JP2020153479A - Temperature expansion valve and refrigeration cycle system using the same - Google Patents

Abstract

To provide a temperature expansion valve that can reduce noise by fragmentation of air bubbles contained in a coolant even as for the use of a long time in many years, prevents the occurrence of clogging by the deposit in a fine foaming member due to foreign matter contained in the coolant and does not close or narrow a flow path of the coolant, and furthermore, does not cause pressure drop to eliminate an effect on the flow rate control characteristics, and provide a refrigeration cycle system using the temperature expansion valve.SOLUTION: A temperature expansion valve is configured such that a diaphragm 68 of a diaphragm device 26 is deformed in an axial direction of a valve body member 44, and thereby the valve body member 44 connected to the diaphragm 68 is axially moved, and a valve member 50 controls an opening degree of a valve port 30 and adjusts a flow rate of the passing coolant through an inlet side port 36, the valve port 30 and an outlet side port 42. A fine foaming member 500 for finely breaking air bubbles contained in the coolant introduced from the inlet side port 36 is included in a facing portion of the valve body member 44 facing an opening 36a of the inlet side port 36.SELECTED DRAWING: Figure 1

Description

The present invention is used, for example, in a refrigerant circulation circuit of a refrigeration cycle system such as an air conditioner or a refrigerator, and automatically adjusts a valve opening in response to the temperature on the outlet side of an evaporator to automatically adjust the valve opening degree of the refrigerant circulation circuit of the refrigeration cycle system. The present invention relates to a temperature expansion valve used for controlling the degree of superheat and a refrigeration cycle system using the temperature expansion valve.

More specifically, the pressure difference between the temperature-sensitive pressure from the temperature-sensitive cylinder attached to the outlet side piping side of the evaporator of the refrigerant circulation circuit of the refrigerating cycle system, for example, and the evaporation pressure of the evaporator. Correspondingly, the diaphragm is deformed in the axial direction, so that the valve body member connected to the diaphragm moves in the axial direction, and the valve portion controls the opening degree of the valve port. The present invention relates to a refrigeration cycle system using a temperature expansion valve.

Conventionally, as a temperature expansion valve, for example, a temperature expansion valve as disclosed in Patent Document 1 (Japanese Unexamined Patent Publication No. 2012-229886) has been proposed.

That is, FIG. 12 is a vertical cross-sectional view of the conventional temperature expansion valve, FIG. 13 is a top view of the conventional temperature expansion valve of FIG. 12, and FIG. 14 is a refrigerant of a refrigeration cycle system to which the conventional temperature expansion valve is connected. It is a schematic diagram of a circulation circuit.

As shown in FIG. 14, in the refrigerant circulation circuit 101 of the refrigeration cycle system, the refrigerant flows inside the circulation pipe 102. A compressor 104 for compressing the refrigerant is provided, and the refrigerant is compressed in the compressor 104.

The refrigerant compressed by passing through the compressor 104 is configured to flow from the compressor 104 to the condenser 106. Then, the compressed refrigerant is condensed and liquefied in the condenser 106.

The outlet side pipe (secondary pipe) 108 of the condenser 106 is connected to the inlet side pipe (primary pipe) 112 of the temperature expansion valve 110.

The refrigerant liquefied in the condenser 106 is introduced into the temperature expansion valve 110 from the outlet side pipe 108 of the condenser 106 via the inlet side pipe 112 of the temperature expansion valve 110.

The temperature expansion valve 110 is configured so that the refrigerant that has been condensed and liquefied in the condenser 106 and introduced into the temperature expansion valve 110 is depressurized (expanded).

Further, the outlet side pipe (secondary pipe) 114 of the temperature expansion valve 110 is connected to the inlet pipe 118 of the evaporator 116.

The refrigerant decompressed (expanded) in the temperature expansion valve 110 is introduced into the evaporator 116 via the inlet pipe 118 of the evaporator 116, and the refrigerant is vaporized and vaporized.

The refrigerant evaporated and vaporized in the evaporator 116 is introduced into the compressor 104 again via the outlet side pipe 120 of the evaporator 116, and the refrigerant is compressed in the compressor 104, as described above. The refrigerant is circulated in the circulation pipe 102 of the refrigerant circulation circuit 101 in the direction indicated by the arrow in FIG.

By the way, as shown in FIGS. 12 to 14, a substantially cylindrical temperature sensitive cylinder 122 is provided on the outlet side pipe 120 side of the evaporator 116 so as to be attached to the outlet side pipe 120. Inside the temperature sensitive cylinder 122, for example, the same refrigerant as the refrigerant flowing in the circulation pipe 102 of the refrigerant circulation circuit 101 is sealed.

Then, the temperature sensing cylinder 122 is connected to the diaphragm device 126 of the temperature expansion valve 110 via the capillary tube 124, as will be described later.

On the other hand, as shown in FIG. 12, the temperature expansion valve 110 includes, for example, a metal valve housing 128 having a substantially cylindrical shape.

In the following, the upper side in FIG. 12 is referred to as "upper side" and "upper side", and the lower side in FIG. 12 is referred to as "lower side" and "lower side". Further, in FIG. 12, the right side is referred to as "right side", and in FIG. 12, the left side is referred to as "left side".

A valve port 130 is formed inside the valve housing 128 at a substantially central portion in the axial direction, and a valve seat 132 is formed around the valve port 130.

Further, on the side of the valve housing 128 opposite to the valve port 130 (upper side in FIG. 12), a valve housing upper wall 134 in which a cylindrical inlet-side valve chamber 131 is defined is formed.

An inlet side port 136 is formed in the valve housing upper wall 134 so as to open to one side (right side in FIG. 12) of the valve housing upper wall 134. An inlet side pipe (primary pipe) 112 constituting an inlet side joint member is connected to the inlet side port 136.

Then, the inlet side pipe 112 is connected so as to communicate with the outlet side pipe 108 of the condenser 106.

On the other hand, on the valve port 130 side (lower side in FIG. 12) of the valve housing 128, a valve housing lower wall 140 is formed in which a cylindrical outlet side valve chamber 138 is defined.

An outlet side port 142 is formed in the valve housing lower wall 140 so as to open to the other side (left side in FIG. 12) of the valve housing lower wall 140. An outlet side pipe (secondary pipe) 114 constituting an outlet side joint member is connected to the outlet side port 142.

The outlet side pipe 114 is connected to the inlet pipe 118 of the evaporator 116 so as to communicate with the inlet pipe 118.

Therefore, the valve port 130 is formed in the valve housing 128 at an intermediate position between the inlet side port 136 and the outlet side port 142.

Further, as shown in FIG. 12, the valve body member 144 moves (slides) in the valve housing upper wall 134 of the valve housing 128 in the axial direction so that the valve housing upper wall 134 constitutes a guide surface. ) It is installed as possible.

The valve body member 144 includes a large-diameter valve shaft member main body 146 that constitutes a sliding portion, and the valve shaft member main body 146 is configured to slide on the inner surface of the valve housing upper wall 134. There is.

Further, a valve rod member 148 having a diameter smaller than that of the valve shaft member main body 146 is formed on the valve port 130 side (lower side in FIG. 12) of the valve shaft member main body 146. The inlet side valve chamber 131 described above is defined in the gap between the outer circumference of the valve rod member 148 and the valve housing upper wall 134.

On the other hand, at the end of the valve rod member 148 on the valve port 130 side (lower side in FIG. 12), a valve portion 150 having a diameter larger than that of the valve port 130 is formed so as to penetrate the valve port 130.

As will be described later, the shoulder surface 152 of the valve portion 150 and the valve seat 132 formed around the valve port 130 are separated from each other to control the opening degree (throttle). There is.

Further, the valve housing upper wall 134 of the valve housing 128 is formed with an opening 154 at the end opposite to the valve port 130 (upper side in FIG. 12) so as to close the opening 154. The diaphragm device 126 is mounted so as to be connected.

That is, a male screw 158 is formed on the outer periphery of the opening 154 of the valve housing 128.

A female screw 164 is formed on the inner circumference of the cylindrical mounting portion 162 on the lower side of the lower lid member 160 of the diaphragm device 126, corresponding to the male screw 158 of the valve housing 128.

As a result, the lower lid member 160 of the diaphragm device 126 is attached to the upper end portion of the valve housing 128 by screwing the female screw 164 of the lower lid member 160 to the male screw 158 of these valve housings 128. ,

On the other hand, in the diaphragm device 126, the diaphragm device 126 is configured by the upper lid member 166 fixing the flange portion 160a of the lower lid member 160 and the flange portion 166a of the upper lid member 166 so as to face the lower lid member 160. ing.

Then, as shown in FIG. 12, the flange portion 168a of the diaphragm 168 is sandwiched and fixed between the flange portion 160a of the lower lid member 160 and the flange portion 166a of the upper lid member 166.

A pressure receiving chamber 170 surrounded by the upper lid member 166 and the diaphragm 168 is formed on the upper side of the diaphragm device 126 via the diaphragm 168.
On the other hand, a pressure equalizing chamber 172 surrounded by the lower lid member 160 and the diaphragm 168 is formed on the lower side of the diaphragm device 126.

A capillary tube 124 is attached to the upper lid member 166 so as to communicate with the pressure receiving chamber 170, and is connected to the temperature sensing cylinder 122 via the capillary tube 124.

On the other hand, a needle portion 174 is formed at the tip of the valve shaft member main body 146 on the opposite side (upper side in FIG. 12) from the valve port 130.

The needle portion 174 extends below the contact member 176, and the step portion 174a of the needle portion 174 extends below the contact member 176 in the central contact hole portion 176a of the contact member 176 fixed below the diaphragm 168. It is inserted so as to come into contact with the installation portion 176b.

A ring-shaped seal member 180 is interposed on the outer periphery of the step portion 174a of the needle portion 174 via a pressing member 178.

