JP2008309345A - Expansion valve having integrated structure with refrigerant flow divider and refrigeration unit using the same - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide an expansion valve having an integrated structure with a refrigerant flow divider reducing discontinuous refrigerant flow sound in the expansion valve and providing a favorable refrigerant flow dividing characteristics in either of a normal-directional refrigerant flow (a refrigerant flow from a part executing an expansion valve function to a part executing a refrigerant flow dividing function) or an inverse refrigerant flow inverse to the normal-directional flow and a refrigeration unit using the expansion valve. <P>SOLUTION: This expansion valve having the integrated structure with the refrigerant flow divider is provided with a first throttle part 10 executing a throttling operation, an approximately cylindrical refrigerant flow dividing chamber 6 for dividing the refrigerant passing through the first throttle part 10 to a flow dividing pipe 12, and a plurality of flow dividing pipes 12 connected to the refrigerant flow dividing chamber 6. The plurality of flow dividing pipes 12 are connected to open in a substantially fixed tangential direction respectively to the side wall of the approximately cylindrical refrigerant flow dividing chamber 6. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to an expansion valve having a refrigerant flow divider integrated structure in which a refrigerant flow divider and an expansion valve are integrated, and a refrigeration apparatus using the expansion valve.

  In a refrigeration apparatus such as an air conditioner, a refrigerator, or a manufacturing process cooling apparatus, an evaporator may be configured with a plurality of passes (a refrigerant flow passage in a heat exchanger). The refrigerant circuit in this case is configured as shown in FIG. 16, for example. The refrigerant pressurized by the compressor 101 is condensed by the condenser (in this case, the outdoor heat exchanger) 102 and sent to the expansion valve 104 through the liquid receiver 103. The refrigerant depressurized by the expansion valve 104 is sent to the refrigerant distributor 106 via the refrigerant pipe 105, is divided by the refrigerant distributor 106, and is sent to a plurality of paths of the evaporator (in this case, the indoor heat exchanger) 107. It is done. The low-pressure refrigerant sent to the evaporator 107 is evaporated by the evaporator 107 and is returned to the compressor 101 through the accumulator 108. When the evaporator 107 is configured in a plurality of paths as described above, the refrigerant decompressed by the expansion valve 104 is evenly divided into the plurality of paths of the evaporator 107 through the refrigerant pipe 105 on the downstream side of the expansion valve 104. A refrigerant flow divider 106 is attached for the purpose. The refrigerant distributor 106 is a container having a predetermined volume of refrigerant distribution space (hereinafter referred to as a refrigerant distribution chamber), as described in Patent Document 1, for example. A diversion pipe mounting hole for connecting each path of the evaporator 107 is formed. Therefore, the refrigerant flowing into the refrigerant flow divider 106 is a low-pressure gas-liquid two-phase flow refrigerant because the refrigerant is decompressed by the expansion valve 104 in a predetermined flow direction. And this gas-liquid two-phase flow refrigerant tends to become a plug flow or slag flow in which large bubbles exist while flowing through the refrigerant pipe 105 connecting the expansion valve 104 and the refrigerant flow divider 106. In addition, when the refrigerant flowing into the refrigerant flow divider 106 becomes a plug flow or a slag flow, bubbles may not flow uniformly into each branch pipe due to the influence of gravity or the like, and it is difficult to perform a uniform flow. There was a problem.

  Therefore, in recent refrigerant flow dividers, for example, as described in Patent Document 1, a throttle part (path reducing member in Patent Document 1) having a constant opening is arranged upstream of the branch pipe mounting hole. Proposals have been made to achieve a uniform diversion by putting the refrigerant on the downstream side of the section into a sprayed state.

On the other hand, apart from the above-described problem of the refrigerant flow divider, discontinuous refrigerant flow noise is a problem in the expansion valve as follows.
The expansion valve is generally based on the fact that the refrigerant flowing in is a high-pressure liquid refrigerant. However, air bubbles may be contained in the refrigerant upstream of the expansion valve, that is, on the outlet of the receiver (or the outlet of the condenser if there is no receiver) due to fluctuations in the operating conditions of the refrigeration system. The high-pressure liquid refrigerant containing bubbles may be heated from the outside of the pipe while flowing through the refrigerant pipe leading to the expansion valve, and the bubbles may increase, or the bubbles in the refrigerant flow may merge. As a result, large bubbles may grow into a plug flow or a slag flow in which intermittently present, and flow into the expansion valve. Further, when the plug flow or the slag flow is sent to the expansion valve, a discontinuous state in which liquid refrigerant and gas refrigerant alternately flow to the throttle portion, and speed fluctuation and pressure fluctuation occur in the refrigerant flow of the expansion valve. For this reason, in the throttle part, the gas-liquid alternately flows to make a squealing sound, or the spraying speed and pressure of the mist refrigerant flowing out from the throttle part to the refrigerant piping system fluctuate and the expansion valve outlet side There was a problem that a discontinuous refrigerant flow sound was generated, such as making a sound of “shashasha”. Furthermore, there has been a problem in that devices around the expansion valve such as the expansion valve and connection piping vibrate due to speed fluctuations and pressure fluctuations in the refrigerant pipe, and vibration noise is generated around the expansion valve. Note that such discontinuous refrigerant flow noise and vibration noise are collectively referred to as discontinuous refrigerant flow noise in the expansion valve in the following description.

  As described above, the refrigerant flow upstream of the expansion valve grows into a plug flow or slag flow due to fluctuations in the operating conditions of the refrigeration system. There is such a possibility in any heating operation. In addition, the discontinuous refrigerant flow noise in the expansion valve caused by the plug flow and slag flow flowing into the inlet of the expansion valve is a heating that is used only during the heating operation in both the cooling and heating operations of the expansion valve that is also used for cooling and heating. The expansion valve for cooling may be generated during the heating operation, and the cooling expansion valve used only during the cooling operation may be generated during the cooling operation.

  For example, in the case of a separate type air conditioner, a heating expansion valve is installed in the outdoor unit at the inlet side of the outdoor heat exchanger during heating, and the indoor unit is used for the indoor heat exchanger during cooling. A cooling expansion valve is often installed on the inlet side. In this case, the above-described problem occurs during the heating operation for the heating expansion valve installed in the outdoor unit, and it goes without saying that the above-described problem occurs for the cooling expansion valve installed in the indoor unit. Furthermore, the cooling expansion valve installed in the indoor unit may be used to adjust the degree of supercooling at the outlet of the indoor heat exchanger during heating. In this case, since the cooling expansion valve is installed in the immediate vicinity of the indoor heat exchanger, the plug flow and the slag flow hardly flow into the expansion valve after the transition period of the heating operation starts. However, since the refrigerant is stored in the gas-liquid two-phase state during the heating operation stop period in the indoor heat exchanger, the plug flow and the slag flow are the The refrigerant may flow into the inlet and generate the same refrigerant flow noise as described above.

As a method for reducing such discontinuous refrigerant flow noise in the expansion valve, conventionally, means for alleviating the speed fluctuation and pressure fluctuation of the refrigerant flow in the expansion valve has been provided in the expansion valve. For example, in patent document 2, the other throttle part which decompresses a refrigerant | coolant flow was provided in the upstream of the throttle part which can be closed. Moreover, in patent document 3, the disturbance generation | occurrence | production part which produces disturbance in a refrigerant | coolant flow was provided in the upstream of the throttle part which can be closed. Moreover, in patent document 4, the other throttle part which decompresses a refrigerant | coolant flow was provided in the downstream of the throttle part which can be closed.
JP 2002-188869 A JP 2005-69644 A JP 2005-351605 A JP 2005-226846 A

  As described above, in the conventional refrigerant flow divider, the throttle portion is provided on the upstream side of the flow dividing tube mounting hole as a means for evenly dividing the flow. However, the throttling portion is a basic component of the expansion valve installed on the upstream side of the refrigerant flow divider, and thus it has been wasteful to arrange the same component redundantly in adjacent devices. On the other hand, in the conventional expansion valve, in order to reduce the discontinuous refrigerant flow noise in the expansion valve, the means for reducing the speed fluctuation and pressure fluctuation of the refrigerant flow has been provided as described above. However, providing such means as a component of the expansion valve alone has a problem that the expansion valve becomes large and costs increase.

  The present invention solves such a problem in the prior art, and integrates the throttle in the expansion valve and the throttle in the refrigerant flow divider, and integrates the refrigerant circuit from the expansion valve to the refrigerant flow divider, It is an object of the present invention to provide an expansion valve having a simplified refrigerant distributor integrated structure. Further, in the expansion valve with such a refrigerant flow divider integrated structure, not only the refrigerant flow noise during the flow of the refrigerant from the portion that performs the expansion valve function to the portion that performs the refrigerant diversion function is reduced, but also the flow direction. An object of the present invention is to suppress the generation of a similar refrigerant flow noise even in the case of a refrigerant flow in the opposite direction. Another object of the present invention is to provide a refrigeration apparatus using an expansion valve having such a refrigerant flow divider integrated structure.

  In order to solve the above-described problem, an expansion valve having a refrigerant flow distributor integrated structure according to the present invention includes a first throttle portion that is formed between the first valve body and the first valve hole and performs a throttle action. A substantially cylindrical refrigerant branch chamber for branching the refrigerant after passing through the first restrictor to the branch pipe; and a plurality of branch pipes connected to the refrigerant branch chamber, wherein the plurality of branch pipes are substantially cylindrical. It is connected to the side wall of the refrigerant branch chamber so as to open in a substantially constant tangential direction.

  According to the expansion valve with the refrigerant flow divider integrated structure configured as described above, by integrating the expansion valve and the refrigerant flow divider, the circuit portion from the expansion valve to the refrigerant flow divider can be simplified and occupied. The space can be reduced and the cost can be reduced.

  Further, according to the expansion valve having the refrigerant flow divider integrated structure configured as described above, in the refrigerant flow (forward direction refrigerant flow) from the portion performing the expansion valve function to the portion performing the refrigerant diversion function, the first throttle portion The refrigerant in the sprayed state after passing is directly led to the refrigerant branch chamber without passing through the refrigerant pipe. Therefore, the gas-liquid two-phase flow does not develop into a plug flow or a slag flow after passing through the throttle portion, and the flow dividing characteristics are improved. Further, the spray energy of the refrigerant flow flowing out from the first throttle portion is diffused by the refrigerant branch chamber acting as an expansion space portion, so that the refrigerant flow upstream of the first throttle portion is plug flow or slag. When it becomes a flow, the pressure fluctuation of the refrigerant flow in the expansion valve can be reduced. As a result, discontinuous refrigerant flow noise in the expansion valve can be reduced in the forward direction refrigerant flow. In this specification, the refrigerant flow from the part that performs the expansion valve function to the part that performs the refrigerant diversion function is referred to as “forward refrigerant flow”, and the refrigerant flow in the direction opposite to the forward direction is referred to as “reverse direction”. It shall be referred to as “refrigerant flow”.

