JP5823078B2 - Expansion valve and refrigeration cycle apparatus using the same - Google Patents

Description

  The present invention relates to an expansion valve having a refrigerant distribution function and a refrigeration cycle apparatus using the expansion valve.

  The refrigeration cycle apparatus is provided with an expansion valve that depressurizes the high-pressure refrigerant to change it to a low-pressure, low-dryness gas-liquid two-phase state, and an evaporator is connected downstream of the expansion valve. Then, the refrigerant enters a gas-liquid two-phase state in the expansion valve, and in the evaporator, the refrigerant exchanges heat with air or water, resulting in a low-pressure, high-dryness gas-liquid two-phase state or a superheated gas state. Here, when an evaporator is comprised with the multipass heat exchanger which consists of a several path | pass (refrigerant flow path), it is necessary to implement refrigerant | coolant distribution appropriately to each path | pass.

  2. Description of the Related Art Conventionally, there has been proposed an expansion valve in which a distributor is provided in the expansion valve and an expansion valve that performs distribution to each path and a refrigerant distributor are integrated (see, for example, Patent Document 1). Patent Document 1 discloses an expansion valve having a valve chamber section and a refrigerant branch chamber section partitioned by a partition wall, and the valve chamber section and the refrigerant branch chamber section are communicated by a throttle section provided on the partition wall. It is disclosed. The refrigerant that has flowed into the expansion valve is decompressed by the throttle and flows into the refrigerant branch chamber in a sprayed state (gas-liquid two-phase state), and is divided into a plurality of branch pipes in the refrigerant branch chamber. .

  Patent Document 2 discloses an expansion valve including a valve body that adjusts the opening degree of the orifice from the refrigerant inlet to the refrigerant outlet through the orifice and the refrigerant branch chamber. The refrigerant outlets are arranged at equal intervals around the orifice in the circumferential direction of the refrigerant distribution chamber, the valve body is downstream of the orifice, and the refrigerant distribution chamber is a flow path that gradually advances to the outer peripheral side. While the refrigerant expands from the orifice to the refrigerant distribution chamber, it is guided by a projecting rectifier provided in the orifice, and is uniformly distributed to the refrigerant outlet.

JP 2009-24937 A JP 2010-32185 A

  Here, the refrigerant immediately after flowing out of the expansion valve is a spray flow and is in a state where it is easily distributed uniformly. However, the refrigerant flowing into the evaporator is not necessarily a spray flow, and is, for example, a slag flow or a plug flow at the evaporator inlet. There is a case. Then, the gas-liquid of the refrigerant in the gas-liquid two-phase state is separated, and there are cases where appropriate distribution to each path cannot be performed due to the influence of gravity. Even if the refrigerant flowing out from the valve chamber is in a spray state in the refrigerant distribution chamber as in Patent Document 1, the refrigerant affects each other in the refrigerant distribution chamber up to each branch pipe, resulting in turbulence. The flow is uniform. If the refrigerant flow rate is sufficiently large, the non-uniform flow collides with the wall surface of the refrigerant distribution chamber to become a uniform flow again, and the refrigerant can be distributed to each branch pipe at the intended distribution ratio in the refrigerant distribution chamber. . However, when the refrigerant flow rate is small, the collision energy is small and the flow is not uniform, and it may not be possible to appropriately distribute to each branch pipe. Furthermore, in the case of operating conditions such as a low refrigeration (air conditioning) load, the flow rate of refrigerant flowing through the expansion valve is small. In other words, the refrigerant may not be distributed to each branch pipe at the intended distribution ratio.

  Further, in Patent Document 2, the refrigerant flowing from the orifice into the refrigerant distribution chamber is expanded and enters the refrigerant outlet provided at equal intervals in the circumferential direction. Instead, it is distributed while being guided by the valve body, the refrigerant distribution chamber, and the rectifying unit. However, similarly to Patent Document 1, in the refrigerant branch chamber leading to the refrigerant outlet, the refrigerants affect each other, resulting in turbulence and an uneven flow. As a result, there is a possibility that it is not uniformly distributed. In addition, a reverse flow is not assumed, and there is a risk of generating refrigerant noise in the case of a gas-liquid two-phase flow. Furthermore, it is not equal distribution and cannot be intentionally distributed to different ratios.

  The present invention has been made to solve the above-described problems, and provides an expansion valve capable of accurately distributing a refrigerant to an intended distribution ratio in a refrigerant distribution chamber and a refrigeration cycle apparatus using the expansion valve. It is for the purpose.

The expansion valve of the present invention has a valve chamber and a refrigerant branch chamber partitioned by a partition wall, and a throttle portion that communicates between the valve chamber and the refrigerant branch chamber opens in the partition wall and communicates with the refrigerant branch chamber. A main body unit in which a plurality of branch ports are formed, a valve body that adjusts the opening of the throttle portion, a plate-like partition portion that is disposed in the refrigerant branch chamber and divides the refrigerant branch chamber into a plurality of branch ports; And at least a part of the upper edge of the partition part is located in the opening of the throttle part in a vertical view with respect to the partition wall, and the maximum separation dimension between the lower surface of the partition wall where the throttle part opens and the upper edge of the partition part is The diameter is smaller than the diameter of the throttle part .

  According to the expansion valve of the present invention, since the partition portion divides the refrigerant distribution chamber for each of the plurality of branch ports, the refrigerant is reduced or reduced while distributing the refrigerant to each branch port at the intended distribution ratio regardless of the refrigerant flow rate. The pressure such as expansion can be adjusted.