The pressure equalizing chamber 172 formed on the lower side of the diaphragm device 126 and the inlet side valve chamber 131 of the valve housing 128 are airtightly separated via the seal member 180.

Further, although not shown, a pressure equalizing path is formed on the valve housing upper wall 134 so as to extend in the axial direction, and one end of the pressure equalizing path is formed in the pressure equalizing chamber 172 formed below the diaphragm device 126. It communicates with.

Then, as shown in FIGS. 12 to 14, the other end of the pressure equalizing path communicates with the pressure equalizing pipe 182 connected to the front side (lower side in FIG. 13) of the valve housing upper wall 134 in FIG. Has been done.

As shown in FIG. 14, the pressure equalizing pipe 182 is connected to the outlet side pipe 120 of the evaporator 116 via the pressure equalizing path 184.

On the other hand, the superheat degree setting portion 188 is attached to the mounting hole 186 formed on the lower side of the valve housing lower wall 140 of the valve housing 128.

That is, the superheat degree setting unit 188 includes the adjustment spindle 190, and the male screw 192a formed on the outer periphery of the base end portion 192 of the adjustment spindle 190 and the female on the inner circumference of the valve housing lower wall 140. The adjusting spindle 190 is configured to be movable in the axial direction by screwing the screw 140a.

Further, as shown in FIG. 12, an adjustment spring accommodating recess 191 is formed in the upper central portion of the adjustment spindle 190. On the other hand, a contact portion 150a is formed so as to project from the lower end of the valve portion 150 of the valve body member 144.

A compressed adjustment spring 196 is interposed between the dish-shaped retainer 194 and the adjustment spring accommodating recess 191 of the adjustment spindle 190 so as to abut the contact portion 150a at the lower end of the valve portion 150. ..

On the other hand, an O-ring member 198 constituting a seal member is interposed at the upper end of the adjustment spindle 190. The outlet side valve chamber 138 and the outside of the mounting hole 186 are airtightly held via the O-ring member 198.

With this configuration, the valve portion 150 of the valve body member 144 is urged in the closing (closing) direction of the valve port 130 by the spring force of the adjusting spring 196. That is, the shoulder surface 152 of the valve portion 150 and the valve seat 132 formed around the valve port 130 are in contact with each other so that the valve is closed.

Then, the diaphragm 168 is configured to be urged upward via the needle portion 174 formed at the upper tip of the valve shaft member main body 146 and the abutting member 176 fixed below the diaphragm 168. ing.

Then, by turning the adjusting spindle 190 and moving the adjusting spindle 190 up and down in the axial direction, the spring force of the adjusting spring 196 is adjusted, and the urging force of the valve body member 144 to the valve portion 150 is adjusted. It is configured as follows.

On the other hand, a retaining ring member 200 for preventing the adjusting spindle 190 from falling off is attached to the mounting hole 186.

A ring-shaped recess 186a is formed around the opening at the lower end of the mounting hole 186, and a female screw 186b is formed around the inside of the mounting hole 186 on the upper side in the axial direction.

For example, a ring-shaped sealing member 202 made of polytetrafluoroethylene (PTFE) is arranged in the recess 186a, and a lid member 204 has a male screw 204a in the lower end of the mounting hole 186. , It is attached by screwing it into the female screw 186b of the attachment hole 186.

As a result, by screwing the lid member 204, the sealing member 202 is slightly crushed and plastically deformed, fixed in the recess 186a, and is configured to maintain airtightness.

In the conventional temperature expansion valve 110 configured as described above, as shown in FIG. 14, the pressure equalizing chamber 172 formed on the lower side of the diaphragm device 126 sandwiching the diaphragm 168 is formed on the pressure equalizing pipe 182 and the pressure equalizing pipe 182. It is connected to the outlet side pipe 120 of the evaporator 116 via the pressure path 184.

Therefore, the evaporation pressure of the outlet side pipe 120 of the evaporator 116 is introduced into the pressure equalizing chamber 172 formed under the diaphragm device 126.

On the other hand, the pressure receiving chamber 170 formed on the upper side of the diaphragm 168 of the diaphragm device 126 is connected to the temperature sensing cylinder 122 via the capillary tube 124.

Therefore, the internal pressure of the pressure receiving chamber 170 is a temperature sensitive pressure that changes according to the sensed temperature on the outlet side pipe 120 side of the evaporator 116, which is sensed by the temperature sensitive cylinder 122.

The diaphragm 168 of the diaphragm device 126 has a shaft according to the pressure difference (differential pressure) between the temperature-sensitive pressure in the pressure receiving chamber 170 and the evaporation pressure of the outlet side pipe 120 of the evaporator 116 in the pressure equalizing chamber 172. It will be deformed up and down in the direction.

The axial deformation of the diaphragm 168 is passed through the abutting member 176 fixed below the diaphragm 168, and the needle portion 174 formed at the upper tip of the valve shaft member main body 146 of the valve body member 144. Therefore, it is configured to be transmitted to the valve shaft member main body 146, the valve rod member 148, and the valve portion 150.

As a result, the shoulder surface 152 of the valve portion 150 and the valve seat 132 formed around the valve port 130 are separated from each other to control the opening degree (throttle).

That is, the temperature expansion valve 110 acts so that the valve portion 150 opens (opens) the valve port 130 when the sensed temperature of the outlet side pipe 120 of the evaporator 116 becomes high.

On the contrary, when the sensed temperature of the outlet side pipe 120 of the evaporator 116 becomes low, the valve portion 150 is configured to act to close (close) the valve port 130.

Further, when the evaporation pressure in the evaporator 116 becomes low, the valve portion 150 acts to open (open) the valve port 130.

On the contrary, when the evaporation pressure in the evaporator 116 becomes high, the valve portion 150 is configured to act to close (close) the valve port 130.

As a result, the diaphragm 168 is axially deformed according to the differential pressure between the temperature-sensitive pressure from the temperature-sensitive cylinder 122 and the evaporation pressure of the evaporator 116, so that the valve body member 144 connected to the diaphragm 168 is formed. By moving in the axial direction, the valve portion 150 controls the opening degree of the valve port 130.

Then, the opening degree at which the refrigerant flows from the outlet side pipe 108 of the condenser 106 to the inlet side pipe 118 of the evaporator 116 via the inlet side port 136, the valve port 130, and the outlet side port 142 is controlled, and the refrigeration cycle ( It is configured to control the degree of superheat of the refrigerant circulation circuit 101) of the air conditioner.

Japanese Unexamined Patent Publication No. 2012-229886 Japanese Unexamined Patent Publication No. 2011-133139

By the way, in such a conventional temperature expansion valve 110, the refrigerant is condensed and liquefied in the condenser 106, and the refrigerant is discharged from the outlet side pipe 108 of the condenser 106 via the inlet side pipe 112 of the temperature expansion valve 110. It is designed to be introduced in 110.

However, the refrigerant introduced into the temperature expansion valve 110 may contain air bubbles. In that case, air bubbles contained in the refrigerant introduced into the temperature expansion valve 110 via the inlet side pipe 112 of the temperature expansion valve 110 are particularly generated in the valve portion 150 of the valve body member 144 and the shoulder surface 152. And, when passing through the throttle portion formed by the valve seat 132 formed around the valve port 130, air bubbles burst, noise is generated, and quietness is impaired.

Therefore, Patent Document 2 (Japanese Unexamined Patent Publication No. 2011-133139) proposes the following measures in order to reduce noise in the expansion valve.

FIG. 15 is a partially enlarged cross-sectional view schematically showing the expansion valve 300 of Patent Document 2.

As shown in FIG. 15, the expansion valve 300 of Patent Document 2 includes a valve main body 302 constituting a valve casing. Further, it is provided with an inlet port 304 into which a compressed and condensed high-pressure refrigerant is introduced by passing through a compressor and a condenser.

Further, the valve body 302 is formed with an outlet port 306 for sending the decompressed (expanded) refrigerant to the evaporator by passing through the expansion valve 300.

On the other hand, a valve chamber 308 is formed in the valve body 302, and in the valve chamber 308, in order to control the opening degree of the valve hole 316, the diaphragm of the diaphragm device (not shown) is deformed in the axial direction. A movable valve member 312 is provided.

Then, a fine foaming member 314 made of a porous metal body is provided on the inlet port 304 side. Further, on the upstream side of the fine foaming member 314, for example, a substantially conical strainer 600 made of a net-like sheet made of plastic, metal, or the like is provided.

As a result, the bubbles contained in the refrigerant are subdivided by the foaming member 314, and the rectified refrigerant is introduced into the valve chamber 308, so that the generation of noise due to the bursting of the bubbles is reduced. It has been proposed that it can be done.

Further, it has been proposed that by passing through the strainer 600, clogging of the fine foaming member 314 made of a porous metal body due to foreign matter in the refrigerant and an increase in pressure loss are suppressed.

However, in the expansion valve 300 of Patent Document 2, the refrigerant passes through a strainer 600 having a substantially conical shape composed of a net-like sheet and a fine foaming member 314 made of a porous metal body.

Therefore, after long-term use of the expansion valve 300 for many years, foreign matter contained in the refrigerant accumulates on the fine foaming member 314 and the strainer 600, causing clogging, blocking the flow path of the refrigerant and narrowing the flow. This causes pressure loss and affects the flow rate control characteristics.

As a result, it also leads to a decrease in the air conditioning efficiency of the refrigeration cycle system, for example, an air conditioner.

In view of this situation, the present invention reduces noise due to the fragmentation of bubbles contained in the refrigerant even after long-term use of the conventional temperature expansion valve 110 as disclosed in Patent Document 1. It is an object of the present invention to provide a temperature expansion valve capable of the above and a refrigeration cycle system using the temperature expansion valve.

