JP6005268B2 - Laminated header, heat exchanger, and air conditioner - Google Patents

Description

  The present invention relates to a laminated header, a heat exchanger, and an air conditioner.

  As a conventional laminated header, a first plate-like body in which a plurality of outlet channels and a plurality of inlet channels are formed, and the first plate-like body are laminated to form a first plate-like body. What is provided with the 2nd plate-like object in which the entrance channel connected with a plurality of exit channels, and the exit channel connected with the plurality of entrance channels formed in the 1st plate-like object were formed. Yes (see, for example, Patent Document 1).

JP 2000-161818 (paragraph [0032] to paragraph [0036], FIG. 7 and FIG. 8)

  In such a stacked header, for example, when a gaseous refrigerant flows into the plurality of inlet channels of the first plate, the plurality of inlet channels of the first plate and the outlet flow of the second plate The pressure loss of the refrigerant generated between the passages increases. And if the refrigerant | coolant which pressure loss increased flows into the compressor from the exit flow path of a 2nd plate-shaped body, the suction pressure of a compressor will fall and the work of a compressor will increase. That is, the conventional laminated header has a problem that the pressure loss of the refrigerant is large.

  The present invention has been made against the background of the above-described problems, and an object thereof is to obtain a laminated header in which the pressure loss of the refrigerant is reduced. Moreover, an object of this invention is to obtain the heat exchanger provided with such a laminated header. Moreover, an object of this invention is to obtain the air conditioning apparatus provided with such a heat exchanger.

The laminated header according to the present invention is attached to the first plate-like body in which a plurality of first inlet flow paths and a plurality of first outlet flow paths are formed, and to the second plate-like body . A second plate-like body formed with an inlet channel and a second outlet channel, and the second plate-like body is supplied with the refrigerant flowing from the second inlet channel. At least one of the distribution flow paths that distribute and flow out to the first outlet flow path and at least one of the merge flow paths that flow into the second outlet flow path by combining the refrigerant flowing in from the plurality of first inlet flow paths. And the one of the plurality of first inlet channels communicates with any one of the plurality of first outlet channels by a heat transfer tube, and is connected to the heat transfer tube. The flow passage area of the first inlet flow channel communicating with the first heat transfer tube is larger than the flow passage area of the first outlet flow passage communicating with the heat transfer tube .

  In the laminated header according to the present invention, one channel area of one of the plurality of first inlet channels is communicated with the one channel of the plurality of first outlet channels. Even if it is used in a situation where the refrigerant in the gas state flows into the plurality of first inlet passages of the first plate-like body, the plurality of first plate-like bodies are large because the flow passage area of the flow passage is large. An increase in refrigerant pressure loss that occurs between the first inlet channel and the second outlet channel of the second plate-like body can be suppressed.

It is a figure which shows the structure of the heat exchanger which concerns on Embodiment 1. FIG. It is a perspective view in the state which decomposed | disassembled the laminated header of the heat exchanger which concerns on Embodiment 1. FIG. FIG. 3 is a development view of a stacked header of the heat exchanger according to the first embodiment. It is a figure which shows the structure of the air conditioning apparatus to which the heat exchanger which concerns on Embodiment 1 is applied. It is a perspective view in the state which decomposed | disassembled the laminated header of the modification-1 of the heat exchanger which concerns on Embodiment 1. FIG. It is a perspective view in the state which decomposed | disassembled the laminated header of the modification-2 of the heat exchanger which concerns on Embodiment 1. FIG. It is a perspective view in the state which decomposed | disassembled the laminated header of the modification-3 of the heat exchanger which concerns on Embodiment 1. FIG. It is the perspective view of the principal part in the state which decomposed | disassembled the laminated header of the modification 4 of the heat exchanger which concerns on Embodiment 1, and sectional drawing of the principal part. It is a perspective view in the state which decomposed | disassembled the laminated header of the modification-5 of the heat exchanger which concerns on Embodiment 1. FIG. It is a perspective view in the state which decomposed | disassembled the laminated header of the modification-6 of the heat exchanger which concerns on Embodiment 1. FIG. It is a figure which shows the structure of the heat exchanger which concerns on Embodiment 2. FIG. It is a perspective view in the state which decomposed | disassembled the laminated header of the heat exchanger which concerns on Embodiment 2. FIG. It is an expanded view of the laminated header of the heat exchanger which concerns on Embodiment 2. FIG. It is a figure which shows the structure of the air conditioning apparatus to which the heat exchanger which concerns on Embodiment 2 is applied.

Hereinafter, the laminated header according to the present invention will be described with reference to the drawings.
In the following, the case where the laminated header according to the present invention distributes the refrigerant flowing into the heat exchanger is described, but the laminated header according to the present invention flows into other devices. A refrigerant may be distributed. Further, the configuration, operation, and the like described below are merely examples, and are not limited to such configuration, operation, and the like. Moreover, in each figure, the same code | symbol is attached | subjected to the same or similar thing, or attaching | subjecting code | symbol is abbreviate | omitted. Further, the illustration of the fine structure is simplified or omitted as appropriate. In addition, overlapping or similar descriptions are appropriately simplified or omitted.

  In addition, the “flow channel area” in the present invention means a cross-sectional area of the flow channel when there is one flow channel, and each of the plurality of flow channels when there are a plurality of flow channels. Means the sum of the cross-sectional areas.

Embodiment 1 FIG.
The heat exchanger according to Embodiment 1 will be described.
<Configuration of heat exchanger>
Below, the structure of the heat exchanger which concerns on Embodiment 1 is demonstrated.
FIG. 1 is a diagram illustrating a configuration of a heat exchanger according to the first embodiment.
As shown in FIG. 1, the heat exchanger 1 includes a stacked header 2, a plurality of first heat transfer tubes 3, a holding member 4, and a plurality of fins 5.

  The stacked header 2 includes a refrigerant inflow portion 2A, a plurality of refrigerant outflow portions 2B, a plurality of refrigerant inflow portions 2C, and a refrigerant outflow portion 2D. A refrigerant pipe is connected to the refrigerant inflow portion 2A of the multilayer header 2 and the refrigerant outflow portion 2D of the multilayer header 2. The first heat transfer tube 3 is a flat tube that has been subjected to hairpin bending. A plurality of first heat transfer tubes 3 are connected between the plurality of refrigerant outflow portions 2B of the multilayer header 2 and the plurality of refrigerant inflow portions 2C of the multilayer header 2.

