CN109564071B

CN109564071B - Heat exchanger and refrigeration system using the same

Info

Publication number: CN109564071B
Application number: CN201780047791.5A
Authority: CN
Inventors: 奥村拓也; 山本宪昭; 名越健二; 大城崇裕
Original assignee: Panasonic Intellectual Property Management Co Ltd
Current assignee: Panasonic Intellectual Property Management Co Ltd
Priority date: 2016-10-21
Filing date: 2017-10-13
Publication date: 2020-09-15
Anticipated expiration: 2037-10-13
Also published as: CN109564071A; JP6767637B2; JPWO2018074342A1; MY195637A; WO2018074342A1

Abstract

The heat exchanger of the present invention includes a plate fin laminate in which a plurality of plate fins each having a flow path through which a 1 st fluid flows are laminated; and a 1 st end plate and a 2 nd end plate respectively arranged at both ends of the plate fin laminate in the stacking direction. The plurality of plate fins each have a flow path region and a header region. The 1 st fluid flow path is constituted by a recessed groove provided in each of the plurality of plate fins. Expansion deformation suppressing portions that suppress expansion deformation of the 1 st header region corresponding portion and the 2 nd header region corresponding portion of the 2 nd header plate are provided at the 1 st header region corresponding portion of the 1 st end plate and the 2 nd header region corresponding portion of the 2 nd end plate.

Description

Heat exchanger and refrigeration system using the same

Technical Field

The present invention relates to a heat exchanger and a refrigeration system using the same. The present invention particularly relates to a plate-fin stacked heat exchanger including a plate-like plate-fin stack through which a refrigerant flows, and a refrigeration system using the same.

Background

In general, a refrigeration system such as an air conditioner or a refrigerator circulates a refrigerant compressed by a compressor through a heat exchanger such as a condenser or an evaporator, and performs cooling or heating by exchanging heat with a 2 nd fluid such as air. In the refrigeration system, the performance and energy saving performance of the system are greatly influenced by the heat exchange efficiency of the heat exchanger. Therefore, the heat exchanger is strongly required to have high efficiency.

Among these, a heat exchanger of a refrigeration system generally uses a fin-tube type heat exchanger in which heat transfer tubes are inserted into fin groups, and can improve heat exchange efficiency and reduce the size by reducing the diameter of the heat transfer tubes.

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

On the other hand, as a heat exchanger used for exchanging thermal energy, a plate fin stacked type heat exchanger in which plate fins having fluid flow passages are stacked is known.

The plate-fin stacked heat exchanger exchanges heat between a fluid flowing through flow passages formed in the plate fins and a 2 nd fluid flowing between the stacked plate fins. It is widely used in air conditioners for vehicles and the like (see patent document 1).

Fig. 36 and 37 show the plate-fin stacked heat exchanger described in patent document 1. In the heat exchanger 100, plate fins 102 having flow passages 101 through which a refrigerant flows are stacked to form a plate fin stacked body 103. End plates 104 are laminated on both side portions of the plate-fin laminated body 103.

Documents of the prior art

Patent document

Patent document 1: japanese Utility model registration No. 3192719

Disclosure of Invention

The plate-fin stacked heat exchanger described in patent document 1 has an advantage that the cross-sectional area of the flow path 101 can be further reduced as compared with a fin-tube type heat transfer tube because the flow path 101 is formed by press-forming concave grooves in the plate fins 102.

However, the area of the header flow path 105 through which the refrigerant flows to each flow path 101 is extremely larger than the area of each flow path 101, and therefore the pressure of the refrigerant in the header flow path 105 portion becomes large. Thereby, portions of the end plate 102 having the header flow channels 105 (upper and lower portions of the plate fin stacked heat exchanger indicated by X in fig. 36) may be deformed to expand outward.

In the case of a heat exchanger of an automobile air conditioner, the expansion deformation of the header flow path 105 portion can be suppressed by the rigidity of the end plate 104 because the refrigerant amount is small and the refrigerant pressure is not so high. The existence of problems is thus not recognized.

However, according to the experiments of the inventors, in the case of a heat exchanger such as a home air conditioner or an industrial air conditioner in which the amount of refrigerant used is larger than that of an automobile air conditioner, the pressure of the expansion deformation of the header flow path 105 portion becomes larger than that of the automobile air conditioner, and it is difficult to suppress the expansion deformation of the header flow path 105 portion. Further, in some cases, the end plate may be deformed to expand outward.

In recent years, in view of preventing global warming, practical use of R1123(1,1, 2-trifluoroethylene) and R1132(1, 2-tetrafluoroethylene) refrigerants having a small Global Warming Potential (GWP) have been studied. Since the pressures of these refrigerants are higher than those of the R410A refrigerant of the related art, when such a refrigerant is used, it is conceivable that expansion deformation of the header flow path 105 portion becomes remarkable. Thus, countermeasures need to be provided.

The present invention has been made in view of these circumstances and the problems that arise when dealing with environmental demands, and it is possible to suppress expansion deformation of a header flow path portion even in a heat exchanger used for a household air conditioner, an industrial air conditioner, or the like. This makes it possible to provide a heat exchanger having high heat exchange efficiency and a high-performance refrigeration system using the heat exchanger.

To achieve the above object, the heat exchanger of the present invention comprises: a plate fin laminate in which a plurality of plate fins are laminated, wherein each plate fin laminate has a flow path through which a 1 st fluid flows; a 1 st end plate and a 2 nd end plate respectively arranged at both ends of the plate fin laminate in the stacking direction; and an inflow/outflow tube including an inflow tube and an outflow tube through which the 1 st fluid flowing through the flow path passes. Flowing a 2 nd fluid between the plate fin lamination layers of the plate fin lamination body, and performing heat exchange between the 1 st fluid and the 2 nd fluid. The plurality of plate fins respectively include: a flow path region having a plurality of 1 st fluid flow paths for the 1 st fluid to flow; and a header area having header flow paths for communicating the plurality of 1 st fluid flow paths with the inflow and outflow tubes, respectively. The 1 st fluid flow path is formed by concave grooves provided in the plurality of plate fins, respectively. An expansion deformation suppressing portion that suppresses expansion deformation of the 1 st header region corresponding portion and the 2 nd header region corresponding portion is provided at the 1 st header region corresponding portion of the 1 st end plate and the 2 nd header region corresponding portion of the 2 nd end plate.

This reduces the diameter of the 1 st fluid flow passage, thereby promoting the improvement and miniaturization of the heat exchange efficiency. Further, even in the heat exchanger having a high pressure in which the flow rate of the refrigerant as the 1 st fluid is large, the expansion deformation of the portion corresponding to the header region to the outside can be suppressed. By using such a heat exchanger, a compact and high-performance refrigeration system having high energy saving performance can be provided.

According to the above configuration of the present invention, in the heat exchanger used for home use, industrial use air conditioning, or the like, expansion deformation of the header region portion can be suppressed. Thereby, a small-sized and high-efficiency heat exchanger and a refrigeration system using the same can be provided.

Drawings

Fig. 1 is a perspective view showing the appearance of a plate-fin stacked heat exchanger according to embodiment 1 of the present invention.

Fig. 2 is an exploded perspective view showing the plate-fin stacked heat exchanger in a vertically separated state.

Fig. 3 is an exploded perspective view of the plate fin stacked type heat exchanger.

Fig. 4 is a side view showing a stacked state of plate fins of the plate fin stacked body in the plate fin stacked heat exchanger.

Fig. 5 is a schematic view showing a cross section a-a of fig. 1.

Fig. 6 is a schematic view showing a B-B section of fig. 1.

Fig. 7 is a schematic view showing a C-C section of fig. 2.

Fig. 8 is a perspective view showing a connection portion of inflow and outflow tubes and a header opening portion in a plate fin stacked heat exchanger according to embodiment 1 of the present invention in a cut-off manner.

Fig. 9 is a perspective view showing a refrigerant flow path group portion of the plate-fin stacked body in the plate-fin stacked heat exchanger in a cut-off manner.

Fig. 10 is a perspective view showing a refrigerant flow path group portion in the plate-fin stacked heat exchanger in a cut-off manner.

Fig. 11 is a perspective view showing a boss hole portion for positioning the plate-fin stacked body in the plate-fin stacked heat exchanger.

Fig. 12 is a perspective view showing a plate-fin stacked body in the plate-fin stacked heat exchanger with a header opening portion cut off.

Fig. 13 is a plan view of a plate fin constituting the plate fin stacked body of the plate fin stacked type heat exchanger.

Fig. 14 is an enlarged plan view showing the header area of the plate fin.

Fig. 15 is an exploded view showing the structure of the plate fin partially enlarged.

Fig. 16A is a plan view of the 1 st plate fin.

Fig. 16B is a plan view of the 2 nd plate fin.

Fig. 16C is a plan view for explaining a state where the 1 st and 2 nd fin plates are overlapped.

Fig. 17 is a diagram for explaining the refrigerant flow operation of the plate fin.

Fig. 18 is an enlarged perspective view showing a protrusion provided in the flow path region of the plate fin.

Fig. 19 is an enlarged perspective view showing a projection provided at the U-shaped portion side end of the refrigerant flow path of the plate fin.

Fig. 20 is a perspective view showing the appearance of a plate-fin stacked heat exchanger according to embodiment 2 of the present invention.

Fig. 21 is a plan view of a plate fin constituting the plate fin stacked body of the plate fin stacked type heat exchanger.

Fig. 22 is an exploded view showing a structure of a plate fin of the plate fin stacked heat exchanger in a partially enlarged manner.

Fig. 23 is a perspective view showing a refrigerant flow path group portion of the plate-fin stacked body in the plate-fin stacked heat exchanger in a cut-off manner.

