wherein the valve member has a needle portion whose diameter decreases from the downstream side to the upstream side facing the valve port, and the needle A flange portion extending in a plane direction intersecting with the axis on the downstream side of the portion, and the asymmetrical shape portion is formed in the flange portion.

  A temperature expansion valve according to claim 5 is the temperature expansion valve according to claim 2, wherein the valve member is opposed to the valve port and has a diameter that decreases from the downstream side to the upstream side, and the needle It is comprised by the plate member which spreads in the surface direction which cross | intersects the said axis line by a member different from this needle part in the downstream of a part, The said asymmetrical shape part is formed in the said plate member, It is characterized by the above-mentioned.

  A temperature expansion valve according to a sixth aspect is the temperature expansion valve according to the third aspect, wherein the asymmetrical shape portion is a bleed groove formed on the downstream side of the valve port.

  The temperature expansion valve according to claim 7 is the temperature expansion valve according to claim 3, wherein the asymmetrical shape portion is formed at a position biased to one side with respect to the axis on the downstream side of the valve port. It is a vertical wall part and a notch part, It is characterized by the above-mentioned.

  The refrigeration cycle according to claim 8 decompresses the refrigerant by expanding the refrigerant between the compressor that compresses the refrigerant that is a fluid, the condenser and the evaporator, and the condenser and the evaporator. And a temperature expansion valve according to any one of the above.

  According to the temperature expansion valve of claim 1, the biasing means causes the force due to the flow of the fluid after passing through the valve port to act asymmetrically on both sides of the valve port axis with respect to the valve member. Is urged in a direction crossing the axis of the valve port, and vibration of the valve member can be suppressed. As a result, it is possible to prevent the valve member from repeatedly colliding with the valve port (or the valve seat), so that no abnormal noise (collision noise) is generated and quietness is obtained. Further, it is possible to prevent the flow rate characteristic from being changed due to wear of the valve port.

  According to the temperature expansion valve of claims 2, 4 and 5, the same effect as in claim 1 can be obtained by setting the shape of the valve seat.

  According to the temperature expansion valve of claims 3, 6 and 7, the same effect as in claim 1 can be obtained by setting the shape of the valve seat.

  According to the refrigeration cycle system of the eighth aspect, the same effects as those of the first to seventh aspects can be obtained.

It is a longitudinal cross-sectional view of the temperature expansion valve of 1st Embodiment of this invention. It is a figure which shows the valve member in 1st Embodiment. It is the top view and sectional drawing which show the modification 1 of the valve member in 1st Embodiment. It is the top view and sectional drawing which show the modification 2 of the valve member in 1st Embodiment. It is a longitudinal cross-sectional view of the temperature expansion valve of 2nd Embodiment of this invention. It is a figure which shows the valve member in 2nd Embodiment. It is a longitudinal cross-sectional view of the temperature expansion valve of 3rd Embodiment of this invention. It is a principal part expanded sectional view of the temperature expansion valve of 3rd Embodiment. It is the principal part expanded sectional view of the temperature expansion valve of 4th Embodiment of this invention, and the bottom view of a valve seat part. It is a schematic block diagram of the refrigerating cycle which concerns on embodiment of this invention.

  Next, an embodiment of the temperature expansion valve of the present invention will be described with reference to the drawings. FIG. 1 is a longitudinal sectional view of a temperature expansion valve according to the first embodiment, and FIG. 2 is a view showing a valve member according to the first embodiment. 2A is a top view of the valve member, and FIG. 2B is a longitudinal sectional view of the valve member.

  The temperature expansion valve 10 according to this embodiment has a metal valve body 1. In the valve body 1, a pipe connection hole 11, a pipe connection hole 12, a valve port 13, a valve chamber 14, a guide hole 15, a bearing hole 16, and a screw hole 17 are formed. A primary side joint 11a into which a fluid flows is attached to the pipe connection hole 11 as shown by an arrow, and a secondary side joint 12a from which a fluid flows out is attached to the pipe connection hole 12 as shown by an arrow. The primary side joint 11 a communicates with the valve chamber 14, and the secondary side joint 12 a communicates with the valve chamber 14 via the valve port 13. The primary side joint 11a and the secondary side joint 12a are assembled integrally with the valve body 1 by brazing or the like.