  Further, according to the expansion valve having the refrigerant flow divider integrated structure configured as described above, when the refrigerant flows from the plurality of flow dividing pipes into the refrigerant flow dividing chamber and merges in the reverse refrigerant flow, the cylindrical refrigerant flow dividing flow Since it flows along the inner peripheral surface of the room, a swirling flow is generated. Thereby, the refrigerant flowing in from each branch pipe is efficiently disturbed by the merge. As a result, even if the plug flow or slag flow flows into the expansion valve, the bubbles in the refrigerant flow are subdivided before passing through the first throttle part, and the discontinuous refrigerant flow noise in the expansion valve is generated in the reverse refrigerant flow. Effectively reduced.

  Further, in the expansion valve having the refrigerant flow divider integrated structure configured as described above, an end portion of the flow dividing pipe on the refrigerant flow dividing chamber side is cut in an oblique direction so as to be substantially along the inner peripheral surface of the refrigerant flow dividing chamber. It is preferable. Here, “cut in an oblique direction” means that it is cut in a straight line so as to substantially follow the inner peripheral surface of the refrigerant distribution chamber, or substantially along the inner peripheral surface of the refrigerant distribution chamber. A case where it is cut obliquely in an arc shape. If comprised in this way, it will be avoided that the front-end | tip part of a shunt flow becomes the obstruction | occlusion of the said swirl | vortex flow generation, Therefore The refrigerant | coolant which flows in from each shunt tube can be merged efficiently and can be disturbed. Thereby, the discontinuous refrigerant flow noise in the expansion valve can be further reduced in the reverse refrigerant flow.

  In the expansion valve having the above-described configuration, the first valve body is housed on one side of the first throttle part, and a valve chamber having an inlet port for connecting a liquid pipe is formed, and the other of the first throttle part is formed. It can be configured such that a refrigerant distribution chamber is formed on the side. With this configuration, the refrigerant distribution chamber and the like can be designed with the configuration of the valve chamber in the conventional expansion valve, so that restrictions on the design of the refrigerant distribution chamber are reduced.

  In the expansion valve having such a configuration, it is preferable that the flow dividing pipe is connected to a position close to a wall body forming the first throttle portion in the side wall of the refrigerant flow dividing chamber. If comprised in this way, in the forward direction refrigerant | coolant flow, the refrigerant | coolant flow ejected from the 1st aperture | diaphragm | squeeze part collides with the wall body which opposes the 1st aperture | diaphragm | squeeze part, reverses a flow direction, and is connected to a refrigerant | coolant distribution pipe after that A detour circuit that flows into is formed. This prevents the refrigerant flow ejected from the first throttle part from flowing directly into the branch pipe.

  Furthermore, in this case, it is preferable that a cylindrical member for urging the refrigerant to be swung when the refrigerant is introduced from the diverter pipe is preferably provided on the refrigerant diversion chamber side of the first throttle portion. In this way, in the reverse refrigerant flow, the generation of the swirling flow by the refrigerant flow flowing from each branch pipe into the refrigerant branch chamber is promoted, so that the disturbing action of the refrigerant flow by the swirling flow is performed more efficiently. Is called. Therefore, the discontinuous refrigerant flow noise in the expansion valve can be further reduced in the reverse refrigerant flow. Further, in the forward direction refrigerant flow, the refrigerant flow ejected from the first throttle portion is ejected toward the wall body facing the first throttle portion while being guided by the cylindrical member, and thus from the first throttle portion. It is more reliably prevented that the jetted refrigerant flow directly flows into the branch pipe. If the jet ejected from the first constriction collides directly with the minute area part that forms the entrance of the shunt pipe, the influence of the component that collides and bounces on the peripheral surface without flowing into the shunt pipe, or the shunt pipe Even the components that flow into the turbulence are disturbed by the influence of the separation flow immediately after the flow, and a large unstable phenomenon occurs. However, in the present invention, as described above, the jet flow from the first throttle portion is bypassed so as to reach the inlet of the branch pipe, so that the above-described problem does not occur. Moreover, the influence of the intermittent fluctuation | variation which the jet flow ejected from the 1st throttle part has can also be reduced.

  The cylindrical member may have a length in the axial direction that forms a wall that faces the inlet of the flow dividing pipe, and may include a flange that protrudes in the outer peripheral direction at the tip. In this way, the swirling flow generated by the refrigerant flow flowing from the plurality of flow dividing pipes into the refrigerant distribution chamber is held by the flange at the tip of the cylindrical member, so that the disturbing action of the refrigerant flow due to the swirling flow is further improved. More efficient. Thereby, the discontinuous refrigerant flow noise in the expansion valve can be further reduced in the reverse refrigerant flow.

  In addition, the refrigerant branch chamber may be formed in an annular groove with the inner peripheral surface of the side wall in the axial direction connecting the branch pipe being recessed. In this way, in the reverse refrigerant flow, the swirling flow generated by the refrigerant flow flowing into the refrigerant branch chamber from the plurality of branch pipes is held by the annular groove, so that the refrigerant flow is disturbed by the swirling flow. It is performed even more efficiently. Thereby, the discontinuous refrigerant flow noise in the expansion valve can be further reduced in the reverse refrigerant flow.

  In addition, bubble fragmentation means may be disposed between the inlet port and the first throttle portion in the valve chamber. With this configuration, in the forward direction refrigerant flow, when the refrigerant flow on the upstream side of the first throttle portion becomes a plug flow or a slag flow, The bubbles are subdivided, the refrigerant flow to the first throttle portion is continued, and the speed fluctuation and pressure fluctuation of the refrigerant flow in the expansion valve are alleviated. Therefore, discontinuous refrigerant flow noise in the expansion valve is reduced. Further, in the positive direction refrigerant flow, the spray state downstream of the first throttle portion is stabilized, and the refrigerant diversion in the refrigerant diversion chamber is stabilized.

  Further, a porous permeable material layer may be disposed between the branch pipe and the first throttle part in the refrigerant branch chamber. With this configuration, the speed fluctuation and pressure fluctuation of the refrigerant flow ejected from the first throttling portion are alleviated in the forward direction refrigerant flow, so that discontinuous refrigerant flow noise in the expansion valve is reduced. Further, in the reverse refrigerant flow, the porous permeable material layer reduces the discontinuous refrigerant flow noise in the expansion valve by subdividing the bubbles in the refrigerant flowing into the first throttle part, and the first The filter function for one aperture part can be exhibited.

  Next, as described above, in the expansion valve of the refrigerant flow divider integrated structure including the first throttle portion, the refrigerant branch chamber, and the plurality of branch pipes, the refrigerant branch chamber is the first throttle portion of the first throttle portion. An inlet that is formed on one side of the first throttle part and is connected to the liquid pipe on the other side of the first throttle part as a valve chamber / refrigerant branch chamber also used as a valve chamber that houses one valve body You may comprise so that a port may be formed. If comprised in this way, the circuit part from an expansion valve to a refrigerant | coolant shunt will be further simplified.

  Moreover, it is preferable that the said branch pipe is connected to the position close | similar to the wall body which forms the 1st throttle part in the side wall of a valve chamber and refrigerant | coolant branch chamber. If comprised in this way, in the forward direction refrigerant | coolant flow, the refrigerant | coolant flow ejected from the 1st aperture | diaphragm | squeeze part will collide with the wall body which opposes a 1st aperture | diaphragm | squeeze part, reverse a flow direction, and after detouring, a refrigerant | coolant split flow Formed in a bypass circuit that flows into the tube. This prevents the refrigerant flow ejected from the first throttle part from flowing directly into the branch pipe.

  In addition, it is preferable that a cylindrical member is provided on the valve chamber / refrigerant distribution chamber side of the first throttle portion to promote the rotation of the refrigerant when the refrigerant is introduced from the distribution pipe. In this way, in the reverse refrigerant flow, the generation of the swirling flow by the refrigerant flow flowing from each branch pipe into the valve chamber / refrigerant branch chamber is promoted, so that the disturbing action of the refrigerant flow by the swirling flow is further enhanced. It is done efficiently. Therefore, the discontinuous refrigerant flow noise in the expansion valve can be further reduced in the reverse refrigerant flow. Further, in the forward direction refrigerant flow, the refrigerant flow ejected from the first constriction portion is ejected toward the wall body that is guided by the cylindrical member and faces the first constriction portion. It is more reliably prevented that the refrigerant flow ejected from the refrigerant flows directly into the branch pipe. If the jet ejected from the first constriction collides directly with the minute area part that forms the entrance of the shunt pipe, the influence of the component that collides and bounces on the peripheral surface without flowing into the shunt pipe, or the shunt pipe Even the components that flow into the turbulence are disturbed by the influence of the separation flow immediately after the flow, and a large unstable phenomenon occurs. However, in the present invention, as described above, the jet flow from the first throttle portion is bypassed so as to reach the inlet of the branch pipe, so that the above-described problem does not occur. Moreover, the influence of the intermittent fluctuation | variation which the jet flow ejected from the 1st throttle part has can also be reduced.

  The cylindrical member may have a length in the axial direction that forms a wall that faces the inlet of the flow dividing pipe, and may include a flange that protrudes in the outer peripheral direction at the tip. In this way, the swirling flow generated by the refrigerant flow flowing from each branch pipe into the refrigerant branch chamber is held by the flange at the tip of the cylindrical member, so that the refrigerant flow is further disturbed by the swirling flow. It is done efficiently. Thereby, the discontinuous refrigerant flow noise in the expansion valve can be further reduced in the reverse refrigerant flow.

  The valve chamber / refrigerant branch chamber may be formed in an annular groove with the inner peripheral surface of the side wall in the axial direction connecting the branch pipe recessed. In this way, the swirl flow generated by the refrigerant flow flowing from each branch pipe into the refrigerant branch chamber is held by the annular groove, so that the disturbing action of the refrigerant flow by the swirl flow is performed more efficiently. Thereby, the discontinuous refrigerant flow noise in the expansion valve can be further reduced in the reverse refrigerant flow.

