JP2009222366A - Refrigerant distributor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To obtain a refrigerant distributor capable of suitably distributing an arbitrary flow rate of a refrigerant to each refrigerant passage while maintaining low cost and saving on space, and hardly generating jamming of foreign objects. <P>SOLUTION: The refrigerant distributor, comprising a large number of heat transfer tubes 31 for flowing the refrigerant in parallel, is connected to a heat exchanger 3 which operates as an evaporator and distributes the refrigerant to the large number of heat transfer tubes for flowing the refrigerant through them. The refrigerant distributor is equipped with a header 57 arranged to be elongated along an inlet side of the many transfer tubes, and a large number of liquid branching pipes 58a-58e branched from the header and respectively extending in a linear fashion. The liquid branching pipes are connected to the inlet side of the many heat transfer tubes, and a spiral groove is formed on an inner face of the liquid branching pipe. The necessary flow rate of the refrigerant can be flowed to the refrigerant passages by choosing suitable dimensions of the spiral groove such as an inner diameter or length. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a refrigerant distributor, and is suitable as a refrigerant distributor that distributes refrigerant to a heat exchanger that mainly operates as an evaporator in an air conditioner or the like.

  On the refrigerant inlet side of a heat exchanger that operates as an evaporator used in an air conditioner, a refrigerant distributor for diverting a plurality of refrigerant passages is used.

  A conventional refrigerant distributor is described in Japanese Patent Laid-Open No. 2-17368 (Patent Document 1). In this refrigerant distributor, the refrigerant in which the refrigerant in the gas-liquid two-phase state before entering the evaporator is compressed through the orifice is introduced and mixed into the gas-liquid mixing chamber, and the mixed refrigerant is derived by a plurality of branch pipes. It is disclosed that a distributor is provided which is introduced into a plurality of heat transfer tubes constituting the evaporator. According to this, since the gas-liquid two-phase refrigerant can be mixed in the gas-liquid mixing chamber in advance, the gas-liquid two-phase refrigerant can be evenly distributed to each branch pipe.

  On the other hand, as another conventional refrigerant distributor, there is one described in Japanese Patent Laid-Open No. 2002-22313 (Patent Document 2). This refrigerant distributor is composed of a container having a large number of refrigerant pipe connection ports in the longitudinal direction and an inflow pipe inserted from one end of the container to the vicinity of the opposite side, and the refrigerant flows between the container and the inflow pipe. Thus, the flow rate of the refrigerant is increased to maintain the mixed state of the gas phase and the liquid phase, and the refrigerant in the lower refrigerant pipe and the upper refrigerant pipe can be evenly divided.

  Still another conventional refrigerant distributor is described in Japanese Patent Application Laid-Open No. 2001-133308 (Patent Document 3). In this prior art, an orifice-shaped flow control plate is incorporated on the upstream side of the branch pipe, and the flow rate is controlled by making a difference in the orifice inner diameter of each branch pipe.

Japanese Patent Laid-Open No. 2-17368 JP 2002-22313 A Japanese Patent Laid-Open No. 2001-133078

  When the refrigerant distributor of Patent Document 1 is arranged at the evaporator inlet, a large space is required due to the structure of the distributor and the branch pipe, and there is a problem that the unit sizes of the indoor unit and the outdoor unit become large. In addition, when the distance between the distributor and the heat transfer tube connecting portion is long, there is a problem that the material cost becomes high because the branch tube becomes long.

  On the other hand, the refrigerant distributor of Patent Document 2 requires an inflow pipe that is inserted from one end of the container to the vicinity of the opposite side, thereby increasing the cost and increasing the flow rate of the refrigerant to equally distribute the refrigerant. For this reason, there has been a problem that even when the refrigerant circulation rate is reduced, the refrigerant cannot be evenly distributed.

  Furthermore, when the vertical velocity distribution of the air passing through the heat exchanger is large, it is desirable to make a difference in the refrigerant flow rate flowing through each branch pipe, but this is not taken into consideration in the distributor of Patent Document 2, When adjusting the inner diameter of the branch pipe with a difference, if the branch pipe is shortened because the distance from the header to the heat transfer pipe is small, the inner diameter of the branch pipe needs to be extremely small, and foreign matter such as metal powder There is a problem that (contamination) is easily clogged and reliability cannot be secured.

  However, in this prior art, when the flow rate flowing through the branch pipe is greatly reduced, the inner diameter needs to be extremely reduced. In this case, there is a problem that foreign matters in the cycle are easily blocked by the flow path.