  The first heat transfer tube 3 is a flat tube in which a plurality of flow paths are formed. The first heat transfer tube 3 is made of, for example, aluminum. Both ends of the plurality of first heat transfer tubes 3 are connected to the plurality of refrigerant outflow portions 2B and the plurality of refrigerant inflow portions 2C of the stacked header 2 while being held by the plate-like holding members 4. The holding member 4 is made of aluminum, for example. A plurality of fins 5 are joined to the first heat transfer tube 3. The fin 5 is made of, for example, aluminum. The first heat transfer tube 3 and the fins 5 may be joined by brazing. In addition, in FIG. 1, although the case where the 1st heat exchanger tube 3 is eight is shown, it is not limited to such a case.

<Flow of refrigerant in heat exchanger>
Below, the flow of the refrigerant in the heat exchanger according to Embodiment 1 will be described.
The refrigerant flowing through the refrigerant pipe flows into the stacked header 2 through the refrigerant inflow portion 2A and is distributed, and flows out to the plurality of first heat transfer tubes 3 through the plurality of refrigerant outflow portions 2B. The refrigerant exchanges heat with, for example, air supplied by a fan in the plurality of first heat transfer tubes 3. The refrigerant that has passed through the plurality of first heat transfer tubes 3 flows into and joins the stacked header 2 through the plurality of refrigerant inflow portions 2C, and flows out to the refrigerant piping through the refrigerant outflow portion 2D. The refrigerant can flow backward.

<Configuration of laminated header>
Below, the structure of the laminated header of the heat exchanger which concerns on Embodiment 1 is demonstrated.
FIG. 2 is a perspective view of the heat exchanger according to Embodiment 1 in a state where the stacked header is disassembled. FIG. 3 is a development view of the stacked header of the heat exchanger according to the first embodiment. In FIG. 3, the illustration of the clad members 24 on both sides is omitted.
As shown in FIGS. 2 and 3, the stacked header 2 includes a first plate-like body 11 and a second plate-like body 12. The first plate-like body 11 and the second plate-like body 12 are stacked.

  The first plate-like body 11 is stacked on the refrigerant outflow side. The first plate-like body 11 has a first plate-like member 21. The first plate-like body 11 is formed with a plurality of first outlet channels 11A and a plurality of first inlet channels 11B. The plurality of first outlet channels 11A correspond to the plurality of refrigerant outflow portions 2B in FIG. The plurality of first inlet channels 11B correspond to the plurality of refrigerant inflow portions 2C in FIG.

  In the first plate-like member 21, a plurality of flow paths 21A and a plurality of flow paths 21B are formed. The plurality of flow paths 21 </ b> A and the plurality of flow paths 21 </ b> B are through holes having an inner peripheral surface along the outer peripheral surface of the first heat transfer tube 3. The channel area (that is, the cross-sectional area) of one channel 21B among the plurality of channels 21B is the channel area of one channel 21A that communicates with the channel 21B among the plurality of channels 21A ( That is, it is larger than the cross-sectional area. When the first plate-like member 21 is stacked, the plurality of channels 21A function as a plurality of first outlet channels 11A, and the plurality of channels 21B function as a plurality of first inlet channels 11B. The 1st plate-shaped member 21 is about 1-10 mm in thickness, for example, and is made from aluminum. When the plurality of flow paths 21A and 21B are formed by pressing or the like, the processing is simplified and the manufacturing cost is reduced.

  The second plate-like body 12 is stacked on the refrigerant inflow side. The second plate-like body 12 includes a second plate-like member 22 and a plurality of third plate-like members 23_1 to 23_3. In the second plate-like body 12, a second inlet channel 12A, a distribution channel 12B, a merging channel 12C, and a second outlet channel 12D are formed. The distribution flow path 12B has a plurality of branch flow paths 12b. The merging channel 12C has a mixing channel 12c. The second inlet channel 12A corresponds to the refrigerant inflow portion 2A in FIG. The second outlet channel 12D corresponds to the refrigerant outflow portion 2D in FIG.

  Note that a part of the distribution channel 12 </ b> B or a part of the merging channel 12 </ b> C may be formed in the first plate-like body 11. In such a case, it is only necessary to form a flow path through which the refrigerant that flows in is returned to the first plate member 21, the second plate member 22, the plurality of third plate members 23_1 to 23_3, and the like. . In the case where the flow path through which the inflowing refrigerant is folded back is not formed, and all of the distribution flow paths 12B or all of the merge flow paths 12C are formed in the second plate-like body 12, the width of the stacked header 2 A dimension can be made substantially equal to the width dimension of the 1st heat exchanger tube 3, and the heat exchanger 1 is compactized.

  In the second plate-shaped member 22, a flow path 22A and a flow path 22B are formed. The channel 22A and the channel 22B are circular through holes. The channel area (that is, the sectional area) of the channel 22B is larger than the channel area (that is, the sectional area) of the channel 22A. When the second plate-like member 22 is stacked, the flow path 22A functions as the second inlet flow path 12A, and the flow path 22B functions as the second outlet flow path 12D. The 2nd plate-shaped member 22 is about 1-10 mm in thickness, for example, and is made from aluminum. When the flow path 22A and the flow path 22B are formed by pressing or the like, the processing is simplified and the manufacturing cost and the like are reduced.

  For example, a base or the like is provided on the surface on which the other members of the second plate-like member 22 are not stacked, and a refrigerant pipe is connected to the second inlet channel 12A and the second outlet channel 12D through the base or the like. The The inner peripheral surfaces of the second inlet flow channel 12A and the second outlet flow channel 12D are shaped to fit with the outer peripheral surface of the refrigerant pipe, and the second inlet flow channel 12A and the second outlet flow are not used without using a base or the like. A refrigerant pipe may be directly connected to the path 12D. In such a case, parts costs and the like are reduced.

  A plurality of flow paths 23A_1 to 23A_3 are formed in the plurality of third plate-like members 23_1 to 23_3. The plurality of flow paths 23A_1 to 23A_3 are through grooves having two end portions 23a and 23b. When the plurality of third plate members 23_1 to 23_3 are stacked, each of the plurality of flow paths 23A_1 to 23A_3 functions as the branch flow path 12b. The plurality of third plate-like members 23_1 to 23_3 are, for example, about 1 to 10 mm in thickness and made of aluminum. In the case where the plurality of flow paths 23A_1 to 23A_3 are formed by pressing or the like, the processing is simplified and the manufacturing cost and the like are reduced.