  In addition, a separate chamber is formed on the other side of the first throttle portion, the inlet port is formed in the separate chamber, and a bubble segmentation means is disposed between the inlet port and the first throttle portion in the separate chamber. You may do it. With this configuration, when the refrigerant flow on the upstream side of the first throttle portion becomes a plug flow or a slag flow in the forward direction refrigerant flow, The bubbles are subdivided, the refrigerant flow to the first throttle portion is continued, and the speed fluctuation and pressure fluctuation of the refrigerant flow in the expansion valve are alleviated. Therefore, discontinuous refrigerant flow noise in the expansion valve is reduced. Further, the spray state downstream of the first throttle portion is stabilized, and the refrigerant diversion in the refrigerant diversion chamber is stabilized.

  In addition, a porous permeable material layer may be disposed between the branch pipe and the first throttle portion in the valve chamber / refrigerant branch chamber. With this configuration, the speed fluctuation and pressure fluctuation of the refrigerant flow ejected from the first throttling portion are alleviated in the forward direction refrigerant flow, so that discontinuous refrigerant flow noise in the expansion valve is reduced. Further, in the reverse refrigerant flow, the porous permeable material layer reduces the discontinuous refrigerant flow noise in the expansion valve by subdividing the bubbles in the refrigerant flowing into the first throttle part, and the first The filter function for one aperture part can be exhibited.

  Moreover, the bubble fragmentation means installed in the valve chamber or the separate chamber may form a second throttle portion. With this configuration, in the forward direction refrigerant flow, when the refrigerant flow upstream of the first throttle portion becomes a plug flow or a slag flow, the bubbles are subdivided in the second throttle portion, and the flow toward the first throttle portion. The refrigerant flow is made continuous, and the speed fluctuation and pressure fluctuation of the refrigerant flow in the expansion valve are alleviated. Moreover, it becomes the structure of the multistage aperture | diaphragm | restriction with a 2nd aperture | diaphragm | squeeze part and a 1st aperture_diaphragm | restriction part, and the ejection energy in a diaphragm | throttle part is disperse | distributed. As a result, the speed fluctuation and pressure fluctuation of the refrigerant flow in the expansion valve are further alleviated, and the discontinuous refrigerant flow noise in the expansion valve is reduced. In addition, the spray state downstream of the first throttle portion is stabilized, and the refrigerant diversion in the refrigerant diversion chamber or the valve chamber / refrigerant diversion chamber is stabilized.

  Further, the bubble subdividing means may be configured such that an enlarged space portion is provided between the second throttle portion and the first throttle portion. With this configuration, in the refrigerant flowing in the forward direction, in the refrigerant in which the bubbles are subdivided in the second throttle portion, the ejection energy is dispersed in the enlarged space portion, and the bubbles in the refrigerant flowing into the first throttle portion are Further subdivided. As a result, the speed fluctuation and pressure fluctuation of the refrigerant flow in the expansion valve are further alleviated, so that the refrigerant flow noise is further reduced and the refrigerant diversion in the refrigerant diversion chamber or the valve chamber / refrigerant diversion chamber is further stabilized. The

  The bubble fragmentation means may be a porous permeable material layer. If comprised in this way, the bubble in the refrigerant | coolant flow which flows into a 1st throttle part will be subdivided in a porous permeation | transmission material layer in a forward direction refrigerant | coolant flow. As a result, the speed fluctuation and pressure fluctuation of the refrigerant flow in the expansion valve are further alleviated, so that the refrigerant flow noise is reduced and the refrigerant diversion in the refrigerant diversion chamber is stabilized. Further, by providing the porous permeable material layer, it is possible to reduce clogging of the first throttle part.

  Moreover, the refrigeration apparatus according to the present invention uses the expansion valve having the refrigerant flow divider integrated structure. Therefore, the discontinuous refrigerant flow noise in the expansion valve can be reduced, the capacity can be improved by improving the shunt characteristics, and a simple refrigeration apparatus can be configured.

  According to the expansion valve of the refrigerant flow divider integrated structure according to the present invention, the circuit portion from the expansion valve to the refrigerant flow divider is simplified by integrating the expansion valve and the refrigerant flow divider, and the occupied space is reduced. The cost can be reduced while reducing the size. Further, in the expansion valve having the refrigerant flow divider integrated structure, in the case of the forward direction refrigerant flow, the sprayed refrigerant after passing through the first throttle part directly passes through the refrigerant branch chamber (here, the valve chamber). In addition, the flow dividing characteristics are improved. In addition, since the spraying energy is diffused by the refrigerant branch chamber (here, including the valve chamber / refrigerant branch chamber) acting as the enlarged space portion, the refrigerant flow upstream of the first throttle portion becomes the plug flow or the slag flow. In this case, discontinuous refrigerant flow noise is reduced. Further, in the case of reverse direction refrigerant flow, a swirl flow is generated when the refrigerant flows into the refrigerant branch chamber from the plurality of branch pipes and joins, so that the refrigerant flow on the expansion valve inlet side becomes a plug flow or slag flow. In this case, discontinuous refrigerant flow noise in the expansion valve is reduced.

  Hereinafter, the expansion valve according to each embodiment of the present invention will be described with reference to the drawings. In addition, the same code | symbol is attached | subjected to the element common to each embodiment, and description is simplified. Moreover, in the following description, when referring to the vertical and horizontal directions, the vertical and horizontal directions in each figure are assumed. In addition, a two-dot chain line in each drawing indicates a forward refrigerant flow, and a solid line arrow indicates a reverse refrigerant flow. For example, when the expansion valve of the refrigerant flow divider integrated structure of the present embodiment is used in the refrigerant cycle (see FIG. 16) according to the previous conventional example, it is used in the forward direction refrigerant flow. Further, in such a refrigerant circuit, when a four-way switching valve is connected to the inlet / outlet of the compressor and this refrigerant circuit is formed in a reversible cycle by switching the four-way switching valve, the expansion valve is not in cooling operation. It is a forward direction refrigerant flow, and becomes a reverse direction refrigerant flow at the time of heating operation. However, in the reverse refrigerant flow, the refrigerant distribution chamber does not exhibit the refrigerant distribution function.

(Embodiment 1)
Hereinafter, an expansion valve having a refrigerant flow divider integrated structure according to Embodiment 1 of the present invention will be described with reference to FIG. FIG. 1 is a drawing showing a schematic configuration of an expansion valve having an integrated refrigerant flow divider structure according to Embodiment 1, wherein (a) is a longitudinal sectional view of a main part, and (b) is a cross-sectional view taken along line AA in (a). FIG. FIG. 5A shows the valve drive device at the upper part of the valve chamber omitted. The expansion valve with the refrigerant flow divider integrated structure according to Embodiment 1 is used in place of a circuit portion from the expansion valve to the refrigerant flow divider in a normal refrigerant circuit.

  The expansion valve with the refrigerant flow divider integrated structure has a valve body 1 formed in a substantially cylindrical shape having a central axis in the vertical direction, and an inlet port 2 is formed on a side surface thereof. A liquid pipe 3 is connected to the inlet port 2. Further, the inside of the valve main body 1 is vertically divided by a partition wall 4, a valve chamber 5 is formed at the upper part (upstream side), and a refrigerant distribution chamber 6 is formed at the lower part (downstream side). The aforementioned inlet port 2 is formed on the side surface of the valve chamber 5.

  The partition wall 4 forms a valve seat, and a first valve hole 7 that forms a throttle portion between the valve chamber 5 and the refrigerant branch chamber 6 is formed at the center thereof. A valve rod 8 is accommodated in the valve chamber 5. The valve stem 8 extends downward from an upper valve driving device (not shown), and is disposed concentrically with the valve body 1 and the valve chamber 5. A first valve body (in this case, a needle valve) 9 is formed at the tip of the valve stem 8. The first valve body 9 is configured to move forward and backward with respect to the first valve hole 7 via the valve rod 8 by driving a valve driving device (not shown). In this way, the first throttle body 10 is formed by the first valve body 9 and the first valve hole 7 so that the opening degree is variable and can be fully closed in accordance with the refrigeration load.

  The refrigerant distribution chamber 6 is formed in a cylindrical shape having a predetermined volume, and a plurality of (in this case, four) distribution pipe mounting holes 11 corresponding to the number of passes of the evaporator are formed at a uniform pitch at the lower portion of the outer peripheral wall. Is formed. Further, a branch pipe 12 that connects the refrigerant branch chamber 6 and the inlet of each path of an evaporator (not shown) is connected to the branch pipe mounting hole 11.

  Further, in the case of the reverse direction refrigerant flow (in the case of the solid line in the figure), the flow dividing pipe mounting hole 11 causes the refrigerant flow flowing out from the flow dividing pipe 12 attached to the flow dividing pipe mounting hole 11 to be tangent to the cylindrical inner peripheral surface. It forms so that it may become a direction (refer FIG.1 (b)). Moreover, the front-end | tip part of the shunt pipe 12 is cut | disconnected by the linear shape which does not protrude | jump out so much from the circular arc substantially the same as the internal peripheral surface of the refrigerant | coolant flow dividing chamber 6 so that it may follow a substantially cylindrical internal peripheral surface. Has been.

The expansion valve of the refrigerant flow divider integrated structure of the first embodiment is configured as described above, and acts as follows in the forward direction refrigerant flow.
Liquid refrigerant condensed by a condenser (not shown) flows from the inlet port 2 into the expansion valve having the refrigerant divider integrated structure. The refrigerant that has entered from the inlet port 2 is reduced in pressure by the first throttle unit 10 and sprayed. Then, it flows into the refrigerant distribution chamber 6 in the sprayed state. For this reason, since the sprayed refrigerant flows through the diversion pipes 12, the refrigerant diversion chamber 6 is equally divided into the diversion pipes 12 without being affected by gravity.

  In addition, the expansion valve having the refrigerant flow divider integrated structure is configured such that when a gas-liquid two-phase flow refrigerant that has become a slag flow or a plug flow in which large bubbles are present enters from the inlet port 2, the refrigerant with respect to the first throttle unit 10. The flow becomes a discontinuous state in which liquid refrigerant and gas refrigerant (bubbles) flow alternately. For this reason, the speed fluctuation and pressure fluctuation of the refrigerant flow in the expansion valve are likely to occur. In addition, discontinuous refrigerant flow noise in the expansion valve is likely to occur due to such fluctuations in the velocity and pressure of the refrigerant flow. However, according to the present embodiment, since the refrigerant branch chamber 6 that expands the refrigerant flow path is formed on the downstream side of the first throttle portion 10, the jet energy is diffused in the refrigerant branch chamber 6. As a result, the speed fluctuation and pressure fluctuation of the refrigerant flow in the expansion valve are alleviated, and the discontinuous refrigerant flow noise in the expansion valve is reduced.

