JP6785408B2 - Heat exchanger and refrigeration system using it - Google Patents

Description

The present invention relates to a heat exchanger and a refrigeration system using the same, and more particularly to a plate fin laminated heat exchanger configured by laminating plate-shaped plate fins through which a refrigerant flows and a refrigeration system using the same.

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

Under such circumstances, the heat exchanger of the refrigeration system generally uses a fin tube type heat exchanger configured by penetrating a heat transfer tube through a group of fins, and the diameter of the heat transfer tube is reduced. The heat exchange efficiency is being improved and the size is being reduced.

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

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

This plate fin laminated heat exchanger exchanges heat between a first fluid flowing through a flow path formed in the plate fins and a second fluid flowing between the laminated plate fins. It is widely used in air conditioners for vehicles and the like (see Patent Document 1).

32 and 33 show the plate fin laminated heat exchanger described in Patent Document 1, and the heat exchanger 100 is a plate fin formed by laminating plate fins 102 having a flow path 101 through which a first fluid flows. The end plates 104 are laminated and arranged on both sides of the laminated body 103.

Utility Model Registration No. 3192719

In the plate fin laminated heat exchanger described in Patent Document 1, since the flow path 101 is formed by press-molding a concave groove in the plate fin 102, the cross-sectional area of the flow path 101 is transmitted to the fin tube type. It has the advantage that it can be made even smaller than a heat tube.

However, since the area of the header flow path 105 through which the refrigerant flows into each of the flow paths 101 is extremely large compared to the area of each flow path 101, the pressure of the refrigerant in the header flow path 105 portion becomes large and the end There is a tendency that the portion of the plate 102 having the header flow path 105 (the upper and lower portions of the plate fin laminated heat exchanger shown by X in FIG. 32) expands and deforms outward.

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

However, according to the experiments of the inventors, in the case of a heat exchanger such as a home air conditioner or a commercial air conditioner in which the amount of refrigerant used is larger than that of an automobile air conditioner, expansion and deformation in the header flow path 105 portion. It was found that the pressure of the air conditioner is considerably larger than that of the air conditioner for automobiles, and it is difficult to suppress the expansion deformation in the header flow path 105 portion, and in some cases, the end plate expands and deforms outward.

It was also found that there is a limit to the stacking direction dimension of the plate fins 102 due to such expansion and deformation, and it is difficult to obtain a heat exchanger having a width dimension suitable for a home air conditioner, a commercial air conditioner, or the like. did.

Furthermore, recent air conditioners use R1123 (1,1,2-trifluoroethylene) refrigerants with a small global warming potential (GWP) and R1132 (1,2-difluoroethylene) refrigerants from the viewpoint of preventing global warming. Practical application is being studied, and the pressure of this refrigerant is higher than that of the conventional R410A refrigerant. Therefore, it is assumed that when such a refrigerant is used, expansion and deformation in the header flow path 105 portion becomes remarkable. To. Therefore, some measures to suppress expansion and deformation are indispensable.

The present invention has been made in anticipation of such findings and problems that occur during environmental measures, and can suppress expansion and deformation in the header flow path even in heat exchangers used for home and commercial air conditioners and the like. It is an object of the present invention to provide a heat exchanger having high heat exchange efficiency and a high-performance refrigeration system using the heat exchanger.

In order to achieve the above object, the heat exchanger includes a plate fin laminate having a flow path through which the first fluid flows, and a second fluid is allowed to flow between the plate fin laminates of the plate fin laminate. , A heat exchanger that exchanges heat between the first fluid and the second fluid.
The plate fin laminate is configured by combining a core laminate composed of a plurality of plate fins having a flow path through which a first fluid flows between the first end plate and the second end plate.
The plate fins of the core laminate communicate with a flow path region having a plurality of first fluid flow paths and each first fluid flow path in the flow path region so that the first fluid flows in parallel. A header region having a flow path is provided, and the first fluid flow path is formed by a concave groove provided in the plate fin.
In addition, the core laminate has an inlet opening and an outlet opening that serve as entrances and exits of the first fluid to the header flow path in the first end plate, and the second end plates are laminated back to back and combined. A reinforcing plate was arranged outside at least the header region-corresponding portion of the first end plate of the back-to-back combined core laminate, and the reinforcing plates were provided so as to penetrate the header region of the back-to-back combined core laminate. The configuration is such that the header region-corresponding portion is prevented from expanding and deforming outward by being connected and fixed by the connecting means.

