JP6872694B2 - Plate fin laminated heat exchanger and refrigeration system using it - Google Patents

Description

The present invention relates to a plate fin laminated heat exchanger and a refrigerating system using the same.

Generally, in a refrigerating system such as an air conditioner or a refrigerator, a refrigerant compressed by a compressor is circulated to a heat exchanger such as a condenser or an evaporator to exchange heat with a second fluid for cooling or heating. The heat exchange efficiency of the exchanger greatly affects the performance and energy saving of the system. Therefore, heat exchangers are strongly required to have high efficiency.

Under such circumstances, as the heat exchanger of a refrigeration system such as an air conditioner or a refrigerator, a fin tube type heat exchanger configured by penetrating a heat transfer tube through a fin group is generally used. Therefore, the heat exchange efficiency is being improved and the size is being reduced by reducing the diameter of the heat transfer tube.

However, since there is a limit to the reduction in diameter of the heat transfer tube, improvement of heat exchange efficiency and miniaturization are approaching the limit.

On the other hand, among the heat exchangers used for exchanging heat energy, a plate fin laminated heat exchanger formed by laminating plate fins having a flow path is known.

This plate fin laminated heat exchanger exchanges heat between the refrigerant flowing through the flow path formed in the plate fins and the second fluid flowing between the laminated plate fins, and the amount of refrigerant is small. It is used in an air conditioner for vehicles having a low refrigerant pressure (see Patent Document 1).

11 and 12 show the plate fin laminated heat exchanger described in Patent Document 1, and the heat exchanger 100 is laminated with a large number of plate fins 102 having a heat transfer flow path 101 (see FIG. 12) through which a refrigerant flows. The end plates 104 are laminated on both end faces of the plate fin laminated body 103, and the inflow side header flow path 105 and the outflow side header flow path 106 are formed at both left and right ends of the heat transfer flow path 101.

Utility Model Registration No. 3192719

In the plate fin laminated heat exchanger described in Patent Document 1, since the heat transfer flow path 101 is formed by press-molding a concave groove in the plate fin 102, the cross-sectional area of the heat transfer flow path 101 is of the fin tube type. It can be made smaller than the heat transfer tube, and the heat exchange efficiency can be improved and the size can be reduced.

However, in the plate fin laminated heat exchanger, the area of the header flow paths 105 and 106 is extremely large compared to the area of each flow path 101, so that the pressure of the refrigerant in the header flow paths 105 and 106 is large. Therefore, there is a tendency that the portions of the end plate 102 having the header flow paths 105 and 106 (the upper and lower portions of the plate fin laminated heat exchanger shown by X in FIG. 10) expand and deform outward.

Therefore, as shown in FIG. 13, in order to prevent expansion and deformation in the header flow path portion, the applicant suppresses expansion and deformation of the portion of the end plate 102 at least in the portion where the header flow path is provided. It is proposed to provide the expansion / deformation suppressing means 107.

As a result, even in a heat exchanger having a large flow rate of refrigerant and high pressure, outward expansion deformation in the header flow path region portion can be suppressed, and the deformation problem in the header flow path region portion can be solved. did it.

The applicant also proposes to improve the heat exchange performance by branching the heat transfer flow path 101 provided between the header flow paths 105 and 106 of the plate fin 102 into a plurality of parts as shown in FIG.

However, when the heat transfer flow path 101 is branched into a plurality of branches, if it is used for a long period of time, deformation occurs in the connecting flow path 108 portion connecting the header flow path 106 on the gas refrigerant side and each of the branched heat transfer flow paths 101. , It has become clear that there is a problem with pressure resistance.