Fig. 24 is a perspective view showing the appearance of a plate-fin stacked heat exchanger according to embodiment 3 of the present invention.

Fig. 25 is a perspective view showing a state in which the flow distribution control tubes are pulled out from the plate-fin stacked heat exchanger.

Fig. 26 is a perspective view showing the flow distribution control tube insertion portions in the plate fin laminate of the plate fin laminate type heat exchanger.

Fig. 27 is a perspective view of the flow dividing control tube of the plate fin stacked type heat exchanger.

Fig. 28 is a schematic cross-sectional view showing a flow dividing control tube portion of the plate fin stacked heat exchanger.

Fig. 29 is a perspective view showing the appearance of a plate-fin stacked heat exchanger according to embodiment 4 of the present invention.

Fig. 30 is a refrigeration cycle diagram of an air conditioner using the plate-stacked heat exchanger of the present invention.

Fig. 31 is a schematic diagram showing a cross section of the air conditioner.

Fig. 32 is a perspective view of a plate-fin stacked heat exchanger according to a modification of the present invention.

Fig. 33 is an exploded perspective view of the plate-fin stacked heat exchanger according to this modification.

Fig. 34 is a perspective view showing a reinforcing plate of the plate-fin stacked heat exchanger according to this modification.

Fig. 35 is a perspective view showing an end plate of the plate-fin stacked heat exchanger according to this modification.

Fig. 36 is a schematic cross-sectional view of a conventional plate-fin stacked heat exchanger.

Fig. 37 is a plan view of the plate fins of the conventional plate fin laminated heat exchanger.

Detailed Description

The heat exchanger of the invention 1 comprises: a plate fin laminate in which a plurality of plate fins are laminated, wherein each plate fin laminate has a flow path through which a 1 st fluid flows; a 1 st end plate and a 2 nd end plate respectively arranged at both ends of the plate fin laminate in the stacking direction; and an inflow/outflow tube including an inflow tube and an outflow tube through which the 1 st fluid flowing through the flow path passes. Flowing a 2 nd fluid between the plate fin lamination layers of the plate fin lamination body, and performing heat exchange between the 1 st fluid and the 2 nd fluid. The plurality of plate fins respectively include: a flow path region having a plurality of 1 st fluid flow paths for the 1 st fluid to flow; and a header area having header flow paths for communicating the plurality of 1 st fluid flow paths with the inflow and outflow tubes, respectively. The 1 st fluid flow path is formed by concave grooves provided in the plurality of plate fins, respectively. An expansion deformation suppressing portion that suppresses expansion deformation of the 1 st header region corresponding portion and the 2 nd header region corresponding portion is provided at the 1 st header region corresponding portion of the 1 st end plate and the 2 nd header region corresponding portion of the 2 nd end plate.

The invention of claim 2 is such that the expansion deformation suppressing portion has a joining portion that joins the 1 st header region corresponding portion and the 2 nd header region corresponding portion.

This can reliably suppress deformation of the header region corresponding portion to be expanded outward, which is caused by applying an outward expansion deformation force to the header region corresponding portion of the end plate. This can reduce the diameter of the 1 st fluid flow path while preventing deformation of the header region corresponding portion, and can promote improvement in heat exchange efficiency and miniaturization.

In the 3 rd aspect of the present invention, a 1 st reinforcing plate is disposed on an outer surface of a portion corresponding to the 1 st header region, a 2 nd reinforcing plate is disposed on an outer surface of a portion corresponding to the 2 nd header region, the 1 st reinforcing plate and the 2 nd reinforcing plate are connected by the connecting portion, and the plate-fin laminate is sandwiched between the 1 st end plate and the 2 nd end plate, and the 1 st reinforcing plate and the 2 nd reinforcing plate.

This can reliably suppress deformation of the header region corresponding portion to be expanded outward, which is caused by applying an outward expansion deformation force to the header region corresponding portion of the end plate. The suppression of the deformation is enhanced by the rigidity of the reinforcing plate itself. This makes it possible to reliably suppress expansion deformation even when an environment-compatible refrigerant having a high pressure is used. That is, the 1 st fluid flow channel can be made smaller while preventing expansion deformation in the header region corresponding portion, thereby promoting improvement in heat exchange efficiency and downsizing. Further, the reinforcing plates are provided at the header region corresponding portions, and therefore the volume increased by the provision of the reinforcing plates becomes the volume increased at the header region corresponding portions on both sides of the plate fin laminated body. This can minimize the increase in volume and improve the heat exchange efficiency without impairing the miniaturization of the heat exchanger.

In the 4 th aspect of the present invention, the 1 st fluid flow channels are each formed in a U shape, and a header flow channel on a fluid inlet side communicating with the inlet pipe and a header flow channel on a refrigerant outlet side communicating with the outlet pipe are disposed on one end side of each of the plate fins.

This makes it possible to increase the heat exchange amount of the refrigerant by increasing the length of the 1 st fluid flow path without increasing the plate fins (increasing the length), and further improve the heat exchange efficiency. In addition, the miniaturization of the heat exchanger can be promoted. Here, by concentrating the inlet-side manifold flow path and the outlet-side manifold flow path on the respective one end sides of the plate fins, the manifold flow path portion most likely to be subjected to stress is biased toward the one end side. This causes a problem in pressure resistance at the corresponding portion of the header region. In contrast, with the above configuration, the expansion deformation of the header region corresponding portion can be reliably prevented.

In the 5 th aspect of the present invention, the flow dividing control pipe extending toward the 2 nd end plate is connected to the 1 st surface of the 1 st reinforcing plate, and the inflow/outflow pipe is connected to the 2 nd surface of the 1 st reinforcing plate.

Thus, the heat exchange efficiency can be further improved by utilizing the flow dividing effect of the flow dividing control tube. Further, the flow distribution control pipe can be provided so as to protrude into the header flow path only by attaching the reinforcing plate. This prevents a defective joining of the plate fins due to melting of the solder at the welded portions of the plate fins, which may occur when the shunt control tube is mounted after being welded or the like, and a quality defect such as leakage of the refrigerant, which may occur therewith. As a result, a high-quality and high-efficiency heat exchanger can be realized.

In the invention according to claim 6, the 1 st reinforcing plate is formed of a material having a potential difference with the flow dividing control tube and the inflow/outflow tube smaller than a potential difference between the flow dividing control tube and the inflow/outflow tube when the flow dividing control tube and the inflow/outflow tube are directly connected to each other.

This can prevent contact corrosion of different metals occurring when the flow distribution control pipe and the inflow/outflow pipe are directly connected, and can greatly improve the reliability in long-term use. In particular, a significant effect can be expected in a heat exchanger for an air conditioner in which an inflow/outflow pipe is often made of a copper pipe and a bypass control pipe is made of stainless steel or the like.

In the 7 th aspect of the present invention, through holes are provided in the plurality of plate fins, the 1 st end plate and the 2 nd end plate, and the 1 st reinforcing plate and the 2 nd reinforcing plate, and the fastening portion penetrates through the through holes to connect the 1 st reinforcing plate and the 2 nd reinforcing plate.

This can prevent the expansion deformation of the header region corresponding portion of the end plate. In addition, when the plate fins and the end plates are laminated by fitting pins (jigs) into through holes for fastening portions of the reinforcing plates, the through holes can be used as positioning portions. Thereby, the expansion deformation of the header region portion can be prevented and the productivity can be improved.

In the 8 th aspect of the present invention, the expansion deformation suppressing portion is formed of a hollow frame, and outer surfaces of the 1 st header region corresponding portion and the 2 nd header region corresponding portion are fitted into the hollow frame.

This makes it possible to easily perform the mounting in a short time and improve the productivity, as compared with the case where the mechanical bonding portion is used for mounting the expansion deformation suppressing portion to the plate-fin laminated body.

In the 9 th aspect of the present invention, the 1 st reinforcing plate is provided with a pipe hole into which the inflow/outflow pipe is inserted.

This enables the reinforcing plate to be fixed to the heat exchanger side surface in the vicinity of the inflow/outflow pipe, thereby enhancing the effect of preventing the expansion deformation of the portion corresponding to the header region.

In the invention according to claim 10, the piping hole is tapered.

Thus, when the inflow/outflow pipe is welded to the heat exchanger, the torch can be efficiently brought into contact with the heat exchanger. Thereby enabling the welding time to be shortened. When the heat exchanger is used as an evaporator, dew generated in the heat exchanger can be discharged without being retained in the pipe hole. Thereby improving the corrosion resistance of the heat exchanger.

In the 11 th aspect of the present invention, the 2 nd reinforcing plate is provided with a communication hole having a thread groove, and a screw portion is provided at an end of the connecting portion.

This allows the reinforcing plate and the coupling portion to be directly fixed, and the number of components can be reduced as compared with the case where no screw groove is provided, and the workability in fixing is improved. Further, even if a force for compressing the heat exchanger is applied in the stacking direction of the heat exchanger, the external force can be alleviated.

In the 12 nd aspect of the present invention, the 2 nd end plate is provided with a through hole having a screw groove.

This allows the end plate and the connecting portion to be directly fixed, and even if a force for compressing the heat exchanger is applied in the stacking direction of the heat exchanger, the external force can be more firmly reduced.

In the 13 th aspect of the present invention, a dew water receiver is disposed at a peripheral edge portion of the 1 st reinforcing plate and a peripheral edge portion of the 2 nd reinforcing plate.

This enables dew-water generated on the surface of the reinforcing plate to flow to a predetermined portion.

The 14 th invention is a refrigeration system having the heat exchanger.

This refrigeration system has a heat exchanger that can suppress expansion deformation in the header region portion, and that is small and efficient. Thus, a high-performance refrigeration system having high energy saving performance can be realized.