It is a refrigerant circuit figure which shows Embodiment 1 of the refrigerating-cycle apparatus of this invention. It is a cross-sectional schematic diagram which shows Embodiment 1 of the expansion valve of this invention. It is a partial section schematic diagram showing Embodiment 1 of the expansion valve of the present invention. It is an upper surface schematic diagram which shows the mode of the division part in the 2nd housing of FIG. 2A. It is a schematic diagram which shows the mode of the A-A 'cross section in the 1st housing of FIG. 2A. It is an upper surface schematic diagram which shows an example of the division part in the expansion valve of FIG. 2A. It is a side surface schematic diagram which shows an example of the division part in the expansion valve of FIG. 2A. It is an expansion | deployment schematic diagram which shows an example of the division part in the expansion valve of FIG. 2A. It is an upper surface schematic diagram which shows Embodiment 2 of the division part in the expansion valve of this invention. It is a side surface schematic diagram which shows Embodiment 2 of the division part in the expansion valve of this invention. It is an expansion | deployment schematic diagram which shows Embodiment 2 of the division part in the expansion valve of this invention. It is a schematic diagram which shows the mode of the A-A 'cross section in the 1st housing of FIG. 2A. It is a cross-sectional schematic diagram which shows Embodiment 3 of the expansion valve of this invention. It is a schematic diagram which shows the mode of the A-A 'cross section in the 1st housing of FIG. 6A. It is a cross-sectional schematic diagram which shows Embodiment 4 of the expansion valve of this invention. FIG. 8 is a schematic top view illustrating a state of a partition portion in the second housing in FIG. 7. FIG. 8 is a schematic view showing a state of an A-A ′ cross section in the first housing of FIG. 7. It is a schematic diagram which shows Embodiment 5 of the refrigeration cycle apparatus of this invention.

Embodiment 1 FIG.
Hereinafter, Embodiment 1 of the expansion valve of the present invention will be described with reference to the drawings. FIG. 1 is a refrigerant circuit diagram showing Embodiment 1 of the refrigeration cycle apparatus of the present invention. The refrigeration cycle apparatus 1 will be described with reference to FIG. The refrigeration cycle apparatus 1 performs both cooling operation and heating operation, and has a configuration in which an outdoor unit 1A and an indoor unit 1B are connected by a liquid pipe 9A and a gas pipe 9B. The outdoor unit 1A includes a compressor 2, a flow path switch 3, and an outdoor heat exchanger 4. The compressor 2 sucks the refrigerant, compresses the refrigerant, and discharges it in a high temperature / high pressure state. The compressor 2 has a discharge side connected to the flow path switch 3 and a suction side connected to the suction pipe 9.

  The flow path switching unit 3 switches between a heating flow path and a cooling flow path in accordance with switching of an operation mode of cooling operation or heating operation, and includes, for example, a four-way valve. During the cooling operation, the flow path switching unit 3 connects the discharge side of the compressor 2 and the outdoor heat exchanger 4 and connects the suction side of the compressor 2 and the gas pipe 9B. Then, the refrigerant discharged from the compressor 2 flows to the outdoor heat exchanger 4 side, and the refrigerant flowing out from the indoor unit 1B flows into the outdoor unit 1A side through the gas pipe 9B. On the other hand, during the heating operation, the flow path switch 3 connects the suction side of the compressor 2 and the outdoor heat exchanger 4 and connects the discharge side of the compressor 2 and the gas pipe 9B. Then, the refrigerant discharged from the compressor 2 flows to the indoor unit 1B side, and the refrigerant flowing out of the indoor unit 1B flows into the outdoor unit 1A through the liquid pipe 9A. In addition, although the case where a four-way valve is used as the flow path switching device 3 is illustrated, the present invention is not limited to this. For example, a plurality of two-way valves may be combined.

  The outdoor heat exchanger 4 performs heat exchange between the refrigerant and air (outside air), and for example, a heat transfer tube that allows the refrigerant to pass therethrough, and a heat transfer area between the refrigerant that flows through the heat transfer tube and the outside air. It has the structure provided with the fin for enlarging. The outdoor heat exchanger 4 is connected between the flow path switch 3 and the liquid pipe 9A and functions as a condenser that condenses and liquefies the refrigerant during the cooling operation, and evaporates and vaporizes the refrigerant during the heating operation. It functions as an evaporator.

  The indoor unit 1B has an expansion valve 5, an indoor heat exchanger 7, and a header 8. The expansion valve 5 functions as a pressure reducing valve or an expansion valve that adjusts the pressure of the refrigerant that passes through the indoor heat exchanger 7, and is connected between the liquid pipe 9 </ b> A and the indoor heat exchanger 7. The indoor heat exchanger 7 functions as an evaporator (heat absorber) during cooling operation and functions as a condenser (heat radiator) during heating operation. And the indoor side heat exchanger 7 heat-exchanges between indoor air and a refrigerant | coolant, and cools and heats a space. In particular, the indoor heat exchanger 7 is a multi-pass heat exchanger having a plurality of paths, for example, a heat exchanger having two paths. The expansion valve 5 has a distribution function of distributing the refrigerant to each path of the indoor heat exchanger 7 through the capillary tube 6. During the cooling operation, the refrigerant distributed by the expansion valve 5 flows into each path of the indoor heat exchanger 7 and merges at the header 8. During the heating operation, the refrigerant flows into each path of the indoor heat exchanger 7 from the header 8, and the refrigerant flowing out from each path joins at the expansion valve 5.

  As the refrigerant used in the refrigeration cycle apparatus 1 described above, it is desirable to use a low GWP refrigerant in a small amount from the viewpoint of preventing global warming, and R32, HFO refrigerant, HCFO refrigerant, flammability having a relatively high GWP. If a refrigerant or the like is used, GWP can be reduced as compared with a conventional chlorofluorocarbon refrigerant.

  Hereinafter, the refrigerant flow in the refrigeration cycle apparatus 1 during the cooling operation and the heating operation will be described. First, an example of the operation of the refrigeration cycle apparatus 1 during the cooling operation will be described with reference to FIG. First, the discharge side of the compressor 2 and the gas pipe 9B are connected by the flow path switch 3, and the outdoor heat exchanger 4 and the suction side of the compressor 2 are connected. And the refrigerant | coolant of a low pressure gas is compressed in the compressor 2, and becomes high pressure gas. The refrigerant in the high-pressure gas state is heat-exchanged with the outside air in the outdoor heat exchanger (condenser) 4 and is condensed by transferring the energy of the refrigerant to a heat source (air or water) to become a high-pressure liquid refrigerant.