That is, the cross-sectional area of the connecting flow path 108 through which the gas refrigerant flows is formed to be larger than the total cross-sectional area of the heat transfer flow paths 101 on the gas refrigerant side from the viewpoint of reducing pressure loss and the like. Therefore, the refrigerant flowing in the connecting flow path 108 flows in a considerably large amount, which is equal to or more than the number of heat transfer channels of the refrigerant flowing in each heat transfer flow path 101. Therefore, in the connecting flow path 108 portion, a large pressure due to a large amount of refrigerant continues to be applied to the entire outer wall surface where the cross-sectional area becomes large and wide. Therefore, it has been found that the connecting flow path 108 portion cannot withstand the pressure continuously applied to the wall surface and starts to be deformed after being used for a long period of time.

The present invention has been made in view of these points, and provides a plate fin laminated heat exchanger with improved reliability by preventing deformation of the connecting flow path portion and a freezing system using the same. It is in.

In order to achieve the above object, the heat exchanger causes the second fluid to flow between the plate fin laminates of the plate fin laminate having the flow path through which the first fluid flows, and the first fluid and the above. A heat exchanger that exchanges heat with a second fluid, the plate fins of the plate fin laminate have a flow path region having a plurality of heat transfer channels through which the first fluid flows in parallel, and the flow path. A header region having an inlet side header flow path and an outlet side header flow path communicating with each heat transfer flow path of the region is provided, and the heat transfer flow path is formed by providing a concave groove in the plate fin. Further, the cross-sectional area of the connecting flow path connecting the header flow path on the outlet side and the plurality of heat transfer flow paths is set to be equal to or less than the total cross-sectional area of the total flow path including the plurality of heat transfer flow paths.

As a result, the pressure of the first fluid applied to the connecting flow path connecting the header flow path and the heat transfer flow path group becomes small, and the pressure resistance performance can be improved, and the connecting flow path portion can be used for a long period of time. It is possible to prevent deformation at.

According to the above configuration, the present invention can provide a highly reliable plate fin laminated heat exchanger by preventing deformation in the connecting flow path portion and a freezing system using the same.

A perspective view showing the appearance of the plate fin laminated heat exchanger according to the first embodiment of the present invention. An exploded perspective view of the plate fin laminated heat exchanger An exploded perspective view showing the plate and end plate of the plate fin laminated heat exchanger. (A) (b) Plan view showing each plate of the plate fin laminated heat exchanger An exploded perspective view showing a laminated state of plate fins in the plate fin laminated heat exchanger. Laminated perspective view of plate fins in the same plate fin laminated heat exchanger Sectional view taken along line AA of FIG. An exploded perspective view showing a modified example of the plate fin laminated heat exchanger according to the first embodiment of the present invention. The refrigerating cycle diagram of the air conditioner according to the second embodiment using the plate laminated heat exchanger of the present invention. Schematic cross-sectional view of the air conditioner Cross-sectional view of a conventional plate fin laminated heat exchanger Top view of plate fins in the conventional plate fin laminated heat exchanger Perspective view showing the appearance of the plate fin laminated heat exchanger proposed by the applicant. Plan view of plate fins proposed by the applicant

The first invention is a heat exchanger, in which a second fluid is allowed to flow between each plate fin laminate of a plate fin laminate having a flow path through which the first fluid flows, and the first fluid and the first fluid. A heat exchanger that exchanges heat with the second fluid, the plate fins of the plate fin laminate have a flow path region having a plurality of heat transfer channels through which the first fluid flows in parallel, and the flow. A header area having an inlet side header flow path and an outlet side header flow path communicating with each heat transfer flow path in the path region is provided, and the heat transfer flow path is formed by providing a concave groove in the plate fin. In addition, the cross-sectional area of the connecting flow path connecting the header flow path on the outlet side and the plurality of heat transfer flow paths is set to be equal to or less than the total cross-sectional area of the total flow path including the plurality of heat transfer flow paths.

As a result, the pressure of the first fluid applied to the connecting flow path connecting the header flow path and the heat transfer flow path group becomes small, and the pressure resistance performance can be improved, and the connecting flow path portion can be used for a long period of time. It is possible to prevent deformation at.