  The periphery of the valve port 13 is a valve seat 13a, and the valve member 2 facing the valve port 13 is disposed inside the valve seat 13a. The valve member 2 includes a needle part 21, a flange part 22, and a boss part 23. The needle portion 21 has a shape that is opposed to the valve port 13 and is reduced in diameter from the downstream side to the upstream side. The needle portion 21 of the valve member 2 is advanced and retracted into the valve port 13 by the action of a diaphragm device 6 described later, and the refrigerant as “fluid” flowing through the valve port 13 according to the position of the valve port 13 in the axis L direction. The flow rate is controlled. Thus, the gap between the valve port 13 and the needle portion 21 constitutes a “throttle portion” that throttles the refrigerant. At least a part of the valve member 2 is located downstream of the throttle portion between the valve port 13 and the valve member 2.

  A ring-shaped stopper tube 12b is disposed in the secondary joint 12a, and the valve spring 3 is disposed between the stopper tube 12b and the valve member 2 in a compressed manner. Thereby, the valve member 2 is biased so as to be seated on the valve seat 13a. The stopper pipe 12b has a conduction path 12b1 in the center and a caulking groove 12b2 on the outer periphery. By caulking the secondary joint 12a at the caulking groove 12b2, the stopper pipe 12b is placed in the secondary side joint 12a. It is fixed.

  A fixed hole 21 a is formed at the center of the needle portion 21 of the valve member 2, and the valve member 2 is fixed to the lower end portion of the operating shaft 4 through the fixed hole 21 a. The operating shaft 4 penetrates the valve port 13 and the guide hole 15 and is supported by a bearing portion 5 provided in the bearing hole 16 and the screw hole 17. The operating shaft 4 transmits the operation of the diaphragm device 6 to the valve member 2.

  The bearing portion 5 includes a packing 51 made of a fluororesin (for example, PTFE), a coil spring 52, and a spring bearing 53. The packing 51 has a tapered surface 51a at the lower end and an insertion hole 51b through which the operating shaft 4 passes at the center. The bottom of the bearing hole 16 is a mortar-shaped tapered surface 16a, and the angle of the tapered surface 51a of the packing 51 is smaller than the opening angle of the tapered surface 16a of the bearing hole 16. The coil spring 52 is compressed and disposed between the packing 51 and the spring receiver 53, and the spring receiver 53 is screwed into the screw hole 17 and fixed.

  As a result, the packing 51 is pressed against the tapered surface 16a of the bearing hole 16, and the tip of the tapered surface 51a of the packing 51 is urged so as to be radially reduced by the inclination of the tapered surface 16a. Thereby, the valve chamber 14 and the pressure equalizing chamber 65 can be separated in an airtight manner. Moreover, moderate sliding resistance arises between the packing 51 and the action | operation axis | shaft 4, and the hunting of the valve member 2 (vibration of the valve member 2 in the axis L direction) can be prevented.

  A diaphragm device 6 is attached to the upper portion of the valve body 1. In the diaphragm device 6, a thin disc-shaped upper lid 61 and a lower lid 62 constitute a case body, and this case body is fitted into an annular rib 1 a on the upper portion of the valve body 1 through an attachment hole 62 a of the lower lid 62. And fixed to the valve body 1 by brazing. Further, a diaphragm 63 is provided between the upper lid 61 and the lower lid 62, and the diaphragm chamber 64 and the pressure equalizing chamber 65 are partitioned by the diaphragm 63. An abutment 66 is disposed in the lower lid 62, and the operating shaft 4 is in contact with the abutment 66. A clearance is provided between the operating shaft 4 and each member of the guide hole 15 and the bearing portion 5. The pressure equalizing chamber 65 is communicated with a pressure equalizing conduit 6C described later by a joint (not shown), and is communicated with the outlet side pipe 20a of the indoor heat exchanger 20 via the pressure equalizing conduit 6C. Thereby, the pressure in the pressure equalizing chamber 65 becomes the pressure of the refrigerant at the outlet of the evaporator.