As a result, even in a heat exchanger having a large refrigerant flow rate and a high pressure, it is possible to suppress outward expansion and deformation of the plate fin laminate in the header region corresponding portion by connecting and fixing the reinforcing plates, and also to stack the cores. In the back-to-back part of the second end plate corresponding to the header area of the body, the outward refrigerant pressure acting on the part corresponding to the header area is offset because the directions of the pressures are opposite to each other, and the back-to-back header area is supported. The reinforcing plate that prevents the expansion and deformation of the portion can be omitted. Moreover, since the core laminates are combined into one plate fin laminate, the dimension width in the plate fin stacking direction can be increased, and long heat exchange suitable for home air conditioners and commercial air conditioners while suppressing expansion and deformation. It can be a vessel. Then, the diameter of the flow path cross-sectional area of the first fluid flow path itself can be reduced to reduce the size of the heat exchanger and improve the heat exchange efficiency. In addition, by using such a heat exchanger, it is possible to provide a compact and highly energy-saving high-performance refrigeration system.

According to the above configuration, the present invention provides a long and highly efficient heat exchanger without expansion and deformation in the header region even if it is a heat exchanger used for home and commercial air conditioners, and energy saving using the heat exchanger. It is possible to provide a high-performance refrigeration system.

A perspective view showing the appearance of the plate fin laminated heat exchanger according to the first embodiment of the present invention. External perspective view of the core laminate constituting the plate fin laminate of the plate fin laminate type heat exchanger An exploded perspective view showing the core laminate separated into upper and lower parts. An exploded perspective view of the same core laminate Side view showing the plate fin laminated state of the same core laminated body AA sectional view of FIG. BB sectional view of FIG. CC sectional view of FIG. Perspective view showing by cutting the connection portion of the inflow / out pipe and the header opening portion in the plate fin laminated heat exchanger according to the first embodiment of the present invention. Perspective view showing the refrigerant flow path group portion of the plate fin laminated body in the plate fin laminated heat exchanger cut out. Perspective view showing the refrigerant flow path group portion of the plate fin laminated heat exchanger cut out. Perspective view showing by cutting the positioning boss hole portion of the plate fin laminated body in the plate fin laminated heat exchanger. The perspective view which shows by cutting the header opening part of the plate fin laminated body in the plate fin laminated type heat exchanger. Top view of the plate fins constituting the plate fin laminate of the plate fin laminate type heat exchanger Enlarged plan view showing the header area of the plate fin Exploded view showing a part of the structure of the plate fins In the plan view of the plate fins, (a) is a plan view of the first plate fin, (b) is a plan view of the second plate fin, and (c) is a state when both the first and second fin plates are stacked. Floor plan to explain The figure for demonstrating the refrigerant flow operation of the plate fin. An enlarged perspective view showing a protrusion provided in the flow path region of the plate fin. An enlarged perspective view showing a protrusion provided at the U-turn side end of the refrigerant flow path of the plate fin. Perspective view showing the appearance of the core laminate of the plate fin laminated heat exchanger according to the second embodiment of the present invention. Plan view of plate fins constituting the plate fin laminate of the same core laminate Exploded view showing a partially enlarged view of the structure of the plate fins in the core laminate Perspective view showing the refrigerant flow path group portion of the core laminate by cutting. Perspective view showing the appearance of the core laminated body of the plate fin laminated type heat exchanger according to the third embodiment of the present invention. A perspective view showing a state in which the shunt control pipe is extracted from the core laminated body. Perspective view showing a shunt control pipe insertion portion in the same core laminate Perspective view of the same shunt control pipe Sectional drawing which shows the shunt control pipe part of the same core laminated body Refrigeration cycle diagram of an air conditioner using the plate laminated heat exchanger of the present invention Schematic cross-sectional view of the air conditioner Cross-sectional view of a conventional plate fin laminated heat exchanger Top view of plate fins in the conventional plate fin laminated heat exchanger