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

The heat exchanger according to the present invention is not limited to the structure of the plate-fin stacked heat exchanger described in the following embodiments, and may include a structure of a heat exchanger equivalent to the technical idea described in the following embodiments.

The embodiments described below are merely examples of the present invention, and the structures, functions, operations, and the like described in the embodiments are illustrative and do not limit the present invention.

(embodiment mode 1)

Fig. 1 is a perspective view showing an appearance of a plate-fin stacked heat exchanger (hereinafter, simply referred to as a heat exchanger) 1 according to the present embodiment. Fig. 2 is an exploded perspective view showing a plate fin stacked heat exchanger in a vertically separated state. Fig. 3 is an exploded perspective view of a plate fin stacked type heat exchanger. Fig. 4 is a side view showing a stacked state of plate fins in the plate fin stacked body. Fig. 5 to 7 are schematic views showing cross sections of the plate-fin stacked heat exchanger.

As shown in fig. 1 to 8, a heat exchanger 1 of the present embodiment includes: an inflow tube (inlet header) 4 into which the refrigerant as the 1 st fluid flows; a plate fin laminate 2 formed by laminating a plurality of plate fins 2a each having a rectangular plate shape; and an outlet pipe (outlet header) 5 for discharging the refrigerant flowing through the flow path in the plate fin 2 a.

On both sides (upper side and lower side in fig. 1) in the stacking direction of the plate-fin stacked body 2,

end plates

3a, 3b having substantially the same shape as the plate fins 2a in a plan view are provided. The

end plates

3a and 3b are formed of a rigid plate material, and are formed by grinding a metal material such as aluminum, an aluminum alloy, or stainless steel and then performing metal processing.

The

end plates

3a and 3b and the plurality of plate fins 2a are welded and integrated in a stacked state. They may also be joined by other fixing methods having heat resistance, for example, using a chemical joining member.

In the present embodiment, the

end plates

3a and 3b disposed on both sides of the plate-fin laminated body 2 are fastened and fixed at both longitudinal end portions thereof by fastening portions 9 such as bolts, nuts, and caulking pins. That is, the

end plates

3a, 3b on both sides of the plate-fin laminated body mechanically connect the fixed plate-fin laminated body 2 so as to sandwich the plate-fin laminated body 2.

In the present embodiment, reinforcing

plates

16a, 16b are further disposed at the header region corresponding portions of the longitudinal end portions (left end portion in fig. 1) of the

end plates

3a, 3 b. Here, the "header region corresponding portion" refers to a portion of the end plate (a predetermined region of the end plate) that overlaps with the header region H (see fig. 13) of the plate fin 2a when the

end plates

3a, 3b and the plate fin 2a overlap. The reinforcing

plates

16a, 16b are fastened and fixed by the fastening portions 9, whereby the reinforcing

plates

16a, 16b mechanically sandwich the

end plates

3a, 3b and the plate-fin stacked body 2.

The reinforcing

plates

16a and 16b are made of a rigid plate material, for example, a metal material such as stainless steel or aluminum alloy, as in the case of the

end plates

3a and 3 b. The reinforcing

plates

16a and 16b are preferably made of a material having higher rigidity than the

end plates

3a and 3b or have a thick plate thickness.

The plate fins 2a have a plurality of refrigerant flow path groups arranged in parallel in which the refrigerant as the 1 st fluid flows (the refrigerant flow path structure of the plate fins 2a including the refrigerant flow path groups will be described later in detail). The refrigerant flow path group is formed in a U shape (including a substantially U shape). The inlet tubes 4 and the outlet tubes 5 connected to the refrigerant flow path group (hereinafter, the inlet tubes 4 and the outlet tubes 5 are collectively referred to as inlet and outlet tubes) are arranged so as to be concentrated on one end portion side (upper side in fig. 1) of the end plate 3a on one side of the plate fin laminate 2.

In the heat exchanger 1 of the present embodiment configured as described above, the refrigerant flows in parallel in the longitudinal direction in the plurality of flow path groups inside the respective plate fins 2a of the plate fin laminate 2, turns around in a U-turn, and is discharged from the outlet pipe 5. On the other hand, air as the 2 nd fluid passes through gaps formed between the stacks of the plate fins 2a constituting the plate fin stacked body 2. Thereby, heat exchange is performed between the refrigerant as the 1 st fluid and the air as the 2 nd fluid.

Next, the plate fins 2a forming the plate fin stacked body 2 constituting the main body of the heat exchanger 1 will be described with reference to fig. 9 to 19.

Fig. 9 to 12 are perspective views showing a plate-fin stacked body in a partially cut state. Fig. 13 to 19 are views showing the structure of the plate fin.

As shown in fig. 9, the plate fin laminate 2 is configured by laminating two types of plate fins 2a (the 1 st plate fin 6 and the 2 nd plate fin 7) having a flow path structure.

As shown in fig. 15, the 1 st plate fin 6 and the 2 nd plate fin 7 of the plate fin 2a are each formed by welding a 1 st plate-like member 6a, which has been press-formed to have a refrigerant flow path structure described later, and a 2 nd plate-like member 6b, which has the same structure as the 1 st plate-like member 6a, to each other. The 1 st plate-like member 6a and the 2 nd plate-like member 6b have concave grooves, respectively, and the 1 st plate-like member 6a and the 2 nd plate-like member 6b are fixed to each other to form a refrigerant flow path. The 1 st plate-like member 6a and the 2 nd plate-like member 6b are made of a thin metal plate such as aluminum, an aluminum alloy, or stainless steel.

The flow path structure formed in the plate fin 2a will be described below.

The 1 st plate fins 6 and the 2 nd plate fins 7 of the plate fins 2a have the same configuration except for the positional displacement of the refrigerant flow paths 11 described later, and therefore the reference numerals for the 1 st plate fins 6 are used in fig. 13 to 15 and the like for explanation.

As shown in fig. 13, the plate fins 2a (6, 7) have a header region H formed at one end portion in the longitudinal direction (the left side in fig. 13), and the other region serves as a flow path region P. An inflow-side header opening 8a and an outlet-side header opening 8b are formed in the header region H, and the inflow tube 4 and the outflow tube 5 are connected to each other.

In addition, a plurality of 1 st fluid flow paths (hereinafter, referred to as refrigerant flow paths) 11 through which the 1 st fluid refrigerant from the header opening 8a flows are formed in parallel in the flow path region P. The group of refrigerant flow paths 11 is folded back at the other end portions (near the right end portions in fig. 13) of the plate fins 2a (6, 7) and connected to the outlet-side header opening 8 b. More specifically, the refrigerant flow path 11 group includes a forward flow path portion 11a connected to the inflow side header opening 8a and a return flow path portion 11b connected to the outlet side header opening 8b, and is formed in a substantially U-shape. The refrigerant flowing from the inflow-side header opening 8a flows from the outward flow path portion 11a to the return flow path portion 11b, U-turns, and then flows to the outlet-side header opening 8 b.

Further, around the inflow-side header opening 8a, as shown enlarged in fig. 14, a header passage 10 is formed through which the refrigerant from the header opening 8a flows to the refrigerant passage 11 group. The header flow path 10 includes: an outer peripheral flow path 10a formed so as to bulge out from the outer periphery of the header opening 8 a; one connection channel 10b extending to the refrigerant channel 11 group side of the outer peripheral channel 10 a; and a multi-branch flow passage 10c connecting the connection flow passage 10b to each of the refrigerant flow passages 11.

The outer peripheral flow path 10a, the connection flow path 10b, and the multi-branch flow path 10c of the header flow path 10 are formed wider than the refrigerant flow paths 11 arranged side by side in the flow path region P. In the header flow passage 10, a vertical cross-sectional shape orthogonal to the flow direction is a rectangular shape.

Further, the opening shape of the inflow-side header opening 8a has a larger diameter than the opening shape of the outlet-side header opening 8 b. This is because, when the heat exchanger is used as a condenser, the volume of the refrigerant after heat exchange is smaller than the volume of the refrigerant before heat exchange.

The number of return-side flow path portions 11b connected to the outlet-side header opening 8b is smaller than the number of outward-side flow path portions 11a into which the refrigerant from the inlet-side header opening 8a flows. This is because the volume of the refrigerant after heat exchange is smaller than the volume of the refrigerant before heat exchange, for the same reason as the difference in diameter between the

header openings

8a and 8 b.

In the present embodiment, the number of the outward flow path sections 11a is 7 and the number of the return flow path sections 11b is 2, but the present invention is not limited thereto.

When the heat exchanger is used as an evaporator, the inlet and outlet of the refrigerant are reversed from the above configuration.

In the plate fins 2a (6, 7), slits 15 are disposed between a region where the outward flow path portion 11a into which the refrigerant from the inflow side header opening 8a flows and a region where the return flow path portion 11b flowing to the outlet side header opening 8b is formed, in order to reduce (insulate) the heat conduction between the refrigerants in the plate fins 2a (6, 7).

The connection channel 10b of the inlet-side header channel 10 is provided so as to be offset to the opposite side of the outward-flow-path-side channel 11a from the return-flow-side channel 11 b. That is, as shown in FIG. 17, the width V of the flow path 11a-1 from the center line O of the connecting flow path 10b to the end on the return-side flow path portion 11b side is configured to be larger than the width W of the flow path 11a-2 from the center line O of the connecting flow path 10b to the end on the opposite side of the return-side flow path portion 11 b. A flow dividing collision wall 17 is formed at the end of the connection flow path 10b, i.e., at the opening portion connected to the outward flow path portion 11 a. The outward flow path portion on the extension of the connection flow path 10b is a non-flow path portion 18. Thereby, the refrigerant flowing from the connecting channel 10b collides with the flow dividing collision wall 17 to be divided (divided vertically in fig. 17), and flows through the multi-branch channel 10c on the downstream side of the connecting channel 10b to the respective channel groups above and below the outward flow channel 11a partitioned by the non-channel 18.