  Moreover, in the thing of patent document 3, since the flow volume is adjusted only by the difference in orifice internal diameter, the request | requirement with respect to the dimensional accuracy becomes high, and processing cost increases. Furthermore, the flow of the refrigerant is disturbed by a sudden change of the flow path by the orifice, and an unpleasant flow noise is likely to be generated.

  An object of the present invention is to obtain a refrigerant distributor capable of appropriately distributing an arbitrary refrigerant flow rate for each refrigerant passage while maintaining low cost and space saving and preventing generation of unpleasant flow noise. .

  In order to achieve the above object, a feature of the present invention is that it has a large number of heat transfer tubes that flow refrigerant in parallel and is connected to a heat exchanger that operates as an evaporator, and distributes and flows the refrigerant to the plurality of heat transfer tubes. The refrigerant distributor includes a distribution section and a plurality of branch pipes branched from the distribution section and extending linearly or curvedly, and the branch pipes are connected to the inlet sides of the plurality of heat transfer tubes. The inner surface of the branch pipe is provided with a spiral resistance portion for adjusting the flow resistance of the refrigerant flowing through the inner surface of the branch pipe.

  Another feature of the present invention is a refrigerant distributor that has a large number of heat transfer tubes that flow refrigerant in parallel and is connected to a heat exchanger that operates as an evaporator, and distributes and distributes the refrigerant to the multiple heat transfer tubes. A header provided long along the inlet side of the plurality of heat transfer tubes; and a plurality of branch tubes branched from the header and extending in a straight line or a curved shape. In addition to being connected to the inlet side of the heat transfer tube, a spiral groove is formed on the inner surface of the branch tube.

  Here, the dimensions (length, inner diameter, etc.) of the spiral groove formed on the inner surface of the branch pipe are appropriately distributed to each refrigerant passage by giving a difference to each branch pipe. Can do. The spiral groove formed on the inner surface of the branch pipe may have a length of 20 to 160 mm and an inner diameter of 1.6 to 3.0 mm.

  Further, a homogeneous flow lower portion connected to the inlet side to the header and having a flow passage cross-sectional area larger than the flow passage cross-sectional area of the header is provided, and a porous body having fine holes is disposed in the body of the homogeneous flow lower portion. Good. Here, it is further preferable to install a mesh filter on the inlet side and the outlet side of the porous body provided in the body of the homogeneous flow lower part.

  Still another feature of the present invention is a refrigerant distributor having a plurality of heat transfer tubes for flowing refrigerant in parallel and connected to a heat exchanger operating as an evaporator, and distributing and flowing the refrigerant to the plurality of heat transfer tubes. , A header long disposed along the inlet side of the plurality of heat transfer tubes, and a plurality of branch tubes branched in a large number from the header and extending in a straight line or a curve, respectively. In addition to being connected to the inlet side of a large number of heat transfer tubes, a piece having a spiral groove shape or a spiral spring-like member is inserted and installed on the inner surface of the branch tube.

  According to the present invention, a large number of branch pipes are provided that extend in a branched manner from the distribution section (header). On the inner surface of the branch pipe, a spiral groove, a piece having a spiral groove shape, or a spiral spring-like member is provided. Therefore, the installation space for the refrigerant distributor can be reduced, and the device can be downsized. Further, since the refrigerant distribution can be optimized according to the velocity distribution of the intake air passing through the heat exchanger, the performance of the heat exchanger can be maximized. Further, since the structure can be simplified, the manufacturing cost can be reduced. In addition, since a resistance portion having a spiral shape is provided to provide the required flow path resistance to each branch pipe, the required flow path resistance can be generated without an extremely small flow path cross-sectional area. There is an effect that the reliability of the air conditioner and the like can be improved by minimizing the risk that the road is blocked by foreign matter (contamination) in the refrigeration cycle. Furthermore, since the flow rate is adjusted by the spiral resistance portion provided on the inner surface of the branch pipe, the length of the spiral resistance portion is reduced without the rapid contraction or expansion of the flow path as in the case where the orifice is provided. Further, since the flow of the refrigerant is not easily disturbed, an unpleasant flow noise can be prevented and any refrigerant flow rate can be appropriately distributed for each refrigerant passage. Furthermore, compared with the case of adjusting the flow rate by providing an orifice, it is possible to adjust the flow rate with a high degree of freedom by selecting various dimensions such as the inner diameter, length, groove height, and twist angle of the spiral resistance portion. Since high dimensional accuracy is not required, machining costs can be reduced.