  The diaphragm chamber 64 is connected to the temperature sensing cylinder 6B through a capillary tube 6A. The temperature sensing cylinder 6B is filled with, for example, the same gas (and liquid) as the refrigerant of the refrigeration cycle, and is attached to the outlet side pipe of the indoor heat exchanger (evaporator) in the refrigeration cycle as described later. Further, the primary side joint 11a is connected to the outlet side pipe of the condenser of the refrigeration cycle, and the secondary side joint 12a is connected to the inlet side pipe of the evaporator.

  Thereby, the internal pressure of the diaphragm chamber 64 changes according to the sensed temperature of the outlet side piping of the evaporator by the temperature sensing cylinder 6B. Further, the pressure equalizing chamber 65 is applied with the outlet pressure of the evaporator. Then, the valve member 2 includes a force in the valve opening direction by the diaphragm 63 and the metal plate 66 displaced according to the temperature sensed by the temperature sensing cylinder 6B, a valve closing force by the valve spring 3, and a pressure in the pressure equalizing chamber 65. Due to the equilibrium relationship, the valve moves up and down in FIG. 1 to increase or decrease the effective opening area (valve opening) of the valve port 13. Thereby, the temperature expansion valve 10 controls the flow rate of the refrigerant supplied to the evaporator.

  The flange portion 22 of the valve member 2 has a D-cut surface 221 cut at a part thereof in a plane parallel to the axis L. That is, the portion of the D-cut surface 221 of the valve member 2 is a non-rotationally symmetric asymmetric shape portion around the axis L. Thereby, the force by the flow of the refrigerant that has passed through the valve port 13 causes the valve member 2 to act asymmetrically on both sides of the axis L of the valve port 13 (left and right sides in FIG. 1). Thus, the flange portion 22 constitutes an “urging means”.

  In this embodiment, the flow rate of the refrigerant passing through the D-cut surface 221 increases, and a pressure difference occurs in the fluid pressure in the left-right direction at the asymmetrical portion of the valve member 2, so that one side ( A force acts in the direction intersecting the axis L). Thereby, the vibration of the valve member 2 can be suppressed. As a result, it is possible to prevent the valve member 2 from repeatedly colliding with the valve seat 13a, so that no abnormal noise is generated and quietness is obtained. Further, it is possible to prevent the flow rate characteristic from being changed due to wear of the valve port 13.

  FIG. 3 is a view showing a first modification of the valve member 2. FIG. 3 (A) is a top view of the valve member, and FIG. 3 (B) is a longitudinal sectional view of the valve member. As shown in FIG. 3A, the valve member 2 of the first modification has a flange portion 24 having a circular shape in plan view, and the flange portion 24 is shown in the cross section of FIG. As described above, the thicknesses on both sides of the axis L are different. That is, the flange portion 24 of the valve member 2 is a non-rotationally symmetric asymmetric shape portion around the axis L.

  Thereby, the force by the flow of the refrigerant that has passed through the valve port 13 causes the valve member 2 to act asymmetrically on both sides of the axis L of the valve port 13 (left and right sides in FIG. 3B). Thus, the flange portion 24 constitutes an “urging means”. In the first modification, the thinner the flange portion 24, the larger the refrigerant flow rate. Therefore, a pressure difference occurs in the fluid pressure in the left-right direction at the asymmetrical portion of the valve member 2, and the valve member 2 A force acts on one side (direction intersecting the axis L). Thereby, the vibration of the valve member 2 can be suppressed similarly to 1st Embodiment, and the effect similar to 1st Embodiment is acquired.

  4A and 4B are diagrams showing a second modification of the valve member 2. FIG. 4A is a top view of the valve member, and FIG. 4B is a longitudinal sectional view of the valve member. As shown in FIG. 4A, the valve member 2 of Modification 2 has a flange portion 25 having a circular shape in plan view, and a hole 251 is formed in a part of the flange portion 25. . That is, the flange portion 25 of the valve member 2 is a non-rotationally symmetric asymmetric shape portion around the axis L.