  Thereafter, the refrigerant is depressurized by the expansion valve 5 through the liquid pipe 9 </ b> A to be in a low-pressure two-phase state, branches at the expansion valve 5, passes through the capillary tube 6, and enters each path of the indoor heat exchanger 7. In the indoor heat exchanger (evaporator) 7, as the refrigerant passes through the path in the indoor heat exchanger 7, the refrigerant absorbs the energy of the load-side water or outdoor air and evaporates to become low-pressure gas. At this time, water or air that has been heat exchanged with the refrigerant is cooled. Then, the refrigerant | coolants of the several path | pass of the indoor side heat exchanger 7 are collected by the header 8, and are suck | inhaled by the compressor 2 via the gas pipe 9B.

  Next, an operation example during the heating operation of the refrigeration cycle apparatus 1 will be described with reference to FIG. First, the discharge side of the compressor 2 and the gas pipe 9B are connected by the flow path switch 3, and the outdoor heat exchanger 4 and the suction side of the compressor 2 are connected. The refrigerant enters the compressor 2 with a low-pressure gas and is compressed into a high-pressure gas. Thereafter, the refrigerant in the high-pressure gas state flows through the gas pipe 9 </ b> B and branches into a plurality of paths of the indoor heat exchanger (condenser) 7 through the header 8. As the refrigerant passes through the path in the indoor heat exchanger 7, the energy of the refrigerant is transferred to water or air on the load side. At this time, the refrigerant condenses to become a high-pressure liquid refrigerant, and heat-exchanged water and indoor air are heated.

  Thereafter, the high-pressure liquid refrigerant flows from the indoor heat exchanger (condenser) 7 into the expansion valve 5 through the capillary tube 6. In the expansion valve 5, the refrigerants that have passed through the plurality of paths of the indoor heat exchanger 7 are collected and reduced in pressure to be in a low-pressure two-phase state. The low-pressure two-phase refrigerant passes through the liquid pipe 9 </ b> A and reaches the outdoor heat exchanger 4. In the outdoor heat exchanger (evaporator) 4, the refrigerant absorbs the energy of outside air and air and evaporates to become low-pressure gas. Thereafter, the flow returns to the suction side of the compressor 2 via the flow path switch 3.

  As described above, the indoor heat exchanger 7 has a plurality of paths, and refrigerant distribution and aggregation are performed by the expansion valve 5. Here, FIG. 2A is a schematic cross-sectional view showing Embodiment 1 of the expansion valve of the present invention, and FIG. 2B is a schematic partial cross-sectional view showing Embodiment 1 of the expansion valve of the present invention, see FIGS. 2A and 2B. The expansion valve 5 will be described. In addition, in FIG. 2A, the case where the number of passes of the indoor side heat exchanger 7 is two is illustrated. The expansion valve 5 has a distribution function of distributing and condensing the refrigerant to each path of the indoor heat exchanger 7, and includes a main body unit 10, a valve body 13, and a partition part 20.

  The main unit 10 has a valve chamber BC and a refrigerant branch chamber SC that are partitioned by a partition wall 11. Specifically, the main body unit 10 includes a first housing 10a in which the valve chamber BC is formed, and a second housing 10b in which the refrigerant distribution chamber SC is formed. The first housing 10a is formed, for example, by cutting a brass cast product into a cylindrical shape, and has a flat partition wall 11 orthogonal to the cylindrical portion. In the first housing 10a, a valve chamber BC partitioned by the cylindrical portion and the partition wall 11 is formed. A connection port P1 leading to the valve chamber BC is formed on the side surface of the first housing 10a, and a pipe 30 leading to the liquid pipe 9A (see FIG. 1) is attached to the connection port. A refrigerant flows between the valve chamber BC and the liquid pipe 9 </ b> A via the connection port P <b> 1 and the pipe 30. The partition wall 11 is formed with a circular throttle portion 12 through which the valve chamber BC and the refrigerant distribution chamber SC communicate.

  The second housing 10b is formed, for example, in a cylindrical shape, one opening is attached to the partition wall 11 side, and the attachment member 14 in which a plurality of branch ports P2 are formed is fixed to the other opening. A branch pipe 15 is attached to each of the plurality of branch ports P2 of the attachment member 14 so as to protrude into the refrigerant distribution chamber SC by brazing or the like.

  The valve body 13 adjusts the opening degree of the throttle portion 12 and is disposed on the throttle portion 12 in the valve chamber BC. The valve body 13 has a conical tip, and is arranged so that the tip moves in the throttle portion 12 by a driving device (not shown) provided in the upper portion of the first housing 10a. And according to the position of this valve body 13, the passage area of the throttle part 12 of the micro passage formed by the periphery (valve seat) of the throttle part 12 and the valve body 13 changes, and the opening degree of the throttle part 12 is changed. Can be adjusted.

  The partition unit 20 partitions the refrigerant branch chamber SC for each of the plurality of branch ports P2, and is disposed in the refrigerant branch chamber SC. 3A is a schematic view showing a state of a partition portion in the second housing 10b of FIG. 2A, FIG. 3B is a schematic view showing a state of an AA ′ cross section in the first housing 10a of FIG. 2A, and FIG. 4 is an expansion of FIG. It is a schematic diagram which shows an example of the division part 20 in the valve 5, and the division part 20 is demonstrated with reference to FIGS. 4A is a schematic top view of the partition part 20, FIG. 4B is a schematic side view of the partition part 20, and FIG. 4C is a developed schematic view of the partition part 20, and the refrigerant is equally distributed to the two branch ports P2. An example of the case of distributing

  The partition portion 20 is integrally formed of, for example, plate-like stainless steel (SUS) and has a fixed piece 21, a partition wall 22, and an elastic piece 23. The fixing piece 21 is a part for fixing the partition part 20 in the refrigerant distribution chamber SC and is formed in a semicircular shape. The outer shape of the fixed piece 21 is the same as the inner diameter of the second housing 10b or smaller than the inner diameter of the second housing 10b. A hole 21a to be inserted into the branch pipe 15 is formed in the fixed piece 21. By inserting the branch pipe 15 into the hole 21a, the partition portion 20 is fixed to the mounting member 14 and brazed. The diameter of the hole 21a is substantially the same as the diameter of the branch pipe 15, or is formed so as to have a minute gap. The fixed piece 21 is fixed to the mounting member 14 and the branch pipe 15 by brazing or the like. The branch pipe 15 described above is projected into the refrigerant branch chamber SC so as to be connected to the fixed piece 21, and one branch pipe 15 among the plurality of branch pipes 15 is placed in the refrigerant branch chamber SC. It only has to protrude.