In addition, a header flow path 14 is also formed in the header opening 8b on the outlet side. The header flow path 14 is formed to have substantially the same shape as the header flow path 10 of the header opening 8a provided on the inlet side, except that the flow dividing collision wall 17 is not provided. In the present embodiment, since the number of the return-side flow path portions 11b of the refrigerant flow path 11 group is two and small, the connection flow path 10b is provided substantially on the center line of the return-side flow path portion 11b group.

In the plate fin 2a (6, 7) configured as described above, as shown in fig. 16A, the plurality of protrusions 12(1 st protrusion: 12a, 12aa, 2 nd protrusion: 12b) are formed in the flow path region P at predetermined intervals in the longitudinal direction in the 1 st plate fin 6.

Fig. 16A shows the 1 st plate fin 6. Fig. 16B shows the 2 nd plate fin 7. Fig. 16C shows a state where both fin plates 2a (6, 7) are overlapped (a diagram showing a displacement of the refrigerant flow path 11 group).

As shown in fig. 16A to 16C, the 1 st projection 12a is formed on a planar end 19a of a long edge portion (long edge portions on both left and right sides in fig. 16A) of the plate fin. The 1 st projection 12aa is formed on the flat end 19b of both side edges of the slit 15. As shown in fig. 10, the 1 st projection 12a abuts against the planar end 19a of the long edge of the 2 nd plate fin 7 adjacent and opposed to each other in the stacking direction. The 1 st projection 12aa abuts against the flat end portions 19b of the 2 nd plate fins 7 adjacent and facing in the stacking direction, the flat end portions being positioned at both side edge portions of the slit 15. Thus, the distance between the 1 st plate fin 6 and the adjacent 2 nd plate fin 7 in the stack is defined to be a predetermined length. The 1 st projection 12a is formed so as to be located at a position separated by 1mm or more from the end edge of each long-side edge portion toward the inside, for example, from the end edge toward the inside (the side closer to the refrigerant flow path 11).

As is apparent from fig. 16A, the 2 nd projections 12b are formed at predetermined intervals between the passages of the refrigerant passage 11 group, in the present embodiment, in the recessed flat portions 20 serving as the non-passage portions 18. The 2 nd projection 12B abuts the recessed flat surface portion 20 of the 2 nd plate fin 7 adjacent in the stacking direction shown in fig. 16B. Thus, the 2 nd protrusions 12b define the distance between the 1 st plate fin 6 and the 2 nd plate fin 7 in the lamination layer to be a predetermined length, similarly to the 1 st protrusions 12 a.

As shown in fig. 18, the projections 12(12a, 12aa, 12b) are formed by cutting (warping) the

flat end portions

19a, 19b of the 1 st plate fin 6 and a part of the recessed flat portion 20. Hereinafter, the protrusions 12(12a, 12aa, 12b) may be referred to as cut-and-form protrusions. The cut-formed end edge Y (see fig. 18) of the cut-formed projection is formed so as to face the flow direction indicated by the arrow of the 2 nd fluid flowing between the stacked layers of the plate fins 2a, and the cut-formed standing piece Z (see fig. 18) is formed so as to follow the flow of the 2 nd fluid. In the present embodiment, the cutting projections are formed so as to be cut and formed so as to have a cross section opened in the flow direction of the 2 nd fluid in a substantially shape

A letter (substantially U-shaped).

When the plate fins 2a (6, 7) and the end plates 3(3a, 3b) are welded, the top surfaces of the cut projections 12(12a, 12aa, 12b) are fixed to the adjacent plate fins 2a (6, 7). Thereby, the plate fins 2a (6, 7) are integrally connected.

In the present embodiment, the 1 st cut-out projections 12a and 12aa and the 2 nd cut-out projection 12b are arranged linearly in the flow direction of the 2 nd fluid (air), but may be arranged in a staggered manner.

As shown in fig. 19, the plate fin 2a (6) also has a plurality of projections 22(22a, 22b) formed on a fin flat surface portion 21 at the end portion on the turn-back side of the flow path region P where the refrigerant flow path 11 group is U-turned. The projections 22(22a, 22b) are also formed by cutting the fin planar portion 21 (hereinafter, the projections 22(22a, 22b) may be referred to as cut projections), and the cut edges Y of the cut projections 22(22a, 22b) face the flow of the 2 nd fluid (see fig. 19). Further, the slit forming projections 22(22a, 22b) are provided on the downstream side of the positioning boss hole 13. The cut-out projection 22a on the downstream side of the positioning boss hole 13 is formed in a shape converging the flow on the downstream side of the positioning boss hole 13, for example, the cross-sectional shape of the flow to the No. 2 fluid is

A shape of a letter (inverted V shape) opening. The projections 22b on the downstream side of the projection 22a are arranged alternately so that the center line thereof is shifted from the center line of the next projection 22b on the downstream side.

Further, the cut-out forming projections 22(22a, 22b) are also fixed by abutting the top surfaces of the cut-out forming projections 22(22a, 22b) against the adjacent plate fin 2a (7) in the same manner as the cut-out forming projections 12(1 st cut-out forming projections: 12a, 12aa, 2 nd cut-out forming projection: 12 b). Thereby, the gaps between the adjacent plate fins 2a are defined to a predetermined length, and the plate fins 2a are connected to each other.

As shown in fig. 11, through holes (hereinafter, referred to as positioning boss holes) 13 for positioning are formed in the plate fins 2a (6, 7) at the end of the header region H. The positioning boss holes 13 are also formed in the

end plates

3a, 3b and the reinforcing

plates

16a, 16b laminated on both sides of the plate fins 2a (6, 7). A positioning pin jig for stacking the plurality of plate fins 2a (6, 7) is attached to the positioning boss hole 13. This enables the plurality of plate fins 2a to be stacked with high accuracy. In the present embodiment, the connection portions 9 (see fig. 3) such as bolts that connect the reinforcing

plates

16a, 16b and the

end plates

3a, 3b of the plate-fin stacked body 2 also serve as positioning pin jigs.

Further, hole outer peripheral portions (hereinafter referred to as positioning boss hole outer peripheral portions) 13a that bulge upward and downward are formed in outer peripheral portions of the positioning boss holes 13 provided at both end portions of the plate fins 2a (6, 7). The positioning boss hole outer peripheral portion 13a forms a space different from a flow path through which the refrigerant flows. As shown in fig. 11, the positioning boss hole outer peripheral portion 13a abuts against the plate fins 2a (6, 7) adjacent in the stacking direction, and constitutes a header region support portion that holds the stacking gap of the plate fins 2 a.

The positioning boss hole outer peripheral portion 13a formed around the positioning boss hole 13 is welded and fixed to the header flow paths 10(10a, 10b, 10c) formed at both the inlet and the outlet of the header region H shown in fig. 12, and the header flow paths 10 of the plate fins 2a (6, 7) and the positioning boss hole outer peripheral portion 13a facing each other in the stacking direction. Thereby, the header region portions of the plate fins 2a (6, 7) are integrally connected.

In the refrigerant flow path 11 of the present invention, for example, a case where the cross-sectional shape orthogonal to the direction in which the refrigerant flows is a circular shape is described, but the present invention is not limited thereto. The cross-sectional shape of the refrigerant flow path 11 may be a rectangular shape or the like, in addition to a circular shape.

In the present embodiment, the case where the refrigerant flow path 11 has a shape protruding to both sides in the stacking direction has been described, but may have a shape protruding only to one side in the stacking direction. In addition, in the present invention, the circular shape also includes a compound curve shape formed by a circle, an ellipse, and a closed curve.

The heat exchanger according to the present embodiment is configured as described above, and its operational effects will be described below.

First, the flow of the refrigerant and the heat exchange action are explained. The refrigerant flows from the inflow tubes 4 connected to the one end portions of the plate fin laminate 2 to the header flow channels 10 of the respective plate fins 2a through the header openings 8a on the inflow side. The refrigerant flows through the outer peripheral flow path 10a around the header opening 8a, the connecting flow path 10b, and the multi-branch flow path 10c to the refrigerant flow path 11 group. The refrigerant flowing through the refrigerant flow path 11 group of the plate fins 2a is turned back from the outward flow path portion 11a to the return flow path portion 11 b. The refrigerant flows from the outflow tube 5 to the refrigerant circuit of the refrigeration system through the outlet-side header passage 14 and the outlet-side header opening 8 b.

When flowing through the refrigerant flow paths 11, the refrigerant exchanges heat with air passing through the stacked layers of plate fins 2a of the plate fin stacked body 2.

At this time, a strong pressure of the refrigerant is applied to the header region H of the plate-fin stacked body 2, and the header region H of the header flow path 10 is subjected to expansion deformation.

That is, the strong pressure of the refrigerant applied to the header flow path 10 strongly acts on the header region corresponding portions of the

end plates

3a, 3b covering both side portions of the plate fin laminated body 2, so that the header region corresponding portions of the

end plates

3a, 3b tend to expand and deform outward.

However, in the heat exchanger of the present embodiment, the header region corresponding portions of the

end plates

3a, 3b covering both sides of the plate-fin stacked body 2 are connected by the connecting portion 9. This prevents the header region corresponding portions of the

end plates

3a and 3b from bulging outward.