The first invention is a heat exchanger, the heat exchanger includes a plate fin laminate having a flow path through which a first fluid such as a refrigerant flows, and a second plate fin laminate between the plate fin laminates. A heat exchanger that allows a fluid to flow and exchange heat between the first fluid and the second fluid.
The plate fin laminate is formed by combining a core laminate composed of a plurality of plate fins having a flow path through which the first fluid flows between the first end plate and the second end plate.
The plate fins of the core laminate communicate with a flow path region having a plurality of first fluid flow paths and each first fluid flow path in the flow path region so that the first fluid flows in parallel. A header region having a flow path is provided, and the first fluid flow path is formed by a concave groove provided in the plate fin.
In addition, the core laminate opens an inlet opening and an outlet opening, which are entrances and exits of the first fluid to the header flow path, in a portion corresponding to the header region of one of the first end plates, and the second end plates are back to back. A reinforcing plate is arranged outside at least a header region-corresponding portion of the first end plate of the core laminate combined in a back-to-back manner, and the reinforcing plates are connected to each other by a connecting means and combined back-to-back. The header region of the core laminate is sandwiched so that the portion corresponding to the header region is prevented from expanding and deforming outward.

As a result, even in a heat exchanger having a large refrigerant flow rate and a high pressure, it is possible to suppress outward expansion and deformation of the plate fin laminate in the header region corresponding portion by connecting and fixing the reinforcing plates, and also to stack the cores. In the back-to-back part of the second end plate corresponding to the header area of the body, the outward refrigerant pressure acting on the part corresponding to the header area is offset because the directions of the pressures are opposite to each other, and the back-to-back header area is supported. The reinforcing plate that prevents the expansion and deformation of the portion can be omitted. Moreover, since the core laminates are combined into one plate fin laminate, the dimension width in the plate fin laminate direction can be increased, and long heat exchange suitable for home air conditioners and commercial air conditioners while suppressing expansion and deformation. It can be a vessel. Then, the diameter of the flow path cross-sectional area of the first fluid flow path itself can be reduced to reduce the size of the heat exchanger and improve the heat exchange efficiency. In addition, by using such a heat exchanger, it is possible to provide a compact and highly energy-saving high-performance refrigeration system.

The second invention is the header flow on the inlet side of the header flow path that communicates with the first fluid flow path by making a U-turn in the first fluid flow path formed in the plate fin in a substantially U shape in the first invention. The header flow path on the path and outlet side is grouped on one end side of the plate fin laminate, and the reinforcing plates of the header area corresponding portion provided by grouping the header flow path on the inlet side and the header flow path on the exit side are connected to each other. The header region of the plate fin laminated body connected by is sandwiched between them and combined back to back.

As a result, the first fluid flow path is lengthened to increase the amount of heat exchange of the refrigerant without enlarging the plate fins (increasing the length dimension), further improving the heat exchange efficiency, and promoting miniaturization. By combining the header flow path on the inlet side and the header flow path on the outlet side, even if the flow rate of the first fluid in the header region portion increases and the pressure increases, the header region corresponding portion will be affected. Expansion and deformation can be reliably prevented.

According to a third aspect of the invention, in the first or second invention, the reinforcing plate arranged outside the first end plate is a shunt control pipe that rushes into the header flow path on a surface facing the header region corresponding portion. The inflow pipe and the outflow pipe of the first fluid are connected and integrated on the opposite surface.