Further, the present invention prevents the conventional temperature expansion valve 110 as disclosed in Patent Document 1 from being accumulated on the fine foaming member due to foreign matter contained in the refrigerant and causing clogging. An object of the present invention is to provide a temperature expansion valve that does not block the flow path of the refrigerant, does not narrow the flow path, does not cause pressure loss, and does not affect the flow control characteristics, and a refrigeration cycle system using the temperature expansion valve. To do.

The present invention has been invented in order to achieve the above-mentioned problems and objects in the prior art, and the temperature expansion valve of the present invention is:
When the diaphragm of the diaphragm device is deformed in the axial direction of the valve body member, the valve body member connected to the diaphragm moves in the axial direction, and the valve portion integrated with the valve body member controls the opening degree of the valve port. hand,
It is configured to regulate the flow rate of refrigerant passing through the inlet side port, valve port, and outlet side port.
The valve body member facing the opening of the inlet side port is provided with a fine foaming member for making bubbles contained in the refrigerant introduced from the inlet side port finer.

With this configuration, a fine foaming member for making bubbles contained in the refrigerant introduced from the inlet side port finer is provided in the facing portion of the valve body member facing the opening of the inlet side port. ..

Therefore, the air bubbles contained in the refrigerant introduced from the inlet side port come into contact with the fine foaming member provided in the facing portion of the valve body member facing the opening of the inlet side port, and the air bubbles are subdivided. Will be.

Moreover, since there is a solid valve body member that is not porous (that is, does not allow the refrigerant that is a fluid to pass through) on the back side of the side facing the opening of the inlet side port of the fine foaming member, it is thin. It will be guided to the valve port side without penetrating the foaming member.

Therefore, it is possible to reduce noise due to the fragmentation of bubbles contained in the refrigerant even after long-term use for many years.

Further, since a solid valve body member that is not porous exists on the back surface side of the port facing the inlet side port of the foaming member, it does not penetrate the foaming member.
Therefore, since the refrigerant does not penetrate the fine foaming member, foreign matter is unlikely to accumulate on the fine foaming member, and even if foreign matter accumulates and the fine foaming member is clogged, the flow path of the refrigerant can be blocked. Absent.
Moreover, it is possible to provide a temperature expansion valve that does not cause pressure loss and does not affect the flow rate control characteristics.

Further, the temperature expansion valve of the present invention is characterized in that the fine foaming member is provided in close contact with a valve body member which is a member through which a fluid refrigerant cannot pass.

With this configuration, the fine foaming member is provided in close contact with the valve body member, which is a member through which the fluid refrigerant cannot pass, so that the refrigerant does not penetrate the fine foaming member. Foreign matter is unlikely to accumulate on the chemical member, and even if foreign matter accumulates and the fine foam member is clogged, the flow path of the refrigerant will not be blocked.

Further, in the temperature expansion valve of the present invention, the fine foaming member is not arranged at a position where the fluid flowing in from the inlet side port blocks a part or all of the flow path toward the valve port. It is a feature.

With this configuration, the fine foaming member is not arranged at a position where the fluid flowing in from the inlet side port blocks a part or all of the flow path toward the valve port, so that a foreign matter is tentatively generated. The fine foaming member does not block the flow path of the refrigerant even when the fine foaming member is clogged with the accumulation of water.

Further, in the temperature expansion valve of the present invention, the finely foamed member is valved in a direction orthogonal to the axial direction of the valve body member at any position from when the valve is opened to when the valve is closed. It is characterized in that it is arranged so that at least a part of it is located at the projected position projected toward the body member.

With this configuration, the foaming member makes the opening of the inlet side port into the valve body member in the direction orthogonal to the axial direction of the valve body member at any position from the valve opening to the valve closing. Since it is arranged so that at least a part of it is located at the projected position projected toward it, it is possible to reduce noise due to the fragmentation of bubbles contained in the refrigerant at any position from when the valve is opened to when the valve is closed. Is.

Further, foreign matter is unlikely to be deposited on the foaming member, and even if the foreign matter is deposited and the foaming member is clogged, the flow path of the refrigerant is not blocked.
Moreover, it is possible to provide a temperature expansion valve that does not cause pressure loss and does not affect the flow rate control characteristics.

Further, in the temperature expansion valve of the present invention, the fine foaming member makes the opening of the inlet side port orthogonal to the axial direction of the valve body member at any position from the valve opening to the valve closing. It is characterized in that the projection range when projected toward the fine foaming member is provided so as to be entirely located on the fine foaming member.

With this configuration, the foaming member foams the opening of the inlet side port in a direction orthogonal to the axial direction of the valve body member at any position from valve opening to valve closing. Since the projection range when projected toward the chemical member is provided so that it is entirely located on the fine foam member, the bubbles contained in the refrigerant are reliably subdivided and noise reduction is improved. To do.

Further, foreign matter is unlikely to be deposited on the foaming member, and even if the foreign matter is deposited and the foaming member is clogged, the flow path of the refrigerant is not blocked.
Moreover, it is possible to provide a temperature expansion valve that does not cause pressure loss and does not affect the flow rate control characteristics.

Further, the temperature expansion valve of the present invention is characterized in that the fine foaming member is provided on the entire outer circumference of the valve body member facing the opening of the inlet side port.

With this configuration, the foaming member is provided on the entire outer circumference of the valve body member facing the opening of the inlet side port, so that the valve body member rotates during the valve operation. However, the foaming member always faces the opening of the inlet side port.

As a result, the bubbles contained in the refrigerant introduced from the inlet side port surely come into contact with the fine foaming member, the bubbles contained in the refrigerant are surely subdivided, and the noise reduction is improved. ..

Further, foreign matter is unlikely to be deposited on the foaming member, and even if the foreign matter is deposited and the foaming member is clogged, the flow path of the refrigerant is not blocked.
Moreover, it is possible to provide a temperature expansion valve that does not cause pressure loss and does not affect the flow rate control characteristics.

Further, since there is a solid valve body member that is not porous (that is, does not allow the refrigerant which is a fluid to pass through) on the back side of the foaming member on the side facing the opening of the inlet side port, it is thin. It will be guided to the valve port side without penetrating the foaming member.

Therefore, it is possible to reduce noise due to the fragmentation of bubbles contained in the refrigerant even after long-term use for many years.

Further, since a solid valve body member that is not porous exists on the back surface side of the port facing the inlet side port of the foaming member, it does not penetrate the foaming member.
Therefore, since the refrigerant does not penetrate the fine foaming member, foreign matter is unlikely to accumulate on the fine foaming member, and even if foreign matter accumulates and the fine foaming member is clogged, the flow path of the refrigerant can be blocked. Absent.
Moreover, it is possible to provide a temperature expansion valve that does not cause pressure loss and does not affect the flow rate control characteristics.

Further, in the temperature expansion valve of the present invention, the fine foaming member inserts the valve body member into the central opening of the cylindrical fine foaming member and the central opening of the valve member to insert the fine foaming member. It is characterized in that it is sandwiched and fixed by the valve body member and the valve member.

With this configuration, the fine foaming member inserts the valve body member into the central opening of the cylindrical fine foaming member and the central opening of the valve member, and the fine foaming member is inserted into the valve body member. And the valve member are sandwiched and fixed.

Therefore, for example, by caulking, fastening members such as nuts and screws, welding, etc., the fine foaming member is sandwiched and fixed between the valve body member and the valve member to stabilize the fine foaming member and to the inlet side port. Can be held in a facing position.

As a result, the bubbles contained in the refrigerant introduced from the inlet side port surely come into contact with the fine foaming member, the bubbles contained in the refrigerant are surely subdivided, and the noise reduction is improved. ..

Further, foreign matter is unlikely to be deposited on the foaming member, and even if the foreign matter is deposited and the foaming member is clogged, the flow path of the refrigerant is not blocked.
Moreover, it is possible to provide a temperature expansion valve that does not cause pressure loss and does not affect the flow rate control characteristics.

Further, the temperature expansion valve of the present invention is characterized in that the fine foaming member is arranged so as to be located on the outer peripheral portion of the valve body member and is fixed by a ring-shaped mounting member from the outer peripheral side.

With this configuration, the foaming member is arranged so as to be located on the outer peripheral portion of the valve body member and is fixed by the ring-shaped mounting member from the outer peripheral side, so that mounting is easy and cost is reduced. In addition to being able to reduce the amount, the foaming member can be stably held on the outer peripheral portion of the valve body member at a position facing the opening of the inlet side port.

As a result, the bubbles contained in the refrigerant introduced from the inlet side port surely come into contact with the fine foaming member, the bubbles contained in the refrigerant are surely subdivided, and the noise reduction is improved. ..

Further, foreign matter is unlikely to be deposited on the foaming member, and even if the foreign matter is deposited and the foaming member is clogged, the flow path of the refrigerant is not blocked.
Moreover, it is possible to provide a temperature expansion valve that does not cause pressure loss and does not affect the flow rate control characteristics.

Further, in the temperature expansion valve of the present invention, the outer peripheral surface of the foaming member is formed of a tapered surface or a curved shape that is inclined with respect to the axial direction of the foaming member, and is introduced from the inlet side port. It is characterized in that it is configured to serve as a guide surface for the refrigerant.

With this configuration, the outer peripheral surface of the fine foaming member is formed of a tapered surface or a curved shape that is inclined with respect to the axial direction of the fine foaming member, and the refrigerant introduced from the inlet side port. Since it is configured to be a guide surface, the refrigerant is guided to the valve port side along this guide surface.

As a result, the bubbles contained in the refrigerant introduced from the inlet side port surely come into contact with the fine foaming member, the bubbles contained in the refrigerant are surely subdivided, and the noise reduction is improved. ..

Further, foreign matter is unlikely to be deposited on the foaming member, and even if the foreign matter is deposited and the foaming member is clogged, the flow path of the refrigerant is not blocked.
Moreover, it is possible to provide a temperature expansion valve that does not cause pressure loss and does not affect the flow rate control characteristics.