  A plurality of flow paths 23B_1 to 23B_3 are formed in the plurality of third plate-like members 23_1 to 23_3. The plurality of flow paths 23B_1 to 23B_3 are rectangular through holes penetrating almost the entire area in the height direction of the third plate-like members 23_1 to 23_3. The channel areas (that is, the cross-sectional areas) of the channels 23B_1 to 23B_3 are larger than the channel areas (that is, the sum of the cross-sectional areas) of the plurality of channels 21A. When the plurality of third plate-like members 23_1 to 23_3 are stacked, each of the plurality of flow paths 23B_1 to 23B_3 functions as a part of the mixing flow path 12c. The plurality of flow paths 23B_1 to 23B_3 may not be rectangular.

  Hereinafter, the plurality of third plate-like members 23_1 to 23_3 may be collectively referred to as the third plate-like member 23 in some cases. Hereinafter, the plurality of flow paths 23A_1 to 23A_3 may be collectively referred to as a flow path 23A. Hereinafter, the plurality of flow paths 23B_1 to 23B_3 may be collectively referred to as a flow path 23B. Below, the holding member 4, the 1st plate-shaped member 21, the 2nd plate-shaped member 22, and the 3rd plate-shaped member 23 may be named generically, and may be described as a plate-shaped member.

  The flow path 23A formed in the third plate-like member 23 has a shape that connects the two end portions 23a and 23b via a straight line portion 23c perpendicular to the direction of gravity. The flow path 23A is blocked by a member stacked adjacent to the refrigerant inflow side, except for a part of the area 23d (hereinafter referred to as the opening 23d) between both ends of the linear portion 23c. The branch channel 12b is formed by closing the region other than the end portions 23a and 23b by the member laminated adjacent to the side.

  In order to branch out and flow out the inflowing refrigerant to different heights, the end 23a and the end 23b are located at different heights. In particular, when one of the end portion 23a and the end portion 23b is on the upper side compared to the straight line portion 23c and the other is on the lower side compared to the straight line portion 23c, the opening 23d through the flow path 23A. The deviation of each distance reaching the end 23a and the end 23b along the line can be reduced without complicating the shape. Since the straight line connecting the end portion 23a and the end portion 23b is parallel to the longitudinal direction of the third plate-like member 23, it is possible to reduce the dimension in the short direction of the third plate-like member 23, and the component Cost, weight, etc. are reduced. Furthermore, since the straight line connecting the end 23a and the end 23b is parallel to the arrangement direction of the first heat transfer tubes 3, the heat exchanger 1 is saved in space.

  The branch flow path 12b branches the flowing refrigerant into two and flows out. Therefore, when there are eight first heat transfer tubes 3 connected, at least three third plate-like members 23 are required. When there are 16 first heat transfer tubes 3 to be connected, at least four third plate members 23 are required. The number of connected first heat transfer tubes 3 is not limited to a power of 2. In such a case, the branched flow path 12b and the non-branched flow path may be combined. Two first heat transfer tubes 3 may be connected.

  Note that the stacked header 2 is not limited to one in which the plurality of first outlet channels 11A and the plurality of first inlet channels 11B are arranged along the direction of gravity. For example, the wall-mounted room air conditioner indoor unit The heat exchanger 1 may be used in a case where the heat exchanger 1 is inclined and disposed like a heat exchanger such as an air conditioner outdoor unit or a chiller outdoor unit. In such a case, the straight part 23 c may be a through groove having a shape that does not become perpendicular to the longitudinal direction of the third plate-like member 23.

  Further, the flow path 23A may have other shapes. For example, the flow path 23A may not have the straight portion 23c. In such a case, the horizontal portion between the end 23a and the end 23b of the flow path 23A that is substantially perpendicular to the direction of gravity is the opening 23d. In the case where the straight portion 23c is provided, it is difficult for the refrigerant to be affected by gravity when the refrigerant branches at the opening 23d. Further, for example, the flow path 23A may be a through groove having a shape in which regions connecting the both ends of the linear portion 23c and the end portions 23a and 23b are branched. In the case where the branch flow path 12b branches the refrigerant flowing into two and further does not branch the branched refrigerant into a plurality, the uniformity of refrigerant distribution can be improved. A region connecting each of both ends of the straight line portion 23c and each of the end portion 23a and the end portion 23b may be a straight line or a curved line.

  Each plate member is laminated by brazing. A brazing material for joining may be supplied by using a double-sided clad material obtained by rolling a brazing material on both sides for all plate-like members or every other plate-like member. A brazing material for joining may be supplied to all the plate-like members by using a one-side clad material in which the brazing material is rolled on one side. The brazing material sheet may be supplied by laminating brazing material sheets between the plate-like members. The brazing material may be supplied by applying a pasty brazing material between the plate members. The brazing material may be supplied by laminating clad materials obtained by rolling the brazing material on both sides between the plate-like members.

  By laminating by brazing and joining, the plate-like members are laminated without gaps, leakage of the refrigerant is suppressed, and pressure resistance is ensured. In the case of brazing and joining the plate-like members while applying pressure, the occurrence of brazing defects is further suppressed. In the case where processing that promotes the formation of fillets, such as formation of ribs, is performed at locations where refrigerant leakage is likely to occur, the occurrence of brazing defects is further suppressed.

  Furthermore, when all the members to be brazed including the first heat transfer tube 3 and the fins 5 are made of the same material (for example, made of aluminum), it is possible to braze and join together. , Productivity is improved. After the brazing joining of the laminated header 2, the first heat transfer tubes 3 and the fins 5 may be brazed. Alternatively, only the first plate 11 may be brazed to the holding member 4 first, and the second plate 12 may be brazed afterwards.

  In particular, a brazing material is preferably supplied by laminating a platy member obtained by rolling a brazing material on both sides, that is, clad materials on both sides, between the respective platy members. As shown in FIG. 2, a plurality of clad members 24_1 to 24_5 are laminated between the plate-like members. Hereinafter, the plurality of both-side clad materials 24_1 to 24_5 may be collectively referred to as the both-side clad material 24.