That is, as shown by the arrows in fig. 7, the high pressure of the refrigerant applied to the header region portion is deformed so as to be directed upward toward the upper end plate 3a and downward toward the lower end plate 3 b. The upward expansion deformation force applied to the upper end plate 3a is subjected to a downward pressure from the refrigerant present in the inflow pipe 4 connected to the upper end plate 3 a. That is, the upward expansion deformation force is cancelled by the downward pressure from the refrigerant existing in the inflow pipe 4. This can prevent the expansion and deformation of the header region corresponding portion of the upper end plate 3a outward. The downward expansion deformation force applied to the lower end plate 3b is alleviated by the connection of the end plate 3b to the upper end plate 3a as described above. This can suppress the expansion deformation of the end plate 3 a. As a result, the expansion deformation of the

end plates

3a and 3b can be alleviated as a whole.

Particularly in the present embodiment, the reinforcing

plates

16a, 16b are provided on the outer surfaces of the header region corresponding portions of the

end plates

3a, 3 b. The reinforcing

plates

16a, 16b are connected to each other by the connecting portion 9, and the

end plates

3a, 3b are pressed against the plate-fin stacked body 2 from the outside. Thus, the strength of the header region corresponding portions of the

end plates

3a, 3b is reinforced by the rigidity of the reinforcing

plates

16a, 16b themselves, and the expansion deformation of the header region corresponding portions is strongly suppressed.

Further, by providing the reinforcing

plates

16a, 16b, even if the refrigerant flow path is U-shaped, the expansion deformation of the portion corresponding to the header region can be reliably suppressed. That is, in the plate fin laminate 2 of the present embodiment, the refrigerant flow paths 11 provided in the plate fins 2a are U-turned in a substantially U-shape, and the inlet-side header flow paths 10 and the outlet-side header flow paths 14 are concentrated on one end portions of the plate fins. Therefore, both the inlet-side and outlet-side pressures are applied to one end side of the plate fin. However, according to the configuration of the present embodiment, even if both the refrigerant pressures on the inlet side and the outlet side are applied, the expansion deformation can be reliably prevented against the force.

Accordingly, when the heat exchanger described above is a heat exchanger with a large amount of refrigerant or an environment-compatible refrigerant with a high compression ratio is used, the expansion deformation of the header region portion of the plate fin laminated body 2 can be prevented. As a result, the heat exchanger can be used in a state where the pressure of the refrigerant is higher, and can be a heat exchanger with high efficiency.

In this heat exchanger, the group of refrigerant flow paths 11 can be reduced in diameter by reducing the cross-sectional area of the concave grooves formed in the plate fins 2a for the refrigerant flow paths. Thereby, heat exchange efficiency can be improved and miniaturization can be achieved.

That is, the expansion deformation of the portion corresponding to the header region of the plate-fin laminated body 2 can be prevented, and the diameter of the flow path cross-sectional area of the refrigerant flow path 11 can be reduced, whereby the heat exchange efficiency can be improved and the downsizing can be promoted.

Further, since the reinforcing

plates

16a and 16b only need to be provided at least at the header region corresponding portions, the increase in volume due to the provision of the reinforcing

plates

16a and 16b can be minimized. This prevents expansion deformation and improves heat exchange efficiency without impairing the miniaturization of the heat exchanger.

In the header region H of the plate fin laminated body 2, the flow path area of the header flow path 10 is the largest. This also maximizes the refrigerant pressure in the header flow path 10. However, since the header flow paths 10 are connected to and welded to the adjacent header flow paths 10, the expansion deformation can be effectively prevented. As a result, the expansion deformation of the header region corresponding portion can be prevented more reliably.

Further, the coupling portions 9 such as bolts can be used as guide pins (jigs) in stacking the plate fins 2a, the

end plates

3a, 3b, and the reinforcing

plates

16a, 16 b. This can improve the lamination accuracy and improve the productivity.

In addition, the strong pressure of the refrigerant applied to the header region H of the plate fin laminate 2 may deform the cross-sectional area of the header flow paths 10 in the header region H. The outer wall (flat surface) of the header flow passage 10 is in a state of being welded in contact with another header flow passage 10 adjacent in the stacking direction. Therefore, the pressures are cancelled by the refrigerant in the header flow paths. This prevents deformation of the header flow path 10 in the header region H, thereby realizing a highly reliable heat exchanger.

In the heat exchanger of the present embodiment, the group of refrigerant flow paths 11 provided in the plate fins 2a is formed in a substantially U shape and folded back. This makes it possible to increase the length of the refrigerant flow path without increasing the size of the plate fin 2a (increasing the length).

This improves the heat exchange efficiency between the refrigerant and the air, and the refrigerant can be reliably brought into the supercooled state, thereby improving the efficiency of the refrigeration system. Further, the heat exchanger can be miniaturized.

Further, as described above, in the header flow path corresponding portion, the

end plates

3a, 3b are coupled to each other and the reinforcing

plates

16a, 16b are provided, whereby deformation can be prevented. Thus, by forming the refrigerant flow paths 11 in a substantially U-shape and concentrating the inlet-side header flow path 10 and the outlet-side header flow path 14 at one end, even if refrigerant pressures on both the inlet side and the outlet side are applied to the header region portion, expansion deformation of the header region corresponding portion can be reliably prevented.

In the present embodiment, the refrigerant that exchanges heat with the air flowing between the plate fin stacked layers of the plate fin stacked body 2 flows from the inlet-side header flow path 10 to the group of the connection flow path 10b, the multi-branch flow path 10c, and the refrigerant flow path 11. Thereby, the flow dividing collision wall 17 is provided on the downstream side of the connection flow path 10b, and the refrigerant collides with the flow dividing collision wall 17 and is divided vertically. The vertically branched refrigerant is further branched from the multi-branch flow path 10c to each refrigerant flow path 11. This prevents the refrigerant from being extremely biased in the flow path at the portion on the extension line of the connection flow path 10 b.

In the present embodiment, the refrigerant flow paths 11 are formed in a U shape in a group, and the refrigerant flow paths are configured to have a turn-back portion. Therefore, as is clear from fig. 17, the flow path length of the group of refrigerant flow paths 11 is longer as it goes closer to the U-shaped outer periphery, in other words, as it goes closer to the flow path side 11a-2 away from the slit 15. Due to the difference in the length of the flow path, a drift current is generated.

However, in the present embodiment, the connection channel 10b from the header channel 10 is provided offset from the center line O of the outgoing channel side channel 11a of the refrigerant channel 11 group on the opposite side of the return channel. This can suppress the drift and allow the refrigerant to flow substantially uniformly through each flow path.

That is, in the present embodiment, even if the flow path resistance varies depending on the flow path length from the header flow path 10 on the inlet side to the header flow path 14 on the outlet side of each flow path of the refrigerant flow path 11 group because the refrigerant flow path 11 group is formed in a U shape, the refrigerant can be uniformly branched into the respective flow paths of the refrigerant flow path 11 group. This is because the connection channel 10b from the inlet-side header channel 10 is located on the opposite side of the outward flow channel 11a from the return flow channel, and therefore the length of the branch channel from the connection channel 10b to each outward flow channel 11a becomes longer as it approaches the return flow channel 11b, so that the difference in channel length is offset.

This makes it possible to achieve a heat exchanger with higher heat exchange efficiency while advancing the downsizing of the heat exchanger by utilizing the synergistic effect of the U-shape of the group of refrigerant flow paths 11 and the uniform distribution of the flow distribution collision wall 17.

A slit 15 is formed between the outward flow path portion 11a and the return flow path portion 11b of the refrigerant flow path 11 group, and thermal shutoff is performed. This prevents heat from moving from the outward flow path portion 11a to the return flow path portion 11b of the refrigerant flow path 11 group, and thus the refrigerant can be efficiently supercooled. As a result, the heat exchange efficiency can be further improved.

In the heat exchanger of the present embodiment, the plurality of cut-and-formed projections 12(12a, 12aa, 12b) are provided in the flow path region P of the plate-fin laminated body 2, and the heat exchange efficiency in the flow path region P is improved.

Specifically, the cut-formed end edge Y of the cut-formed protrusion 12(12a, 12aa, 12b) faces the flow direction of the 2 nd fluid flowing between the stacked layers of the plate fin 2 a. This makes the interval between the plate-fin stacked layers constant. Furthermore, the dead water region that is likely to occur downstream of the cut forming projections 12(12a, 12aa, 12b) is minimized, and the front edge effect occurs at the cut forming edge Y portion. Further, since the slit projections 12(12a, 12aa, 12b) are formed by slit forming so as to face the flow direction of the 2 nd fluid, the flow resistance to the 2 nd fluid becomes small. This can significantly improve the heat exchange efficiency of the heat exchanger while suppressing an increase in flow path resistance in the flow path region P of the plate fin laminated body 2.

The arrangement structure of the cut projections 12(12a, 12aa, 12b) provided on the plate fin 2a may be a staggered arrangement with respect to the 2 nd fluid, or may be formed more on the leeward side than on the windward side. The optimum structure for improving the heat conductivity may be selected according to the specification, structure and user's requirement of the heat exchanger.

The cut-out projections 12(12a, 12aa, 12b) are cut out so as to open in the direction of flow of air flowing through the gaps of the plate-fin stacked body 2. This eliminates the need to form a reduced thickness portion from the recessed flat surface 20 between the refrigerant flow paths in the direction in which air flows, i.e., in the direction intersecting the refrigerant flow paths. Thus, the recessed flat surface 20 located between the refrigerant flow paths can be narrowed by eliminating the need to form a reduced thickness portion, as compared with a structure in which the cut-out projections 12b are formed to be raised in the form of cylindrical projections or the like. Since the depressed flat surface 20 can be narrowed, the width of the plate fin 2a, in other words, the heat exchanger can be miniaturized accordingly.