Further, the refrigeration cycle system of the present invention is characterized in that the temperature / temperature expansion valve described in any of the above is connected to a pipe between the condenser and the evaporator of the refrigerant circulation circuit of the refrigeration cycle system.

With such a configuration, the temperature expansion valve of the present invention is the conventional temperature expansion valve 110 as disclosed in Patent Document 1, and even if it is used for many years and for a long time, the bubbles contained in the refrigerant are subdivided. It is possible to provide a temperature expansion valve capable of reducing noise due to the conversion and a refrigeration cycle system using the temperature expansion valve.

Further, according to the present invention, in the conventional temperature expansion valve 110 as disclosed in Patent Document 1, bubbles contained in the refrigerant introduced from the inlet side port surely come into contact with the fine foaming member. The bubbles contained in the refrigerant can be reliably subdivided, noise can be reduced, and foreign matter is less likely to accumulate on the foaming member, and foreign matter is temporarily accumulated on the foaming member. To provide a temperature expansion valve that does not block the flow path of the refrigerant even if it is clogged, does not cause pressure loss, and does not affect the flow rate control characteristics, and a refrigeration cycle system using the temperature expansion valve. It will be possible to provide.

According to the present invention, a foaming member for making bubbles contained in the refrigerant introduced from the inlet side port finer is provided on the facing portion of the valve body member facing the opening of the inlet side port.

Therefore, the air bubbles contained in the refrigerant introduced from the inlet side port come into contact with the fine foaming member provided in the facing portion of the valve body member facing the opening of the inlet side port, and the air bubbles are subdivided. Will be.

Moreover, since there is a solid valve body member that is not porous (that is, does not allow the refrigerant that is a fluid to pass through) on the back side of the side facing the opening of the inlet side port of the fine foaming member, it is thin. It will be guided to the valve port side without penetrating the foaming member.

Therefore, it is possible to reduce noise due to the fragmentation of bubbles contained in the refrigerant even after long-term use for many years.

Further, since a solid valve body member that is not porous exists on the back surface side of the port facing the inlet side port of the foaming member, it does not penetrate the foaming member.
Therefore, since the refrigerant does not penetrate the fine foaming member, foreign matter is unlikely to accumulate on the fine foaming member, and even if foreign matter accumulates and the fine foaming member is clogged, the flow path of the refrigerant can be blocked. Absent.
Moreover, it is possible to provide a temperature expansion valve that does not cause pressure loss and does not affect the flow rate control characteristics.

FIG. 1 is a vertical cross-sectional view of the temperature expansion valve 10 of the present invention. FIG. 2 is a top view of the temperature expansion valve 10 of the present invention of FIG. FIG. 3 is a schematic view of a refrigerant circulation circuit of an air conditioner to which the temperature expansion valve 10 of the present invention is connected. FIG. 4 is a partially enlarged cross-sectional view of the temperature expansion valve 10 of the present invention of FIG. FIG. 5 is a cross-sectional view taken along the line AA of FIG. FIG. 6 is a vertical cross-sectional view of the temperature expansion valve 10 of another embodiment of the present invention. FIG. 7 is a partially enlarged cross-sectional view of the temperature expansion valve 10 of the present invention. 8A and 8B are schematic views illustrating a method of attaching and fixing the fine foaming member 500 of the temperature expansion valve 10 of the embodiment of FIG. 6, FIG. 8A is a front view, and FIG. 8B is a front view. A side view and FIG. 8C is a cross-sectional view taken along the line BB of FIG. 8A. 9A and 9B are schematic views showing a ring-shaped mounting member 53, FIG. 9A is a front view, FIG. 9B is a side view, and FIG. 9C is a top view. 10A and 10B are schematic views showing another embodiment of the ring-shaped mounting member 53, FIG. 10A is a front view, and FIG. 10B is a side view. FIG. 11 is a schematic view showing an axial cross section of the fine foaming member 500 showing another embodiment of the fine foaming member 500 of the temperature expansion valve 10 of another embodiment of the present invention. FIG. 12 is a vertical sectional view of a conventional temperature expansion valve. FIG. 13 is a top view of the conventional temperature expansion valve of FIG. FIG. 14 is a schematic view of a refrigerant circulation circuit of an air conditioner to which a conventional temperature expansion valve is connected. FIG. 15 is a partially enlarged cross-sectional view schematically showing the expansion valve 300 of Patent Document 2.

Hereinafter, embodiments (examples) of the present invention will be described in more detail with reference to the drawings.
(Example 1)

1 is a vertical sectional view of the temperature expansion valve 10 of the present invention, FIG. 2 is a top view of the temperature expansion valve 10 of the present invention of FIG. 1, and FIG. 3 is an air to which the temperature expansion valve 10 of the present invention is connected. A schematic view of the refrigerant circulation circuit of the harmonizer, FIG. 4 is a partially enlarged sectional view of the temperature expansion valve 10 of the present invention of FIG. 1, and FIG. 5 is a sectional view taken along the line AA of FIG.

In FIG. 1, reference numeral 10 indicates the temperature expansion valve of the present invention as a whole.

As shown in FIG. 3, in the refrigerant circulation circuit 101 of a refrigeration cycle system, for example, an air conditioner, the refrigerant flows inside the circulation pipe 102. A compressor 104 for compressing the refrigerant is provided, and the refrigerant is compressed in the compressor 104.

The refrigerant compressed by passing through the compressor 104 is configured to flow from the compressor 104 to the condenser 106. Then, the compressed refrigerant is condensed and liquefied in the condenser 106.

The outlet side pipe (secondary pipe) 108 of the condenser 106 is connected to the inlet side pipe (primary pipe) 12 of the temperature expansion valve 10.

The refrigerant liquefied in the condenser 106 is introduced into the temperature expansion valve 10 from the outlet side pipe 108 of the condenser 106 via the inlet side pipe 12 of the temperature expansion valve 10.

The temperature expansion valve 10 is configured so that the refrigerant that has been condensed and liquefied in the condenser 106 and introduced into the temperature expansion valve 10 is depressurized (expanded).

Further, the outlet side pipe (secondary pipe) 14 of the temperature expansion valve 10 is connected to the inlet pipe 118 of the evaporator 116.

Then, the refrigerant decompressed (expanded) in the temperature expansion valve 10 is introduced into the evaporator 116 via the inlet pipe 118 of the evaporator 116, and the refrigerant is vaporized and vaporized.

The refrigerant evaporated and vaporized in the evaporator 116 is introduced into the compressor 104 again via the outlet side pipe 120 of the evaporator 116, and the refrigerant is compressed in the compressor 104, as described above. The refrigerant is circulated in the circulation pipe 102 of the refrigerant circulation circuit 101 in the direction indicated by the arrow in FIG.

By the way, as shown in FIGS. 1 to 3, a substantially cylindrical temperature sensitive cylinder 122 is provided on the outlet side pipe 120 side of the evaporator 116 so as to be attached to the outlet side pipe 120. Inside the temperature sensitive cylinder 122, for example, the same refrigerant as the refrigerant flowing in the circulation pipe 102 of the refrigerant circulation circuit 101 is sealed.

Then, the temperature sensing cylinder 122 is connected to the diaphragm device 26 of the temperature expansion valve 10 via the capillary tube 124, as will be described later.

On the other hand, as shown in FIG. 1, the temperature expansion valve 10 includes, for example, a metal valve housing 28 having a substantially cylindrical shape.

In the following, the upper side in FIG. 1 is referred to as "upper side" and "upper side", and the lower side in FIG. 1 is referred to as "lower side" and "lower side". Further, in FIG. 1, the right side is referred to as "right side", and in FIG. 1, the left side is referred to as "left side".

A valve port 30 is formed inside the valve housing 28 at a substantially central portion in the axial direction, and a valve seat 32 is formed around the valve port 30.

Further, on the side of the valve housing 28 opposite to the valve port 30 (upper side in FIG. 1), a valve housing upper wall 34 is formed in which a cylindrical inlet side valve chamber 31 is defined.

An inlet side port 36 is formed in the valve housing upper wall 34 so as to open to one side (right side in FIG. 1) of the valve housing upper wall 34. An inlet side pipe (primary pipe) 12 constituting an inlet side joint member is connected to the inlet side port 36.

Then, the inlet side pipe 12 is connected so as to communicate with the outlet side pipe 108 of the condenser 106.

On the other hand, on the valve port 30 side (lower side in FIG. 1) of the valve housing 28, a valve housing lower wall 40 is formed in which a cylindrical outlet side valve chamber 38 is defined.

An outlet side port 42 is formed in the valve housing lower wall 40 so as to open to the other side (left side in FIG. 1) of the valve housing lower wall 40. An outlet side pipe (secondary pipe) 14 constituting an outlet side joint member is connected to the outlet side port 42.

The outlet side pipe 14 is connected to the inlet pipe 118 of the evaporator 116 so as to communicate with the inlet pipe 118.

Therefore, the valve port 30 is formed in the valve housing 28 at an intermediate position between the inlet side port 36 and the outlet side port 42.

Further, as shown in FIG. 1, the valve body member 44 moves (slides) in the valve housing upper wall 34 of the valve housing 28 in the axial direction so that the valve housing upper wall 34 constitutes a guide surface. ) It is installed as possible.

The valve body member 44 includes a large-diameter valve shaft member main body 46 that constitutes a sliding portion, and the valve shaft member main body 46 is configured to slide on the inner surface of the valve housing upper wall 34. There is.

Further, on the valve port 30 side (lower side in FIG. 1) of the valve shaft member main body 46, a valve rod member 48 having a diameter smaller than that of the valve shaft member main body 46 is provided. The inlet side valve chamber 31 described above is defined in the gap between the outer circumference of the valve rod member 48 and the valve housing upper wall 34.

On the other hand, at the end of the valve rod member 48 on the valve port 30 side (lower side in FIG. 1), the valve port 30 is penetrated and a diameter larger than that of the valve port 30 is formed.