The partition wall 22 is a flat plate-like member extending from the fixed piece 21 toward the throttle portion 12, and divides the refrigerant branch chamber SC into a plurality of branch ports (see arrows in FIG. 2A). The width of the partition wall 22 is formed larger than the inner diameter of the second housing 10b, and both ends of the partition wall 22 are fixed to the inner peripheral surface of the second housing 10b. The upper edge 22 a of the partition wall 22 is located in the opening of the diaphragm 12 in a vertical view with respect to the partition wall 11. That is, as shown in FIG. 3B, in FIG. 2A, the partition wall is located at a position where the upper edge 22 a of the partition wall 22 can be seen through the opening of the throttle portion 12 when viewed downward from the valve chamber BC in the AA ′ cross-sectional direction. 22 is arranged.
The height of the partition wall 22 is formed to extend to a position directly below the throttle portion 12. Specifically, a recess 22b is formed in the approximate center of the upper edge 22a of the partition wall 22, and the distance D1 between the lowermost end of the recess 22b and the lower surface 11a of the partition wall 11 where the throttle portion 12 is open is It is formed to be smaller than the diameter R1 of the portion 12 (D1 <R1). That is, the maximum separation dimension between the lower surface 11a of the partition wall 11 where the throttle part 12 opens and the upper edge 22a of the partition wall 22 is smaller than the dimension of the diameter R1 of the throttle part 12. As described above, the upper edge 22a of the partition wall 22 (the lowermost end of the recess 22b) extends to a position directly below the throttle portion 12, so that the refrigerant immediately flows out of the throttle portion 12 and before it diffuses unevenly. Since the refrigerant is distributed, the refrigerant is distributed at the distribution ratio as designed for each branch port P2 regardless of the flow rate of the refrigerant and the state of the refrigerant, and generation of refrigerant flow noise can be minimized. The recess 22b is formed to prevent the valve element 13 from contacting the upper edge 22a of the partition wall 22.
In the first embodiment, the example in which the concave portion 22b is formed in the approximate center of the upper edge 22a of the partition wall 22 is shown. However, if the distance from which the valve body 13 does not contact is secured from the lower surface 11a of the partition wall 11, It is not necessary to form the recess 22b in the edge 22a. In this case, the distance D1 is a distance between the upper edge 22a of the partition wall 22 and the lower surface 11a of the partition wall 11 in which the throttle portion 12 is opened.

FIG. 2B is a partial schematic cross-sectional view showing Embodiment 1 of the expansion valve of the present invention.
As shown in FIG. 2B, a taper portion 22 c in which the plate thickness of the partition wall 22 decreases toward the throttle portion 12 side may be formed on the upper edge 22 a of the partition wall 22. By providing the tapered portion 22c on the upper edge 22a in this way, even if the upper edge 22a (recessed portion 22b) of the partition wall 22 is brought close to the throttle portion 12 and the refrigerant hits the upper edge 22a, the resistance of the refrigerant is reduced and the flow is divided. Therefore, refrigerant flow noise and pressure loss can be reduced.
Moreover, the partition wall 22 is arrange | positioned so that the refrigerant | coolant branch chamber SC may be divided | segmented according to the distribution ratio to several branch piping 15 (branch port P2). For example, when the distribution ratio to the two paths is equal, the sectional area of the refrigerant distribution chamber SC (the area of the throttle portion 12) is divided at an equal area ratio. As described above, since the distribution ratio is set as intended by changing the arrangement position of the partition wall 22, the distribution ratio can be easily set according to the type of the heat exchanger.

  The elastic piece 23 is in contact with the partition wall 11 and biases the partition wall 22 toward the fixed piece 21 by an elastic force, and is formed in a semicircular shape. The outer shape of the elastic piece 23 is the same as the inner diameter of the second housing 10b or smaller than the inner diameter of the second housing 10b. Further, an opening 23 a is formed in the elastic piece 23, and the refrigerant flows through the opening 23 a between the throttle portion 12 and the branch pipe 15. The diameter of the semicircle of the opening 23a is formed to be substantially the same as or slightly larger than the diameter of the throttle portion (valve seat) 12.

  Here, an example of the assembly procedure of the expansion valve 5 will be described with reference to FIGS. First, the second housing 10b, the valve body 13, and a driving device (not shown) are attached to the first housing 10a, and the first assembly assembly is assembled. On the other hand, the branch pipe 15 is inserted and fixed to the branch port P2 of the mounting member 14 so as to protrude. And the hole 21a of the division part 20 is inserted in the branch piping 15 protruded from the attachment member 14, and a 2nd assembly assembly is assembled. Thereafter, the second assembly assembly is attached to the first assembly assembly, and the expansion valve 5 is completed. At this time, the elastic piece 23 comes into contact with the partition wall 11 and the partition wall 22 is urged toward the mounting member 14, and the phase (rotation direction) of the mounting member 14 so that the partition wall 22 is positioned at a predetermined position. Is adjusted. Thus, after attaching the branch pipe 15 and the partition part 20 to the attachment member 14 side, the attachment member 14 is fixed to the second housing 10b, so that the restriction part 12 on the main body unit 10 side and the partition on the attachment member 14 side are provided. It is possible to easily align the phase (rotation direction) with the unit 20.