As a result, the heat exchange efficiency can be further improved by the diversion effect of the diversion control pipe, and the diversion control pipe can be projected into the header flow path simply by attaching a reinforcing plate, so that the diversion control pipe can be provided. A high-quality and high-efficiency heat exchanger that can prevent plate fin joint defects due to melting of brazing in the plate fin brazed part and quality defects such as refrigerant leakage that accompany it, which is a concern when retrofitting by welding, etc. Can be done.

The fourth invention is the third invention, in which the potential difference between the shunt control pipe and the inflow pipe or the outflow pipe is the potential difference between the shunt control pipe and the inflow pipe or the outflow pipe when the shunt control pipe and the inflow pipe or the outflow pipe are directly connected. The structure is made of a material smaller than the size of the material.

As a result, it is possible to prevent the occurrence of contact corrosion between dissimilar metals that occurs when the shunt control pipe and the inflow pipe or the outflow pipe are directly connected, and it is possible to greatly improve the reliability during long-term use.

According to a fifth aspect of the present invention, in the first to fourth inventions, the header flow path provided in the header region of the core laminate includes an outer peripheral flow path around the header opening provided in the plate fin and the outer peripheral flow path. The connecting means for connecting the reinforcing plate for preventing the expansion and deformation of the header region of the core laminate is provided through both side portions of the connecting flow path. There is.

As a result, the entire amount of the refrigerant flowing through the header flow path in the header region portion flows through the connecting flow path and the refrigerant pressure becomes the highest, but since both side portions of the connecting passage are connected and fixed by the connecting means, the expansion and deformation thereof. Can be effectively prevented, and expansion and deformation of the portion corresponding to the header region can be more reliably prevented.

In the sixth aspect of the invention, in the first to fifth inventions, through holes are provided at appropriate positions on the periphery of the header region corresponding portion of the plate fins, end plates, and reinforcing plates, and the reinforcing plates are connected to each other through fastening means through the through holes. It is a configuration that has been made.

This prevents expansion and deformation of the header region-corresponding portion of the first end plate, and at the same time, positions the plate fins, the first and second end plates when they are laminated by fitting a pin (jig) into the through hole. This can also be done to prevent expansion and deformation of the header region portion and at the same time improve productivity.

A seventh invention is a refrigeration system, in which the heat exchanger constituting the refrigeration cycle is the heat exchanger according to any one of the first to sixth inventions.

As a result, this refrigeration system can be a high-performance refrigeration system with high energy saving because the heat exchanger is compact and highly efficient without expansion and deformation in the header region portion.

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

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

Moreover, the embodiment described below shows an example of the present invention, and the configuration, function, operation and the like shown in the embodiment are examples and do not limit the present disclosure.

FIG. 1 is a perspective view showing the appearance of the plate fin laminated heat exchanger (hereinafter, simply referred to as a heat exchanger) 1 of the present embodiment, and FIG. 2 constitutes a plate fin laminated body of the plate fin laminated heat exchanger. External perspective view of the core laminate, FIG. 3 is an exploded perspective view showing the core laminate separated vertically, FIG. 4 is an exploded perspective view of the core laminate, and FIG. 5 is a plate fin of the core laminate. It is a side view sectional view which shows the laminated state.

As shown in FIG. 1, the heat exchanger 1 of the present embodiment includes a plate fin laminate 200 that is mainly a heat exchanger by combining a core laminate 2 formed by laminating a plurality of plate fins 2a. It is configured.

As shown in FIGS. 2 and 3, each core laminate 2 constituting the plate fin laminate 200 is configured by laminating a plurality of plate fins 2a, and the refrigerant as the first fluid exchanges heat. It has an inflow pipe (inlet header) 4 that flows in when the vessel is used as a condenser, and an outflow pipe (outlet header) 5 that discharges the refrigerant that has flowed through the flow path in the plate fins 2a.