As will be described later, the shoulder surface 52 of the valve member 50 and the valve seat 32 formed around the valve port 30 are separated from each other to control the opening degree (throttle). There is.

Further, the valve housing upper wall 34 of the valve housing 28 is formed with an opening 54 at the end opposite to the valve port 30 (upper side in FIG. 1) so as to close the opening 54. , The diaphragm device 26 is mounted so as to be connected.

That is, a male screw 58 is formed on the outer periphery of the opening 54 of the valve housing 28.

A female screw 64 is formed on the inner circumference of the cylindrical mounting portion 62 on the lower side of the lower lid member 60 of the diaphragm device 26, corresponding to the male screw 58 of the valve housing 28.

As a result, the lower lid member 60 of the diaphragm device 26 is airtightly attached to the upper end portion of the valve housing 28 by screwing the female screw 64 of the lower lid member 60 to the male screw 58 of these valve housings 28. ing.

On the other hand, in the diaphragm device 26, the diaphragm device 26 is configured by the upper lid member 66 fixing the flange portion 60a of the lower lid member 60 and the flange portion 66a of the upper lid member 66 so as to face the lower lid member 60. ing.

Then, as shown in FIG. 1, the flange portion 68a of the diaphragm 68 is airtightly fixed between the flange portion 60a of the lower lid member 60 and the flange portion 66a of the upper lid member 66 by welding.

A pressure receiving chamber 70 surrounded by the upper lid member 66 and the diaphragm 68 is formed on the upper side of the diaphragm device 26 via the diaphragm 68.
On the other hand, a pressure equalizing chamber 72 surrounded by the lower lid member 60 and the diaphragm 68 is formed on the lower side of the diaphragm device 26.

A capillary tube 124 is attached to the upper lid member 66 so as to communicate with the pressure receiving chamber 70, and is connected to the temperature sensing cylinder 122 via the capillary tube 124.

On the other hand, a needle portion 74 is formed at the tip of the valve shaft member main body 46 on the opposite side (upper side in FIG. 1) to the valve port 30.

The step portion 74a of the needle portion 74 extends below the contact member 76 in the central contact hole portion 76a of the contact member 76 in which the needle portion 74 is fixed below the diaphragm 68. It is inserted so as to come into contact with the installation portion 76b.

A ring-shaped seal member 80 is interposed on the outer periphery of the step portion 74a of the needle portion 74 via a pressing member 78.

The pressure equalizing chamber 72 formed on the lower side of the diaphragm device 26 and the inlet side valve chamber 31 of the valve housing 28 are airtightly separated via the seal member 80.

Further, although not shown, a pressure equalizing path is formed on the valve housing upper wall 34 so as to extend in the axial direction, and one end of the pressure equalizing path is formed on the lower side of the diaphragm device 26. It communicates with.

Then, as shown in FIGS. 1 to 3, the other end of the pressure equalizing path communicates with the pressure equalizing pipe 82 connected to the front side (lower side in FIG. 2) of the valve housing upper wall 34 in FIG. Has been done.

As shown in FIGS. 2 and 3, the pressure equalizing pipe 82 is connected to the outlet side pipe 120 of the evaporator 116 via the pressure equalizing path 84.

On the other hand, the superheat degree setting portion 88 is attached to the mounting hole 86 formed on the lower side of the valve housing lower wall 40 of the valve housing 28.

That is, the superheat degree setting unit 88 includes the adjustment spindle 90, and the male screw 92a formed on the outer circumference of the base end portion 92 of the adjustment spindle 90 and the female screw 92a formed on the inner circumference of the valve housing lower wall 40. The adjustment spindle 90 is configured to be movable in the axial direction by screwing the screw 40a.

Further, as shown in FIG. 1, an adjustment spring accommodating recess 91 is formed in the central portion above the adjustment spindle 90. On the other hand, a contact portion 50a (in the case of this embodiment, a caulking portion) is formed so as to project from the lower end of the valve member 50 of the valve body member 44.

A dish-shaped retainer 94 having a projecting portion projecting upward so as to abut the contact portion 50a at the lower end of the valve member 50 is in a compressed state between the adjusting spindle 90 and the adjusting spring accommodating recess 91. It is intervened by the adjusting spring 96 of.

On the other hand, an O-ring member 98 constituting a seal member is interposed at the upper end of the adjustment spindle 90. The outlet side valve chamber 38 and the outside of the mounting hole 86 are hermetically held via the O-ring member 98.

With this configuration, the valve member 50 of the valve body member 44 is urged to close (close) the valve port 30 (upward in FIG. 1) by the spring force of the adjusting spring 96. That is, the shoulder surface 52 of the valve member 50 and the valve seat 32 formed around the valve port 30 are in contact with each other so that the valve is closed.

Then, the diaphragm 68 is configured to be urged upward via the needle portion 74 formed at the upper tip of the valve shaft member main body 46 and the contact member 76 fixed below the diaphragm 68. ing.

Then, by turning the adjusting spindle 90 and moving the adjusting spindle 90 up and down in the axial direction, the spring force of the adjusting spring 96 is adjusted, and the urging force of the valve body member 44 on the valve member 50 is adjusted. It is configured as follows.

On the other hand, a retaining ring member 21 for preventing the adjusting spindle 90 from falling off is attached to the mounting hole 86.

A ring-shaped recess 86a is formed around the opening at the lower end of the mounting hole 86, and a female screw 86b is formed around the inside of the mounting hole 86 on the upper side in the axial direction.

For example, a ring-shaped sealing member 22 made of polytetrafluoroethylene (PTFE) is arranged in the recess 86a, and a lid member 24 has a male screw 24a in the lower end of the mounting hole 86. , It is attached by screwing it into the female screw 86b of the attachment hole 86.

As a result, by screwing the lid member 24, the sealing member 22 is slightly crushed and plastically deformed, fixed in the recess 86a, and is configured to maintain airtightness.

In the temperature expansion valve 10 of the present invention configured as described above, as shown in FIG. 3, the pressure equalizing chamber 72 formed on the lower side of the diaphragm device 26 with the diaphragm 68 interposed therebetween is the pressure equalizing pipe 82. It is connected to the outlet side pipe 120 of the evaporator 116 via the pressure equalizing path 84.

Therefore, the evaporation pressure of the outlet side pipe 120 of the evaporator 116 is introduced into the pressure equalizing chamber 72 formed under the diaphragm device 26.

On the other hand, the pressure receiving chamber 70 formed on the upper side of the diaphragm 68 of the diaphragm device 26 is connected to the temperature sensing cylinder 122 via the capillary tube 124.

Therefore, the internal pressure of the pressure receiving chamber 70 is a temperature sensitive pressure that changes according to the sensed temperature on the outlet side pipe 120 side of the evaporator 116, which is sensed by the temperature sensitive cylinder 122.

The diaphragm 68 of the diaphragm device 26 has a shaft according to the pressure difference (differential pressure) between the temperature-sensitive pressure in the pressure receiving chamber 70 and the evaporation pressure of the outlet side pipe 120 of the evaporator 116 in the pressure equalizing chamber 72. It will be deformed up and down in the direction.

The axial deformation of the diaphragm 68 is via a contact member 76 fixed below the diaphragm 68, and a needle portion 74 formed at the upper tip of the valve shaft member main body 46 of the valve body member 44. Therefore, it is configured to be transmitted to the valve shaft member main body 46, the valve rod member 48, and the valve member 50.

As a result, the shoulder surface 52 of the valve member 50 and the valve seat 32 formed around the valve port 30 are separated from each other to control the opening degree (throttle).

That is, the temperature expansion valve 10 acts so that the valve member 50 opens (opens) the valve port 30 when the sensed temperature of the outlet side pipe 120 of the evaporator 116 becomes high.

On the contrary, when the sensed temperature of the outlet side pipe 120 of the evaporator 116 becomes low, the valve member 50 is configured to act to close (close) the valve port 30.

Further, when the evaporation pressure in the evaporator 116 becomes low, the valve member 50 acts to open (open) the valve port 30.

On the contrary, when the evaporation pressure in the evaporator 116 becomes high, the valve member 50 is configured to act to close (close) the valve port 30.

As a result, the diaphragm 68 is axially deformed according to the differential pressure between the temperature-sensitive pressure from the temperature-sensitive cylinder 122 and the evaporation pressure of the evaporator 116, so that the valve body member 44 connected to the diaphragm 68 is formed. The valve member 50 controls the opening degree of the valve port 30 by moving in the axial direction.

Then, the opening degree at which the refrigerant flows from the outlet side pipe 108 of the condenser 106 to the inlet side pipe 118 of the evaporator 116 via the inlet side port 36, the valve port 30, and the outlet side port 42 is controlled, and the refrigeration cycle ( In the case of this embodiment, for example, the degree of superheat control of the refrigerant circulation circuit 101) of the air conditioner is configured.

By the way, the temperature expansion valve 10 of the present invention configured as described above is configured so that noise can be reduced due to the fragmentation of bubbles contained in the refrigerant even after long-term use for many years.

Further, since a solid valve body member 44 that is not porous is present on the surface of the inlet side port 36 of the foaming member 500 opposite to the side facing the opening 36a, the foaming member 500 penetrates the foaming member 500. It is configured so that there is nothing to do.
Therefore, since the refrigerant does not penetrate the fine foaming member, foreign matter is unlikely to accumulate on the fine foaming member, and even if foreign matter accumulates and the fine foaming member is clogged, the flow path of the refrigerant can be blocked. Absent.
Moreover, it is configured so that pressure loss does not occur and the flow rate control characteristics are not affected.

That is, as shown in FIGS. 1, 4, and 5, fine bubbles contained in the refrigerant introduced from the inlet side port are finely divided in the facing portion of the valve body member 44 facing the opening 36a of the inlet side port 36. It is configured to include a fine foaming member 500 for the purpose.