  A case where the refrigerant is distributed to the plurality of branch pipes 15 during the cooling operation in the expansion valve 5 will be described with reference to FIGS. 2 to 4. First, high-pressure liquid refrigerant enters the valve chamber BC from the pipe 30 and is depressurized in the throttle unit 12. At this time, the passage area in the throttle portion 12 is adjusted by the valve body 13. Then, the refrigerant becomes a uniform spray flow and flows from the valve chamber BC of the first housing 10a into the refrigerant distribution chamber SC of the second housing 10b. Thereafter, the refrigerant in the spray flow is distributed in the partition part 20 and flows into each branch pipe 15.

  Here, the smaller the flow path area in the throttle portion 12, the more the refrigerant flow tends to flow along the generatrix of the conical portion of the valve body 13. Therefore, when the refrigerant flows into the refrigerant branch chamber SC from the throttle portion 12, all the refrigerant flows collide with each other in the refrigerant branch chamber SC and affect each other. If the flow rate is small, the collision energy is small and the flow is not sufficiently uniform. At this time, the spraying flow immediately after the throttle unit 12 is branched regardless of the flow rate flowing through the expansion valve 5 by the partition unit 20, so that the refrigerant flows to the branch pipes 15 are prevented from affecting each other. Can do. Therefore, the refrigerant can be distributed to each branch pipe 15 at an intended distribution ratio regardless of the refrigerant flow rate and the refrigerant state. In particular, since the refrigerant is branched by the partition part 20 immediately below the throttle part 12, it can be distributed regardless of the flow rate.

  Further, when the refrigerant flow rate is large, there is a possibility that a refrigerant flow noise may be generated due to collision (front) with the wall surface of the refrigerant branch chamber SC when the refrigerant flow is branched. Further, when the refrigerant state in the pipe 30 is a gas-liquid two-phase state such as a slag flow or a plug flow, a discontinuous state in which gas and liquid alternately flow into the throttle portion 12 enters the refrigerant branch chamber SC. At this time, since it enters into the refrigerant branch chamber SC that is branched at the partition part 20 and expands the path, it is easy to diffuse the energy, and generation of discontinuous refrigerant flow noise can be suppressed. Moreover, since the partition part 20 is a plate-shaped member and the area of the normal part direction of the partition part 20 is small, generation | occurrence | production of a refrigerant | coolant flow noise can be suppressed. Furthermore, since the contact is made by the elasticity (spring) of the partition portion 20, sound generation due to vibration of the contact portion can be prevented.

  A case where the refrigerant is concentrated from the plurality of branch pipes 15 to the pipes 30 during the heating operation in the expansion valve 5 will be described with reference to FIGS. 2 to 4. First, the refrigerant flows into the refrigerant branch chamber SC of the second housing 10b from the plurality of branch pipes 15 and flows into the valve chamber BC of the first housing 10a through the throttle portion 12. Thereafter, the refrigerant in the valve chamber BC flows from the connection port P1 toward the liquid pipe 9A via the pipe 30.

  Here, when the refrigerant state passing through each branch pipe 15 is a gas-liquid two-phase state such as a slag flow or a plug flow, gas and liquid flow discontinuously from the throttle portion 12 into the valve chamber BC. In particular, when the refrigerant at the outlet of the indoor heat exchanger (condenser) 7 is in a gas-liquid two-phase state, the refrigerant is concentrated in the refrigerant branch chamber SC where the flow velocity becomes slow, so that the discontinuity of the gas-liquid becomes remarkable and the throttle Since the refrigerant flows into the portion 12, the refrigerant flow noise may increase. At this time, since the refrigerant flowing into the refrigerant branch chamber SC from each branch pipe 15 is aggregated immediately before entering the throttle section 12 (valve seat) without being affected by the partition section 20, a discontinuous refrigerant flow is generated. It is possible to suppress the occurrence of discontinuous refrigerant flow noise.

  As described above, according to the expansion valve 5, since the expansion valve 5 has a refrigerant distribution function, the refrigerant flow can be performed while performing distribution at an intended distribution ratio regardless of the refrigerant flow rate and the refrigerant state. Generation of sound can be suppressed. Further, since the refrigerant can be depressurized or expanded while having a distribution function, the number of parts is small, and space saving, high workability, and low cost can be achieved. In particular, when the diameter of the heat exchanger is reduced in order to reduce the refrigerant amount, the number of passes inevitably increases, but it is possible to cope with the increase in the number of passes without additionally providing a distributor.

  In the refrigerant branch chamber SC, the refrigerant can be in a uniform state, and the refrigerant can be evenly distributed. To intentionally distribute the refrigerant at different flow rates, a pipe connecting the branch pipe and the evaporator is used. There is no choice but to adjust the flow resistance (pipe length). Since the pressure loss increases accordingly, it is necessary to increase the required port diameter or pipe diameter of the expansion valve 5, which increases the cost. On the other hand, as described above, the distribution ratio can be adjusted depending on the position where the partition wall 22 is arranged, so that it can be easily set to the intended distribution ratio.

Embodiment 2. FIG.
FIG. 5 is a schematic view showing Embodiment 2 of the partition portion in the expansion valve of the present invention, and the partition portion 120 will be described with reference to FIG. 5A is a schematic top view of the partition part 120, FIG. 5B is a schematic side view of the partition part 120, FIG. 5C is a developed schematic view of the partition part 120, and FIG. 5D is AA ′ in the first housing 10a of FIG. The schematic diagram which shows the mode of a cross section is shown, respectively, In the partition part 120 of FIG. 5, the site | part which has the same structure as the partition part 20 of FIG. 4 is attached | subjected, and the description is abbreviate | omitted. The partition 120 in FIG. 5 is different from the partition 20 in FIG. 4 in the number of branches and the structure of the elastic piece 123.

  The partition 120 in FIG. 5 is attached to the mounting member 14 having the three branch ports P2, and is formed so as to partition the refrigerant distribution chamber SC into three spaces by bending a plate-like member. The A branch pipe 15 is inserted into each of the plurality of branch ports P2, and the fixed piece 121 is disposed on the two branch ports P2 and has a hole 121a for insertion into the two branch pipes 15. ing. Further, three partition walls 122 are formed on the fixed piece 121 corresponding to the three branch ports P2. The elastic piece 123 is formed of a plate-like piece that contacts the partition wall 11 while avoiding the throttle portion 12. As in the first embodiment, the upper edge 122 a of the partition wall 122 is located in the opening of the diaphragm 12 in a vertical view with respect to the partition wall 11. That is, as shown in FIG. 5D, in FIG. 2A, the partition wall is located at a position where the upper edge 122 a of the partition wall 122 can be seen through the opening of the throttle portion 12 when viewed from the inside of the valve chamber BC in the AA ′ cross-sectional direction. 122 is arranged.