  A flow path 24A and a flow path 24B penetrating the both-side clad material 24 are formed in the both-side clad material 24. When the flow path 24A and the flow path 24B are formed by pressing or the like, the processing is simplified and the manufacturing cost and the like are reduced. When all the members to be brazed including the clad members 24 are made of the same material (for example, made of aluminum), it is possible to collectively braze and improve productivity.

  The flow path 24A formed in the both-side clad material 24 laminated on the second plate member 22 and the third plate member 23 is a circular through hole. The flow path 24B formed in the both-side clad material 24 laminated on the third plate-like members 23_1 and 23_2 is a rectangular through-hole penetrating almost the entire area of the both-side clad material 24 in the height direction. The flow path 24B may not be rectangular. The channel area (that is, the cross-sectional area) of the channel 24B is larger than the channel area (that is, the sum of the cross-sectional areas) of the plurality of channels 21A. The plurality of flow paths 24B formed in the both-side clad material 24_4 laminated between the third plate-like member 23_3 and the first plate-like member 21 are rectangular through holes. The plurality of flow paths 24B may not be rectangular. The channel area (that is, the cross-sectional area) of one channel 24B among the plurality of channels 24B is the flow of one channel 21A communicated with the one channel 24B among the plurality of channels 21A. Larger than the road area (ie, cross-sectional area).

  The plurality of flow paths 24A and the plurality of flow paths 24B formed in the both-side clad material 24_5 laminated between the first plate member 21 and the holding member 4 have an inner peripheral surface that is the outer peripheral surface of the first heat transfer tube 3. It is a through-hole of a shape along. The channel area (that is, the cross-sectional area) of one channel 24B among the plurality of channels 24B is the channel area of one channel 21A communicated with the channel 24B among the plurality of channels 21A ( That is, it is larger than the cross-sectional area.

  When the clad members 24 are laminated on each other, the flow path 24A functions as a refrigerant isolation flow path for the first outlet flow path 11A, the distribution flow path 12B, and the second inlet flow path 12A. It functions as a refrigerant isolation channel for the inlet channel 11B, the merging channel 12C, and the second outlet channel 12D. By forming the coolant isolation channel by the clad members 24 on both sides, the coolant is reliably isolated. In addition, since the separation of the refrigerants is ensured, the degree of freedom in designing the flow path is improved. In addition, the clad material 24 may be laminated between some plate-like members, and the brazing material may be supplied between other plate-like members by other methods.

  The end portion of the first heat transfer tube 3 protrudes from the surface of the holding member 4, both side clad materials 24_5 are laminated on the holding member 4, and the flow paths 24A and 24B of the both side clad materials 24_5 are formed on the outer peripheral surface of the end portions. By fitting the inner peripheral surface, the first heat transfer tube 3 is connected to the first outlet channel 11A and the first inlet channel 11B. The first outlet channel 11A, the first inlet channel 11B, and the first heat transfer tube 3 are, for example, fitted with a convex portion formed in the holding member 4 and a concave portion formed in the first plate-like body 11 or the like. In such a case, the end portion of the first heat transfer tube 3 may not protrude from the surface of the holding member 4. The holding member 4 may not be provided, and the first heat transfer tube 3 may be directly connected to the first outlet channel 11A and the first inlet channel 11B. In such a case, parts costs and the like are reduced.

<Refrigerant flow in stacked header>
Hereinafter, the flow of the refrigerant in the stacked header of the heat exchanger according to Embodiment 1 will be described.
As shown in FIGS. 2 and 3, the refrigerant that has passed through the flow path 22A of the second plate member 22 flows into the opening 23d of the flow path 23A formed in the third plate member 23_1. The refrigerant that has flowed into the opening 23d hits the surface of a member stacked adjacently, and branches into two toward each end of the straight portion 23c. The branched refrigerant reaches the end portions 23a and 23b of the flow path 23A and flows into the opening 23d of the flow path 23A formed in the third plate member 23_2.

  Similarly, the refrigerant that has flowed into the opening 23d of the flow path 23A formed in the third plate-like member 23_2 hits the surface of the adjacent laminated member, and is divided into two toward each of both ends of the linear portion 23c. Branch. The branched refrigerant reaches the end portions 23a and 23b of the flow path 23A and flows into the opening 23d of the flow path 23A formed in the third plate member 23_3.

  Similarly, the refrigerant that has flowed into the opening 23d of the flow path 23A formed in the third plate-like member 23_3 hits the surface of the adjacent laminated member, and is divided into two toward each of both ends of the linear portion 23c. Branch. The branched refrigerant reaches the end portions 23 a and 23 b of the flow path 23 </ b> A, passes through the flow path 21 </ b> A of the first plate-like member 21, and flows into the first heat transfer tube 3.

  The refrigerant that has flowed out of the flow path 21 </ b> A of the first plate-shaped member 21 and passed through the first heat transfer tube 3 flows into the flow path 21 </ b> B of the first plate-shaped member 21. The refrigerant that has flowed into the flow path 21 </ b> B of the first plate-shaped member 21 flows into the flow path 23 </ b> B formed in the third plate-shaped member 23 and is mixed therewith. The mixed refrigerant passes through the flow path 22B of the second plate-like member 22 and flows out to the refrigerant pipe.

<Usage of heat exchanger>
Below, an example of the usage aspect of the heat exchanger which concerns on Embodiment 1 is demonstrated.
In addition, although the case where the heat exchanger which concerns on Embodiment 1 is used for an air conditioning apparatus is demonstrated below, it is not limited to such a case, For example, the other refrigeration cycle which has a refrigerant circulation circuit It may be used in the device. Moreover, although the case where an air conditioning apparatus switches between cooling operation and heating operation is demonstrated, it is not limited to such a case, You may perform only cooling operation or heating operation.

FIG. 4 is a diagram illustrating a configuration of an air-conditioning apparatus to which the heat exchanger according to Embodiment 1 is applied. In FIG. 4, the refrigerant flow during the cooling operation is indicated by solid arrows, and the refrigerant flow during the heating operation is indicated by dotted arrows.
As shown in FIG. 4, the air conditioner 51 includes a compressor 52, a four-way valve 53, a heat source side heat exchanger 54, an expansion device 55, a load side heat exchanger 56, a heat source side fan 57, A load-side fan 58 and a control device 59. The compressor 52, the four-way valve 53, the heat source side heat exchanger 54, the expansion device 55, and the load side heat exchanger 56 are connected by refrigerant piping to form a refrigerant circulation circuit.