The narrow flat surfaces 20a and the wide flat surfaces 20b are arranged at the edges of the long side portions of the plate fins 2a by alternately arranging the refrigerant flow paths 11 in a staggered manner (see fig. 6). Cut projections 12b are formed on the wide flat surface 20b side, and the top surfaces of the cut projections 12b are fixed to the narrow flat surfaces 20a of the adjacent plate fins 2 a. This prevents the width of the narrow flat surface 20a from being increased to form a protrusion. That is, the slit-formed projections are provided on the wide flat surface side of the wide flat surface 20b, and the projections are configured to be abutted against and fixed to the narrow flat surfaces 20a of the adjacent plate fins 2 a. This makes it possible to maintain the width of the long side portion of the plate fin on the narrow plane side without increasing the width of the long side portion of the plate fin, thereby facilitating downsizing of the heat exchanger.

Further, when the plate fins 2a and the

end plates

3a, 3b are welded, the top surfaces of the cut projections 12 are fixed to the adjacent plate fins 2 a. Thereby, the plate fins 2a are integrally connected. As a result, the rigidity of the plate-fin laminate 2 can be improved.

In particular, in the present embodiment, the non-flow path section 18 is formed at the upper portion of the extension line of the connection flow path 10b of the group of refrigerant flow paths 11, and the 2 nd cut-and-form projection 12b, which is a part of the projection 12(12a, 12aa, 12b), is provided in the non-flow path section 18. This can reliably maintain the fin plate lamination interval at the group portion of the refrigerant flow path 11 at a constant value. This allows the air to flow stably in the group of the refrigerant flow paths 11 without variation, thereby improving the heat exchange efficiency.

The 1 st cut-formed projections 12a provided on the long side portions of the plate fin laminate 2 improve the strength of the long side edge portions of the plate fin laminate 2, which tends to be weakened. In particular, the 1 st cut forming projections 12aa provided on both side edge portions of the slit 15 of the plate-fin laminated body 2 improve the strength of the slit edge portion whose strength is reduced by the provision of the slit 15. This can improve the heat exchange efficiency and prevent deformation in the vicinity of the slit.

The 1 st cut forming protrusions 12aa provided at both side edge portions of the slit 15 may be formed in one piece so as to straddle the slit 15. At this time, heat conduction occurs between the outward flow path portion 11a and the return flow path portion 11b of the refrigerant flow path 11 group, and there is a concern that the heat insulating effect of the slit 15 is reduced. However, in the present embodiment, since the projections 12aa are provided so as to be divided into the side edges of the slit 15, there is no fear of occurrence of such heat conduction.

The 1 st cut projections 12a, 12aa provided on the long side portions of the laminated plate fin body 2 and on both side portions of the slit 15 are provided at positions apart from the end edges of the long sides of the plate fins of the laminated plate fin body 2. As a result, when dew condensation water is generated in the plate fins 2a of the plate-fin laminated body 2 and flows along the end edges of the plate fins 2a and is discharged, it is possible to prevent various failures from occurring due to the dew condensation water being retained in the cut-forming projections 12a and 12aa portions as a result of the flow of dew condensation water being blocked by the 1 st cut-forming

projections

12a and 12 aa. This enables a highly reliable heat exchanger to be realized.

Further, in the heat exchanger of the present embodiment, the cut-and-raised portions 22(22a, 22b) are provided at the U-shaped end portions of the plate fins 2a in the refrigerant flow path. This can improve the degree of contribution of heat exchange at the U-shaped side end portions of the plate fins 2a without the refrigerant flow channels 11. This can improve the heat exchange efficiency over the entire length of the flow path region of the plate fin 2a, and can improve the heat efficiency of the heat exchanger.

In particular, the U-shaped side end of the plate fin 2a has the positioning boss hole 13, and the downstream side thereof is a dead water region, so that the heat exchange contribution is extremely low. In the present embodiment, since the plurality of cut-out projections 22(22a, 22b) are provided on the downstream side of the positioning boss hole 13, the heat exchange contribution degree can be improved over the entire downstream side of the positioning boss hole 13.

Further, the slit forming projections 22a provided closest to the downstream side of the positioning boss hole 13 constrict the flow on the downstream side of the positioning boss hole 13. This minimizes the dead water region having a low heat exchange contribution generated downstream of the positioning screw hole. As a result, the heat exchange efficiency can be further improved.

The respective cut-out projections 22(22a, 22b) are formed by cutting in the same manner as the cut-out projections 12(12a, 12aa, 12b) provided in the flow path region P, and the cut-out edge Y is configured to face the flow of the 2 nd fluid. This can generate a leading edge effect at the cut-formed edge portion, and accordingly, the heat exchange efficiency can be further improved.

The plurality of slit-formed projections 22(22a, 22b) provided on the downstream side of the positioning boss hole 13 are arranged in a zigzag pattern with respect to the flow of the 2 nd fluid. This effectively exerts the heat exchange function, and increases the degree of contribution of heat exchange.

Further, the top of each slit protrusion 22(22a, 22b) is fixed to the adjacent plate fin 2 a. According to this structure, the short side portions of the plate fins 2a are connected and fixed in a stacked state, and therefore the rigidity of the plate-fin stacked body 2 is improved.

The slit protrusion 22 provided closest to the downstream side of the positioning boss hole 13 is formed by slit forming in the present embodiment so as to be directed in the flow direction of the 2 nd fluid

The cross-sectional shape of the letter-shaped (inverted V-shaped) opening. However, the cut-out projection 22 may be formed by cutting out a substantially L-shaped cut-out, and may be provided so as to face a pair of the cut-out projections. That is, any shape may be used as long as it is a shape capable of contracting the flow on the downstream side of the positioning boss hole 13.

In the present embodiment, as described above, the coupling portion 9 and the reinforcing

plates

16a and 16b correspond to the expansion deformation suppressing portion.

(embodiment mode 2)

As shown in fig. 20 to 23, the heat exchanger of the present embodiment differs from the heat exchanger of embodiment 1 in the shape of the refrigerant flow path group and the installation position of the header opening. The same reference numerals are used for portions having the same functions as those of the heat exchanger of embodiment 1, and different portions will be mainly described below.

Fig. 20 is a perspective view showing an external appearance of the heat exchanger according to embodiment 2. Fig. 21 is a plan view of a plate fin constituting the plate fin stacked body of the plate fin stacked type heat exchanger. Fig. 22 is an exploded view showing a part of the structure of the plate fin of the heat exchanger in an enlarged manner. Fig. 23 is a perspective view of a portion of the refrigerant flow path group that cuts the plate-fin stacked body showing the heat exchanger.

In the heat exchanger of the present embodiment shown in fig. 20 to 23, the group of refrigerant flow paths 11 provided in the plate fins 2a is linear. An inlet-side header opening 8a is provided on one end side of the refrigerant flow path 11 group, and an outlet-side header opening 8b is provided on the other end side. The inlet pipe 4 is connected to the inlet-side header opening 8a, the outlet pipe 5 is connected to the outlet-side header opening 8b, and the refrigerant flows linearly from one end side to the other end side of the plate fin 2a and then flows out.

Further, the manifold flow path 10 formed around the manifold opening 8a on the inlet side includes an outer peripheral flow path 10a around the manifold opening, a connection flow path 10b, and a multi-branch flow path 10 c. The connection flow path 10b is formed to extend from the outer peripheral flow path 10a in the short side direction of the plate fin 2a, and then is connected to the multi-branch flow path 10 c. The outlet-side header passage 14 is also configured in the same manner as the inlet-side header passage 10, and both are formed in a symmetrical shape.

The

end plates

3a and 3b on both sides of the plate-fin laminated body 2 are connected by the connection portion 9 without using the reinforcing

plates

16a and 16 b. This can prevent the expansion deformation of the header region corresponding portions at both ends of the

end plates

3a, 3 b.

The heat exchanger configured as described above is similar to the heat exchanger described in embodiment 1 in its configuration and effects including details except that the refrigerant flow path 11 is formed in a U shape, and the description thereof is omitted.

The slit projections 22 provided at the U-shaped side end portions of the plate fins 2a in embodiment 1 may be provided in the header regions on both the inlet and outlet sides as appropriate in the present embodiment. For example, the slit projections 22 may be formed on the downstream side of the header flow channel 10 which is a dead water region.

In the present embodiment, as described above, the coupling portion 9 corresponds to the dilatant deformation inhibitor. In this embodiment, a reinforcing plate may be provided in the same manner as in embodiment 1. At this time, the coupling portion 9 and the reinforcing plate correspond to the expansion deformation suppressing portion.

(embodiment mode 3)

The heat exchanger of the present embodiment is suitable for the case where the refrigerant inlet and outlet of the heat exchanger are used as evaporators in contrast to embodiment 1. In the present embodiment, as shown in fig. 24 to 28, a refrigerant flow dividing control tube 24 is provided in the header passage 14 on the outlet side.

In this embodiment, a heat exchanger having the structure of embodiment 1 is used as an evaporator, for example.

Fig. 24 is a perspective view showing an external appearance of a heat exchanger according to embodiment 3. Fig. 25 is a perspective view showing a state in which the flow dividing control tube is removed from the heat exchanger. Fig. 26 is a perspective view showing a flow distribution control tube insertion portion in the plate fin laminate of the heat exchanger. Fig. 27 is a perspective view of the flow dividing control tube of the heat exchanger. Fig. 28 is a schematic diagram showing a cross section of a flow dividing control tube portion of the heat exchanger.