In the second invention, in the first invention, the cross-sectional area of the connecting flow path is set to be equal to or less than the cross-sectional area of at least one flow path of the plurality of heat transfer flow paths.

As a result, the surface area of the wall surface of the connecting flow path can be suppressed to the level of the surface area of the wall surface of the heat transfer flow path, the pressure from the first fluid applied to the connecting flow path portion can be significantly reduced, and the deformation can be prevented more reliably. The reliability can be greatly improved.

In the third invention, in the first invention, the cross-sectional area of the connecting flow path is 3 m ² or less.

As a result, the pressure of the first fluid such as the refrigerant applied to the wall surface of the connecting flow path can be suppressed to the pressure specified for the household and commercial air conditioners or less, and the pressure of the first fluid such as the household and commercial air conditioners can be suppressed. Even if the equipment has a large amount of refrigerant and a high pressure, it is possible to reliably prevent deformation of the connecting flow path portion and obtain a highly reliable heat exchanger.

A fourth invention is a freezing system, in which the heat exchanger constituting the freezing cycle is a plate fin laminated heat exchanger according to any one of the first to third inventions.

As a result, this refrigeration system can be made into a highly reliable refrigeration system while taking advantage of the small size and high performance effect that are the characteristics of the plate fin laminated heat exchanger.

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

The heat exchanger of the present disclosure is not limited to the configuration of the plate fin laminated heat exchanger described in the following embodiments, and has the same heat as the technical idea described in the following embodiments. It includes the configuration of the exchanger.

(Embodiment 1)
FIG. 1 is a perspective view showing the appearance of the plate fin laminated heat exchanger according to the first embodiment of the present invention, FIG. 2 is an exploded perspective view of the plate fin laminated heat exchanger, and FIG. 3 is a plate fin laminated heat exchanger. 4 (a) and 4 (b) are plan views showing each plate of the plate fin laminated heat exchanger, and FIG. 5 is a laminated plate fin in the plate fin laminated heat exchanger. An exploded perspective view showing a state, FIG. 6 is a laminated perspective view of plate fins in a plate fin laminated heat exchanger, and FIG. 7 is a sectional view taken along line AA of FIG.

As shown in FIGS. 1 and 2, in the heat exchanger 1 of the present embodiment, end plates 3a and 3b having substantially the same plan view are joined and integrated on both sides of a substantially bow-shaped plate fin laminate 2. It is composed of. A tube A4, which serves as an inlet when used as an evaporator and an outlet when used as a condenser, and a tube B5 which vice versa are provided on one end side of a substantially bow-shaped shape.

The end plates 3a and 3b on both sides of the plate fin laminate 2 are brazed so as to sandwich the plate fin laminate 2, and both ends in the longitudinal direction are connected and fixed by fastening means 9 such as bolts, nuts or caulking pin shafts. However, it retains the rigidity as a heat exchanger.

Further, the plate fins 2a constituting the plate fin laminate 2 are a heat transfer flow in which a first fluid such as a refrigerant (hereinafter referred to as a refrigerant) flows by joining the pair of plates 6a and 6b shown in FIG. 4 by brazing or the like. The configuration includes a flow path region having a path and a header area having header flow paths on the inlet side and the outlet side communicating with each heat transfer flow path in the flow path region, and a large number of them are stacked as shown in FIG. A stacking interval is formed between the plate fins 2a through which a second fluid such as air (hereinafter referred to as air) flows. Then, heat is exchanged between the refrigerant flowing through the heat transfer flow path provided in the plate fins 2a and the air flowing through the stacking gap between the plate fins 2a.

As shown in FIG. 5, the pair of plates 6a and 6b constituting the plate fins 2a have an opening 8a, which serves as a header flow path A8 and a header flow path B10 connected to the pipe A4 and the pipe B5 in one of the plates 6a. Ring-shaped concave grooves 8b and 10b provided at 10a and its opening edge, connecting flow path concave grooves 11a derived from ring-shaped concave grooves 8b and 10b, and diversion provided at the end of the connecting flow path concave groove 11a. A concave groove 12a for a road and a plurality of concave grooves 14a for forming a flow path that are branched and formed from the concave groove 12a for a branch flow path and are parallel to each other in a substantially U shape are provided.