  For example, a compressor 52, a four-way valve 53, a throttle device 55, a heat source side fan 57, a load side fan 58, various sensors, and the like are connected to the control device 59. By switching the flow path of the four-way valve 53 by the control device 59, the cooling operation and the heating operation are switched. The heat source side heat exchanger 54 acts as a condenser during the cooling operation, and acts as an evaporator during the heating operation. The load side heat exchanger 56 acts as an evaporator during the cooling operation, and acts as a condenser during the heating operation.

The flow of the refrigerant during the cooling operation will be described.
The high-pressure and high-temperature gas refrigerant discharged from the compressor 52 flows into the heat source side heat exchanger 54 via the four-way valve 53 and condenses by heat exchange with the outside air supplied by the heat source side fan 57. It becomes a high-pressure liquid refrigerant and flows out of the heat source side heat exchanger 54. The high-pressure liquid refrigerant flowing out of the heat source side heat exchanger 54 flows into the expansion device 55 and becomes a low-pressure gas-liquid two-phase refrigerant. The low-pressure gas-liquid two-phase refrigerant flowing out of the expansion device 55 flows into the load-side heat exchanger 56 and evaporates by heat exchange with the indoor air supplied by the load-side fan 58, thereby causing a low-pressure gas state. And flows out of the load-side heat exchanger 56. The low-pressure gaseous refrigerant flowing out from the load-side heat exchanger 56 is sucked into the compressor 52 through the four-way valve 53.

The flow of the refrigerant during the heating operation will be described.
The high-pressure and high-temperature gas refrigerant discharged from the compressor 52 flows into the load-side heat exchanger 56 through the four-way valve 53 and condenses by heat exchange with the indoor air supplied by the load-side fan 58. And becomes a high-pressure liquid refrigerant and flows out of the load-side heat exchanger 56. The high-pressure liquid refrigerant flowing out of the load-side heat exchanger 56 flows into the expansion device 55 and becomes a low-pressure gas-liquid two-phase refrigerant. The low-pressure gas-liquid two-phase refrigerant that flows out of the expansion device 55 flows into the heat source side heat exchanger 54 and evaporates by heat exchange with the outside air supplied by the heat source side fan 57, so that the low-pressure gas state It becomes a refrigerant and flows out of the heat source side heat exchanger 54. The low-pressure gaseous refrigerant flowing out from the heat source side heat exchanger 54 is sucked into the compressor 52 through the four-way valve 53.

  The heat exchanger 1 is used for at least one of the heat source side heat exchanger 54 and the load side heat exchanger 56. In the heat exchanger 1, when the heat exchanger 1 acts as an evaporator, the refrigerant flows into the first heat transfer tube 3 from the distribution flow path 12 </ b> B of the stacked header 2, and the stacked header 2 is transferred from the first heat transfer tube 3. It is connected so that the refrigerant flows into the merging flow path 12C. That is, when the heat exchanger 1 acts as an evaporator, a gas-liquid two-phase refrigerant flows from the refrigerant pipe into the distribution flow path 12B of the multilayer header 2 and flows from the first heat transfer tube 3 to the multilayer header 2. The refrigerant in the gas state flows into the merging channel 12C. Further, when the heat exchanger 1 acts as a condenser, a gaseous refrigerant flows from the refrigerant pipe into the merged flow path 12 </ b> C of the laminated header 2, and the distribution flow path of the laminated header 2 from the first heat transfer tube 3. Liquid refrigerant flows into 12B.

<Operation of heat exchanger>
Below, the effect | action of the heat exchanger which concerns on Embodiment 1 is demonstrated.
In the laminated header 2, the flow area of one first inlet flow path 11B among the plurality of first inlet flow paths 11B is equal to the first inlet flow path 11B of the plurality of first outlet flow paths 11A. It is larger than the channel area of one first outlet channel 11A communicated. Therefore, even if it is used in a situation in which a gaseous refrigerant flows into the plurality of first inlet channels 11B of the first plate-like body 11, the plurality of first inlet channels 11B of the first plate-like body 11 The increase in the pressure loss of the refrigerant generated between the second plate-like body 12 and the second outlet channel 12D can be suppressed.

  Further, in the laminated header 2, the flow channel area of the mixing flow channel 12c is larger than the flow channel areas of the plurality of first outlet flow channels 11A. Therefore, even if it is used in a situation in which a gaseous refrigerant flows into the plurality of first inlet channels 11B of the first plate-like body 11, the plurality of first inlet channels 11B of the first plate-like body 11 The increase in the pressure loss of the refrigerant generated between the second plate-like body 12 and the second outlet channel 12D can be suppressed.

  Further, in the stacked header, the flow passage area of the second outlet flow passage 12D is larger than the flow passage area of the second inlet flow passage 12A. Therefore, the plurality of first inlet flows of the first plate-like body 11 Even if it is used in a situation where a gaseous refrigerant flows into the passage 11B, an increase in refrigerant pressure loss that occurs in the second outlet channel 12D of the second plate 12 can be suppressed.

  In particular, even when the refrigerant flowing from the laminated header 2 into the first heat transfer tube 3 is used in a gas-liquid two-phase state and the refrigerant flowing from the first heat transfer tube 3 into the laminated header 2 is in a gas state, An increase in refrigerant pressure loss that occurs between the plurality of first inlet channels 11B of the first plate 11 and the second outlet channels 12D of the second plate 12 can be suppressed. And when the heat exchanger 1 acts as an evaporator and the refrigerant in the gas state flowing out from the laminated header 2 is sucked into the compressor 52, the refrigerant whose increase in pressure loss is suppressed is As a result, it is suppressed that the suction pressure of the compressor 52 decreases and the work amount of the compressor 52 increases, for example, the air conditioner 51 and the like have high performance. Is done.

  In particular, in conventional laminated headers, if the heat transfer tube is changed from a circular tube to a flat tube for the purpose of reducing the amount of refrigerant and saving space in the heat exchanger, the circumferential direction is perpendicular to the refrigerant inflow direction. However, the stacked header 2 does not have to be enlarged in the entire circumferential direction perpendicular to the refrigerant inflow direction, and the heat exchanger 1 is saved in space. In other words, in the conventional laminated header, when the heat transfer tube is changed from a circular tube to a flat tube, the flow passage cross-sectional area in the heat transfer tube is reduced, and the pressure loss generated in the heat transfer tube increases. It is necessary to further reduce the angular interval between the grooves forming the branch flow path to increase the number of passes (that is, the number of heat transfer tubes), and the stacked header is large in the entire circumferential direction perpendicular to the refrigerant inflow direction. It becomes. On the other hand, in the laminated header 2, even if it is necessary to increase the number of passes, the number of the third plate-like members 23 only needs to be increased. An increase in size is suppressed. The laminated header 2 is not limited to the case where the first heat transfer tube 3 is a flat tube.