In fig. 24 to 28, the flow dividing control tube 24 is inserted into the outlet-side header passage 14, which is the header opening 8b on the outlet side as the evaporation outlet of the refrigerant. As shown in fig. 28, the front end portion of the flow distribution control tube 24 extends to the end plate 3b on the side where the header opening is not provided. The front end portion of the flow dividing control tube 24 is closed by the end plate 3 b. The flow dividing control tube 24 is formed of a tube having a smaller diameter than the inner diameter of the header opening 8 b. A refrigerant flow communication gap 25 is formed between the flow dividing control tube 24 and the inner surface of the header opening. A plurality of flow distribution ports 26 are provided at substantially equal intervals in the longitudinal direction of the flow distribution control tubes 24, that is, in the stacking direction of the plate fins 2 a.

The plurality of branch flow ports 26 are formed such that the hole diameters thereof become smaller as going in the direction of refrigerant flow, i.e., as approaching the header opening 8b on the outlet side.

As shown in fig. 25 and 27, the flow distribution control pipe 24 is attached to the reinforcing plate 16 a. The flow distribution control tubes 24 are inserted and disposed in the header openings 8b by fixing the reinforcing plates 16a to the end plates 3a on both sides of the plate-fin laminate 2.

The inflow pipe 4 is connected and fixed to the surface of the reinforcing plate 16a to which the flow distribution control pipe 24 is attached, the surface facing the flow distribution control pipe 24.

The reinforcing plate 16a is connected to the fixed outflow pipe 5. The flow distribution control tube 24 may abut against the end plate 3b so that the distal end portion thereof is closed.

In the heat exchanger configured as described above, the refrigerant gas flowing from the inlet-side header opening 8a to the outlet-side header passage 14 through the group of refrigerant passages 11 flows into the flow dividing control tubes 24 from the refrigerant flow common gaps 25 through the plurality of flow dividing ports 26(26a, 26b) formed in the tube walls of the flow dividing control tubes 24, as indicated by arrows in fig. 28. The refrigerant flows out from the outlet-side header opening 8b to the outflow pipe 5.

Here, the branch flow port 26 provided in the branch flow control tube 24 is formed such that the diameter of the flow port decreases as the outlet-side header opening 8b approaches. This can equalize the amounts of the refrigerants flowing through the respective channels of the refrigerant channel 11 group.

That is, in the heat exchanger of the present embodiment, the refrigerant flow path 11 is made smaller in diameter, so that the pressure loss of the refrigerant is several times larger in the outlet-side header flow path 14 than in the inlet-side header flow path 10. On the other hand, the refrigerant split flow is greatly affected by the distribution of the pressure loss. Thus, even if the flow dividing control tube 24 is provided in the header passage 10 on the inlet side, which is conventionally provided, the pressure loss of the header passage 14 on the outlet side is several times higher than that on the inlet side, and therefore the pressure loss of the refrigerant flowing through the refrigerant passage 11 is controlled by the pressure loss of the header passage 14 on the outlet side. This prevents the diversion from being performed as designed.

However, in the heat exchanger of the present embodiment, the flow dividing control tube 24 is provided in the header passage 14 on the outlet side where the pressure loss is high. This makes the pressure loss distribution in the axial direction in the outlet-side header flow path 14, which greatly affects the flow separation, uniform. This makes it possible to equalize the flow rates of the refrigerants flowing through the respective flow paths of the refrigerant flow path 11 group.

In the heat exchanger of the present embodiment, the refrigerant flowing in from the inflow tube 4 is introduced into the refrigerant flow paths 11 inside the respective plate fins through the inlet-side header opening 8a, and flows into the outlet-side header opening 8 b. The refrigerant then flows out of the outflow pipe 5.

At this time, due to the pressure loss generated in each flow path, the refrigerant flows more easily through the refrigerant flow paths 11 of the plate fins close to the inlet tube 4 (the refrigerant flow paths of the plate fins further to the left in fig. 28) than through the refrigerant flow paths 11 of the plate fins far from the inlet tube 4 (the refrigerant flow paths of the plate fins further to the right in fig. 28). In other words, there is a possibility that a deviation in the flow rate of the refrigerant occurs.

In the present embodiment, the flow dividing control tube 24 is inserted into the header opening 8b on the outlet side, and the flow dividing port 26a on the outermost outlet side (the portion on the left side in fig. 28) is made smaller than the flow dividing port on the opposite side (the portion on the right side in fig. 28) to the outlet side of the flow dividing control tube 24. This increases the pressure loss of the refrigerant passing through the outlet-side flow dividing port. As a result, the refrigerant flow rate can be prevented from being biased, the refrigerant amount in the 1 st fluid flow path 11 inside each plate fin can be equalized, and the heat exchange efficiency can be improved.

As a result, the heat exchanger of the present embodiment can improve the heat exchange efficiency in the group portion of the refrigerant flow paths 11, and can provide a heat exchanger with higher heat efficiency.

Further, the structure for uniformizing the refrigerant flow distribution by the flow distribution control tube 24 is a simple structure in which the flow distribution port 26 is formed by punching a hole in the flow distribution control tube 24, and therefore, the heat exchanger can be provided at low cost.

The flow distribution control pipe 24 is integrally provided in the reinforcing plate 16 a. Thus, the flow distribution control tubes 24 can be inserted and installed in the header flow path 14 only by attaching the reinforcing plate 16 a. As a result, it is possible to prevent a defective plate-fin joint due to solder melting at the welded portions of the plate fins, which may occur when the flow distribution control tubes 24 are mounted by soldering or the like, and a quality defect such as refrigerant leakage which may occur therewith, and to realize a high-quality and high-efficiency heat exchanger.

The reinforcing plate 16a is made of a material (the reinforcing plate 16a is made of stainless steel, the flow distribution control pipe 24 is made of aluminum, and the outflow pipe 5 is made of copper) which has a smaller potential difference between the flow distribution control pipe 24 and the outflow pipe 5 than the potential difference between the flow distribution control pipe 24 and the outflow pipe 5 when they are directly connected. This prevents contact corrosion of dissimilar metals that occurs when the flow dividing control pipe 24 and the outflow pipe 5 are directly connected. As a result, reliability of long-term durability can be improved. In particular, a heat exchanger for an air conditioner in which the inflow/outflow pipe is often made of a copper pipe and the flow dividing control pipe 24 is made of aluminum or the like can be expected to have a remarkable effect.

In the present embodiment, the flow distribution control pipe 24 is provided on the reinforcing plate 16a, but is not limited thereto. The flow distribution control pipe 24 may be provided on the end plate 3a side, and in the case of a type not using the reinforcing plate 16a, the flow distribution control pipe 24 and the outflow pipe 5 may be provided on a surface facing the end plate 3 a.

In the present embodiment, the group of refrigerant flow paths 11 has a U-shape, but the present invention is not limited to this. The straight refrigerant flow path 11 group described in embodiment 2 may be used.

In the present embodiment, as described above, the reinforcing

plates

16a and 16b correspond to the bulging deformation suppressing portions.

(embodiment mode 4)

The heat exchanger according to embodiment 4 shows another example of the structure for preventing the expansion deformation of the header region of the plate-fin laminated body 2.

Fig. 29 is a perspective view showing the appearance of the heat exchanger according to embodiment 4.

As shown in fig. 29, in this heat exchanger, a hollow frame 27 is used as an expansion deformation suppressing portion for preventing expansion deformation of the header region H of the plate-fin laminated body 2. That is, the hollow frame 27 is configured as shown in fig. 29. The hollow frame 27 is fitted into the outer surfaces of at least the header region corresponding portions of the

end plates

3a, 3b on both sides of the plate-fin stacked body 2, thereby preventing the expansion deformation of the

end plates

3a, 3 b.

According to this configuration, since at least the outer surface of the header region corresponding portion is fitted into the hollow frame 27, the mounting can be easily performed in a shorter time than the mechanical coupling portion such as the bolt coupling, and the productivity can be improved.

In the present embodiment, as described above, the hollow frame 27 corresponds to the expansion deformation suppressing portion.

(embodiment 5)

Embodiment 5 is a refrigeration system configured using the heat exchanger according to each of the embodiments described above.

In the present embodiment, an air conditioner will be described as an example of a refrigeration system. Fig. 30 is a refrigeration cycle diagram of the air conditioner. Fig. 31 is a schematic cross-sectional view showing an indoor unit of the air conditioner.

In fig. 30 and 31, the air-conditioning apparatus includes an outdoor unit 51 and an indoor unit 52 connected to the outdoor unit 51. The outdoor unit 51 includes: a compressor 53 that compresses a refrigerant; a four-way valve 54 for switching a refrigerant circuit during cooling/heating operation; an outdoor heat exchanger 55 for exchanging heat between the refrigerant and outside air; and a decompressor 56 that decompresses the refrigerant. Further, the indoor unit 52 is provided with: an indoor heat exchanger 57 that exchanges heat between the refrigerant and the indoor air; and an indoor fan 58. 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 refrigeration cycle.

In the refrigerant circuit of the present embodiment, a refrigerant is used in which tetrafluoropropene or trifluoropropene is used as a base component, and difluoromethane, pentafluoroethane, or tetrafluoroethane is mixed with 2 components or 3 components so that the global warming potential is 5 or more and 750 or less, preferably 350 or less, and more preferably 150 or less.

In the air conditioner, the four-way valve 54 switches so that the discharge side of the compressor 53 communicates with the outdoor heat exchanger 55 during the cooling operation. 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. The refrigerant exchanges heat with outside air to dissipate heat, becomes a high-pressure liquid refrigerant, and is sent to the decompressor 56. The refrigerant is decompressed by the decompressor 56 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 indoor air, absorbs heat, evaporates and gasifies, and becomes a low-temperature gas refrigerant. At this time, the indoor air is cooled to cool the room. The refrigerant then returns to the outdoor unit 51, and returns to the compressor 53 via the four-way valve 54.