On the other hand, the other plate 6b has openings 8c and 10c serving as header flow paths A8 and header flow paths B10, ring-shaped concave grooves 8d and 10d provided at the openings edges thereof, and concave grooves for connecting flow paths of the plate 6a. A groove 12b for branch flow path located at a portion facing the end portion of 11a and a plurality of concave grooves 14b for forming a flow path that are branched and formed from the concave groove 12b for branch flow path and are parallel to each other in a substantially U shape are provided. ..

The pair of plates 6a and 6b are formed by the ring-shaped concave grooves 8b, 10b and 8d, 10d provided at the openings 8a, 10a and 8c, 10c and the opening edges thereof, and the groove 12a and 12b for the branch flow path. The groove 14a and 14b for forming a flow path are joined by brazing so as to match each other, and at the openings 8a, 10a, 8c, 10c and the ring-shaped concave grooves 8b, 10b, 8d, 10d at the opening edge. The header flow path A8 and the header flow path B10 are formed, the connecting flow path 11 is formed by the connecting flow path concave groove 11a, and the diversion flow path concave grooves 12a and 12b and the flow path forming concave grooves 14a and 14b are separated from each other. The path 12 and the heat transfer flow path 14 are formed.

As shown in the overall view of the plate fins of FIG. 4, the heat transfer flow path 14 has a shape that is bent in a substantially bow shape and then makes a U-turn, similar to the outer shape of the plate fins 2a, and is shown in FIGS. 5 and 6. As described above, the two heat transfer flow paths 14-1 group connected to the header flow path A8 and on the side where the gas refrigerant flows, and the six heat transfer return flow paths connected to the header flow path B10 on the side where the liquid refrigerant flows. A heat insulating slit 16 is formed between the group 14-2 and the group 14-2 to prevent heat transfer between the two groups.

Then, in the plate fins 2a of the plate fin laminate 2 having the above configuration, air flows between the heat transfer flow paths 14 by a plurality of protrusions 15 (see FIG. 4) appropriately provided along the longitudinal direction of the plate fins 2a. A stacking interval T1 (see FIG. 7) is formed.

Further, an interval T2 is also formed between the connecting flow paths 11, and air flows through the interval T2 to improve the heat exchange efficiency.

Here, the connecting flow path 11 on the side through which the gas refrigerant flows is the total cross-sectional area of the flow paths including the heat transfer flow paths 14, and here, the six heat transfer return flow paths 14 on the side through which the gas refrigerant flows. It is formed so that the total cross-sectional area of each of the two groups of heat transfer channels is equal to or less than the total cross-sectional area of the flow paths combined. In particular, in the present embodiment, the cross-sectional area of the connecting flow path 11 is set to be equal to or less than the cross-sectional area of one heat transfer flow path of the heat transfer return flow path 14-2 group.

Next, the operation and effect of the plate fin laminated heat exchanger configured as described above will be described.

When the heat exchanger of the present embodiment is used, for example, under evaporation conditions, a liquid refrigerant in a gas-liquid two-phase state flows from the pipe A4 into the header flow path A8 on the inlet side of the plate fin laminate 2. As is clear from the flow path configurations shown in FIGS. 6 and 7, the liquid refrigerant flowing into the header flow path A8 is transferred to the heat transfer flow path 14 via the communication flow path 11 and the branch flow path 12 of each plate fin 2a. It flows to the heat transfer flow path 14-1 group. The refrigerant flowing into the heat transfer outflow flow path 14-1 group of each plate fin 2a makes a U-turn and flows out from the pipe B5 to the refrigerant circuit of the refrigeration system via the heat transfer return flow path 14-2 group and the header flow path B10. To do.