  Next, the expansion valve of this refrigerant flow divider integrated structure is used, for example, in a refrigerant circuit that circulates the refrigerant reversibly to cool and heat, and the refrigerant circuit is switched from the cooling circuit to the heating circuit so that the refrigerant flows in the reverse direction. When used, it operates as follows. When the gas-liquid two-phase flow refrigerant that has become the slag flow or the plug flow flows in from the branch pipe 12, the refrigerant flows into the refrigerant branch chamber 6 from the plurality of branch pipes 12, and is merged and disturbed. In addition, the refrigerant flowing in from each branch pipe 12 is introduced so as to be substantially along the inner peripheral surface of the refrigerant branch chamber 6, thereby generating a swirling flow. Thereby, the merged refrigerant is further disturbed. As a result, since the bubbles in the gas-liquid two-phase flow refrigerant are subdivided, the expansion valve of the refrigerant flow divider integrated structure according to the present embodiment is a discontinuous refrigerant in the expansion valve even in the reverse refrigerant flow. Flowing sound can be effectively reduced.

Since the expansion valve of the refrigerant flow divider integrated structure according to the present embodiment is configured as described above, the following effects can be achieved.
(1) Since the expansion valve and the refrigerant flow divider are integrated, the circuit portion from the expansion valve to the refrigerant flow divider is simplified, and the occupied space is saved.

(2) When used in the forward direction refrigerant flow, the sprayed refrigerant flows into the refrigerant distribution chamber 6 and is therefore equally divided into the respective distribution pipes 12 without being affected by gravity.
(3) In the forward-direction refrigerant flow, the first throttle unit 10 installed upstream of the refrigerant branch chamber 6 is throttled to have a variable opening degree corresponding to the refrigeration load, and is therefore attached to a conventional refrigerant distributor. Unlike the throttle part with a constant opening, the throttle degree changes to an appropriate throttle degree according to the operating conditions such as the flow rate and the dryness, whereby the refrigerant distribution characteristics can be further improved.

  (4) In the forward direction refrigerant flow, the refrigerant branch chamber 6 that expands the refrigerant flow path is formed on the downstream side of the first throttle portion 10, so that the ejection energy is diffused. Thereby, the speed fluctuation | variation and pressure fluctuation | variation of a refrigerant | coolant flow are relieve | moderated, and the discontinuous refrigerant | coolant flow noise in an expansion valve is reduced.

  (5) In the reverse-direction refrigerant flow, the refrigerant flowing into the refrigerant branch chamber 6 from the branch pipe 12 is disturbed by the refrigerant joining from the plurality of branch pipes 12, and on the inner peripheral surface of the refrigerant branch chamber 6. On the other hand, when the refrigerant is introduced in a substantially tangential direction, a swirling flow is generated and the refrigerant flow is further disturbed. Thereby, since the bubbles in the gas-liquid two-phase flow refrigerant are subdivided, discontinuous refrigerant flow noise in the expansion valve is effectively reduced.

  (6) The valve chamber 5 is formed on one side of the first throttle unit 10, and the refrigerant distribution chamber 6 is formed on the other side of the first throttle unit 10. Therefore, since the refrigerant distribution chamber 6 and the like can be designed with the valve chamber configuration in the conventional expansion valve, design restrictions on the refrigerant distribution chamber 6 are reduced.

(Embodiment 2)
Next, Embodiment 2 will be described with reference to FIG. 2A and 2B are diagrams showing a schematic configuration of an expansion valve having an integrated refrigerant flow distributor structure according to Embodiment 2, wherein FIG. 2A is a longitudinal sectional view of an essential part, and FIG. 2B is a cross-sectional view taken along line BB in FIG. It is sectional drawing. Similarly to the first embodiment, the expansion valve with the refrigerant flow divider integrated structure according to the second embodiment is also used instead of the circuit portion from the expansion valve to the refrigerant flow divider in the normal refrigerant circuit. is there.

  The expansion valve of the refrigerant flow divider integrated structure has a substantially cylindrical valve body 21 formed in a substantially cylindrical shape with a central axis in the vertical direction, and an inlet port 23 is formed in the lower wall 22 thereof. Yes. A liquid pipe 24 is connected to the inlet port 23. In addition, a substantially cylindrical valve chamber / refrigerant branch chamber 25 is formed inside the valve body 21. Above the valve chamber / refrigerant distribution chamber 25 is a drive unit 26 that houses a valve drive device (not shown), and a partition wall 27 is formed between the drive unit 26 and the valve chamber / refrigerant distribution chamber 25. ing.

  The lower wall 22 forms a valve seat, and the central portion is formed with the inlet port 23 as described above, and a first valve hole that forms a throttle portion between the valve chamber and the refrigerant distribution chamber 25. 28 is formed. A valve rod 29 is accommodated in the valve chamber / refrigerant branch chamber 25. The valve rod 29 extends downward from an upper valve driving device (not shown), and is disposed concentrically with the valve main body 21 and the valve chamber / refrigerant distribution chamber 25. A first valve body (in this case, a needle valve) 30 is formed at the tip of the valve rod 29. The first valve body 30 is configured to move forward and backward with respect to the first valve hole 28 via the valve rod 29 by driving of the valve driving device. In this way, the first throttle body 31 is formed by the first valve body 30 and the first valve hole 28 so that the opening degree is variable and can be fully closed corresponding to the refrigeration load.

  The valve chamber / refrigerant branch chamber 25 is formed in a cylindrical shape having a predetermined volume. Further, on the side of the side wall of the valve chamber / refrigerant distribution chamber 25 close to the upper partition wall 27, a plurality of (in this case, four) distribution pipe mounting holes 32 corresponding to the number of passes of the evaporator are provided at an equal pitch. Is formed. The branch pipe mounting hole 32 is connected to a branch pipe 33 that connects the valve chamber / refrigerant branch chamber 25 and an inlet of each path of an evaporator (not shown).

  Further, in the case of the reverse direction refrigerant flow (in the case of the solid line in the figure), the flow dividing pipe mounting hole 32 is configured so that the refrigerant flow flowing out from the flow dividing pipe 33 attached to the flow dividing pipe mounting hole 32 is substantially the cylindrical inner peripheral surface. It is formed so as to be in a tangential direction (see FIG. 2B). Further, the distal end portion of the flow dividing pipe 33 is substantially the same arc as the inner peripheral surface of the valve chamber / refrigerant flow dividing chamber 25 so as to be substantially along the inner peripheral surface of the cylinder, or a straight line that does not protrude greatly from the arc. It is cut into a shape.

The expansion valve of the refrigerant flow divider integrated structure of the second embodiment is configured as described above, and operates as follows.
When the expansion valve of this refrigerant flow divider integrated structure is used in a forward direction refrigerant flow, liquid refrigerant condensed by a condenser (not shown) flows from the inlet port 23. The refrigerant that has entered from the inlet port 23 is reduced in pressure by the first throttle 31 and sprayed. Then, it flows into the valve chamber / refrigerant branch chamber 25 in the sprayed state. For this reason, since the sprayed refrigerant flows through the branch pipes 33, the refrigerant is evenly divided into the respective branch pipes 33 without being affected by gravity in the valve chamber / refrigerant branch chamber 25.

  Further, the expansion valve having the refrigerant flow divider integrated structure is used to flow the refrigerant in the forward direction, and the slag flow or plug flow in which the liquid refrigerant condensed by the condenser has large bubbles from the inlet port 23 is used. When the gas-liquid two-phase flow refrigerant that has entered the refrigerant flow enters the discontinuous state where the liquid refrigerant and the gas refrigerant (bubbles) alternately flow. For this reason, the speed fluctuation and pressure fluctuation of the refrigerant flow in the expansion valve are likely to occur. In addition, discontinuous refrigerant flow noise in the expansion valve is likely to occur due to such fluctuations in the velocity and pressure of the refrigerant flow. However, according to the present embodiment, since the valve chamber / refrigerant branch chamber 25 that expands the refrigerant flow path is formed on the downstream side of the first throttle portion 31, the jet energy in the valve chamber / refrigerant branch chamber 25 is Is diffused. As a result, the speed fluctuation and pressure fluctuation of the refrigerant flow in the expansion valve are alleviated, and the discontinuous refrigerant flow noise in the expansion valve is reduced.

  The expansion valve with the refrigerant flow divider integrated structure is used, for example, in a refrigerant circuit that circulates refrigerant in a reversible manner for cooling and heating, and the refrigerant circuit is switched from a cooling circuit to a heating circuit to be used in a reverse refrigerant flow. In this case, the operation is as follows. When the gas-liquid two-phase flow refrigerant that has become the slag flow or the plug flow flows in from the branch pipe 33, the refrigerant flows into the valve chamber / refrigerant branch chamber 25 from the plurality of branch pipes 33, and is merged to be disturbed. Is done. In addition, the refrigerant flowing in from each branch pipe 33 is introduced so as to be substantially along the inner peripheral surface of the valve chamber / refrigerant branch chamber 25, thereby generating a swirling flow. Thereby, the merged refrigerant is further disturbed. As a result, since the bubbles in the gas-liquid two-phase flow refrigerant are subdivided, the expansion valve of the refrigerant flow divider integrated structure according to the present embodiment is a discontinuous refrigerant in the expansion valve even in the reverse refrigerant flow. Flowing sound can be effectively reduced.

Since the expansion valve of the refrigerant flow divider integrated structure according to the present embodiment is configured as described above, the following effects can be achieved.
(1) Since the expansion valve and the refrigerant flow divider are integrated, and the valve chamber and the refrigerant flow dividing chamber are formed in common, the circuit portion extending from the expansion valve to the refrigerant flow divider is more than that in the first embodiment. Furthermore, it is simplified and the occupied space is saved.

  (2) When used in the forward direction refrigerant flow, since the sprayed refrigerant flows into the valve chamber / refrigerant branch chamber 25, the refrigerant is evenly divided into the respective branch pipes 33 without being affected by gravity.

  (3) In the case of being used for the forward direction refrigerant flow, the first throttle portion 31 installed on the upstream side of the valve chamber / refrigerant branch chamber 25 is throttled to have a variable opening corresponding to the refrigeration load. Therefore, the first throttle part 31 installed on the upstream side of the valve chamber / refrigerant branching chamber 25 is different from the throttle part having a constant opening degree as attached to the conventional refrigerant distributor, such as the flow rate and the dryness. Depending on the operating conditions, the degree of throttling is changed to an appropriate degree, whereby the refrigerant distribution characteristics can be further improved.

  (4) In the forward direction refrigerant flow, since the valve chamber / refrigerant branch chamber 25 that expands the refrigerant flow path is formed on the downstream side of the first throttle portion 31, the ejection energy is diffused. Thereby, the speed fluctuation | variation and pressure fluctuation | variation of a refrigerant | coolant flow are relieve | moderated, and the discontinuous refrigerant | coolant flow noise in an expansion valve is reduced.