  Hereinafter, specific embodiments of the present invention will be described with reference to the drawings.

  FIG. 1 shows an example of a refrigeration cycle using the refrigerant distributor of the present invention. In FIG. 1, the solid line arrows indicate the refrigerant flow during the cooling operation, and the broken line arrows indicate the refrigerant flow during the heating operation.

  A refrigeration cycle during heating operation indicated by a broken line arrow will be described. The gas refrigerant compressed by the compressor 1 and having a high temperature and high pressure passes through the four-way valve 2, passes through the gas blocking valve 10 and the gas side connection pipe 9, and is guided to the indoor unit 200. The refrigerant guided to the indoor unit 200 is cooled and condensed by the indoor air blown by the indoor blower 33 in the indoor heat exchanger 8, and becomes a liquid refrigerant. The indoor heat exchanger 8 acts as a condenser during heating operation. This liquid refrigerant passes through the indoor expansion valve 7 in the open state (normally fully open), returns to the outdoor unit 100 side through the liquid side connection pipe 6 and the liquid blocking valve 5.

  The liquid refrigerant returned to the outdoor unit 100 is depressurized and boiled by the outdoor expansion valve 4 and enters a gas-liquid two-phase state. As shown in FIG. 2, the gas-liquid two-phase refrigerant flows into the homogeneous flow lower part 50, and the gas phase and liquid phase of the two-phase flow are refined and uniformized. After that, the liquid header 57 branches upward to a plurality of liquid branch pipes (branch pipes) 58 while flowing upward. The refrigerant branched into each liquid branch pipe 58 flows into each heat transfer pipe 31 of the outdoor heat exchanger 3 and is heated and evaporated by the outdoor air blown by the outdoor blower 30 to become a gas refrigerant. The outdoor heat exchanger 3 acts as an evaporator during heating operation. The gas refrigerant from the outdoor heat exchanger 3 passes through the four-way valve 2 and returns to the compressor 1 through the accumulator 11. This constitutes a series of refrigeration cycles through which the refrigerant circulates.

  Here, HFC refrigerants such as R410A, R404A, R407C, and R134a are generally used as refrigerants in the refrigeration cycle, but natural refrigerants such as carbon dioxide, ammonia, propane, and isobutane, or R32, HFO-1234yf. And by using refrigerants with low GWP (Global Warming Potential) such as mixtures of these, the direct impact of global warming caused by refrigerant leakage from air conditioners and refrigerant leakage during recovery Can be reduced.

  Further, by switching the four-way valve 2 as shown by the solid line in FIG. 1, the flow direction of the refrigerant is switched, and the cooling operation can be performed. In this case, the outdoor heat exchanger 3 functions as a condenser and the indoor heat exchanger 8 functions as an evaporator.

  Next, the configuration and operation of the outdoor heat exchanger 3 that functions as an evaporator during the heating operation and the refrigerant distributor 40 provided on the outdoor heat exchanger side will be described with reference to FIGS.

  As shown in FIG. 2, the outdoor heat exchanger 3 is configured by a finned tube heat exchanger including a large number of heat transfer tubes 31 and fins 32 that flow refrigerant in parallel. The heat transfer tube 31 is formed of a U-shaped tube, and the inlet side and the outlet side of each heat transfer tube 31 are positioned on one surface of the heat exchanger, and a large number of heat transfer tubes 31 are arranged in the vertical direction.

  The refrigerant distributor 40 provided on the outdoor heat exchanger side is for distributing and flowing the refrigerant to the large number of heat transfer tubes 31 of the outdoor heat exchanger 3, and as shown in FIG. A liquid branch pipe 58, a homogeneous flow lower part 50, a gas header 70 and a gas branch pipe 71 are provided.

  The liquid header 57 is disposed so as to extend long in the vertical direction so as to face the inlets of the heat transfer tubes 31. The flow path cross-sectional area of the liquid header 57 is set larger than the flow path cross-sectional areas of the heat transfer pipe 31 and the liquid branch pipe 58. A number of liquid branch pipes 58 are branched from the liquid header 57 and extend in a straight line, and their tip ends are connected to the inlet side of each heat transfer pipe 31.