  Thereby, the force by the flow of the refrigerant that has passed through the valve port 13 causes the valve member 2 to act asymmetrically on both sides of the axis L of the valve port 13 (left and right sides in FIG. 4B). Thus, the flange portion 25 constitutes an “urging means”. In the second modified example, since the flow rate of the refrigerant increases on the side of the flange portion 25 where the hole 251 is present, a pressure difference is generated in the fluid pressure in the left-right direction at the asymmetrical portion of the valve member 2, A force acts on one side (direction intersecting the axis L). Thereby, the vibration of the valve member 2 can be suppressed similarly to 1st Embodiment, and the effect similar to 1st Embodiment is acquired.

  FIG. 5 is a longitudinal sectional view of a temperature expansion valve according to the second embodiment, and FIG. 6 is a view showing a valve member according to the second embodiment. 6A is a top view of the valve body constituting the valve member, FIG. 6B is a longitudinal sectional view of the valve body, FIG. 6C is a top view of the plate member constituting the valve member, FIG. (D) is a longitudinal sectional view of the plate member, and FIG. 6 (E) is a longitudinal sectional view of the valve member. The major difference between the second embodiment and the first embodiment is the configuration of the valve member. Hereinafter, in the second to fourth embodiments, the same elements as those in the first embodiment and corresponding elements are denoted by the same reference numerals, and redundant description is omitted.

  The valve member 7 according to the second embodiment includes a valve body 7A having substantially the same shape as the valve member 2 of the first embodiment, and a plate member 7B. The valve body 7 </ b> A includes a needle portion 71, a flange portion 72, and a boss portion 73. The needle portion 71 is formed with a fixing hole 71 a for fixing to the lower end portion of the operating shaft 4. The plate member 7B is a thin plate press part and has a dish shape. A D-cut portion 741 cut along a plane parallel to the axis L is formed in a part thereof, and a fitting hole 75 is formed in the center. ing. Then, by inserting the boss portion 73 of the valve body 7A into the fitting hole 75, the valve body 7A and the plate member 7B are assembled together.

  Also in the second embodiment, the needle portion 71 of the valve member 7 is advanced and retracted into the valve port 13 by the action of the operating shaft 4, and the flow rate of the refrigerant flowing through the valve port 13 is changed according to the position of the valve port 13 in the axis L direction. Be controlled. In addition, the gap between the valve port 13 and the needle portion 71 constitutes a “throttle portion” that throttles the refrigerant. And at least a part of the valve member 7 is located downstream of the throttle portion.

  In the second embodiment, as shown in FIG. 6C, the portion of the D-cut portion 741 of the plate member 7 </ b> B in the valve member 7 is a non-rotationally symmetric asymmetric shape portion around the axis L. Thereby, the force by the flow of the refrigerant that has passed through the valve port 13 causes the valve member 7 to act asymmetrically on both sides of the axis L of the valve port 13 (left and right sides in FIG. 5). In this way, the plate member 7B constitutes an “urging means”. Then, since the flow rate of the refrigerant passing through the D-cut portion 741 side increases, a pressure difference is generated in the fluid pressure in the left-right direction at the asymmetrical portion of the valve member 7, and one side (axis L Force in the direction intersecting Thereby, the vibration of the valve member 7 can be suppressed and the same effect as 1st Embodiment is acquired. Further, the plate member 7B of the second embodiment is a thin press part, and the processing costs of the valve member and the valve seat can be suppressed.

  FIG. 7 is a longitudinal sectional view of a temperature expansion valve according to the third embodiment, and FIG. 8 is an enlarged sectional view of a main part of the temperature expansion valve according to the third embodiment. The major difference between the third embodiment and the first embodiment is the shape of the valve seat 13a, and the valve member 2 according to the third embodiment eliminates the hole 251 of the flange portion 25 in the modified example 2 of FIG. Shape.

  As shown in FIG. 8, a bleed groove 13a1 is formed in the valve seat 13a at one location on the end of the valve port 13 on the secondary joint 12a side. That is, in the third embodiment, the gap between the valve port 13 and the needle portion 21 and the bleed groove 13a constitute a “throttle portion” that squeezes the refrigerant. And at least a part of the valve member 2 is located downstream of the throttle portion.