A concave portion 122b is formed on the upper edge 122a of the partition wall 122, and a distance D1 between the lowermost end of the concave portion 122b and the lower surface 11a of the partition wall 11 where the throttle portion 12 opens is a diameter R1 of the throttle portion 12. (D1 <R1, see FIG. 2A). That is, the maximum distance between the lower surface 11a of the partition wall 11 where the aperture 12 is opened and the upper edge 122a of the partition wall 122 is smaller than the diameter R1 of the aperture 12. As described above, the upper edge 122a of the partition wall 122 (the lowermost end of the recess 122b) extends to a position immediately below the throttle portion 12, so that the refrigerant immediately flows out of the throttle portion 12 and diffuses unevenly. Since the refrigerant is distributed, the refrigerant is distributed at the distribution ratio as designed for each branch port P2 regardless of the flow rate of the refrigerant and the state of the refrigerant, and generation of refrigerant flow noise can be minimized. The recess 122b is formed to prevent the valve body 13 from contacting the upper edge 122a of the partition wall 122.
In the second embodiment, the example in which the concave portion 122b is formed in the approximate center of the upper edge 122a of the partition wall 122 is shown. However, if the distance that the valve body 13 does not contact is secured from the lower surface 11a of the partition wall 11, It is not necessary to form the recess 122b in the edge 122a. In this case, the distance D1 is a distance between the upper edge 122a of the partition wall 122 and the lower surface 11a of the partition wall 11 in which the throttle portion 12 is opened.
Further, as in the first embodiment, the upper edge 122a of the partition wall 122 may be formed with a tapered portion in which the thickness of the partition wall 122 decreases toward the throttle portion 12 as shown in FIG. 2B. .

  Even in such a partition part 120, as in the first embodiment, it is possible to suppress the generation of refrigerant flow noise while performing distribution according to the intended distribution ratio regardless of the refrigerant flow rate and the refrigerant state. In particular, when the diameter of the heat exchanger is reduced in order to reduce the refrigerant amount, the number of passes inevitably increases, but it is possible to cope with the increase in the number of passes without additionally providing a distributor.

Embodiment 3 FIG.
6A is a schematic diagram showing Embodiment 3 of the expansion valve of the present invention, and FIG. 6B is a schematic diagram showing a cross-sectional view taken along the line AA ′ in the first housing 10a of FIG. 6A. Refer to FIGS. 6A and 6B. The expansion valve 205 will be described. In addition, in the expansion valve 205 of FIG. 6A, the same code | symbol is attached | subjected to the site | part which has the same structure as the expansion valve 5 of FIG. 2A, and the description is abbreviate | omitted. 6A is different from the expansion valve 5 in FIG. 2A in that the partition 220 is made of a wall surface of the branch pipe 15.

6A, an auxiliary housing 10c is fixed to the second housing 10b by brazing or the like, and an attachment member 14 having a branch port is attached to the auxiliary housing 10c. The plurality of branch pipes 15 are arranged in the refrigerant distribution chamber SC in a state of extending from the branch port P2 to just below the throttle portion 12. And the wall surface of the branch pipe 15 functions as the partition part 220, and in the refrigerant | coolant branch chamber SC, it divides into the space inside the branch pipe 15, and the external space. In other words, the refrigerant that has flowed out of the throttle portion 12 flows into each branch pipe 15 immediately below the throttle portion 12.
As in the first and second embodiments, the upper edge 220 a of the partition part 220 (branch pipe 15) is located in the opening of the throttle part 12 in a vertical view with respect to the partition wall 11. That is, as shown in FIG. 6B, in FIG. 6A, the partitioning portion is located at a position where the upper edge 220a of the partitioning portion 220 can be seen through the opening of the throttle portion 12 when viewed downward in the valve chamber BC in the AA ′ cross-sectional direction. 220 is arranged.

Further, the distance D1 between the upper edge 220a of the partition 220 and the lower surface 11a of the partition wall 11 where the diaphragm 12 opens is formed to be smaller than the diameter R1 of the diaphragm 12 (D1 <R1). As described above, since the upper edge 220a of the partition part 220 extends to a position immediately below the throttle part 12, the refrigerant is distributed immediately after flowing out from the throttle part 12 and before spreading unevenly. Regardless of the size of the refrigerant and the state of the refrigerant, the refrigerant is distributed at the distribution ratio as designed for each branch port P2, and generation of refrigerant flow noise can be minimized.
As in the first and second embodiments, the upper edge 220a of the partition part 220 is formed with a tapered part in which the plate thickness of the partition part 220 decreases toward the throttle part 12 as shown in FIG. 2B. Also good.

  As described above, even when the partition 220 is formed of a branch pipe, the distribution can be performed with the intended distribution ratio regardless of the refrigerant flow rate and the refrigerant state. In addition, since the branch pipe 15 also serves as the partition portion 20, the number of parts is small, and the cost and the work efficiency can be improved. Furthermore, since the partition part 220 (branch pipe 15) is not in direct contact with the second housing 10b in the refrigerant distribution chamber SC, it is possible to prevent the generation of noise due to the installation of the partition part 220.

  Further, when assembling the expansion valve 205 described above, the second assembly assembly is assembled by fixing the attachment member 14 to the auxiliary housing 10c with the plurality of branch pipes 15 attached thereto, and the auxiliary housing 10c is assembled to the first assembly. It is designed to be fixed to the assembly. Thereby, the operation | work which attaches the attachment member 14 to main body unit 10 itself becomes unnecessary, and an assembly operation can be performed efficiently. Further, since the distance between the joining position of the branch port P2 and the branch pipe 15 in the mounting member 14 and the joining position of the second housing 10b and the auxiliary housing 10c can be separated, the mounting member 14 The possibility of remelting the brazed portion with the branch pipe 15 is low, and the workability is improved.