  Here, as shown in FIG. 3, the liquid branch pipe 58 has a spiral groove (spiral resistance portion) formed on the inner surface thereof, and with respect to the refrigerant flowing through each refrigerant passage (including the liquid branch pipe). I try to give resistance. The amount of the refrigerant flowing in each passage can be arbitrarily determined by using the spiral grooves provided in the liquid branch pipes 58a to 58e having different dimensions such as the length, pitch or groove height of the spiral grooves. It becomes possible to adjust.

  As shown in FIGS. 2 and 4, the homogeneous flow lower part 50 is connected to an inlet side of the liquid header 57 and has a body 51 having a channel cross-sectional area larger than the channel cross-sectional area of the liquid header 57, and the inside of the body 51. It is comprised from the porous body 53 etc. which are arrange | positioned in the intermediate part of this, and have a fine hole. The porous body 53 is fixed by caulking 55a, 55b so that there is no gap between the porous body 53 and the body 51.

  For this reason, all of the gas-liquid two-phase refrigerant flowing in from the inlet 52 passes through the porous body 53 and flows out from the outlet 54 to the liquid header 57. Here, the porous body 53 is composed of a sintered body of nickel metal or aluminum alloy or a compression member of a demister material, and the pores and gaps are formed to have a size of about 0.3 to 1.0 mm. I am using something.

  FIG. 5 shows another example of the homogeneous flow lower part 50 shown in FIG. In the example of FIG. 5, mesh filters 56 a and 56 b are arranged on both front and rear sides of the porous body 53. Specifically, the inlet-side mesh filter 56 a having a mesh diameter smaller than the average pore diameter of the porous body 53 on the inlet side of the porous body 53, and the outlet area of the porous body 53 on the outlet side of the porous body 53 is larger. A mesh filter 56b having a channel area and a mesh diameter smaller than the average pore diameter of the porous body 53 is provided. The mesh filter 56a on the inlet side is formed so as to protrude in a conical shape on the inlet side, and the mesh filter 56b on the outlet side is formed so as to protrude in a conical shape on the outlet side. As the mesh filters 56a and 56b, those having a mesh size finer than the average pore size of 0.3 to 1.0 mm are used, and for example, those having a mesh size of 100 mesh (0.254 mm pitch) are used.

  By providing the mesh filters 56a and 56b in this way, it is possible to prevent foreign matters (contamination) such as metal powder in the refrigeration cycle from being clogged in the gap between the porous bodies.

  The gas header 70 is disposed so as to extend in the vertical direction along the outlet sides of the large number of heat transfer tubes 31 so as to face the outlet sides. The flow path cross-sectional area of the gas header 70 is set larger than the flow path cross-sectional areas of the heat transfer pipe 31 and the gas branch pipe 71. A large number of gas branch pipes 71 are branched from the gas header 70 and extend in a straight line, and their tips are connected to the outlet side of each heat transfer pipe 31. The liquid header 57 and the gas header 70 are disposed adjacent to each other on the left and right.

  The liquid refrigerant that has flowed into the outdoor unit 100 during the heating operation is reduced in pressure and boiled when passing through the outdoor expansion valve 4 to be in a gas-liquid two-phase state. The gas phase and liquid phase of the phase flow are made fine and uniform. For this reason, since the gas-liquid two-phase flow is kept homogenized at the inlet of the liquid branch pipe 58, the dryness (gas phase mass flow ratio) of any of the liquid branch pipes 58 from the lower part to the upper part is maintained. Are equal. Therefore, in the case where the outdoor air passing through the outdoor heat exchanger 3 has a substantially uniform wind speed distribution, if the refrigerant flow rate and the dryness are equally distributed, which state of the refrigerant is in the gas branch pipe 71 at the heat exchanger outlet? Even in the flow path, the refrigerant state has substantially the same specific enthalpy, and as a result, the heat exchange amount of the heat exchanger can be maximized. FIG. 6 shows the relationship of the refrigerant flow rate with respect to the wind speed distribution in this almost uniform wind speed distribution state.

  On the other hand, when the outdoor air passing through the outdoor heat exchanger 3 has a non-uniform wind speed distribution, the performance of the heat exchanger is not adjusted unless the refrigerant flow rate of each refrigerant flow path is adjusted as shown in FIG. Can not be maintained. In such a case, a difference is made in the inner diameter, length, groove height, pitch, twist angle, and the like of the spiral groove formed on the inner surface of each liquid branch pipe 58 in accordance with the wind speed distribution. The flow rate can be adjusted as shown in FIG.