<Modification-1>
FIG. 5 is a perspective view of a modified example-1 of the heat exchanger according to Embodiment 1 in a state in which the stacked header is disassembled.
As shown in FIG. 5, in the third plate-like member 23, the periphery of the flow path 23B may be enlarged so as to be close to the periphery of the flow path 23A. When the flow path 23B has the same shape in all the third plate-like members 23, the pressure loss is reduced. Therefore, the flow path 23B penetrates a region that does not overlap with all the flow paths 23A. The flow paths 24B of the clad members 24 laminated between the second plate member 22 and the third plate member 23_3 have the same shape.

<Modification-2>
FIG. 6 is a perspective view of a modified example-2 of the heat exchanger according to Embodiment 1 in a state in which the stacked header is disassembled.
As shown in FIG. 6, a plurality of flow paths 22 </ b> A are formed in the second plate-shaped member 22, that is, a plurality of second inlet flow paths 12 </ b> A are formed in the second plate-shaped body 12. The number of 23 sheets may be reduced. By being configured in this way, parts cost, weight, etc. are reduced. The channel area (that is, the sectional area) of the channel 22B is larger than the channel area (that is, the sum of the sectional areas) of the plurality of channels 22A.

<Modification-3>
FIG. 7 is a perspective view of Modification 3 of the heat exchanger according to Embodiment 1 in a state where the stacked header is disassembled.
As shown in FIG. 7, a plurality of flow paths 22 </ b> B and flow paths 23 </ b> B may be formed in the second plate-like member 22 and the third plate-like member 23. That is, the merging channel 12C may have a plurality of mixing channels 12c. The plurality of flow paths 24B of the both-side clad material 24 laminated between the second plate-shaped member 22 and the third plate-shaped member 23_3 have the same shape as the plurality of flow paths 23B. The channel area (that is, the sum of the cross-sectional areas) of the plurality of channels 22B is larger than the channel area (that is, the cross-sectional area) of the channel 22A. The flow passage areas of the plurality of flow passages 23B (that is, the sum of the cross-sectional areas) are larger than the flow passage areas of the plurality of flow passages 21A (that is, the sum of the cross-sectional areas). The flow area (that is, the sum of the cross-sectional areas) of the plurality of flow paths 24B is larger than the flow area (that is, the sum of the cross-sectional areas) of the plurality of flow paths 21A.

<Modification-4>
FIG. 8 is a perspective view of a main part and a cross-sectional view of the main part in a state in which the stacked header is disassembled in Modification 4 of the heat exchanger according to the first embodiment. 8A is a perspective view of the main part in a state where the laminated header is disassembled, and FIG. 8B is a third plate-like member taken along line AA of FIG. 8A. FIG.
As shown in FIG. 8, any of the flow paths 23A formed in the third plate-like member 23 may be a bottomed groove. In such a case, a circular through hole 23e is formed in each of the end 23a and the end 23b on the bottom surface of the groove of the flow path 23A. By being configured in this way, both sides of the clad material 24 do not have to be laminated between the plate-like members in order to interpose the flow path 24A functioning as the refrigerant isolation flow path between the branch flow paths 12b, and production Efficiency is improved. 8 shows the case where the refrigerant outflow side of the flow path 23A is the bottom face, the refrigerant inflow side of the flow path 23A may be the bottom face. In such a case, a through hole may be formed in a region corresponding to the opening 23d.

<Modification-5>
FIG. 9 is a perspective view of a modified example-5 of the heat exchanger according to Embodiment 1 in a state where the stacked header is disassembled.
As shown in FIG. 9, the flow path 22A functioning as the second inlet flow path 12A is formed in a laminated member other than the second plate-like member 22, that is, other plate-like members, both-side clad members 24, and the like. May be. In such a case, the flow path 22A may be, for example, a through hole that penetrates from the side surface of another plate-like member to the surface on the side where the second plate-like member 22 is present.

<Modification-6>
FIG. 10 is a perspective view of Modified Example-6 of the heat exchanger according to Embodiment 1 in a state where the stacked header is disassembled.
As shown in FIG. 10, the flow path 22B functioning as the second outlet flow path 12D is formed in other plate-like members other than the second plate-like member 22 of the second plate-like body 12, both-side clad material 24, and the like. May be. In such a case, for example, a cutout that communicates a part of the flow path 23B or the flow path 24B with the side surfaces of the third plate-like member 23 or the clad members 24 may be formed. The flow path 22B which functions as 2nd exit flow path 12D may be formed in the 1st plate-shaped member 21 by folding the mixing flow path 12c.

Embodiment 2. FIG.
A heat exchanger according to Embodiment 2 will be described.
Note that description overlapping or similar to that in Embodiment 1 is appropriately simplified or omitted.
<Configuration of heat exchanger>
Below, the structure of the heat exchanger which concerns on Embodiment 2 is demonstrated.
FIG. 11 is a diagram illustrating a configuration of the heat exchanger according to the second embodiment.
As shown in FIG. 11, the heat exchanger 1 includes a stacked header 2, a plurality of first heat transfer tubes 3, a plurality of second heat transfer tubes 6, a holding member 4, and a plurality of fins 5. Have.

  The stacked header 2 has a plurality of refrigerant folding portions 2E. Similar to the first heat transfer tube 3, the second heat transfer tube 6 is a flat tube that has been subjected to hairpin bending. A plurality of first heat transfer tubes 3 are connected between the plurality of refrigerant outflow portions 2B and the plurality of refrigerant folding portions 2E of the multilayer header 2, and the plurality of refrigerant folding portions 2E and the plurality of refrigerant inflows of the multilayer header 2 are connected. A plurality of second heat transfer tubes 6 are connected between the portion 2C.