Embodiment 4 FIG.
FIG. 7 is a schematic view showing the fourth embodiment of the expansion valve of the present invention, FIG. 8A is a schematic view showing a state of a partitioning portion in the second housing 10b of FIG. 7, and FIG. 8B is an A- in the first housing 10a of FIG. FIG. 7 is a schematic view showing a state of an A ′ cross section, and the expansion valve 305 will be described with reference to FIGS. 7, 8A, and 8B. 7, 8 </ b> A, and 8 </ b> B, portions where the expansion valve 305 has the same configuration as the expansion valve 5 of FIG. 2 are denoted by the same reference numerals, and description thereof is omitted. The expansion valve 305 of FIGS. 7, 8A, and 8B is different from the expansion valve 5 of FIG.

  7, 8 </ b> A, and 8 </ b> B are made of a single member integrally formed of resin or a metal such as casting or forging. For example, the partition 320 has the same outer shape as the inner surface of the refrigerant branch chamber SC, and has a cylindrical shape that is the same as or smaller than the radius of the second housing 10b. Thereby, generation | occurrence | production of the noise by the division part 320 contacting the inner peripheral surface of the 2nd housing 10b is prevented.

A plurality of through holes 320 a extending from the narrowed portion 12 to the branch port P <b> 2 are formed in the partition portion 320, and an annular leaf spring 321 is disposed between the partition wall 11 and the partition portion 320. Each through hole 320a is curved so that the cross-sectional area decreases from the narrowed portion 12 toward the branch port P2, and adjacent through holes 320a are partitioned by a plate-like portion having a curved surface. Further, the leaf spring 321 urges the partition part 320 toward the mounting member 14 to suppress the generation of mechanical sound due to the vibration of the partition part 320. In the attachment member 14 of FIG. 7, the branch pipe 15 does not protrude from the branch port P2 to the refrigerant branch chamber SC side, and the distributed refrigerant flows directly into the branch port P2.
As in the first to third embodiments, the upper edge 320 b of the partition part 320 is located in the opening of the throttle part 12 in a vertical view with respect to the partition wall 11. That is, as shown in FIG. 8B, in FIG. 7, the upper edge is located at a position where the upper edge 320b of the partition part 320 can be seen through the opening of the throttle part 12 when looking downward in the valve chamber BC in the AA ′ cross-sectional direction. 320b is arranged.

In addition, a recess 320c is formed in the upper edge 320b of the partition part 320, and the distance D1 between the lowermost end of the recess 320c and the lower surface 11a of the partition wall 11 where the throttle part 12 opens is the diameter R1 of the throttle part 12. (D1 <R1). That is, the maximum separation dimension between the lower surface 11a of the partition wall 11 where the throttle part 12 opens and the upper edge 320b of the partition part 320 is smaller than the dimension of the diameter R1 of the throttle part 12. As described above, the upper edge 320b of the partition 320 (the lowermost end of the recess 320c) extends to a position directly below the throttle 12, so that the refrigerant has just flowed out of the throttle 12 and before it diffuses unevenly. Since the refrigerant is distributed, the refrigerant is distributed at the distribution ratio as designed for each branch port P2 regardless of the flow rate of the refrigerant and the state of the refrigerant, and generation of refrigerant flow noise can be minimized. In addition, the recessed part 320c is formed in order to prevent the valve body 13 from contacting the upper edge 320b of the partition part 320. FIG.
In the fourth embodiment, the example in which the concave portion 320c is formed on the upper edge 320b of the partition portion 320 is shown. However, if the distance from which the valve body 13 does not contact is secured from the lower surface 11a of the partition wall 11, the concave portion is formed on the upper edge 320b. There is no need to form 320c. In this case, the distance D1 is a distance between the upper edge 320b of the partition part 320 and the lower surface 11a of the partition wall 11 where the throttle part 12 opens.
Further, as in the first to third embodiments, the upper edge 320b of the partition part 320 is formed with a tapered part in which the plate thickness of the upper edge 320b decreases toward the throttle part 12 as shown in FIG. 2B. Also good.

  Even with the expansion valve 305 having such a structure of the partition 320, the refrigerant can be distributed at an intended distribution ratio regardless of the refrigerant flow rate and the refrigerant state, as in the first to third embodiments. At the same time, generation of refrigerant flow noise can be suppressed. Moreover, since the partition part 320 is made of an integrally molded product, the number of parts is small, and the cost and workability can be improved.

Embodiment 5 FIG.
FIG. 9 is a schematic view showing Embodiment 5 of the refrigeration cycle apparatus of the present invention. The refrigeration cycle apparatus 400 will be described with reference to FIG. In addition, the part which the refrigerating cycle apparatus 400 of FIG. 9 has the same structure as the refrigerating cycle apparatus 1 of FIG. 1 attaches | subjects the same code | symbol, and abbreviate | omits the description. The refrigeration cycle apparatus 400 of FIG. 9 is different from the refrigeration cycle apparatus 1 of FIG. 1 in that the outdoor heat exchanger 404 of the outdoor unit 400A is a multi-pass heat exchanger, and an expansion valve having a distribution function is used. It is a point. In addition, although the case where the expansion valve 5 of FIG. 2 is used is illustrated, the expansion valves 205 and 305 of FIGS. 5 and 6 may be used.

  The refrigeration cycle apparatus 400 has a configuration in which a plurality of indoor units 1B are connected to a single outdoor unit 400A. Furthermore, the outdoor unit 400A has an accumulator 405 on the suction side of the compressor 2. The accumulator 405 stores surplus refrigerant or surplus refrigerant with respect to a transient change in operation. The accumulator 405 is supplied with refrigerant from the flow path switching unit 3 side and to the suction side of the compressor 2 via the suction pipe 9. A refrigerant is supplied.