  FIG. 8 shows the measured flow resistance at the time of refrigerant flow in a spiral pipe provided with a spiral groove and a smooth pipe without a spiral groove. Here, the shape of the inner spiral groove used for the measurement is a metric coarse screw M5 (inner diameter: 4.134 mm, groove height: 0.433 mm) defined in JIS B0205. From this measurement result, it can be confirmed that the spiral grooved tube has about twice the pressure loss of the smooth tube in the tube having the same inner diameter. From this, in order to obtain the flow path resistance necessary for adjusting the refrigerant flow rate, the length of the spiral grooved tube can be reduced to half or less. Therefore, in the header type refrigerant distributor, it is possible to reduce the distance between the header and the heat exchanger, and it is possible to save the space of the device and reduce the cost of the branch pipe material. In addition, it is not necessary to select a pipe having an extremely small inner diameter of the branch pipe, and it is possible to prevent the blockage of the flow path due to foreign matters in the refrigeration cycle such as metal powder, and the reliability can be improved.

  Next, FIG. 9 shows an example in which the inner diameter and the required length of the spiral groove for each refrigerant passage (branch pipe) are examined for a heat exchanger having a wind speed distribution as shown in FIG. In a heat exchanger having a wind speed distribution as shown in FIG. 7, the required flow path resistance for each refrigerant path is different. Moreover, since the required length of the refrigerant flow path is shortened as the inner diameter of the inner spiral groove is smaller, the material cost of the branch pipe with the spiral groove is reduced. On the other hand, there is an increased risk that the branch pipe will be blocked by foreign matter, and high groove processing accuracy is required, which increases the processing cost. Therefore, it is desirable to select the inner diameter of the spiral groove portion from 1.6 to 3.0 mm and the length from 20 to 160 mm.

  Examples of the spiral groove shape in the liquid branch pipe 58 are shown in FIGS. It is desirable that the distance between the liquid header 57 and the heat transfer pipe 31 be the same in any refrigerant passage, and that all the liquid branch pipes 58 have the same length, because this leads to simplification of the structure. For this purpose, it is necessary to change the length of the spiral groove. In FIG. 10, the length of the inner spiral groove is Lm with respect to the total length Lt of the liquid branch pipe 58, and the remaining portion has an inner diameter larger than the outer diameter of the groove. With this structure, it is possible to arbitrarily select the length of the spiral groove without changing the length of the liquid branch pipe 58.

  In the example of the liquid branch pipe 58 shown in FIG. 11, a piece 59 having a spiral groove shape is inserted into the liquid branch pipe 58 and the piece 59 is fixed by caulking 62. When this structure is used, the inner surface groove-shaped piece 59 having an arbitrary length can be selected and used. Moreover, if the pipe which processed the spiral groove process is processed, and it cut | disconnects to length suitably after that and will make a piece, processing cost can be reduced.

  In the example of FIG. 12, instead of forming a spiral groove on the inner surface of the branch pipe or inserting a piece having the spiral groove shape shown in FIG. 11, a spring-like member 61 is inserted. The cross-sectional shape of the wire constituting the spring-like member is generally circular, but if it is made trapezoidal, etc., it can realize a spiral groove shape close to the inner surface shape of the screw when wound in a spring shape. It is more desirable to select a shape. Further, in this structure, there is no need for grooving, and only the spiral winding process of the wire is performed, so that the processing cost can be further reduced as compared with the case of using another structure described above.

  As described above, in the case of the heating operation in which the outdoor heat exchanger 3 operates as an evaporator, the refrigerant distributor 40 connected to the outdoor heat exchanger has been described, but the indoor heat exchanger 8 functions as an evaporator. Even in the cooling operation, the configuration and operation of the refrigerant distributor 60 connected to the indoor heat exchanger are basically the same as those of the refrigerant distributor connected to the outdoor heat exchanger. Is omitted. However, since the indoor unit 200 is generally smaller in size required for the unit than the outdoor unit 100, more space is required and the distribution of air passing through the indoor heat exchanger tends to be biased. strong. Therefore, the effect when the refrigerant distributor of the present invention is applied is further increased.