Further, on both sides (upper side and lower side in FIG. 3) of the core laminated body 2 in the laminating direction, rectangular first end plates 3a and second end plates 3b having substantially the same plan view as the plate fins 2a are provided. ing. The first and second end plates 3a and 3b are formed of a plate material having rigidity, and are formed by metal processing a metal material such as aluminum, an aluminum alloy, or stainless steel by grinding.

The first and second end plates 3a and 3b and the plurality of plate fins 2a are brazed and joined in a laminated state to be integrated. These may be joined using other heat resistant fixing methods, such as chemical joining members.

As shown in FIG. 1, the core laminate 2 configured as described above is a combination of the second end plates 3b laminated back to back, and the core laminates 2 and 2 combined back to back. Reinforcing plates 16a and 16b are laminated and arranged on the outside of at least the portion corresponding to the header region of the end plate 3a.

The reinforcing plates 16a and 16b on both sides of the core laminates 2 and 2 are bolts and nuts that penetrate the first end plate 3a, the back-to-back second end plate 3b, and the opposite first end plate 3a. Alternatively, the plate fin laminate 200 is formed by connecting and fixing the core laminate 2 at both ends in the longitudinal direction by a connecting means 9 such as a caulking pin shaft.

That is, the plate fin laminate 200 is formed by mechanically connecting and fixing both ends of the core laminates 2 and 2 in the longitudinal direction by the reinforcing plates 16a and 16b.

The reinforcing plates 16a and 16b are also made of a plate material having rigidity similar to the end plates 3a and 3b, for example, a metal material such as stainless steel or an aluminum alloy, but the material has higher rigidity than the end plates 3a and 3b. Or, it is preferable to use a thick plate.

Further, the plate fin 2a has a plurality of parallel refrigerant flow path groups through which the refrigerant as the first fluid flows (the refrigerant flow path configuration of the plate fin 2a including the refrigerant flow path group will be described in detail later). The refrigerant flow path group is formed in a substantially U shape, and the inflow pipe 4 and the outflow pipe 5 connected to the refrigerant flow path group are end plates 3a on one side (upper side in FIG. 1) of the core laminate 2. It is arranged collectively on one end side of.

In the heat exchanger 1 of the present embodiment configured as described above, the refrigerant flows in parallel in the longitudinal direction through a plurality of flow paths inside each plate fin 2a of the core laminate 2, makes a U-turn, and is a folded outflow pipe. It is discharged from 5. On the other hand, air, which is the second fluid, passes through the gap formed between the stacks of the plate fins 2a constituting the core laminate 2. As a result, heat exchange between the refrigerant as the first fluid and the air as the second fluid is performed.

Next, the configuration of the core laminate 2 of the plate fin laminate 200 that forms the main body of the heat exchanger 1 and the plate fins 2a that constitute the core laminate 2 will be described.

6 to 13 are perspective views showing a part of the core laminate 2 cut out, and FIGS. 14 to 20 are views showing the configuration of the plate fins 2a.

As shown in FIG. 10, the core laminate 2 is configured by laminating plate fins 2a (first plate fins 6 and second plate fins 7) having two types of flow path configurations.

As shown in FIG. 16, the first plate fin 6 and the second plate fin 7 of the plate fin 2a are the same as the first plate-shaped member 6a in which the refrigerant flow path configuration described in detail later is press-formed. It is configured by brazing and joining the second plate-shaped member 6b of the configuration so as to face each other. The first plate-shaped member 6a and the second plate-shaped member 6b are made of a rectangular metal thin plate such as aluminum, aluminum alloy, or stainless steel.

Hereinafter, the flow path configuration formed in the plate fin 2a will be described.

Since the first plate fin 6 and the second plate fin 7 of the plate fin 2a have the same configuration except that the positions of the refrigerant flow paths 11 described later are displaced, the first plate fin 6 is shown in FIGS. 14 to 16 and the like. The explanation will be given by giving a drawing number only in the case.