<Flow of refrigerant in heat exchanger>
Below, the flow of the refrigerant in the heat exchanger according to the second embodiment will be described.
The refrigerant flowing through the refrigerant pipe flows into the stacked header 2 through the refrigerant inflow portion 2A and is distributed, and flows out to the plurality of first heat transfer tubes 3 through the plurality of refrigerant outflow portions 2B. The refrigerant exchanges heat with, for example, air supplied by a fan in the plurality of first heat transfer tubes 3. The refrigerant that has passed through the plurality of first heat transfer tubes 3 flows into the plurality of refrigerant folding portions 2 </ b> E of the stacked header 2, is turned back, and flows out to the plurality of second heat transfer tubes 6. The refrigerant exchanges heat with, for example, air supplied by a fan in the plurality of second heat transfer tubes 6. The refrigerant that has passed through the plurality of second heat transfer tubes 6 flows into and joins the stacked header 2 through the plurality of refrigerant inflow portions 2C, and flows out to the refrigerant pipe through the refrigerant outflow portion 2D. The refrigerant can flow backward.

<Configuration of laminated header>
Below, the structure of the laminated header of the heat exchanger which concerns on Embodiment 2 is demonstrated.
FIG. 12 is a perspective view of the heat exchanger according to Embodiment 2 in a state where the stacked header is disassembled. FIG. 13 is a development view of the stacked header of the heat exchanger according to the second embodiment. In FIG. 13, the illustration of the clad material 24 on both sides is omitted.
As shown in FIGS. 12 and 13, the stacked header 2 includes a first plate-like body 11 and a second plate-like body 12. The first plate-like body 11 and the second plate-like body 12 are stacked.

  In the first plate-like body 11, a plurality of first outlet channels 11A, a plurality of first inlet channels 11B, and a plurality of folded channels 11C are formed. The plurality of folding channels 11C correspond to the plurality of refrigerant folding sections 2E in FIG.

  A plurality of flow paths 21 </ b> C are formed in the first plate member 21. The plurality of flow paths 21 </ b> C have through-holes whose inner peripheral surfaces surround the outer peripheral surface of the refrigerant outflow side end of the first heat transfer tube 3 and the outer peripheral surface of the end of the second heat transfer tube 6 on the refrigerant inflow side. It is. When the first plate-like member 21 is stacked, the plurality of channels 21C function as the plurality of folded channels 11C.

  In particular, the brazing material is preferably supplied by laminating both clad materials 24 in which the brazing material is rolled on both sides between the plate-like members. The flow path 24C formed in the both-side clad material 24_5 laminated between the holding member 4 and the first plate-like member 21 has an inner peripheral surface that is the outer peripheral surface of the end portion on the refrigerant outflow side of the first heat transfer tube 3. And a through hole having a shape surrounding the outer peripheral surface of the end of the second heat transfer tube 6 on the refrigerant inflow side. When the clad members 24 on both sides are laminated, the flow path 24C functions as a refrigerant isolation flow path for the return flow path 11C.

<Refrigerant flow in stacked header>
Below, the flow of the refrigerant in the stacked header of the heat exchanger according to Embodiment 2 will be described.
As shown in FIGS. 12 and 13, the refrigerant that has flowed out of the flow path 21A of the first plate member 21 and passed through the first heat transfer tube 3 flows into the flow path 21C of the first plate member 21, It is folded and flows into the second heat transfer tube 6. The refrigerant that has passed through the second heat transfer tube 6 flows into the flow path 21 </ b> B of the first plate member 21. The refrigerant that has flowed into the flow path 21 </ b> B of the first plate-shaped member 21 flows into the flow path 23 </ b> B formed in the third plate-shaped member 23 and is mixed therewith. The mixed refrigerant passes through the flow path 22B of the second plate-like member 22 and flows out to the refrigerant pipe.

<Usage of heat exchanger>
Below, an example of the usage condition of the heat exchanger which concerns on Embodiment 2 is demonstrated.
FIG. 14 is a diagram illustrating a configuration of an air-conditioning apparatus to which the heat exchanger according to Embodiment 2 is applied.
As shown in FIG. 14, the heat exchanger 1 is used for at least one of the heat source side heat exchanger 54 and the load side heat exchanger 56. In the heat exchanger 1, when the heat exchanger 1 acts as an evaporator, the refrigerant flows into the first heat transfer tube 3 from the distribution flow path 12 </ b> B of the stacked header 2, and the stacked header 2 from the second heat transfer tube 6. It is connected so that the refrigerant flows into the merging flow path 12C. That is, when the heat exchanger 1 acts as an evaporator, a gas-liquid two-phase refrigerant flows from the refrigerant pipe into the distribution flow path 12B of the multilayer header 2 and flows from the second heat transfer pipe 6 to the multilayer header 2. The refrigerant in the gas state flows into the merging channel 12C. Further, when the heat exchanger 1 acts as a condenser, a gaseous refrigerant flows from the refrigerant pipe into the merged flow path 12 </ b> C of the laminated header 2, and the distribution flow path of the laminated header 2 from the first heat transfer tube 3. Liquid refrigerant flows into 12B.

  Furthermore, when the heat exchanger 1 acts as a condenser, the first heat transfer tube 3 is compared with the second heat transfer tube 6 on the upstream side (windward side) of the airflow generated by the heat source side fan 57 or the load side fan 58. ), The heat exchanger 1 is disposed. That is, the refrigerant flow from the second heat transfer tube 6 to the first heat transfer tube 3 and the airflow face each other. The refrigerant of the first heat transfer tube 3 has a lower temperature than the refrigerant of the second heat transfer tube 6. The airflow generated by the heat source side fan 57 or the load side fan 58 has a lower temperature on the upstream side of the heat exchanger 1 than on the downstream side of the heat exchanger 1. As a result, in particular, the refrigerant can be supercooled (so-called SC) with a low-temperature airflow flowing upstream of the heat exchanger 1, and the condenser performance is improved. The heat source side fan 57 and the load side fan 58 may be provided on the leeward side or may be provided on the leeward side.