It is a refrigerating cycle block diagram of the air conditioner provided with the refrigerant distributor of the present invention. It is a detailed explanatory drawing (at the time of heating operation) of the outdoor heat exchanger shown in FIG. 1 and its periphery. It is a figure which shows the cross-section of the refrigerant distributor shown in FIG. It is sectional drawing of the homogeneous flow lower part in the refrigerant distributor shown in FIG. It is a figure which shows the other example of a homogeneous flow lower part, and is a figure equivalent to FIG. It is a diagram which shows an example of a refrigerant | coolant flow volume and wind velocity distribution at the time of the heat exchanger provided with the refrigerant distributor of this invention acting as an evaporator. It is a figure which shows the other example of a refrigerant | coolant flow volume and wind speed distribution, and is equivalent to FIG. It is the diagram which measured the channel resistance at the time of the refrigerant | coolant distribution | circulation in the thing which provided the spiral groove in the branch pipe inner surface, and the smooth pipe which does not provide a spiral groove. It is a diagram which shows the example which examined the internal diameter and required length of the spiral groove for every refrigerant path with respect to the heat exchanger which has a wind speed distribution as shown in FIG. It is sectional drawing which shows an example of the branch pipe part in the refrigerant distributor of this invention. It is sectional drawing which shows the other example of the branch pipe part in the refrigerant distributor of this invention. It is sectional drawing which shows the further another example of the branch pipe part in the refrigerant distributor of this invention.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Compressor 2 Four-way valve 3 Outdoor heat exchanger 4 Outdoor expansion valve 5 Liquid blocking valve 6 Liquid side connection piping 7 Indoor expansion valve 8 Indoor heat exchanger 9 Gas side connection piping 10 Gas blocking valve 11 Accumulator 31 Heat transfer tube 32 Fin 40 Outdoor refrigerant distributor 50 Homogeneous flow lower part 51 Body 52 Inlet 53 Porous body 54 Outlet 55a, 55b, 62 Caulking 56a, 56b Mesh filter 57 Liquid header 58, 58a-58e Liquid branch pipe (branch pipe)
59 pieces 60 indoor refrigerant distributor 61 spring-like member 70 gas header 71 gas branch pipe 100 outdoor unit 200 indoor unit

Claims (7)

In a refrigerant distributor having a large number of heat transfer tubes that flow the refrigerant in parallel and connected to a heat exchanger that operates as an evaporator, and distributing and flowing the refrigerant to the multiple heat transfer tubes,
A distribution unit;
A number of branch pipes extending from the distribution section and branching into a large number;
The branch pipe is connected to the inlet side of the plurality of heat transfer pipes, and a spiral resistance portion for adjusting the flow resistance of the refrigerant flowing through the inner face of the branch pipe is provided on the inner surface of the branch pipe. A refrigerant distributor characterized by. In a refrigerant distributor having a large number of heat transfer tubes that flow the refrigerant in parallel and connected to a heat exchanger that operates as an evaporator, and distributing and flowing the refrigerant to the multiple heat transfer tubes,
A header disposed long along an inlet side of the plurality of heat transfer tubes;
A plurality of branch pipes extending from the header to be branched in a large number;
The branch pipe is connected to the inlet side of the plurality of heat transfer pipes, and a spiral groove is formed on the inner surface of the branch pipe.   3. The refrigerant distributor according to claim 2, wherein the dimension of the spiral groove formed on the inner surface of the branch pipe is different for each branch pipe.   4. The refrigerant distributor according to claim 3, wherein the spiral groove formed on the inner surface of the branch pipe has a length of 20 to 160 mm and an inner diameter of 1.6 to 3.0 mm.   3. A homogeneous flow lower portion connected to an inlet side to the header and having a flow passage cross-sectional area larger than the flow passage cross-sectional area of the header is provided, and the body of the homogeneous flow lower portion has a fine hole. A refrigerant distributor in which a porous body is disposed.   6. The refrigerant distributor according to claim 5, wherein a mesh filter is provided on an inlet side and an outlet side of the porous body provided in the body of the homogeneous flow lower part. In a refrigerant distributor having a large number of heat transfer tubes that flow the refrigerant in parallel and connected to a heat exchanger that operates as an evaporator, and distributing and flowing the refrigerant to the multiple heat transfer tubes,
A header disposed long along an inlet side of the plurality of heat transfer tubes;
A plurality of branch pipes extending from the header to be branched in a large number;
The branch pipe is connected to the inlet side of the plurality of heat transfer tubes, and a piece having a spiral groove shape or a spiral spring-like member is inserted and installed on the inner surface of the branch pipe. Distributor.

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