As shown in FIG. 14, the plate fins 2a (6, 7) have a header region H formed at one end in the longitudinal direction (left side in FIG. 14), and the other region serves as a flow path region P. ing. Then, both the header opening 8a on the inflow side and the header opening 8b on the outlet side are formed in the header region H, and the inflow pipe 4 and the outflow pipe 5 are connected to each other.

Further, in the flow path region P, a plurality of first fluid flow paths (hereinafter referred to as refrigerant flow paths) 11 through which the refrigerant which is the first fluid flows from the header opening 8a are formed in parallel, and the refrigerant flow paths 11 group Is folded back at the other end of the plate fins 2a (6, 7) (near the right end in FIG. 14) and is connected to the header opening 8b on the outlet side. More specifically, the refrigerant flow path 11 group is composed of an outward path side flow path portion 11a connected to the header opening 8a on the inflow side and a return path side flow path portion 11b connected to the header opening 8b on the outlet side. The refrigerant is folded back in a shape so that the refrigerant from the header opening 8a on the inflow side makes a U-turn from the flow path portion 11a on the outward path side to the flow path portion 11b on the return path side and flows to the header opening 8b on the outlet side. It has become.

Further, around the header opening 8a on the inflow side, as shown in an enlarged manner in FIG. 15, a header flow path 10 in which the refrigerant from the header opening 8a flows into the refrigerant flow path 11 group is formed. The header flow path 10 includes an outer peripheral flow path 10a formed so as to bulge from the outer periphery of the header opening 8a, a single connecting flow path 10b extending toward the refrigerant flow path 11 group side of the outer peripheral flow path 10a, and the same. It is composed of a multi-branch flow path 10c that connects the communication flow path 10b to each flow path of the refrigerant flow path 11 group.

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

Further, the opening shape of the header opening 8a on the inflow side has a diameter larger than the opening shape of the header opening 8b on the outlet side. This is a case where the heat exchanger is used as a condenser, because in that case, the volume of the refrigerant after the heat exchange is reduced.

Further, the number of the return path side flow path portions 11b connected to the header opening 8b on the outlet side is set to be smaller than the number of the outward path side flow path portions 11a into which the refrigerant flows from the header opening 8a on the inflow side. This is the same reason that the diameters of the header openings 8a and 8b are different, and the volume of the refrigerant after heat exchange becomes small.

In the present embodiment, the number of the outward path side flow path portion 11a is 7, and the number of the return path side flow path portion 11b is 2, but the number is not limited to this.

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

The first and second end plates 3a and 3b are arranged on both sides of the laminated body of the plate fins 2a configured as described above, and the first and second end plates 3a and 3b are as shown in FIG. An inlet opening 8aa and an outlet opening 8bb are formed in a portion of the plate fin 2a facing the header opening 8a on the inlet side and the header opening 8b on the outlet side. Then, the inflow pipe 4 and the outflow pipe 5 are connected to the inlet opening 8aa and the outlet opening 8bb.

Further, in the plate fins 2a (6, 7), a region in which the outward path side flow path portion 11a through which the refrigerant flows from the header opening 8a on the inflow side is formed, and a return path side flow flowing to the header opening 8b on the outlet side. As shown in FIGS. 14 and 15, there is a slit 15 between the region where the road portion 11b is formed for the purpose of reducing (insulating) heat conduction between the refrigerants in the plate fins 2a (6, 7). Is formed.

The connecting flow path 10b of the header flow path 10 on the inlet side is provided so as to be biased toward a portion of the outbound path side flow path portion 11a opposite to the return path side flow path portion 11b. That is, as shown in FIG. 18, the width V from the center line O of the connecting flow path 10b to the flow path 11a-1 at the end on the return path side flow path portion 11b is opposite to the return path side flow path portion 11b. It is configured to be larger than the width W up to the end flow path 11a-2. A shunt collision wall 17 is formed at the end of the connecting flow path 10b, that is, at the opening portion connected to the outward path side flow path portion 11a, and the outward path side flow path portion on the extension line of the communication flow path 10b is non-flow. It is a road portion 18. Therefore, the refrigerant from the connecting flow path 10b collides with the shunting collision wall 17 and shunts (splits vertically in FIG. 18), and at the non-flow path portion 18 via the multi-branch flow path 10c on the downstream side of the connecting flow path 10b. It flows to each of the upper and lower flow path groups of the divided outbound side flow path portion 11a.