  Here, the outdoor heat exchanger 404 is connected to the flow path switching unit 3 through the header 403 and is connected to the liquid pipe 9 </ b> A through the expansion valve 5. During the cooling operation, the expansion valve 5 collects the refrigerant that has flowed out from each path of the outdoor heat exchanger 404 and flows out toward the liquid pipe 9A. On the other hand, during the heating operation, the expansion valve 5 distributes the refrigerant flowing from the liquid pipe 9A to each path of the outdoor heat exchanger 404 and flows out.

  As described above, the outdoor heat exchanger 404 can use the expansion valve 5 in which the refrigerant flow noise is suppressed at the intended distribution ratio with respect to the multi-pass heat exchanger. In addition, since the liquid pipe density is reduced by providing the expansion valves 5 on the outdoor unit 400A side and the indoor unit 1B side, respectively, the amount of refrigerant can be reduced. Furthermore, since the expansion valve 5 is provided at both ends of the liquid pipe 9A, the expansion valve 5 can be controlled so that the refrigerant in the liquid pipe 9A is in a gas-liquid two-phase state. Thereby, since the pressure loss of the refrigerant in the two-phase gas phase state is larger than the pressure loss of the liquid refrigerant, unnecessary pressure loss can be reduced.

  The embodiment of the present invention is not limited to the above embodiment. For example, the indoor heat exchanger 7 in FIG. 1 and the outdoor heat exchanger 404 in FIG. 9 exemplify the case where the number of passes is two, and FIG. 3 exemplifies the case where the number of passes is three. Four or more may be provided.

  2 and 5 exemplify the case where the main body unit 10 includes the first housing 10a and the second housing 10b as separate members, but may be integrally formed. . Further, in the first and second embodiments, the case where the branch pipe 15 protrudes from the branch port P2 toward the refrigerant distribution chamber SC is illustrated, but the fixing piece 21 is attached so that the hole 21a is positioned on the branch port P2. It may be fixed to the member 14.

  DESCRIPTION OF SYMBOLS 1,400 Refrigeration cycle apparatus, 1A, 400A outdoor unit, 1B indoor unit, 2 compressor, 3 flow path switch, 4, 404 outdoor heat exchanger, 5, 205, 305 expansion valve, 6 capillary tube, 7 chambers Inner heat exchanger, 8 header, 9 suction pipe, 9A liquid pipe, 9B gas pipe, 10 body unit, 10a first housing, 10b second housing, 10c auxiliary housing, 11 partition wall, 12 restrictor, 13 valve body, 14 Mounting member, 15 Branch pipe, 20, 120, 220, 320 Partition, 21, 121 Fixed piece, 21a, 121a Hole, 22, 122 Partition wall, 22a, 122a, 220a, 320b Upper edge, 22b, 122b, 320c Concave part, 22c taper part, 23, 123 elastic piece, 23a opening, 30 piping, 205 expansion valve, 320 Through hole, 321 a leaf spring, 404 header 405 accumulator, BC valve chamber, P1 connection port, P2 branch port, SC refrigerant flow chamber.

Claims (11)

A plurality of branch ports that have a valve chamber and a refrigerant branch chamber partitioned by a partition wall, and that have a throttle portion that opens between the valve chamber and the refrigerant branch chamber, and communicates with the refrigerant branch chamber; A main body unit formed with,
A valve body for adjusting the opening of the throttle part;
A plate-shaped partitioning portion that is disposed in the coolant branching chamber and partitions the coolant branching chamber for each of the plurality of branch ports;
With
At least a part of the upper edge of the partition part is located in the opening of the throttle part in a vertical view with respect to the partition wall ,
The expansion valve according to claim 1, wherein a maximum separation dimension between a lower surface of the partition wall where the throttle portion opens and an upper edge of the partition portion is smaller than a diameter of the throttle portion . On the upper edge of the partition part, a recess is formed at a position facing the throttle part,
2. The expansion valve according to claim 1 , wherein the maximum separation dimension is a separation dimension between a lower surface of the partition wall where the throttle portion is opened and a lower end of a concave portion of the upper edge. 3. The expansion valve according to claim 1, wherein a tapered portion having a thickness that decreases toward the throttle portion is formed at an upper edge of the partition portion. The main unit is
A first housing forming the valve chamber on one side of the partition wall;
The expansion valve according to any one of claims 1 to 3 , further comprising: a second housing that forms the refrigerant distribution chamber attached to the other surface side of the partition wall. The expansion valve according to claim 4 , wherein the main body unit includes an attachment member in which the plurality of branch ports attached to the second housing are formed. The said partition part is arrange | positioned so that the said refrigerant | coolant distribution chamber may be divided | segmented according to the distribution ratio of the refrigerant | coolant to these branch ports, The any one of Claims 1-5 characterized by the above-mentioned. Expansion valve. The partition portion includes a fixed piece fixed to the main body unit, a flat partition wall extending from the fixed piece toward the throttle portion, and a partition provided on the partition wall in contact with the partition wall. expansion valve according to any one of claims 1 to 6, characterized in that it has an elastic piece which urges the wall to the fixed side. Branch piping is inserted into the plurality of branch ports so as to protrude into the refrigerant distribution chamber,
8. The expansion valve according to claim 7 , wherein the fixed piece has a hole for inserting a protruding portion of the branch pipe, and the branch pipe is inserted into the hole and fixed to the main unit. The expansion valve according to any one of claims 1 to 6 , wherein the partition portion includes a wall surface of a plurality of branch pipes arranged to protrude from the branch port toward the throttle portion. The partition section is formed by forming a plurality of through holes connected from the throttle section to the branch port in one member having the same shape as the inner surface of the refrigerant distribution chamber. Item 7. The expansion valve according to any one of Items 1 to 6 . In a refrigeration cycle apparatus in which an indoor unit provided with an indoor heat exchanger and an outdoor unit provided with an outdoor heat exchanger are connected by piping,
The indoor heat exchanger and / or the outdoor heat exchanger is a multi-pass heat exchanger having a plurality of paths,
The chamber is the inner heat exchanger and / or the chamber outer heat exchanger, the refrigeration cycle apparatus characterized by the expansion valve is connected according to any one of claims 1-10.

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