Then, when the refrigerant flows from the heat transfer flow path 14-1 of the heat transfer flow path 14 to the pipe B5 via the heat transfer return flow path 14-2 group, the refrigerant is gasified and the plate fins of the plate fin laminate 2 are used. It exchanges heat with the air that passes through the stacking interval.

The heat exchange is performed as described above, and the connecting flow path 11 on the gas refrigerant side that flows the gas refrigerant from the heat transfer return flow path 14-2 group through which the gasified refrigerant flows to the header flow path B10 is the same. Since the cross-sectional area is equal to or less than the total total cross-sectional area of the total cross-sectional area of the combined heat transfer flow paths of the plurality of heat transfer return flow paths 14-2 groups, the flow rate of the refrigerant flowing inside the cross-sectional area is small. Therefore, the refrigerant pressure applied to the wall surface of the connecting flow path 11 becomes small, and the pressure resistance performance is improved. Therefore, even if it is used for a long period of time, it is possible to prevent deformation in the connecting flow path portion.

In particular, in the present embodiment, since the cross-sectional area of the connecting flow path 11 is equal to or less than the cross-sectional area of at least one of the plurality of heat transfer return flow paths 14-2 groups, the pressure applied to the wall surface thereof is significantly reduced. It is possible to more reliably prevent deformation in the connecting flow path portion and greatly improve reliability.

Further, when the cross-sectional area of the connecting flow path 11 is set to 3 m ² or less, the pressure of the refrigerant applied to the wall surface of the connecting flow path 11 can be suppressed to the pressure specified for the home and commercial air conditioners or less. Therefore, even in a heat exchanger having a large amount of refrigerant as described above or a heat exchanger using an environment-friendly refrigerant having a high compression ratio, the connecting flow path 11 on the gas refrigerant side of the plate fin laminate 2 It is possible to prevent expansion and deformation of the part. Then, the pressure of the refrigerant can be used in a higher state to obtain a highly efficient heat exchanger.

Further, as described above, the cross-sectional area of the connecting flow path 11 is equal to or less than the total cross-sectional area of the total cross-sectional area of the combined heat transfer flow paths of the plurality of heat transfer return flow paths 14-2 groups, or the heat transfer return flow path 14-. By setting the cross-sectional area of at least one of the two groups to be less than or equal to the cross-sectional area of one of the flow paths, or not more than 3 m ² , the interval T2 can be formed between the connecting flow paths 11 as shown in FIG. As a result, air can flow through the interval T2, and the heat exchange efficiency can be improved while ensuring the pressure resistance of the connecting flow path 11.

That is, in order to secure the pressure resistance of the connecting flow path 11, for example, if the outer wall surfaces of the connecting flow paths 11 overlapping in the stacking direction are butted against each other, the pressure resistance can be secured without reducing the cross-sectional area of the connecting flow path 11. However, in this case, since the distance between the connecting flow paths 11 is eliminated, the portion cannot be used as the heat exchange region. However, if it is configured as in the present embodiment, as described above, a space T2 can be formed between the connecting flow paths 11 to be used as a heat exchange region, and the heat exchange efficiency can be improved.

Regarding the pressure loss caused by reducing the cross-sectional area of the connecting flow path 11, there are a plurality of heat transfer flow paths 14 of the heat transfer flow path 14, that is, the heat transfer return flow path 14-2 through which the gas-side refrigerant having a large pressure loss flows. Since the multi-pass type is provided, the flow rate per flow path is reduced, the influence on the performance can be minimized, and the level can be set to a level that does not cause a problem in practical use.

Further, in the heat exchanger of the present embodiment, since the heat transfer flow path 14 group provided in the plate fin 2a is formed in a substantially U shape and folded back, the plate fin 2a is made large (the length dimension is made long). It is possible to lengthen the length of the refrigerant flow path without doing so.