Specifically, as shown in the enlarged views of FIGS. 4 to 5, a substantially cylindrical fine foaming member 500 is provided on the facing portion of the valve body member 44 facing the opening 36a of the inlet side port 36. ing.

Further, in the temperature expansion valve 10 of the present invention, the fine foaming member 500 is provided in close contact with the valve body member 44, which is a member through which the fluid refrigerant cannot pass.

With this configuration, the fine foaming member 500 is provided in close contact with the valve body member 44, which is a member through which the fluid refrigerant cannot pass, so that the refrigerant does not penetrate the fine foaming member 500. It is configured so that foreign matter does not easily accumulate on the fine foaming member 500, and even if foreign matter accumulates and the fine foaming member 500 is clogged, the flow path of the refrigerant is not blocked.

Further, in the temperature expansion valve 10 of the present invention, the fine foaming member 500 is arranged at a position where the fluid flowing from the inlet side port 36 closes a part or all of the flow path toward the valve port 30. Absent.

With this configuration, the fine foaming member 500 is not arranged at a position where the fluid flowing from the inlet side port 36 blocks a part or all of the flow path toward the valve port 30. Even if foreign matter is accumulated and the fine foaming member 500 is clogged, the fine foaming member 500 does not block the flow path of the refrigerant.

Further, in the temperature expansion valve 10 of the present invention, as shown in FIG. 4, the fine foaming member 500 valves the opening 36a of the inlet side port 36 at any position from the valve opening to the valve closing. It is arranged so that at least a part of the body member 44 is projected at the projected position projected toward the valve body member 44 in a direction orthogonal to the axial direction of the body member 44.

That is, as shown in the partially enlarged view of FIG. 4, in the axial cross section of the valve body member 44, the upper end portion and the lower end portion of the opening 36a of the inlet side port 36 are directed toward the valve body member 44, respectively. In the range sandwiched between the projected lines P and P, the fine foaming member 500 is present at least in part.

Further, as shown in the partially enlarged view of FIG. 5, in the horizontal cross section of the valve body member 44, the left and right widthwise ends of the opening 36a of the inlet side port 36 are respectively in the direction of the valve body member 44. There is even a part of the fine foaming member 500 within the range sandwiched by the projection lines Q and Q projected toward.

With this configuration, the fine foaming member 500 makes the opening 36a of the inlet side port 36 orthogonal to the axial direction of the valve body member 44 at any position from the valve opening to the valve closing. Since it is arranged so that at least a part of it is located at the projected position projected toward the valve body member 44, the bubbles contained in the refrigerant are subdivided at any position from the valve opening to the valve closing. It is possible to reduce noise.

Further, it is difficult for foreign matter to accumulate on the fine foaming member 500, and even if foreign matter accumulates and the fine foaming member is clogged, the flow path of the refrigerant is not blocked.
Moreover, it is possible to provide the temperature expansion valve 10 which does not cause pressure loss and does not affect the flow rate control characteristics.

Further, in the temperature expansion valve 10 of the present invention, the fine foaming member 500 makes the opening 36a of the inlet side port 36 orthogonal to the axial direction of the valve body member 44 at any position from the valve opening to the valve closing. The projection range when projected toward the fine foaming member 500 in the direction in which the foam is formed may be arranged so as to be entirely located on the fine foaming member 500. ..

With this configuration, the foaming member 500 makes the opening 36a of the inlet side port 36 orthogonal to the axial direction of the valve body member 44 at any position from the valve opening to the valve closing. Since the projection range when projected toward the fine foaming member 500 is arranged so as to be located on the fine foaming member 500, the bubbles contained in the refrigerant are surely subdivided and noise is generated. Reduction is improved.

Further, foreign matter is unlikely to be deposited on the fine foaming member 500, and even if foreign matter is deposited and the fine foaming member 500 is clogged, the flow path of the refrigerant is not blocked.
Moreover, it is possible to provide the temperature expansion valve 10 which does not cause pressure loss and does not affect the flow rate control characteristics.

Further, as shown in the enlarged views of FIGS. 4 to 5, in the temperature expansion valve 10 of this embodiment, the foaming member 500 is the valve rod member 48 of the valve body member 44 facing the inlet side port 36. It is provided on the outer circumference.

Further, the fine foaming member 500 is interposed between the small diameter portion 48a of the valve rod member 48 and the valve member 50.

That is, in the temperature expansion valve 10 of this embodiment, as shown in the enlarged view of FIG. 4, the foaming member 500 is a valve member by the attachment portion 51 of the tip 48b on the valve member 50 side of the valve rod member 48. It is fixed together with 50.

Specifically, in the temperature expansion valve 10 of this embodiment, the central opening of the substantially cylindrical fine foaming member 500 is inserted into the small diameter portion 48a of the valve rod member 48.

Then, by projecting the tip 48b of the valve rod member 48 on the valve member 50 side into the central opening 50b of the separate valve member 50, the attachment portion 51 is formed by caulking to form fine bubbles. The member 500 is fixed (pinched and fixed) together with the valve member 50 by the mounting portion 51.

In this case, the mounting portion 51 is not limited to caulking, and for example, a known fixing method such as a fastening member such as a nut or a screw, or welding can be adopted.

As a result, the bubbles contained in the refrigerant introduced from the inlet side port 36 surely come into contact with the fine foaming member 500, and the bubbles contained in the refrigerant are surely subdivided to reduce noise. improves.

Further, foreign matter is unlikely to be deposited on the fine foaming member 500, and even if foreign matter is deposited and the fine foaming member 500 is clogged, the flow path of the refrigerant is not blocked.
Moreover, it is possible to provide the temperature expansion valve 10 which does not cause pressure loss and does not affect the flow rate control characteristics.

The fine foaming member 500 is not particularly limited, but for example, a porous sintered filter, a demister filter, a foaming member, a laminated flat plate, a laminated curved plate, or two layers. It is possible to make appropriate changes such as combining two or more of these, such as a coil spring and two layers of punching metal.

Further, in the temperature expansion valve 10 of the present invention, as shown in FIGS. 4 to 5, the size of the projected portion in which the opening 36 of the inlet side port 36 of the foaming member 500 is projected in the direction of the valve body member 44. It is desirable that the H1 is provided so as to have a size H2 or more of the opening projection portion obtained by projecting the opening 36a of the inlet side port 36 in the direction of the valve body member 44.

With this configuration, the size of the projected portion of the opening 36 of the inlet side port 36 of the fine foaming member 500 projected in the direction of the valve body member 44 makes the opening 36a of the inlet side port 36 the valve body. Since the size is larger than the size of the aperture projection portion projected in the direction of the member 44, the bubbles contained in the refrigerant are surely subdivided, and the noise reduction is improved.

Further, foreign matter is unlikely to be deposited on the fine foaming member 500, and even if foreign matter is deposited and the fine foaming member 500 is clogged, the flow path of the refrigerant is not blocked.
Moreover, it is possible to provide the temperature expansion valve 10 which does not cause pressure loss and does not affect the flow rate control characteristics.

Specifically, in the temperature expansion valve 10 of the present invention, as shown in FIG. 4, the height H1 of the projected portion of the fine foaming member 500 is the height of the opening projected portion of the opening 36a of the inlet side port 36. For H2
It is desirable that the structure is such that H1 ≧ H2.

Therefore, since the microfoaming member 500 is present over the entire height H2 of the opening projection portion of the opening 36a of the inlet side port 36, the bubbles contained in the refrigerant are surely subdivided. Noise reduction is improved.

Further, foreign matter is unlikely to be deposited on the fine foaming member 500, and even if foreign matter is deposited and the fine foaming member 500 is clogged, the flow path of the refrigerant is not blocked.
Moreover, it is possible to provide the temperature expansion valve 10 which does not cause pressure loss and does not affect the flow rate control characteristics.

Further, in the temperature expansion valve 10 of the present invention, as shown in FIG. 5, the width W1 of the projected portion of the fine foaming member 500 in the horizontal cross-sectional view is the opening projection of the opening 36a of the inlet side port 36. With respect to the width W2 in the horizontal cross-sectional view of the part
It is desirable that the structure is such that W1 ≧ W2.

Therefore, since the fine foaming member 500 is present over the entire width W2 of the opening projection portion of the opening 36a of the inlet side port 36 in the horizontal cross-sectional view, the bubbles contained in the refrigerant can be subdivided. It is done reliably and noise reduction is improved.

Further, foreign matter is unlikely to be deposited on the fine foaming member 500, and even if foreign matter is deposited and the fine foaming member 500 is clogged, the flow path of the refrigerant is not blocked.
Moreover, it is possible to provide the temperature expansion valve 10 which does not cause pressure loss and does not affect the flow rate control characteristics.

Further, in the temperature expansion valve 10 of the present invention, the fine foaming member 500 has the height H1 of the projected portion of the fine foaming member 500 and the inlet side port 36 at any position from the valve opening to the valve closing. It is desirable that the height H2 of the opening projection portion of the opening 36a of the above overlaps with the height H2.

With this configuration, the fine foaming member 500 has the height H1 of the projected portion of the fine foaming member 500 and the opening of the inlet side port 36 at any position from the valve opening to the valve closing. Since the height H2 of the opening projection portion of 36a overlaps with each other, the fine foaming member 500 is present at any position from the valve opening to the valve closing, so that the bubbles contained in the refrigerant are contained. Subdivision is surely performed and noise reduction is improved.

Further, foreign matter is unlikely to be deposited on the fine foaming member 500, and even if foreign matter is deposited and the fine foaming member 500 is clogged, the flow path of the refrigerant is not blocked.
Moreover, it is possible to provide the temperature expansion valve 10 which does not cause pressure loss and does not affect the flow rate control characteristics.

In the temperature expansion valve 10 of the present invention configured as described above, as shown by the arrows in FIGS. 4 to 5, the inlet side is on the facing portion of the valve body member 44 facing the opening 36a of the inlet side port 36. A fine foaming member 500 for making air bubbles contained in the refrigerant introduced from the port 36 fine is provided.