A header flow path 14 is also formed in the header opening 8b on the outlet side, and the header flow path 14 does not have a shunt collision wall 17, but is provided in the header opening 8a on the inlet side. It is formed in substantially the same shape as 10. In this embodiment, since the number of the return path side flow path portions 11b of the refrigerant flow path 11 group is as small as two, the connecting flow path 10b is provided on the substantially center line of the return path side flow path portion 11b group.

On the other hand, the plate fins 2a (6, 7) configured as described above have the first plate fins 6 in this example, as shown in FIG. 17A, in the flow path region P. A plurality of protrusions 12 (first protrusions: 12a, 12aa, second protrusions: 12b) are formed at predetermined intervals in the longitudinal direction.

FIG. 17 (a) shows the first plate fin 6, (b) shows the second plate fin 7, and (c) shows both fin plates 2a (6, 7) superimposed (position of the refrigerant flow path 11 group). Figure to show the deviation).

As shown in FIG. 17, the first protrusions 12a and 12aa are the flat end portions 19a of the long side edges of the plate fins (long side edges on both the left and right sides in FIG. 17A) and the side edges of the slit 15. The first protrusions 12a are formed on the plane end portions 19b, respectively, and as shown in FIG. 7, the first protrusion 12a abuts on the plane end portion 19a of the long edge portion of the second plate fin 7 adjacent to each other in the stacking direction, and the first The protrusion 12aa abuts on the plane end 19b of both side edges of the slit 15 and defines the distance between layers with the second plate fin 7 to a predetermined length. The first protrusion 12a is formed so as to be located inside the edge of each long edge, for example, 1 mm or more inside (closer to the refrigerant flow path 11) from the edge.

As is clear from FIG. 17A, the second protrusions 12b are formed at predetermined intervals between the flow paths of the refrigerant flow paths 11 groups, in the recessed flat surface portion 20 which is the non-flow path portion 18 in this example. There is. The second protrusion 12b abuts on the recessed flat surface portion 20 of the second plate fin 7 adjacent to the stacking direction shown in FIG. 17B and is between the second protrusion 12a and the second plate fin 7 as well as the first protrusions 12a and 12aa. The distance between layers is specified to a predetermined length.

Further, each of the protrusions 12 (12a, 12aa, 12b) is formed by cutting up a part of the flat end portions 19a, 19b and the recessed flat portion 20 of the first plate fin 6, as shown in FIG. (Hereinafter, protrusions 12 (12a, 12aa, 12b) are referred to as cut-up protrusions), and the cut-up edge Y faces the flow direction indicated by the arrow of the second fluid flowing between the laminated plates of the plate fins 2a. The cut-up rising piece Z is adapted to follow the flow of the second fluid. In the present embodiment, the second fluid is cut and raised in a substantially U-shaped cross section so as to open in the flow direction of the second fluid.

Then, each of the raised protrusions 12 (12a, 12aa, 12b) has plate fins 2a whose top surfaces are adjacent to each other at the time of brazing joining of the plate fins 2a (6, 7) and the end plates 3 (3a, 3b). It is fixed to (6, 7), and each plate fin 2a (6, 7) is integrally connected.

The first cut-up protrusions 12a and 12aa and the second cut-up protrusions 12b are arranged so as to be linear along the flow direction of the second fluid (air), but are arranged in a staggered arrangement. It may be installed.