  (5) In the reverse direction refrigerant flow, the refrigerant flowing into the valve chamber / refrigerant branch chamber 25 from the branch pipe 33 is disturbed by the merge of refrigerant from the plurality of branch pipes 33, and the valve chamber / refrigerant branch flow By introducing the refrigerant in a substantially tangential direction with respect to the inner peripheral surface of the chamber 25, a swirling flow is generated and the refrigerant flow is further disturbed. Thereby, since the bubbles in the gas-liquid two-phase flow refrigerant are subdivided, discontinuous refrigerant flow noise in the expansion valve is effectively reduced.

  (6) In the reverse direction refrigerant flow, since the valve chamber / refrigerant branch chamber 25 that expands the refrigerant flow path is formed on the upstream side of the first throttle portion 31, the jet energy is diffused. Thereby, the speed fluctuation and pressure fluctuation of the refrigerant flow are alleviated, and the discontinuous refrigerant flow noise in the expansion valve is further reduced.

(Embodiment 3)
Next, Embodiment 3 will be described with reference to FIG. FIG. 3 is a drawing showing a schematic configuration of an expansion valve having a refrigerant flow distributor integrated structure according to Embodiment 3, wherein (a) is a longitudinal sectional view of the main part, and (b) is a CC line in (a). It is sectional drawing. As shown in the figure, the expansion valve aims to improve the refrigerant diversion effect in the forward refrigerant flow and the bubble fragmentation effect in the reverse refrigerant flow in the first embodiment. Hereinafter, the difference from the first embodiment will be mainly described.

  The expansion valve of the refrigerant flow divider integrated structure according to this embodiment is different from the first embodiment in the attachment position of the flow dividing pipe 12 first. In this embodiment, the flow dividing pipe 12 is attached to a plurality of flow dividing pipes at a position above the side wall of the refrigerant flow dividing chamber 6, that is, at a position close to the partition wall 4 forming the first throttle portion 10 on the side wall of the refrigerant flow dividing chamber 6. A hole 11 is formed, and a plurality of branch pipes 12 are attached to the plurality of branch pipe attachment holes 11 toward the tangential direction of the inner peripheral surface of the refrigerant branch chamber 6. Further, compared to the first embodiment, the cylindrical member 13 is suspended from the partition wall 4 forming the first throttle portion 10 so as to surround the first valve hole 7 with respect to the refrigerant distribution chamber side. The length of the cylindrical member 13 in the axial direction is such that a wall facing the inlet of the flow dividing pipe 12 is formed. In the forward direction refrigerant flow, the cylindrical member 13 blows the refrigerant flow ejected from the first throttle unit 10 onto the wall opposite to the first throttle unit 10, that is, the lower wall of the refrigerant distribution chamber 6. It performs the role of diverting the flow and diverting it to the inlet of the branch pipe 12. Further, the cylindrical member 13 constitutes an axial member that efficiently turns the refrigerant flow that flows in the tangential direction of the inner peripheral surface of the refrigerant distribution chamber 6 from the plurality of distribution pipes 12 in the reverse refrigerant flow.

  Since the third embodiment is configured as described above, in the forward direction refrigerant flow, the refrigerant flow ejected from the first throttle portion 10 is guided by the cylindrical member 13 and the bottom wall of the refrigerant distribution chamber 6. That is, it collides with the wall body (the bottom wall of the refrigerant distribution chamber 6) facing the first throttle portion 10, changes its direction upward, and flows in a detour direction toward the inlet of the distribution pipe 12. For this reason, the refrigerant flow ejected from the first throttle unit 10 does not flow directly to the inlet of the branch pipe 12, and therefore pressure fluctuations and velocity fluctuations in the refrigerant flow ejected from the first throttle unit 10 are directly affected by the direct branch pipe 12. It is configured so as not to affect the refrigerant circulation in the inside.

  Further, in the reverse refrigerant flow, when the gas-liquid two-phase flow refrigerant enters from the inlet port 2 as a slag flow or a plug flow in which large bubbles are present, the refrigerant flow with respect to the first throttle unit 10 is the refrigerant branch chamber. 6 is introduced in a tangential direction with respect to the inner peripheral surface of 6 and a swirling flow is formed. In this case, since the cylindrical member 13 is in the center and functions as the axial member of the swirling flow, generation of the swirling flow is promoted, and the disturbing action of the refrigerant flow by the swirling flow is further efficiently performed. . Therefore, the discontinuous refrigerant flow noise in the expansion valve can be further reduced in the reverse refrigerant flow.

(Embodiment 4)
Next, Embodiment 4 will be described with reference to FIG. FIG. 4 is a longitudinal sectional view of an essential part of an expansion valve having an integrated refrigerant flow distributor structure according to the fourth embodiment. As shown in this figure, in the third embodiment, the expansion valve smoothly spreads the refrigerant flow sprayed on the wall body (lower wall of the refrigerant distribution chamber 6) facing the first throttle portion 10 to the periphery. The guide part which acts so as to be reversed is provided. More specifically, a conical protruding portion 15 is formed as a guide portion at a portion facing the first throttle portion 10, and a corner portion between the bottom wall surface and the side wall is formed on the arc surface 16.

  Since the fourth embodiment is configured as described above, it is possible to suppress turbulence when the jet flow from the first throttle unit 10 changes direction in the forward direction refrigerant flow. That is, when a gas-liquid two-phase flow enters from the inlet port 2, this guide portion promotes the action of changing the flow direction of the refrigerant flow to reduce the jet energy of the refrigerant flow, and subdivides the bubbles in the refrigerant flow. The discontinuous refrigerant flow noise in the expansion valve can be reduced.

(Embodiment 5)
Next, the fifth embodiment will be described with reference to FIG. FIG. 5 is a longitudinal sectional view of an essential part of an expansion valve having an integrated refrigerant flow distributor according to a fifth embodiment. As shown in this figure, in the third embodiment, the expansion valve protects the swirl flow on the side wall of the refrigerant diversion chamber 6 in order to strengthen the swirl flow generated by the refrigerant flow introduced from the diversion pipe 12. An annular groove 17 is formed.

  That is, in this embodiment, the refrigerant flow dividing chamber 6 has a side wall at the axial position connecting the flow dividing pipe 12 having a larger diameter than the side wall portion at the other axial position. An annular groove 17 having a recessed inner peripheral surface is formed.

  Therefore, in the reverse direction refrigerant flow, the swirl flow generated by the refrigerant flow flowing from the plurality of flow dividing pipes 12 into the refrigerant branch chamber 6 is easily held by the annular groove 17, so that the refrigerant flow is disturbed by the swirl flow. It is performed even more efficiently. Thereby, in the reverse direction refrigerant flow, discontinuous refrigerant flow noise in the expansion valve is further reduced.

(Embodiment 6)
Next, the sixth embodiment will be described with reference to FIG. FIG. 6 is a longitudinal sectional view of an essential part of an expansion valve having a refrigerant flow distributor integrated structure according to the sixth embodiment. As shown in this figure, in the third embodiment, the expansion valve protrudes in the outer circumferential direction at the distal end portion of the cylindrical member 13 in order to strengthen the swirl flow generated by the refrigerant flow introduced from the diversion pipe 12. The flange 13a to be formed is formed. Further, the same guide portion as that of the fourth embodiment is formed on the wall body (the lower wall of the refrigerant distribution chamber 6) facing the first throttle portion 10.

  Since the present embodiment is configured as described above, the swirl flow generated by the refrigerant flow flowing into the refrigerant branch chamber 6 from the plurality of branch pipes 12 in the refrigerant flow in the reverse direction is a flange portion at the tip of the cylindrical member 13. 13a. Therefore, the disturbing action of the refrigerant flow by the swirling flow is performed more efficiently. Thereby, the discontinuous refrigerant flow noise in the expansion valve can be further reduced in the reverse refrigerant flow.

  Further, in the forward direction refrigerant flow, it is possible to suppress turbulence when the jet flow from the first throttle unit 10 changes direction. That is, when a gas-liquid two-phase flow enters from the inlet port 2, this guide portion promotes the action of changing the flow direction of the refrigerant flow to reduce the jet energy of the refrigerant flow, and subdivides the bubbles in the refrigerant flow. Is done. Thereby, the discontinuous refrigerant | coolant flow noise in an expansion valve can be reduced in a positive direction refrigerant | coolant flow.

(Embodiment 7)
Next, Embodiment 7 will be described with reference to FIG. FIG. 7 is a longitudinal sectional view of an essential part of an expansion valve having a refrigerant flow distributor integrated structure according to the seventh embodiment. As shown in this figure, in the sixth embodiment, the expansion valve is provided with a second throttle portion 35 as a bubble subdividing means in the valve chamber 5 and between the second throttle portion 35 and the first throttle portion 10. The enlarged space portion 36 is provided. Hereinafter, the difference from the sixth embodiment will be mainly described.

  As shown in FIG. 7, the expansion valve of the refrigerant flow divider integrated structure according to Embodiment 7 is provided with a second partition wall 37 having a large height at the center of the valve chamber 5. An enlarged space portion 36 is formed below, that is, between the second partition wall 37 and the first throttle portion 10. A tapered hole having a hole diameter that decreases downward is formed as a second valve hole 38 at the center of the second partition wall 37. Further, the valve stem 8 is arranged concentrically with the valve body 1 as in the case of the sixth embodiment, and a diameter-enlarged portion is formed above the first valve body 9, that is, in the intermediate portion of the valve stem 8. This is the second valve body 39. The second valve body 39 is formed as a tapered surface whose outer diameter decreases toward the lower outer peripheral surface, and a spiral groove is formed on the tapered surface. Thereby, a substantially spiral path is formed between the second valve hole 38 and the second valve body 39. This spiral passage forms the second throttle portion 35. The second throttle portion 35 changes the cross-sectional area and length of the spiral passage when the valve stem 8 is driven in the vertical direction. For example, when the refrigeration load is small, the valve stem 8 moves downward to reduce the cross-sectional area of the spiral passage and to increase the refrigerant passage resistance by increasing the length of the spiral passage (opening degree). To be smaller). The second throttle part 35 is thus formed with a variable opening. The first throttle portion 10 is formed between the first valve hole 7 and the first valve body 9 as described above, and the opening degree is variable by driving the valve stem 8 in the vertical direction. And it is formed to be fully closed.