Therefore, the air bubbles contained in the refrigerant introduced from the inlet side port 36 come into contact with the fine foaming member 500 provided in the facing portion of the valve body member 44 facing the opening 36a of the inlet side port 36. The bubbles will be subdivided.

Moreover, there is a solid valve body member 44 that is not porous (that is, does not allow the fluid refrigerant to pass through) on the side facing the opening 36a of the inlet side port 36 of the fine foaming member 500 and on the back surface side. Therefore, the foaming member 500 is guided to the side of the valve port 30 without penetrating the foaming member 500.

Therefore, it is possible to reduce noise due to the fragmentation of bubbles contained in the refrigerant even after long-term use for many years.

Further, since there are solid valve body members 44 that are not porous on the side facing the opening 36a of the inlet side port 36 of the foaming member 500 and the back surface side, the foaming member 500 penetrates the foaming member 500. Never.
Therefore, since the refrigerant does not penetrate the fine foaming member 500, foreign matter is unlikely to accumulate on the fine foaming member 500, and even if foreign matter accumulates and the fine foaming member is clogged, the flow path of the refrigerant is blocked. Never.
Moreover, it is possible to provide a temperature expansion valve that does not cause pressure loss and does not affect the flow rate control characteristics.

Further, since the foaming member 500 is arranged at a position facing the opening 36a of the inlet side port 36 at any position from the valve opening to the valve closing, the foaming member 500 is arranged at a position facing the opening 36a from the valve opening to the valve closing. At any position, it is possible to reduce noise by subdividing the bubbles contained in the refrigerant.

Further, the size of the projected portion obtained by projecting the opening 36 of the inlet side port 36 of the fine foaming member 500 in the direction of the valve body member 44 makes the opening 36a of the inlet side port 36 in the direction of the valve body member 44. Since it is larger than the size of the projected aperture projection portion, the bubbles contained in the refrigerant are surely subdivided, and the noise reduction is improved.

Further, foreign matter is unlikely to be deposited on the fine foaming member 500, and even if foreign matter is deposited and the fine foaming member 500 is clogged, the flow path of the refrigerant is not blocked.
Moreover, it is possible to provide the temperature expansion valve 10 which does not cause pressure loss and does not affect the flow rate control characteristics.

Further, since the fine foaming member 500 is provided on the outer periphery of the valve rod member 48 of the valve body member 44 facing the opening 36 of the inlet side port 36, the valve body member 44 rotates during the valve operation. Even so, the fine foaming member 500 always faces the inlet side port 36.

As a result, the bubbles contained in the refrigerant introduced from the inlet side port 36 surely come into contact with the fine foaming member 500, and the bubbles contained in the refrigerant are surely subdivided to reduce noise. improves.

Further, since the fine foaming member 500 is interposed between the small diameter portion 48a of the valve rod member 48 and the valve member 50, the fine foaming member 500 is stabilized and the opening of the inlet side port 36 is opened. It can be held at a position facing 36.

As a result, the bubbles contained in the refrigerant introduced from the inlet side port 36 surely come into contact with the fine foaming member 500, and the bubbles contained in the refrigerant are surely subdivided to reduce noise. improves.

Further, the fine foaming member is fixed together with the valve portion between the small diameter portion 48a of the valve rod member 48 and the valve member 50 by the attachment portion 51 at the tip of the valve rod member 48 on the valve member 50 side. ..

Therefore, for example, by caulking, fastening members such as nuts and screws, welding, etc., the fine foaming member 500 is stably placed between the small diameter portion 48a of the valve rod member 48 and the valve member 50, and the inlet side port. Can be held in a position facing the.

In the temperature expansion valve of the present invention, it is desirable that the fine foaming member 500 is provided on the entire outer circumference of the valve body member 44 facing the opening 36a of the inlet side port 36.

With this configuration, the fine foaming member 500 is provided on the entire outer circumference of the valve body member facing the opening 36a of the inlet side port 36, so that the valve body member 44 is in the middle of valve operation. Even if the foaming member rotates, the foaming member always faces the opening of the inlet side port.

As a result, the bubbles contained in the refrigerant introduced from the inlet side port 36 surely come into contact with the fine foaming member 500, and the bubbles contained in the refrigerant are surely subdivided to reduce noise. improves.

Further, foreign matter is unlikely to be deposited on the fine foaming member 500, and even if foreign matter is deposited and the fine foaming member 500 is clogged, the flow path of the refrigerant is not blocked.
Moreover, it is possible to provide the temperature expansion valve 10 which does not cause pressure loss and does not affect the flow rate control characteristics.

Further, a solid valve body member 44 that is not porous (that is, does not allow a fluid refrigerant to pass through) is formed on the surface of the fine foaming member 500 opposite to the side facing the opening 36a of the inlet side port 36. Since it exists, it will be guided to the valve port 30 side without penetrating the fine foaming member 500.

Therefore, it is possible to reduce noise due to the fragmentation of bubbles contained in the refrigerant even after long-term use for many years.

Further, since the solid valve body member 44, which is not porous, exists on the surface of the inlet side port 36 of the foaming member 500 opposite to the side facing the opening 36a, it penetrates the foaming member. Never.
Therefore, since the refrigerant does not penetrate the fine foaming member 44, foreign matter is unlikely to accumulate on the fine foaming member 500, and even if foreign matter accumulates and the fine foaming member is clogged, the flow path of the refrigerant is blocked. Never.
Moreover, it is possible to provide the temperature expansion valve 10 which does not cause pressure loss and does not affect the flow rate control characteristics.
(Example 2)

6 is a vertical sectional view of the temperature expansion valve 10 of another embodiment of the present invention, FIG. 7 is a partially enlarged sectional view of the temperature expansion valve 10 of the present invention, and FIG. 8 is an enlarged sectional view of the temperature expansion valve 10 of FIG. FIG. 8A is a schematic view illustrating a method of attaching and fixing the fine foaming member 500 of the temperature expansion valve 10, FIG. 8A is a front view, FIG. 8B is a side view, and FIG. 8C is a side view. 8 (A) is a cross-sectional view taken along the line BB, FIG. 9 is a schematic view showing a ring-shaped mounting member 53, FIG. 9 (A) is a front view, and FIG. 9 (B) is a side surface. 9 (C) is a top view, FIG. 8 (A) is a sectional view taken along line BB, and FIG. 10 is a schematic view showing another embodiment of the ring-shaped mounting member 53. 10 (A) is a front view, and FIG. 10 (B) is a side view.

The temperature expansion valve 10 of this embodiment has basically the same configuration as the temperature expansion valve 10 of the first embodiment shown in FIGS. 1 to 4, and the same constituent members are designated by the same reference number. The detailed description thereof will be omitted.

In the temperature expansion valve 10 of this embodiment, as shown in FIG. 6, unlike the temperature expansion valve 10 of the first embodiment of FIGS. 1 to 5, the valve body member 44 has a small diameter of the valve rod member 48. The portion 48a and the valve member 50 are integrated.

Then, as shown in FIGS. 7 to 9, the fine foaming member 500 has, for example, a plate shape or a plate shape having a curved cross section in advance, and the fine foaming member 500 is a valve rod member 48. It is wound and mounted between the small diameter portion 48a and the valve member 50.

In this way, the fine foaming member 500 that is wound and mounted between the small diameter portion 48a of the valve rod member 48 and the valve member 50 is formed by the leaf spring-shaped attachment member 53 that has a substantially ring shape. It is fixed between the small diameter portion 48a of the above and the valve member 50.

That is, the fine foaming member 500 is covered so as to cover the outer peripheral portion of the valve body member 44, and is fixed by the ring-shaped mounting member 53 from the outer peripheral side.

With this configuration, the fine foaming member 500 is covered so as to cover the outer peripheral portion of the valve body member 44, and is fixed by the ring-shaped mounting member 53 from the outer peripheral side, so that mounting is easy. The cost can be reduced, and the fine foaming member 500 can be stably held on the outer peripheral portion of the valve body member 44 at a position facing the opening 36a of the inlet side port 36.

As a result, the bubbles contained in the refrigerant introduced from the inlet side port 36 surely come into contact with the fine foaming member 500, and the bubbles contained in the refrigerant are surely subdivided to reduce noise. improves.

Further, it is difficult for foreign matter to accumulate on the fine foaming member 500, and even if foreign matter accumulates and the fine foaming member is clogged, the flow path of the refrigerant is not blocked.
Moreover, it is possible to provide the temperature expansion valve 10 which does not cause pressure loss and does not affect the flow rate control characteristics.

That is, as shown in FIGS. 8 to 9, the mounting member 53 is attached to the pair of upper and lower ring portions 53a, 53a, the axially connecting portion 53b that connects these ring portions 53a, 53a, and the ring portion 53a. It is composed of notches 53c formed respectively.

Then, the fine foaming member 500 mounted by being wound between the small diameter portion 48a of the valve rod member 48 and the valve member 50 via the notch portions 53c formed in the ring portion 53a (spreading out). It is configured so that it can be stopped, attached, and fixed.

As shown in FIG. 10, the mounting member 53 may be composed of a pair of upper and lower separate mounting members 53.

With this configuration, the fine foaming member 500 is fixed between the small diameter portion 48a of the valve rod member 48 and the valve member 50 by a ring-shaped mounting member 53, so that mounting is easy. The cost can be reduced, and the defoaming member 500 can be stably held between the small diameter portion 48a of the valve rod member 48 and the valve member 50 at a position facing the opening 36a of the inlet side port 36. ..

As a result, the bubbles contained in the refrigerant introduced from the inlet side port 36 surely come into contact with the fine foaming member 500, and the bubbles contained in the refrigerant are surely subdivided to reduce noise. improves.