<Operation of heat exchanger>
Below, the effect | action of the heat exchanger which concerns on Embodiment 2 is demonstrated.
In the heat exchanger 1, a plurality of folded flow paths 11 </ b> C are formed in the first plate-like body 11, and a plurality of second heat transfer tubes 6 are connected in addition to the plurality of first heat transfer tubes 3. For example, it is possible to increase the amount of heat exchange by increasing the area of the heat exchanger 1 as viewed from the front, but in that case, the housing containing the heat exchanger 1 is enlarged. End up. In addition, it is possible to increase the number of fins 5 by reducing the interval between the fins 5 and increase the amount of heat exchange, but in that case, from the viewpoint of drainage, frosting performance, dust resistance, It is difficult to make the interval between the fins 5 less than about 1 mm, and the increase in the heat exchange amount may be insufficient. On the other hand, when the number of rows of heat transfer tubes is increased as in the heat exchanger 1, the heat exchange amount is increased without changing the area of the heat exchanger 1 as viewed from the front, the spacing between the fins 5, and the like. It is possible to make it. When the number of rows of heat transfer tubes becomes two, the amount of heat exchange increases by about 1.5 times or more. Note that the number of rows of heat transfer tubes may be three or more. Furthermore, the area of the heat exchanger 1 as viewed from the front, the interval between the fins 5 and the like may be changed.

  Further, a header (laminated header 2) is provided only on one side of the heat exchanger 1. In order to increase the mounting volume of the heat exchanging part, for example, when the heat exchanger 1 is bent and arranged along a plurality of side surfaces of the housing incorporating the heat exchanger 1, Due to the fact that the curvature radius of the bent portion is different for each row of heat tubes, the end portion is shifted for each row of heat transfer tubes. When the header (stacked header 2) is provided only on one side of the heat exchanger 1 as in the stacked header 2, even if the end is shifted for each row of heat transfer tubes, only the end on one side The degree of freedom in design and production efficiency can be improved. In particular, it is possible to bend the heat exchanger 1 after joining the members of the heat exchanger 1, and the production efficiency is further improved.

  Further, when the heat exchanger 1 acts as a condenser, the first heat transfer tube 3 is located on the windward side compared to the second heat transfer tube 6. When headers are provided on both sides of the heat exchanger, it is difficult to improve the condenser performance by giving a temperature difference of the refrigerant for each row of heat transfer tubes. In particular, when the first heat transfer tube 3 and the second heat transfer tube 6 are flat tubes, unlike a circular tube, the degree of freedom of bending is low, so that a temperature difference of the refrigerant is given to each row of heat transfer tubes. It is difficult to realize by deforming the refrigerant flow path. On the other hand, when the first heat transfer tube 3 and the second heat transfer tube 6 are connected to the laminated header 2 as in the heat exchanger 1, a temperature difference of the refrigerant inevitably occurs for each row of heat transfer tubes. In other words, it is possible to easily realize the relationship in which the refrigerant flow and the airflow face each other without deforming the refrigerant flow path.

  As mentioned above, although Embodiment 1 and Embodiment 2 were demonstrated, this invention is not limited to description of each embodiment. For example, it is possible to combine all or a part of each embodiment, each modification, and the like.

  DESCRIPTION OF SYMBOLS 1 Heat exchanger, 2 Stack type header, 2A Refrigerant inflow part, 2B Refrigerant outflow part, 2C Refrigerant inflow part, 2D Refrigerant outflow part, 2E Refrigerant return part, 3 1st heat exchanger tube, 4 Holding member, 5 Fin, 6 1st 2 heat transfer tubes, 11 first plate-like body, 11A first outlet flow channel, 11B first inlet flow channel, 11C folding channel, 12 second plate-like body, 12A second inlet flow channel, 12B distribution flow channel, 12C Junction channel, 12D second outlet channel, 12b branch channel, 12c mixing channel, 21 first plate member, 21A-21C channel, 22 second plate member, 22A, 22B channel, 23, 23_1 -23_3 3rd plate-like member, 23A, 23B, 23A_1 to 23A_3, 23B_1 to 23B_3 channel, 23a, 23b end, 23c straight part, 23d opening, 23e through hole, 24, 24_1 to 24_5 both Clad material, 24A-24C flow path, 51 air conditioner, 52 compressor, 53 four-way valve, 54 heat source side heat exchanger, 55 throttle device, 56 load side heat exchanger, 57 heat source side fan, 58 load side fan, 59 Control device.

Claims (9)

A first plate-like body in which a plurality of first inlet channels and a plurality of first outlet channels are formed;
A second plate-like body attached to the first plate-like body and having a second inlet channel and a second outlet channel formed;
The second plate-like body includes at least a part of a distribution channel that distributes the refrigerant flowing from the second inlet channel to the plurality of first outlet channels and flows out, and the plurality of first inlet channels. And at least a part of the merged flow channel that merges the refrigerant flowing in from the channel and flows out to the second outlet flow channel ,
Any one of the plurality of first inlet channels is communicated with any one of the plurality of first outlet channels by a heat transfer tube,
The channel area of the first inlet channel communicating with the heat transfer tube is larger than the channel area of the first outlet channel communicating with the heat transfer tube ,
A laminated header characterized by that. The flow path area of the flow path through which the refrigerant after merging among the merging flow paths is larger than the flow area of the plurality of first outlet flow paths,
The laminated header according to claim 1, wherein The channel area of the second outlet channel is larger than the channel area of the second inlet channel,
The laminated header according to claim 1 or 2, wherein In the first plate-like body, a plurality of folded flow passages are formed for folding and flowing out the flowing refrigerant.
The laminated header according to any one of claims 1 to 3, wherein The laminated header according to any one of claims 1 to 3,
A plurality of first heat transfer tubes connected to each of the plurality of first outlet channels and each of the plurality of first inlet channels;
With,
A heat exchanger characterized by that. The laminated header according to claim 4,
A plurality of first heat transfer tubes connected to each of the plurality of first outlet channels and to the respective inlet sides of the plurality of folded channels;
A plurality of second heat transfer tubes connected to the respective outlet sides of the plurality of folded flow passages and the plurality of first inlet flow passages;
With,
A heat exchanger characterized by that. The heat transfer tube is a flat tube,
The heat exchanger according to claim 5 or 6, characterized in that. Comprising the heat exchanger according to any one of claims 5 to 7,
The distribution channel flows out the refrigerant to the plurality of first outlet channels when the heat exchanger acts as an evaporator.
An air conditioner characterized by that. A heat exchanger according to claim 6,
When the heat exchanger acts as an evaporator, the distribution channel flows the refrigerant into the plurality of first outlet channels,
The first heat transfer tube is located on the windward side as compared to the second heat transfer tube when the heat exchanger acts as a condenser.
An air conditioner characterized by that.

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