  Since the expansion valve of the refrigerant flow divider integrated structure according to the seventh embodiment has the refrigerant flow dividing chamber 6 formed in the lower part (downstream side) of the partition wall 4 as in the case of the sixth embodiment as described above. The same effects as those of the sixth embodiment can be obtained. In addition, since the second throttle part 35 and the expansion space part 36 are formed in the valve chamber 5 at the upper part (upstream side) of the partition wall 4 as described above, the following operational effects are obtained. Can play.

  In the case of the above-described sixth embodiment (the same applies to the first, third, fourth, and fifth embodiments), in the forward direction refrigerant flow, the gas-liquid becomes a slag flow or a plug flow from the inlet port 2. When the two-phase flow refrigerant entered, the bubbles in the refrigerant flow were not subdivided before the slag flow or the plug flow passed through the first throttle portion 10. However, in the seventh embodiment, the gas-liquid two-phase flow refrigerant such as the slag flow or the plug flow that enters from the inlet port 2 passes through the second constriction portion 35, and the bubbles are subdivided. Thereby, the refrigerant | coolant flow to the 1st throttle part 10 is continued, and the discontinuous refrigerant | coolant flow noise in an expansion valve is reduced effectively. In particular, since the second throttle portion 35 is configured by a spiral passage, the throttle passage can be lengthened and the bubble fragmentation effect can be improved.

  Further, in the case of the seventh embodiment, since the two-stage throttle part is formed by the second throttle part 35 and the first throttle part 10, the ejection energy itself in each throttle part becomes small. Therefore, also from this viewpoint, speed fluctuation and pressure fluctuation of the refrigerant flow passing through the expansion valve are alleviated. Furthermore, in this embodiment, an enlarged space portion 36 is provided in addition to the second restricting portion 35, and the refrigerant flow after passing through the second restricting portion 35 has an ejection energy generated by expanding the flow path in the enlarged space portion 36. The bubbles in the refrigerant are further diffused and further subdivided in the enlarged space 36. Therefore, compared with the case of only the second throttle part 35, the bubble fragmentation effect is further improved, and the speed fluctuation and pressure fluctuation of the refrigerant flow flowing through the expansion valve can be further alleviated. As a result, discontinuous refrigerant flow noise in the expansion valve can be further reduced as compared with the case of the sixth embodiment.

  Further, in the expansion valve having the refrigerant flow divider integrated structure according to the seventh embodiment, in the reverse direction refrigerant flow, the refrigerant flow flowing out from the first throttle unit 10 has the ejection energy due to the flow passage expansion in the expansion space 36. Due to the diffusion, the two-stage aperture of the first aperture 10 and the third aperture reduces the ejection energy at each aperture. Therefore, even in the reverse direction refrigerant flow, the speed fluctuation and pressure fluctuation of the refrigerant flow flowing through the expansion valve are further alleviated, and the discontinuous refrigerant flow noise in the expansion valve is further reduced as compared with the sixth embodiment. be able to.

(Embodiment 8)
Next, an eighth embodiment will be described with reference to FIG. FIG. 8 is a longitudinal sectional view of an essential part of an expansion valve having a refrigerant flow distributor integrated structure according to the eighth embodiment. As shown in this figure, the expansion valve according to the eighth embodiment includes a porous permeable material layer 18 as a means for subdividing bubbles in the refrigerant flow flowing into the first throttle portion 10 in the forward direction refrigerant flow. It is. Further, the eighth embodiment is the same as the seventh embodiment in that the bubble fragmentation means is provided in the valve chamber 5, but the point that the bubble fragmentation means is a porous permeable material layer 18 is the same. Is different.

  As shown in FIG. 8, the expansion valve with the refrigerant flow divider integrated structure according to the eighth embodiment is provided with a porous permeable material layer 18 in the valve chamber 5. The porous permeable material layer 18 is formed in a cylindrical shape surrounding the valve stem 8 from the upper surface of the partition wall 4 to the upper portion of the inlet port 2, and is supported on the inner surface of the valve chamber 5 at the upper and lower portions. Support plates 18a and 18b are formed. As a material of the porous permeable material layer 18, foamed metal, ceramic, foamable resin, mesh, porous plate, or the like can be used.

  Since the expansion valve of the refrigerant flow divider integrated structure according to Embodiment 8 is configured as described above, the refrigerant flow enters the slag flow or the plug flow from the inlet port 2 in the forward direction refrigerant flow. In this case, the refrigerant flow passes through the porous permeable material layer 18, so that bubbles in the refrigerant flow flowing to the first throttle portion 10 are subdivided in the porous permeable material layer 18. Thereby, the discontinuous refrigerant | coolant flow noise in an expansion valve can be reduced. Moreover, since the porous permeation | transmission material layer 18 can remove the dust in the refrigerant | coolant to pass, it can serve as a filter with respect to the 1st aperture | diaphragm | squeeze part 10. FIG.

  Further, in the expansion valve having the refrigerant flow divider integrated structure configured as described above, in the reverse direction refrigerant flow, the refrigerant flow flowing out from the first throttle portion 10 is diffused by the flow energy in the valve chamber 5 due to the expansion of the flow path. At the same time, the ejection energy is consumed by passing through the porous permeable material layer 18. Thereby, the speed fluctuation and pressure fluctuation of the refrigerant flow passing through the expansion valve are alleviated, and the discontinuous refrigerant flow noise in the expansion valve is reduced.

(Embodiment 9)
Next, Embodiment 9 will be described with reference to FIG. FIG. 9 is a longitudinal sectional view of a main part of an expansion valve having an integrated refrigerant flow distributor according to the ninth embodiment. As shown in this figure, in the third embodiment, the expansion valve is provided with a porous permeable material layer 19 on the upstream side of the first throttle portion 10 in the reverse direction refrigerant flow, that is, in the refrigerant distribution chamber 6. It is. Hereinafter, the difference from the third embodiment will be mainly described.

  In the expansion valve of the refrigerant flow divider integrated structure of the ninth embodiment, a step portion 13 b that is fitted and inserted into the cylindrical porous permeable material layer 19 is formed at the lower end portion of the cylindrical member 13. In addition, an annular groove 6 a that fits the lower end of the cylindrical porous permeable material layer 19 is formed in the wall body facing the first throttle portion 10. And the step part 13b is inserted in the upper end part of the cylindrical porous permeable material layer 19, and the lower end part of the cylindrical porous permeable material layer 19 is inserted in the annular groove 6a. A cylindrical porous permeable material layer 19 is provided between the wall and the first throttle portion 10. Other points are the same as those of the third embodiment. The porous permeable material layer 19 can be made of foam metal, ceramic, foamable resin, mesh, porous plate, or the like, similar to the porous permeable material layer 18 in the above-described eighth embodiment.

  Since the ninth embodiment is configured as described above, in the forward direction refrigerant flow, the speed fluctuation and pressure fluctuation of the refrigerant flow ejected from the first throttle portion 10 are alleviated, and the discontinuous refrigerant in the expansion valve Flowing sound is reduced. Further, in the reverse refrigerant flow, the porous permeable material layer 19 is subdivided into bubbles in the refrigerant flowing into the first throttle portion 10, thereby reducing discontinuous refrigerant flow noise in the expansion valve. In the reverse refrigerant flow, the porous permeable material layer 19 can exhibit a filter function for the first throttle portion 10.

(Embodiment 10)
Next, Embodiment 10 will be described with reference to FIG. FIG. 10 is a longitudinal sectional view of an essential part of an expansion valve having a refrigerant flow distributor integrated structure according to the tenth embodiment. As shown in this figure, the expansion valve is porous on the upstream side of the first throttle portion 10 in the reverse direction refrigerant flow, that is, in the refrigerant branch chamber 6 in the third embodiment, as in the ninth embodiment. A transmission material layer 20 is provided. Hereinafter, the difference from the third embodiment will be mainly described. Note that the shape of the porous permeable material layer is different from that of the ninth embodiment.

  In the expansion valve of the refrigerant flow divider integrated structure according to the tenth embodiment, a step portion 13 b that is fitted and inserted into the cup-shaped porous permeable material layer 20 is formed at the lower end portion of the cylindrical member 13. The cup-shaped porous permeable material layer 20 is formed in a size that fits between the cylindrical member 13 and the wall facing the first throttle portion 10, and has a step portion 13 b on the inner peripheral side of the upper end portion. The cup-shaped porous permeable material layer 20 is attached to the refrigerant branching chamber 6 by being fitted and inserted. The other points are the same as those of the third embodiment, and the shape of the porous permeable material layer 20 is different from that of the ninth embodiment. The porous permeable material layer 20 may be made of foam metal, ceramic, foamable resin, mesh, porous plate, etc., similar to the porous permeable material layer 18 in the above-described eighth embodiment. .

  Since the tenth embodiment is configured as described above, the speed fluctuation and pressure fluctuation of the refrigerant flow ejected from the first throttle portion 10 are alleviated in the forward direction refrigerant flow. The refrigerant flow noise is reduced. Further, in the reverse refrigerant flow, the porous permeable material layer 20 is subdivided into bubbles in the refrigerant flowing into the first throttle portion 10, thereby reducing discontinuous refrigerant flow noise in the expansion valve. Further, in the reverse refrigerant flow, the porous permeable material layer 20 can exhibit a filter function for the first throttle portion 10.

(Embodiment 11)
Next, Embodiment 11 will be described with reference to FIG. FIG. 11 is a longitudinal sectional view of a main part of an expansion valve having an integrated refrigerant flow divider according to an eleventh embodiment. As shown in this figure, the expansion valve aims to improve the refrigerant diversion effect in the forward refrigerant flow and the bubble fragmentation effect in the reverse refrigerant flow in the second embodiment. Hereinafter, the difference from the second embodiment will be mainly described.

  The expansion valve of the refrigerant flow divider integrated structure according to this embodiment is different from the second embodiment in the attachment position of the flow dividing pipe 33 first. In this embodiment, the flow dividing pipe 33 is positioned below the side wall of the valve chamber / refrigerant distribution chamber 25, that is, at a position close to the lower wall 22 forming the first throttle portion 31 on the side wall of the valve chamber / refrigerant distribution chamber 25. A plurality of (in this case, four) branch pipe mounting holes 32 are formed. The plurality of branch pipes 33 are attached to the plurality of branch pipe attachment holes 32 toward the tangential direction of the inner peripheral surface of the refrigerant branch chamber 6. Further, compared to the second embodiment, a cylindrical member 34 is suspended from the lower wall 22 forming the first throttle portion 31 so as to surround the first valve hole 28 with respect to the refrigerant branching chamber side. The length of the cylindrical member 34 in the axial direction is such that a wall facing the inlet of the flow dividing pipe 33 is formed. In the forward direction refrigerant flow, the cylindrical member 34 is configured so that the refrigerant flow ejected from the first throttle portion 31 is a wall opposite to the first throttle portion 31, that is, the upper wall of the valve chamber / refrigerant branch chamber 25, In this case, it blows on the partition wall 27 with the drive unit 26 to perform a role of diverting the refrigerant flow to the entrance of the branch pipe 33. Further, the cylindrical member 34 constitutes an axial member that efficiently swirls the refrigerant flow introduced in the tangential direction of the inner peripheral surface of the refrigerant distribution chamber 6 from the plurality of distribution pipes 33 in the reverse direction refrigerant flow.