During the heating operation, the four-way valve 54 is switched to communicate the discharge side of the compressor 53 with the indoor unit 52. The refrigerant compressed by the compressor 53 becomes a high-temperature and high-pressure refrigerant, and is sent to the indoor unit 52 through the four-way valve 54. The high-temperature and high-pressure refrigerant enters the indoor heat exchanger 57, exchanges heat with 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. Thereafter, the refrigerant is sent to the decompressor 56, and is decompressed in the decompressor 56 to become a low-temperature low-pressure two-phase refrigerant. The refrigerant is sent to the outdoor heat exchanger 55 to be heat-exchanged with the outside air, evaporated and gasified. The refrigerant then returns to the compressor 53 via the four-way valve 54.

In the refrigeration system configured as described above, the heat exchangers described in the above embodiments are used for the outdoor heat exchanger 55 and the indoor heat exchanger 57. This enables a high-performance refrigeration system with high energy saving performance to be realized.

(modification example)

The above embodiment exemplifies the form that the heat exchanger 1 of the present invention can take, but does not limit the form. The present invention may include modifications other than the embodiments described below with reference to fig. 32 to 35.

In the reinforcing plate 59a of the present modification, tapered

pipe holes

65a and 66a into which the inflow/outflow pipes are inserted are disposed. This greatly improves the workability of the process of mounting the connection pipe to the heat exchanger 1. That is, when the reinforcing plate 59a is placed on the side surface of the heat exchanger 1 and the connection pipe is joined to the heat exchanger 1 by means of welding or the like, the flame of the welding gun can contact the openings of the pipe holes 65a and 66a spreading in a tapered shape. This enables heat to be efficiently transferred to the heat exchanger 1, and the welding time can be significantly shortened.

Further, by making the

pipe holes

65a, 66a tapered, dew water generated when the heat exchanger 1 is used as an evaporator is easily drained from the

pipe holes

65a, 66 a. As a result, corrosion of the aluminum material due to dew retention can be prevented. The reinforcing plate 59a shown in fig. 32 to 34 is disposed so as to cover the entire surface of the end plate 60a, but the reinforcing plate 59a may be disposed at least in the header region corresponding portion of the end plate 60 a.

In the present modification, screw holes are provided in the communication holes 62 and 63 of the reinforcing plate 59b and the end plate 60b, and screw portions are provided at the end portions of the fastening mechanism 61. The reinforcing plate 59b and the fastening mechanism 61 are fixed. This improves workability in assembling the heat exchanger 1. For example, when the reinforcing plate 59b is formed with only through holes and no thread cutting is performed, if a long thread is used for the fastening means 61, a fixing member such as a nut must be fastened to an end portion of the thread in order to suppress expansion of the heat exchanger 1 in the longitudinal direction. As a result, the operability of the heat exchanger 1 in which the piping and the like are arranged in a complicated manner is significantly reduced. When the reinforcing plate 59b is directly subjected to the thread cutting process, fastening by a fixing member such as a nut is not necessary, and the workability is greatly improved. In the present modification, since the reinforcing plate 59b and the fastening mechanism 61 are directly fixed, even when a compressive force is applied in the longitudinal direction of the heat exchanger 1, the force can be alleviated. In addition, from the viewpoint of operability, it is more preferable to fix the communication holes provided in the reinforcing plates 59b and the end plates 60b on one side to the fastening members as screw holes, rather than to use screw holes as the communication holes provided in the reinforcing

plates

59a and 59b on both sides and the

end plates

60a and 60b on both sides.

Further, a dew water receiving portion 64a and a dew water receiving portion 64b are provided in the peripheral edge portion of the reinforcing plate 59a and the peripheral edge portion of the reinforcing plate 59b in the present modification example, respectively. This allows mist attached to the end of the fastening mechanism 61 extending from the reinforcing plate 59a and dew-water generated on the surface of the reinforcing

plates

59a and 59b to flow into a predetermined portion. This makes it possible to make the volume of the container for receiving dew water smaller at the lower portion of the heat exchanger 1.

Industrial applicability of the invention

The invention provides a small-sized and high-efficiency heat exchanger and a refrigeration system using the same, wherein an expansion deformation suppressing part is provided at a portion corresponding to a header region of a plate-fin laminated body, and expansion deformation of the header region portion can be suppressed. As a result, the present invention can be widely applied to heat exchangers used in household and industrial air conditioners, various refrigeration systems, and the like, and has a great industrial value.

Description of the reference numerals

1 Heat exchanger

2-plate fin laminated body

2a plate fin

3. 3a, 3b end plate

4 inflow pipe (inlet header)

5 outflow pipe (outlet header)

6 st plate fin

6a 1 st plate-like member

6b 2 nd plate-like member

7 nd 2 nd plate fin

8. 8a, 8b header openings

9 connecting part (bolt-nut)

10 manifold flow path

10a peripheral flow path

10b connecting channel

10c multiple branch flow path

11 refrigerant flow path (1 st fluid flow path)

11a forward flow path part

11b return side channel part

12 cutting and forming the projection

12a, 12aa protrusions (1 st cut forming protrusion)

12b projection (2 nd cut forming projection)

13 through hole (boss hole for positioning)

13a hole peripheral part (positioning boss hole peripheral part)

14 manifold flow path

15 slit

16a, 16b reinforcing plate

17 shunting collision wall

18 non-flow path part

19a, 19b planar end portions

20 depressed plane part

20a narrow plane

20b broad width plane

21 fin plane part

22(22a, 22b) projection (cut-out projection)

24-flow dividing control tube

25 gap for refrigerant circulation

26. 26a branch outlet

27 hollow frame

51 outdoor machine

52 indoor machine

53 compressor

54 four-way valve

55 outdoor heat exchanger

56 pressure reducer

57 indoor heat exchanger

58 indoor fan

59a reinforcing plate

59b reinforcing plate

60a end plate

60b end plate

61 connecting mechanism

Communication hole of 62 reinforcing plate

63 communication hole of end plate

64a, 64b dew receiving part

65a, 65b piping hole

66a, 66b piping holes.

Claims

1. A heat exchanger, comprising:

a plate fin laminate in which a plurality of plate fins each having a flow path through which the 1 st fluid flows are laminated;

a 1 st end plate and a 2 nd end plate respectively arranged at both ends of the plate fin laminate in the stacking direction; and

an inflow/outflow pipe including an inflow pipe and an outflow pipe through which the 1 st fluid flowing through the flow path passes,

a 2 nd fluid flows between the plate fin lamination layers of the plate fin lamination body to perform heat exchange between the 1 st fluid and the 2 nd fluid, wherein

The plurality of plate fins respectively include: a flow path region having a plurality of 1 st fluid flow paths for the 1 st fluid to flow; and a header area having header flow paths for communicating the plurality of 1 st fluid flow paths with the inflow and outflow tubes, respectively,

the 1 st fluid flow path is formed by concave grooves provided in the plurality of plate fins,

an expansion deformation suppressing portion that suppresses expansion deformation of the 1 st header region corresponding portion and the 2 nd header region corresponding portion of the 2 nd end plate is provided at the 1 st header region corresponding portion of the 1 st end plate and the 2 nd header region corresponding portion,

the bulging deformation suppression portion has a joining portion that joins the 1 st header region corresponding portion and the 2 nd header region corresponding portion,

a 1 st reinforcing plate is disposed on an outer surface of a portion corresponding to the 1 st header region,

a 2 nd reinforcing plate is provided on an outer surface of a corresponding portion of the 2 nd header region,

the bulging deformation suppression portion is constituted by the coupling portion, the 1 st reinforcing plate, and the 2 nd reinforcing plate,

the 1 st reinforcing plate and the 2 nd reinforcing plate are connected by the connecting portion, the plate-fin laminate is sandwiched by the 1 st end plate and the 2 nd end plate and the 1 st reinforcing plate and the 2 nd reinforcing plate,

a flow distribution control pipe extending toward the 2 nd end plate is connected to the 1 st surface of the 1 st reinforcing plate,

the inflow/outflow pipe is connected to the 2 nd surface of the 1 st reinforcing plate opposite to the 1 st surface,

the 1 st reinforcing plate is formed of a material such that a potential difference between the flow dividing control tube and the inflow/outflow tube is smaller than a potential difference when the flow dividing control tube and the inflow/outflow tube are directly connected.

2. The heat exchanger of claim 1, wherein:

the 1 st fluid flow paths are formed in a U shape,

a header flow path on a fluid inlet side communicating with the inlet pipe and a header flow path on a fluid outlet side communicating with the outlet pipe are disposed on one end side of each of the plurality of plate fins.

3. The heat exchanger of claim 1, wherein:

through holes are provided in the plurality of plate fins, the 1 st end plate and the 2 nd end plate, and the 1 st reinforcing plate and the 2 nd reinforcing plate,

the 1 st reinforcing plate and the 2 nd reinforcing plate are coupled to each other by the coupling portion penetrating the through hole.

4. The heat exchanger of any one of claims 1 to 3, wherein:

the 1 st reinforcing plate is provided with a pipe hole into which the inflow/outflow pipe is inserted.

5. The heat exchanger of claim 4, wherein:

the tubing aperture is tapered.

6. The heat exchanger of any one of claims 1 to 3, wherein:

the through hole provided in the 2 nd reinforcing plate is provided with a thread groove, and a thread portion is provided at an end of the connecting portion.

7. The heat exchanger of claim 6, wherein:

the through hole provided in the 2 nd end plate is provided with a thread groove.

8. The heat exchanger of claim 4, wherein:

a dew water receiving portion is disposed at a peripheral edge portion of the 1 st reinforcing plate and a peripheral edge portion of the 2 nd reinforcing plate.

9. A refrigeration system, characterized by:

comprising a heat exchanger according to any one of claims 1 to 8.