As a result, it is possible to improve the efficiency of the refrigerating system by increasing the heat exchange efficiency between the refrigerant and the air while reducing the size of the heat exchanger.

The heat exchanger 1 has been described in a form in which the heat transfer flow path 14 makes a U-turn, but as shown in FIG. 8, this is a header flow path tube A8 on one end side of the plate fin 2a and a header flow on the opposite side. The heat transfer flow path 14 provided with the passage pipe B10 and connecting the passage pipes B10 may be linear in only one direction. In this case, the heat transfer forward flow path 14-1 group and the heat transfer return flow path 14-2 group described in the above embodiment are the same heat transfer flow path 14, and the header flow path on the gas refrigerant side, for example, the outlet. The cross-sectional area of the connecting flow path 11 on the side header flow path B10 is the total cross-sectional area of the heat transfer flow path 14 in which the heat transfer forward flow path 14-1 group and the heat transfer return flow path 14-2 group are combined. Below, or at least one flow path cross-sectional area or less, or 3 m ² or less may be used.

As described above, in the present embodiment, the case where the heat exchanger is used as the evaporator has been described as an example. Therefore, for convenience, the header flow path on the gas refrigerant side is the header flow path on the outlet side and the header flow on the liquid side. The path is called the header flow path on the inlet side, but when used as a condenser, the outlet side and the inlet side are reversed. Therefore, the header flow path on the outlet side in the claims of the present invention means the header flow path on the gas refrigerant side, and the header flow path on the inlet side means the header flow path on the liquid side.

(Embodiment 2)
The second embodiment is an air conditioner configured by using the plate fin laminated heat exchanger according to the first embodiment.

FIG. 9 is a refrigeration cycle diagram of the air conditioner, and FIG. 10 is a schematic cross-sectional view showing the indoor unit of the air conditioner.

In FIGS. 9 and 10, the air conditioner is composed of an outdoor unit 51 and an indoor unit 52 connected to the outdoor unit 51. The outdoor unit 51 includes a compressor 53 for compressing the refrigerant, a four-way valve 54 for switching the refrigerant circuit during cooling and heating operation, an outdoor heat exchanger 55 for exchanging heat between the refrigerant and the outside air, a decompressor 56 for reducing the refrigerant, and an outdoor unit. A blower 59 is arranged. Further, the indoor unit 52 is provided with an indoor heat exchanger 57 for exchanging heat between the refrigerant and the indoor air, and an indoor blower 58. Then, the compressor 53, the four-way valve 54, the indoor heat exchanger 57, the decompressor 56, and the outdoor heat exchanger 55 are connected by a refrigerant circuit to form a heat pump type refrigeration cycle.

In the refrigerant circuit according to the present embodiment, a refrigerant in which tetrafluoropropene or trifluoropropene, difluoromethane or pentafluoroethane or tetrafluoroethane is used alone, or a mixture of two components or three components, respectively, is used.

The air conditioner having the above configuration switches the four-way valve 54 so that the discharge side of the compressor 53 and the outdoor heat exchanger 55 communicate with each other during the cooling operation. As a result, the refrigerant compressed by the compressor 53 becomes a high-temperature and high-pressure refrigerant and is sent to the outdoor heat exchanger 55 through the four-way valve 54. Then, it exchanges heat with the outside air to dissipate heat, becomes a high-pressure liquid refrigerant, and is sent to the decompressor 56. In the decompressor 56, the pressure is reduced to become a low-temperature low-pressure two-phase refrigerant, which is sent to the indoor unit 52. In the indoor unit 52, the refrigerant enters the indoor heat exchanger 57, exchanges heat with the indoor air, absorbs heat, evaporates and vaporizes, and becomes a low-temperature gas refrigerant. At this time, the indoor air is cooled to cool the room. Further, the refrigerant returns to the outdoor unit 51 and is returned to the compressor 53 via the four-way valve 54.