  Since the eleventh embodiment is configured as described above, in the forward direction refrigerant flow, the refrigerant flow ejected from the first throttle portion 31 is guided by the cylindrical member 34 and faces the first throttle portion 31. It collides with the body (in this case, the partition wall 27), changes its direction downward, and flows in a detour toward the inlet of the branch pipe 33. For this reason, since the jet does not flow directly to the inlet of the branch pipe 33, the pressure fluctuation and the speed fluctuation in the jet from the first throttle part 31 are not directly affected by the refrigerant flow in the branch pipe 33. .

  Further, in the reverse direction refrigerant flow, when the gas-liquid two-phase flow refrigerant enters from the inlet port 23 as a slag flow or a plug flow in which large bubbles exist, the refrigerant flow with respect to the first throttle portion 31 is the valve chamber function. It is introduced in a tangential direction with respect to the inner peripheral surface of the refrigerant branch chamber 25 to form a swirling flow. In this case, since the cylindrical member 34 is in the center and functions as a shaft center member of the swirling flow, generation of the swirling flow is promoted, and the disturbing action of the refrigerant flow by the swirling flow is further efficiently performed. . Therefore, the discontinuous refrigerant flow noise in the expansion valve can be further reduced in the reverse refrigerant flow.

(Embodiment 12)
Next, Embodiment 12 will be described with reference to FIG. FIG. 12 is a longitudinal sectional view of a main part of an expansion valve having an integrated refrigerant flow distributor according to a twelfth embodiment. As shown in this figure, in the eleventh embodiment, the expansion valve is provided on the side wall of the valve chamber / refrigerant branch chamber 25 in order to strengthen the swirl flow generated by the refrigerant flow introduced from the branch pipe 33. An annular groove 45 that protects the swirling flow is formed.

  That is, in this embodiment, the valve chamber / refrigerant branch chamber 25 has a side wall at the axial position connecting the flow dividing pipe 33 having a larger diameter than the side wall portion at the other axial position. Thus, an annular groove 45 is formed in which the inner peripheral surface of the side wall is recessed.

  Therefore, in the reverse refrigerant flow, the swirl flow generated by the refrigerant flow flowing from the plurality of flow dividing pipes 33 into the valve chamber / refrigerant flow diversion chamber 25 is easily held by the annular groove 45. The action is performed more efficiently. Thereby, in the reverse direction refrigerant flow, discontinuous refrigerant flow noise in the expansion valve is further reduced.

(Embodiment 13)
Next, Embodiment 13 will be described with reference to FIG. FIG. 13 is a longitudinal sectional view of an essential part of an expansion valve having an integrated refrigerant flow distributor according to a thirteenth embodiment. As shown in this figure, in the eleventh embodiment, the expansion valve is provided in the outer peripheral direction at the distal end portion of the cylindrical member 34 in order to strengthen the swirl flow generated by the refrigerant flow introduced from the diversion pipe 33. A protruding collar 34a is formed.

  Since the present embodiment is configured as described above, the swirl flow generated by the refrigerant flow flowing into the valve chamber / refrigerant branch chamber 25 from the plurality of branch pipes 33 in the refrigerant flow in the reverse direction is the tip of the cylindrical member 34. Is held by the flange 34a. Therefore, the disturbing action of the refrigerant flow by the swirling flow is performed more efficiently. Thereby, the discontinuous refrigerant flow noise in the expansion valve can be further reduced in the reverse refrigerant flow.

(Embodiment 14)
Next, a fourteenth embodiment will be described with reference to FIG. FIG. 14 is a longitudinal sectional view of an essential part of an expansion valve having a refrigerant flow distributor integrated structure according to a fourteenth embodiment. In the thirteenth embodiment, in the forward direction refrigerant flow, the expansion valve is provided with bubble fragmentation means on the upstream side of the first throttle portion 31, and more smoothly the jet flow from the first throttle portion 31. A guide portion 27a for changing the direction is provided. Hereinafter, the difference from the thirteenth embodiment will be mainly described.

  In the expansion valve with the refrigerant flow divider integrated structure according to this embodiment, unlike the case of the thirteenth embodiment, a separate chamber 47 is formed on the opposite side of the valve chamber / refrigerant flow dividing chamber 25 of the first throttle portion 31, An inlet port 23 is provided in the lower wall 47 a of the separate chamber 47, and a liquid pipe 24 is connected to the inlet port 23. The lower wall 22 of the valve main body 21 functions as a partition wall between the valve chamber / refrigerant distribution chamber 25 and the separate chamber 47, and the first valve hole 28 constituting the first throttle portion 31 is formed in the lower wall 22. ing. In addition, a bubble subdividing means is installed between the inlet port 23 and the first throttle part 31 in the separate chamber 47. This bubble segmentation means is a disc-shaped porous permeation material layer 48 disposed in the separate chamber 47 so as to cross the intermediate position of the separate chamber 47. The material of the porous permeable material layer 48 may be the same as that of the porous permeable material layer 18 in the eighth embodiment, and foam metal, ceramic, foam resin, mesh-like material, perforated plate, etc. are used. .

  In addition, the partition wall 27 that forms the upper wall of the valve chamber / refrigerant branch chamber 25 has the lower wall 22 of the valve body 21 that forms the lower wall of the valve chamber / refrigerant branch chamber 25 with the jet blown from the first throttle 31. A guide portion 27a is formed to be reversed toward the flow dividing pipe 33 formed near the pipe. The guide portion 27a is configured such that the wall surface of the partition wall 27 on the valve chamber / refrigerant distribution chamber 25 side is shaped along the flow of the refrigerant flow.

  Since the expansion valve with the refrigerant flow divider integrated structure according to Embodiment 14 is configured as described above, the refrigerant flow enters the slag flow or the plug flow from the inlet port 23 in the forward direction refrigerant flow. In this case, when the refrigerant flow passes through the porous permeable material layer 48, the bubbles in the refrigerant flow flowing to the first throttle portion 31 are subdivided in the porous permeable material layer 48. Thereby, the discontinuous refrigerant | coolant flow noise in an expansion valve can be reduced. Further, since the porous permeable material layer 48 can remove dust in the refrigerant passing therethrough, it can also serve as a filter for the first throttle portion 31.

  Further, the refrigerant flow guided and blown out by the cylindrical member 34 toward the partition wall 27 that forms the upper wall of the valve chamber / refrigerant distribution chamber 25 from the first throttle portion 31 is guided by the guide portion 27 a formed in the partition wall 27. The flow direction of the refrigerant flow is smoothly changed by the guide function. The facilitating action related to the change in the flow direction of the guide portion 27a reduces the jet energy of the refrigerant flow, subdivides the bubbles in the refrigerant flow, and reduces discontinuous refrigerant flow noise in the expansion valve. .

  Further, in the expansion valve with the refrigerant flow divider integrated structure configured as described above, in the reverse direction refrigerant flow, the refrigerant flow flowing out from the first throttling portion 31 has its ejection energy diffused by the flow path expanding action in the separate chamber 47. At the same time, the ejection energy is consumed by passing through the porous permeable material layer 48. Thereby, the speed fluctuation and pressure fluctuation of the refrigerant flow passing through the expansion valve are alleviated, and the discontinuous refrigerant flow noise in the expansion valve is reduced.

(Embodiment 15)
Next, Embodiment 15 will be described with reference to FIG. FIG. 15 is a longitudinal sectional view of main parts of an expansion valve having an integrated refrigerant flow distributor according to the fifteenth embodiment. As shown in this figure, in the eleventh embodiment, the expansion valve has a porous permeable material layer 51 on the upstream side of the first throttle 31 in the reverse direction refrigerant flow, that is, in the valve chamber / refrigerant branch chamber 25. It is provided. Hereinafter, the difference from the eleventh embodiment will be mainly described.

  The expansion valve with the refrigerant flow divider integrated structure of the fifteenth embodiment has a valve chamber / refrigerant flow dividing chamber 25 between the upper end portion of the cylindrical member 13 and the wall opposite to the first throttle portion 31, that is, the partition wall 27. The cylindrical porous permeable material layer 51 is attached by an appropriate means substantially concentrically. Other points are the same as those of the eleventh embodiment. Further, the porous permeable material layer 51 is made of foam metal, ceramic, foamable resin, mesh, porous plate, etc., like the porous permeable material layer 18 in the above-described eighth embodiment. .

  Since the fifteenth embodiment is configured as described above, in the forward direction refrigerant flow, the speed fluctuation and pressure fluctuation of the refrigerant flow ejected from the first throttle portion 31 are alleviated, and the discontinuous refrigerant in the expansion valve Flowing sound is reduced. Further, in the reverse direction refrigerant flow, the porous permeable material layer 51 is subdivided into bubbles in the refrigerant flowing into the first throttle portion 31, thereby reducing discontinuous refrigerant flow noise in the expansion valve. Further, in the reverse refrigerant flow, the porous permeable material layer 51 can exhibit a filter function with respect to the first throttle portion 31.

(Modification)
(1) In each of the above embodiments, the refrigerant distribution chamber 6 or the valve chamber / refrigerant distribution chamber 25 is not limited to a shape that is long in the axial direction as shown in the figure, but is formed to be large in the lateral direction. May be good.

(2) Although four flow dividing pipes 12 and 33 are shown in each embodiment, the present invention is not limited to this and is applicable to all two or more flow dividing pipes.
(3) In the first and second embodiments, the partition wall 4 or the lower wall in which the first throttle portions 10 and 31 are formed as in the third or eleventh embodiment at the attachment positions of the flow dividing pipes 12 and 33. It may be changed to a position close to 22. In this way, the refrigerant flow ejected from the first throttle parts 10, 31 collides with the wall body facing the first throttle parts 10, 31, reversely bypasses, and flows into the branch pipes 12, 33. Therefore, the refrigerant diversion effect is improved as compared with the first and second embodiments. However, in this case, since the cylindrical members 13 and 34 are not formed as in the third embodiment or the eleventh embodiment, the jet flow from the first throttle portions 10 and 31 directly reaches the branch pipes 12 and 33. This is inferior to Embodiments 3 and 11 in terms of preventing this.