  In this third embodiment, the portion of the bleed groove 13a1 of the valve seat 13a is a non-rotationally symmetric asymmetric shape portion around the axis L. Thereby, the force by the flow of the refrigerant that has passed through the valve port 13 causes the valve member 2 to act asymmetrically on both sides of the axis L of the valve port 13 (left and right sides in FIG. 7). Thus, the bleed groove 13a1 constitutes an “urging means”. And in this 3rd Embodiment, since the flow volume of the refrigerant | coolant which passes the bleed groove | channel 13a1 side increases, a pressure difference arises in the fluid pressure in the left-right direction in the asymmetric part of the valve member 2, and with respect to the valve member 2 The force acts on one side (direction intersecting the axis L). Thereby, the vibration of the valve member 2 can be suppressed and the effect similar to 1st Embodiment is acquired.

  FIG. 9 is an enlarged sectional view (FIG. 9 (A)) of a main part of the temperature expansion valve of the fourth embodiment and a bottom view (FIG. 9 (B)) of the valve seat part. In this 4th Embodiment, the big difference with 1st Embodiment is the shape of the valve seat 13a, and the valve member 2 in this 4th Embodiment is the same as that of 3rd Embodiment. The valve seat 13a is formed with an arcuate vertical wall portion 13a2 extending to the secondary joint 12a side (downstream side) around the valve port 13 and a notch portion 13a3 in which a part of the vertical wall portion 13a2 is lowered. Yes. That is, the vertical wall portion 13a2 and the cutout portion 13a3 are formed at positions that are offset to one side with respect to the axis L on the downstream side of the valve port 13.

  In the fourth embodiment, the vertical wall portion 13a2 and the notch portion 13a3 are non-rotationally symmetric asymmetrical shape portions around the axis L. Thereby, the force by the flow of the refrigerant that has passed through the valve port 13 acts on the valve member 2 asymmetrically with respect to both sides of the axis L of the valve port 13 (left and right sides in FIG. 9A). Thus, the vertical wall portion 13a2 and the notch portion 13a3 constitute “biasing means”. And in this 4th Embodiment, since the flow volume of the refrigerant | coolant which passes the notch part 13a3 side increases, a pressure difference arises in the fluid pressure in the left-right direction in the asymmetric part of the valve member 2, and the valve member 2 On the other hand, a force acts on one side (direction intersecting the axis L). Thereby, the vibration of the valve member 2 can be suppressed and the effect similar to 1st Embodiment is acquired.

  FIG. 10 is a schematic configuration diagram of a refrigeration cycle according to the embodiment. The refrigeration cycle 100 is used for an air conditioner such as a room air conditioner. In FIG. 10, 10 is a temperature expansion valve of each embodiment, 20 is an indoor heat exchanger that is an evaporator, 30 is an outdoor heat exchanger that is a condenser, and 40 is a compressor. The refrigerant compressed by the compressor 40 flows into the outdoor heat exchanger 30, is throttled by the temperature expansion valve 10, and is circulated in the order of the compressor 40 through the indoor heat exchanger 20. The outdoor heat exchanger 30 functions as a condenser, and the indoor heat exchanger 20 functions as an evaporator, thereby cooling the room or the like.

  A temperature sensing cylinder 6B is attached to an outlet side pipe 20a of the indoor heat exchanger 20 (evaporator) via a capillary 6A extending from the temperature expansion valve 10. The temperature sensing cylinder 6A senses the temperature of the outlet pipe 20a, applies a pressure corresponding to the temperature to the diaphragm device 6, and changes the valve opening of the temperature expansion valve 10 as described above.

  There are two types of temperature type expansion valves, an internal pressure equalizing type and an external pressure equalizing type, which are selectively used depending on the pressure loss inside the evaporator. When the pressure loss is constant or small, the internal pressure equalization method is used, and when the pressure loss is large, the external pressure equalization method is used. In the embodiment, the example of the external pressure equalization type in which the outlet pressure of the evaporator is introduced into the pressure equalizing chamber 65 has been described. Applicable to pressure equalization.