During the heating operation, the four-way valve 54 is switched so that the discharge side of the compressor 53 and the indoor unit 52 communicate with each other. As a result, the refrigerant compressed by the compressor 53 becomes a high-temperature and high-pressure refrigerant, passes through the four-way valve 54, and is sent to the indoor unit 52. The high-temperature and high-pressure refrigerant enters the indoor heat exchanger 57, exchanges heat with the indoor air to dissipate heat, and is cooled to become a high-pressure liquid refrigerant. At this time, the indoor air is heated to heat the room. After that, the refrigerant is sent to the compressor 56, decompressed in the compressor 56 to become a low-temperature low-pressure two-phase refrigerant, sent to the outdoor heat exchanger 55 to exchange heat with the outside air, evaporate and vaporize, and pass through the four-way valve 54. Then, it is returned to the compressor 53.

The air conditioner configured as described above has a small size and high performance by using the heat exchanger shown in the above embodiment for the outdoor heat exchanger 55 or the indoor heat exchanger 57. Since it is a highly reliable plate fin laminated heat exchanger, it can be a highly energy-saving and highly reliable refrigeration system.

The plate fin laminated heat exchanger according to the present invention and the refrigerating system using the same have been described above using the above-described embodiment, but the present invention is not limited thereto. That is, the embodiments disclosed this time are exemplary and not restrictive in all respects, and the scope of the present invention is indicated by the claims and has the same meaning and scope as the claims. All changes are included.

As described above, the present invention provides a highly reliable, compact, high-performance plate fin laminated heat exchanger that prevents deformation in the connecting flow path portion that connects the header flow path and the heat transfer flow path, as described above. The refrigeration system used can be provided. Therefore, it can be widely used in heat exchangers and various refrigerating devices used for home and commercial air conditioners, and has great industrial value.

1 Heat exchanger 2 Plate fin laminate 2a Plate fin 3a, 3b End plate 4 Tube A
5 Tube B
6a plate 6b plate 8 header flow path A
8a, 8c Opening 8b, 8d Ring-shaped concave groove 9 Fastening means (bolts and nuts)
10 Header flow path B
10a, 10c Opening 10b, 10d Ring-shaped concave groove 11 Communication flow path 11a, 11b Concave groove for communication flow path 12-minute flow path 12a, 12b Concave groove for branch flow path 14 Heat transfer flow path 14-1 Heat transfer flow path 14-2 Heat transfer return flow path 14a Concave groove for flow path formation 14b Concave groove for flow path formation 15 Protrusion 16 Insulation slit 51 Outdoor unit 52 Indoor unit 53 Compressor 54 Four-way valve 55 Outdoor heat exchanger 56 Decompressor 57 Indoor heat exchanger 58 Indoor blower

Claims (3)

A heat exchanger in which a second fluid is allowed to flow between each plate fin laminate of a plate fin laminate having a flow path through which the first fluid flows, and heat is exchanged between the first fluid and the second fluid. The plate fins of the plate fin laminate communicate with a flow path region having a plurality of heat transfer flow paths through which the first fluid flows in parallel and each heat transfer flow path in the flow path region below the heat transfer flow path. A header region having an inlet side header flow path and an outlet side header flow path is provided, and the heat transfer flow path is formed by providing a concave groove in the plate fin, and the outlet side header flow. The connecting flow path connecting the path and the heat transfer flow path group is composed of a single flow path, and the cross-sectional area of the connecting flow path is equal to or less than the total total cross-sectional area of the flow path including the plurality of heat transfer flow paths. A plate fin laminated heat exchanger with a road cross-sectional area of 3 mm ² or less. The plate fin laminated heat exchanger according to claim 1, wherein the cross-sectional area of the connecting flow path is equal to or less than the cross-sectional area of at least one of the plurality of heat transfer channels. A refrigeration system in which the heat exchanger constituting the refrigeration cycle is the plate fin laminated heat exchanger according to any one of claims 1 and 2.

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