  (4) In the fourteenth embodiment, instead of the disk-shaped porous transmission member layer as the bubble subdividing means, the second throttle part 35 and the expansion space part 36 may be combined as in the seventh embodiment. Good. In the fourteenth embodiment, the disc-shaped porous permeable material layer 48 can be changed to a cylindrical porous permeable material layer. In order to do this, for example, the inlet port 23 to which the liquid pipe 24 is attached may be provided on the side wall of the separate chamber 47.

  (5) In the seventh embodiment, the tapered second valve body 39 and the second valve hole 38 may be shaped parallel to the center line. Further, the spiral groove provided in the second valve body 39 may be formed by a plurality of spiral grooves to form a plurality of throttle passages. Moreover, it may replace with a spiral groove and may be formed with a plurality of concave grooves extending linearly in the vertical direction. Such a groove may be formed not on the outer peripheral surface of the second valve body 39 but on the inner peripheral surface of the second valve hole 38. Moreover, it is good also as a throttle part which does not form these groove | channels in either the 2nd valve body 39 or the 2nd valve hole 38. FIG. Further, the step shape of these grooves may be various shapes such as a semi-circle, a triangle, and a quadrangle. Such a modification can be similarly applied to the modification of the fourteenth embodiment described in the fourth modification.

  (6) In addition, the bubble fragmentation means is not limited to the combination of the second throttle part 35 and the enlarged space part 36 as described above, or the cylindrical or disk-shaped porous transmission material layer 18. Alternatively, other bubble fragmentation means may be provided in the valve chamber 5 or the separate chamber 47. For example, only one of the second aperture portion 35 and the enlarged space portion 36 may be provided. In addition, other means for disturbing the refrigerant flow, for example, means for giving a swirling flow to the refrigerant flow or meandering the refrigerant flow may be used.

  (7) Although the porous permeable material layers 19 and 20 are provided in the refrigerant branch chamber 6 in the ninth and tenth embodiments, the porous permeable material layers are also provided in the fourth and fifth embodiments as in these embodiments. May be attached. In Embodiments 1, 6 and 7 as well, a cylindrical or cup-shaped porous permeable material layer may be attached by an appropriate means.

  (8) Although the porous permeable material layer 51 is provided in the valve chamber / refrigerant distribution chamber 25 in the fifteenth embodiment, the porous permeable material layer is attached in the twelfth embodiment as in this embodiment. Also good. In the thirteenth and fourteenth embodiments, a cylindrical porous permeable material layer may be attached to the upper part of the cylindrical member 34 by an appropriate means.

It is drawing which shows schematic structure of the expansion valve of the refrigerant | coolant divider | distributor integrated structure which concerns on Embodiment 1, (a) is a principal part longitudinal cross-sectional view, (b) is AA sectional drawing in (a). . It is drawing which shows schematic structure of the expansion valve of the refrigerant | coolant divider | distributor integrated structure which concerns on Embodiment 2, (a) is a principal part longitudinal cross-sectional view, (b) is BB sectional drawing in (a). . It is drawing which shows schematic structure of the expansion valve of the refrigerant | coolant flow divider integrated structure which concerns on Embodiment 3, (a) is a principal part longitudinal cross-sectional view, (b) is CC sectional drawing in (a). . It is a principal part longitudinal cross-sectional view of the expansion valve of the refrigerant | coolant flow divider integrated structure which concerns on Embodiment 4 of this invention. It is a principal part longitudinal cross-sectional view of the expansion valve of the refrigerant | coolant divider | distributor integrated structure which concerns on Embodiment 5 of this invention. It is a principal part longitudinal cross-sectional view of the expansion valve of the refrigerant | coolant flow divider integrated structure which concerns on Embodiment 6 of this invention. It is a principal part longitudinal cross-sectional view of the expansion valve of the refrigerant | coolant flow divider integrated structure which concerns on Embodiment 7 of this invention. It is a principal part longitudinal cross-sectional view of the expansion valve of the refrigerant | coolant flow divider integrated structure which concerns on Embodiment 8 of this invention. It is a principal part longitudinal cross-sectional view of the expansion valve of the refrigerant | coolant flow divider integrated structure which concerns on Embodiment 9 of this invention. It is a principal part longitudinal cross-sectional view of the expansion valve of the refrigerant | coolant divider | distributor integrated structure which concerns on Embodiment 10 of this invention. It is a principal part longitudinal cross-sectional view of the expansion valve of the refrigerant | coolant flow divider integrated structure which concerns on Embodiment 11 of this invention. It is a principal part longitudinal cross-sectional view of the expansion valve of the refrigerant | coolant divider | distributor integrated structure which concerns on Embodiment 12 of this invention. It is a principal part longitudinal cross-sectional view of the expansion valve of the refrigerant | coolant divider | distributor integrated structure which concerns on Embodiment 13 of this invention. It is a principal part longitudinal cross-sectional view of the expansion valve of the refrigerant | coolant divider | distributor integrated structure which concerns on Embodiment 14 of this invention. It is a principal part longitudinal cross-sectional view of the expansion valve of the refrigerant | coolant flow divider integrated structure which concerns on Embodiment 15 of this invention. It is a common refrigerant circuit figure in the conventional freezing apparatus.

Explanation of symbols

  2, 23 ... Inlet port, 3, 24 ... Liquid pipe, 5 ... Valve chamber, 6 ... Refrigerant branch chamber, 7, 28 ... First valve hole, 9, 30 ... First valve body, 10, 31 ... First throttle Part, 12, 33 ... shunt pipe, 13, 34 ... cylindrical member, 13a, 34a ... collar part, 17, 45 ... annular groove, 18, 19.20, 48, 51 ... porous permeable material layer, 25 ... valve chamber Cumulative refrigerant distribution chamber, 35 ... second throttle, 36 ... expanded space, 47 ... separate chamber.

Claims (20)

A first throttle part that performs a throttling action formed between the first valve body and the first valve hole; and a substantially cylindrical refrigerant branch chamber that divides the refrigerant after passing through the first throttle part into a branch pipe. A plurality of branch pipes connected to the refrigerant branch chamber,
The plurality of flow dividing pipes are connected to side walls of a substantially cylindrical refrigerant flow dividing chamber so as to open in a substantially constant tangential direction, respectively. An expansion valve having an integrated refrigerant flow divider structure.   2. The expansion of the refrigerant flow divider integrated structure according to claim 1, wherein an end portion of the flow dividing pipe on the refrigerant flow dividing chamber side is cut in an oblique direction so as to be substantially along the inner peripheral surface of the refrigerant flow dividing chamber. valve. In the expansion valve of the refrigerant flow divider integrated structure according to claim 1 or 2,
The first valve body is housed on one side of the first throttle portion, a valve chamber having an inlet port for connecting a liquid pipe is formed, and a refrigerant branch chamber is formed on the other side of the first throttle portion. An expansion valve with an integrated refrigerant flow distributor.   The expansion valve of the refrigerant flow divider integrated structure according to claim 3, wherein the flow dividing pipe is connected to a position close to a wall body forming the first throttle portion in the side wall of the refrigerant flow dividing chamber.   5. The refrigerant flow divider according to claim 4, wherein a cylindrical member is provided on the refrigerant flow dividing chamber side of the first throttle portion to promote the rotation of the refrigerant when the refrigerant is introduced from the flow dividing pipe. Integrated expansion valve.   The said cylindrical member is provided with the collar part which protrudes in the outer peripheral direction at the front-end | tip part while it has the axial direction length of the grade which forms the wall facing the inlet_port | entrance of the said shunt pipe. An expansion valve having an integrated structure of the refrigerant flow divider.   The refrigerant distribution chamber according to any one of claims 3 to 6, wherein the refrigerant distribution chamber is formed in an annular groove with an inner peripheral surface of a side wall at an axial position connecting a distribution pipe being recessed. Expansion valve with integrated structure.   The expansion of the refrigerant flow divider integrated structure according to any one of claims 3 to 7, wherein bubble fragmentation means is disposed between the inlet port and the first throttle portion in the valve chamber. valve.   The refrigerant flow divider integrated structure according to any one of claims 3 to 8, wherein a porous permeable material layer is disposed between the flow dividing pipe and the first throttle portion in the refrigerant flow dividing chamber. Expansion valve. In the expansion valve of the refrigerant flow divider integrated structure according to claim 1 or 2,
The refrigerant branch chamber is formed on one side of the first throttle portion as a valve chamber / refrigerant branch chamber that also serves as a valve chamber that houses the first valve body of the first throttle portion. An expansion port with an integrated refrigerant flow divider, characterized in that an inlet port to which a liquid pipe is connected is formed on the other side of the refrigerant flow divider.   11. The expansion valve of the refrigerant flow divider integrated structure according to claim 10, wherein the flow dividing pipe is connected to a position close to a wall body forming the first throttle portion on the side wall of the valve chamber / refrigerant flow dividing chamber. .   The cylindrical member for urging the refrigerant to turn when the refrigerant is introduced from the diverter pipe is provided on the valve chamber / refrigerant branch chamber side of the first throttle part. Expansion valve with integrated refrigerant flow divider.   The cylindrical member has an axial length sufficient to form a wall facing the inlet of the flow dividing pipe, and is provided with a flange portion protruding in an outer peripheral direction at a tip portion thereof. An expansion valve having an integrated structure of the refrigerant flow divider.   The valve chamber / refrigerant branch chamber is formed in an annular groove with an inner peripheral surface of a side wall at an axial position connecting a branch pipe being recessed. Expansion valve with integrated refrigerant flow divider.   A separate chamber is formed on the other side of the first throttle portion, the inlet port is formed in the separate chamber, and bubble segmentation means is disposed between the inlet port and the first throttle portion in the separate chamber. The expansion valve of the refrigerant flow divider integrated structure according to any one of claims 10 to 14.   The refrigerant distributor according to any one of claims 10 to 15, wherein a porous permeable material layer is disposed between the branch pipe and the first throttle part in the valve chamber / refrigerant branch chamber. Integrated expansion valve.   The expansion valve of the refrigerant flow divider integrated structure according to claim 8, 9, 15 or 16, wherein the bubble subdividing means is a second throttle portion.   18. The expansion valve of the refrigerant flow divider integrated structure according to claim 17, wherein the bubble subdividing means includes an enlarged space portion between the second throttle portion and the first throttle portion.   The expansion valve of the refrigerant flow divider integrated structure according to claim 8, 9, 15 or 16, wherein the bubble subdividing means is a porous permeable material layer.   A refrigerating apparatus using the expansion valve having an integrated refrigerant distributor structure according to any one of claims 1 to 19.

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