  Moreover, although the above description demonstrated the case where the refrigerant | coolant which flows in from the primary side coupling 11a was expanded and was made to flow out from the secondary side coupling 12a, the temperature expansion valve 10 of embodiment flows in from the secondary side coupling 12a. It can also be used when the refrigerant is expanded to flow out of the primary side joint 11a. For example, the temperature expansion valve 10 of the embodiment is applied even when the cooling mode and the heating mode are switched by providing a flow path switching valve in the refrigeration cycle described in FIG. 10 and switching the flow path of the refrigerant. Can do. In the heating mode in this case, since the indoor heat exchanger 20 functions as a condenser and the outdoor heat exchanger 30 functions as an evaporator, for example, the temperature sensing cylinder 6B and the pressure equalizing conduit 6C are connected to the suction side and the flow path of the compressor 40. The temperature expansion valve 10 is used by being mounted between the switching valve.

  As described above, the embodiments of the present invention have been described in detail with reference to the drawings. However, the specific configuration is not limited to these embodiments, and the design can be changed without departing from the scope of the present invention. Is included in the present invention.

1 Valve body 11 Piping connection hole 12 Piping connection hole 13 Valve port 13a Valve seat 13a1 Bleed groove (urging means)
13a2 Vertical wall (biasing means)
13a3 Notch (biasing means)
14 Valve chamber 15 Guide hole 16 Bearing hole 17 Screw hole 2 Valve member 21 Needle portion 22 Flange portion (biasing means)
221 D-cut surface 23 Boss part 24 Flange part (biasing means)
25 Flange part (biasing means)
251 Hole 3 Valve spring 4 Actuation shaft 5 Bearing portion 6 Diaphragm device 6A Capillary tube 6B Temperature sensing tube 61 Upper lid 62 Lower lid 63 Diaphragm 64 Diaphragm chamber 65 Pressure equalizing chamber 66 Metal 7 Valve member 7A Valve body 7B Plate member means)
71 Needle part 72 Flange part 73 Boss part 741 D cut part 75 Fitting hole 10 Thermal expansion valve 20 Indoor heat exchanger (evaporator)
20a Outlet side piping 30 Outdoor heat exchanger (condenser)
40 Compressor 100 Refrigeration cycle L axis

Claims (8)

A temperature expansion valve that controls the circulating flow rate of the fluid in the refrigeration cycle in response to the temperature of the outlet side piping of the evaporator of the refrigeration cycle,
At least a part of the valve member that opens and closes the valve port through which the fluid flows is located downstream of the throttle portion between the valve port and the valve member, and the valve member is moved by the force of the fluid flowing from the valve port. A temperature expansion valve comprising urging means for urging one side with respect to the axis of the valve port.   2. The temperature expansion valve according to claim 1, wherein the biasing means is configured by an asymmetrical shape portion that is non-rotationally symmetric about the axis of the valve member.   2. The temperature expansion valve according to claim 1, wherein the biasing means is formed of an asymmetrical shape portion that is non-rotationally symmetric about the axis formed in a valve seat around the valve port.   The valve member has a needle portion that is diameter-reduced from the downstream side to the upstream side facing the valve port, and a flange portion that extends in a plane direction intersecting the axis on the downstream side of the needle portion, The temperature expansion valve according to claim 2, wherein the asymmetric shape portion is formed in the flange portion.   The valve member is opposed to the valve port and has a needle portion whose diameter is reduced from the downstream side to the upstream side, and the needle portion is separated from the needle portion on the downstream side of the needle portion and extends in a plane direction intersecting the axis. The temperature expansion valve according to claim 2, wherein the asymmetric shape portion is formed in the plate member.   4. The temperature expansion valve according to claim 3, wherein the asymmetric shape portion is a bleed groove formed on the downstream side of the valve port.   4. The temperature expansion according to claim 3, wherein the asymmetrical shape portion is a vertical wall portion and a notch portion formed at a position offset to one side with respect to the axis on the downstream side of the valve port. valve.   The compressor which compresses the refrigerant | coolant which is a fluid, a condenser, an evaporator, and expands a refrigerant | coolant between the said condenser and the said evaporator, and decompresses it as described in any one of Claim 1 thru | or 7. A refrigeration cycle comprising a temperature expansion valve.

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