Moreover, foreign matter contained in the refrigerant surely prevents clogging due to accumulation on the fine foaming member 500, does not block the flow path of the refrigerant, does not narrow, and does not cause pressure loss. , It is possible to provide an effective temperature expansion valve 10 that does not affect the flow rate control characteristics.
(Example 3)

FIG. 11 is a schematic view showing an axial cross section of the fine foaming member 500 showing another embodiment of the fine foaming member 500 of the temperature expansion valve 10 of another embodiment of the present invention.

In the temperature expansion valve 10 of this embodiment, as shown in FIGS. 11 (A) to 11 (C), the fine foaming member 500 has a thickness of guide for the refrigerant introduced from the inlet side port 36. It is configured to be different so as to be a surface 500a.

That is, in the temperature expansion valve 10 of the present invention, the outer peripheral surface of the fine foaming member 500 is formed of a tapered surface or a curved shape that is inclined with respect to the axial direction of the fine foaming member 500, and the inlet side port 36. It is characterized in that it is configured to be a guide surface 500a of the refrigerant introduced from.

With this configuration, the outer peripheral surface of the fine foaming member 500 is formed of a tapered surface or a curved shape that is inclined with respect to the axial direction of the fine foaming member 500, and is introduced from the inlet side port 36. Since it is configured to be the guide surface 500a of the refrigerant, the refrigerant is guided to the valve port 30 side along the guide surface 500a.

As a result, the bubbles contained in the refrigerant introduced from the inlet side port 36 surely come into contact with the fine foaming member 50, and the bubbles contained in the refrigerant are surely subdivided to reduce noise. improves.

Further, it is difficult for foreign matter to accumulate on the fine foaming member 500, and even if foreign matter accumulates and the fine foaming member is clogged, the flow path of the refrigerant is not blocked.
Moreover, it is possible to provide the temperature expansion valve 10 which does not cause pressure loss and does not affect the flow rate control characteristics.

That is, the fine foaming member 500 shown in FIG. 11A has a tapered shape in which the thickness gradually decreases toward the valve port 30 side.

Further, in the fine foaming member 500 of FIG. 11B, the thickness on the valve port 30 side is thick, and the taper shape gradually decreases toward the center in the height direction of the fine foaming member 500. It has become.

The fine foaming member 500 of FIG. 11C has a tapered shape in which the thickness on the valve port 30 side is thin and the thickness gradually increases toward the center of the fine foaming member 500 in the height direction. ing.

With this configuration, the fine foaming member 500 is configured so that its thickness is different so as to be the guide surface 500a of the refrigerant introduced from the inlet side port 36. Since the refrigerant is guided to the valve port 30 side along the 500a, it is possible to prevent foreign matter contained in the refrigerant from accumulating on the fine foaming member 500 and causing clogging, and block the flow path of the refrigerant. It is possible to provide a temperature expansion valve 10 that does not become narrow and does not cause pressure loss and does not affect the flow rate control characteristics.

Although the preferred embodiment of the present invention has been described above, the present invention is not limited to this, and is not limited to the temperature expansion valve 10 having the structure as in the above embodiment, and has other structures. Various changes can be made without departing from the object of the present invention, such as being applicable to the temperature expansion valve 10.

The present invention is used, for example, in a refrigerant circulation circuit of a refrigeration cycle system such as an air conditioner or a refrigerator, and automatically adjusts a valve opening in response to the temperature on the outlet side of an evaporator to automatically adjust the valve opening degree of the refrigerant circulation circuit of the refrigeration cycle system. It can be applied to a temperature expansion valve used for controlling the degree of superheat and a refrigeration cycle system using the temperature expansion valve.

More specifically, the pressure difference between the temperature-sensitive pressure from the temperature-sensitive cylinder attached to the outlet side piping side of the evaporator of the refrigerant circulation circuit of the refrigerating cycle system, for example, and the evaporation pressure of the evaporator. Correspondingly, the diaphragm is deformed in the axial direction, so that the valve body member connected to the diaphragm moves in the axial direction, and the valve portion controls the opening degree of the valve port. It can be applied to a refrigeration cycle system using a temperature expansion valve.

10 Temperature expansion valve 12 Inlet side piping (primary piping)
14 Outlet side piping (secondary piping)
21 Stop ring member 22 Sealing member 24 Lid member 24a Male screw 26 Diaphragm device 28 Valve housing 30 Valve port 31 Inlet side valve chamber 32 Valve seat 34 Valve housing upper wall 36 Inlet side port 36a Opening 38 Outlet side valve chamber 40 Valve Housing lower wall 40a Female screw 42 Outlet side port 44 Valve body member 46 Valve shaft member Main body 48 Valve rod member 48a Small diameter 48b Tip 50 Valve member 50a Abutment 50b Opening 51 Mounting 52 Shoulder surface 53 Member 53a Ring 53b Coupling part 53c Notch 54 Opening 58 Male screw 60 Lower lid member 60a Flange part 62 Mounting part 64 Female screw 66 Upper lid member 66a Flange part 68 Diaphragm 68a Flange part 70 Pressure receiving chamber 72 Pressure equalizing chamber 74 Needle part 74a Step part 76 Abutment member 76a Abutment hole 76b Extension 78 Holding member 80 Sealing member 82 Pressure equalizing piping 84 Pressure equalizing path 86 Mounting hole hole 86a Recess 86a Female screw 88 Female screw 88 Superheat setting part 90 Adjustment spindle 91 Adjustment spring accommodating recess 92 End 92a Male screw 94 Retainer 96 Adjusting spring 98 O-ring member 100 Temperature expansion valve 101 Coolant circulation circuit 102 Circulation piping 104 Compressor 106 Condenser 108 Outlet side piping (secondary piping)
110 Temperature expansion valve 112 Inlet side piping (primary piping)
114 Outlet side piping (secondary piping)
116 Evaporator 118 Inlet pipe 120 Outlet side pipe 122 Temperature sensitive tube 124 Capillary tube 126 Diaphragm device 128 Valve housing 130 Valve port 131 Inlet side valve chamber 132 Valve seat 134 Valve housing upper wall 136 Inlet side port 138 Outlet side valve chamber 140 valve Housing lower wall 140a Female screw 142 Outlet side port 144 Valve body member 146 Valve shaft member Main body 148 Valve rod member 150 Valve part 150a Abutment part 152 Shoulder surface 154 Opening part 158 Male screw 160 Lower lid member 160a Flange part 162 Mounting part 164 Female screw 166 Top lid member 166a Flange part 168 Diaphragm 168a Flange part 170 Pressure receiving chamber 172 Pressure equalizing chamber 174 Needle part 174a Step part 176 Contacting member 176a Contact hole part 176b Extension part 178 Holding member 180 Sealing member 182 Pressure equalizing pipe 184 Pressure equalizing path 186 Mounting hole 186a Recess 186b Female screw 188 Superheat setting part 190 Adjustment spindle 191 Adjustment spring storage recess 192 Base end 192a Male screw 194 Retainer 196 Adjustment spring 198 O-ring member 200 Stop ring member 202 Sealing member 204 Lid member 204a Male screw 300 Expansion valve 302 Valve body 304 Inlet port 306 Outlet port 308 Valve chamber 310 Valve hole 312 Valve member 314 Foaming member 316 Valve hole 500 Foaming member 500 Valve part 500a Guide surface 600 Strainers H1, H2 Height W1, W2 Width P, Q Projection line

Claims (10)

When the diaphragm of the diaphragm device is deformed in the axial direction of the valve body member, the valve body member connected to the diaphragm moves in the axial direction, and the valve portion integrated with the valve body member controls the opening degree of the valve port. hand,
It is configured to regulate the flow rate of refrigerant passing through the inlet side port, valve port, and outlet side port.
A temperature expansion valve characterized in that a foaming member for making bubbles contained in the refrigerant introduced from the inlet side port finer is provided on a portion of the valve body member facing the opening of the inlet side port. The temperature expansion valve according to claim 1, wherein the fine foaming member is provided in close contact with a valve body member which is a member through which a fluid refrigerant cannot pass. Any of claims 1 and 2, wherein the defoaming member is not arranged at a position where the fluid flowing in from the inlet side port blocks a part or all of the flow path toward the valve port. The temperature expansion valve described in Crab. The finely foamed member projects the opening of the inlet side port toward the valve body member in a direction orthogonal to the axial direction of the valve body member at any position from when the valve is opened to when the valve is closed. The temperature expansion valve according to any one of claims 1 to 3, wherein at least a part thereof is arranged so as to be located. When the foaming member projects the opening of the inlet side port toward the foaming member in a direction orthogonal to the axial direction of the valve body member at any position from the valve opening to the valve closing. The temperature expansion valve according to claim 4, wherein the projection range of the above is entirely located on the fine foaming member. The temperature expansion valve according to any one of claims 1 to 5, wherein the fine foaming member is provided on the entire outer circumference of the valve body member facing the opening of the inlet side port. The fine foaming member inserts the valve body member into the central opening of the cylindrical fine foaming member and the central opening of the valve member, and holds and fixes the fine foaming member between the valve body member and the valve member. The temperature expansion valve according to any one of claims 1 to 5, wherein the temperature expansion valve is characterized. The temperature according to any one of claims 1 to 7, wherein the fine foaming member is covered so as to cover the outer peripheral portion of the valve body member and is fixed by a ring-shaped mounting member from the outer peripheral side. Expansion valve. The outer peripheral surface of the foaming member is formed of a tapered surface or a curved shape that is inclined with respect to the axial direction of the foaming member, and is configured to be a guide surface for the refrigerant introduced from the inlet side port. The temperature expansion valve according to any one of claims 1 to 8, wherein the temperature expansion valve is characterized. A refrigeration cycle system according to any one of claims 1 to 9, wherein the temperature expansion valve is connected to a pipe between a condenser and an evaporator of a refrigerant circulation circuit of the refrigeration cycle system.

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