Further, as shown in FIG. 20, the plate fins 2a (6) also have a plurality of protrusions 22 (on the fin flat surface portion 21 at the end on the folded side of the flow path region P in which the refrigerant flow path 11 group makes a U-turn. 22a, 22b) are formed. The protrusions 22 (22a, 22b) are also formed by cutting up the fin flat surface portion 21 (hereinafter, the protrusions 22 (22a, 22b) are also referred to as cut-up protrusions), and the cut-up protrusions 22 (22a, 22b). ) Is opposed to the flow of the second fluid. Further, the cut-up protrusions 22 (22a, 22b) are provided on the downstream side of the positioning boss hole 13, and the cut-up protrusion 22a closest to the downstream side of the positioning boss hole 13 allows the flow on the downstream side of the positioning boss hole 13. It is cut and raised in a shape that contracts, for example, a shape that opens in a V shape toward the flow of the second fluid. Each of the protrusions 22b further downstream than the protrusion 22a is staggered so that its center line deviates from the center line of the protrusion 22b on the downstream side.

The plate fins 22 (22a, 22b) having their respective top surfaces adjacent to each other are also the same as the raised protrusions 12 (first cut-up protrusions: 12a, 12aa, second cut-up protrusions: 12b). It abuts and is fixed to 2a (7), defines a gap between adjacent plate fins 2a to a predetermined length, and connects the plate fins 2a to each other.

Further, as shown in FIG. 12 and the like, the plate fins 2a (6, 7) have a through hole for positioning (hereinafter, referred to as a boss hole for positioning) 13 at the ends of the header region H and the flow path region P. Is formed. The positioning boss holes 13 are also formed in the end plates 3a and 3b and the reinforcing plates 16a and 16b laminated on both sides of the plate fins 2a (6, 7). The positioning boss hole 13 is equipped with a positioning pin jig for laminating a plurality of plate fins 2a (6, 7) to enable highly accurate laminating of other plate fins 2a. In the above, a connecting means 9 (see FIG. 4) such as a bolt for connecting the reinforcing plates 16a and 16b of the core laminate 2 and the end plates 3a and 3b is also used as a positioning pin jig.

Further, the outer peripheral portion of the positioning boss hole 13 provided at both ends of the plate fins 2a (6, 7) has a hole outer peripheral portion (hereinafter, referred to as a positioning boss hole outer peripheral portion) 13a that bulges up and down. Is formed. The outer peripheral portion 13a of the positioning boss hole forms a space different from the flow path through which the refrigerant flows, and as shown in FIG. 12, is in contact with the plate fins 2a (6, 7) adjacent to each other in the stacking direction. , It is a header region support portion that holds the stacking gap of the plate fins 2a.

The outer peripheral portion 13a of the positioning boss hole formed around the positioning boss hole 13 is the header flow paths 10 and 14 (10a, 10b) of both the inlet and the outlet formed in the header region H shown in FIG. 10c), the other header flow paths 10 and 14 facing in the stacking direction and the outer peripheral portion 13a of the positioning boss hole are brazed and fixed, and the header region portions of the plate fins 2a (6, 7) are integrally connected. ing.

The refrigerant flow path 11 in the present disclosure is described with a circular shape having a cross-sectional shape orthogonal to the flow direction of the refrigerant, but includes a rectangular shape and the like in addition to the circular shape.

Further, in the present embodiment, the refrigerant flow path 11 is described as having a shape protruding on both sides in the stacking direction, but may be formed so as to project on only one side in the stacking direction. In the present disclosure, the circular shape also includes a compound curved shape formed by a circle, an ellipse, and a closed curve.

The heat exchanger of the present embodiment is configured as described above, and its operation and effect will be described below.

First, the flow of the refrigerant and the heat exchange action will be described.

The refrigerant flows from the inflow pipe 4 connected to one end side of each core laminate 2 to the header flow path 10 of each plate fin 2a via the header opening 8a on the inflow side, that is, the outer peripheral flow path 10a around the header opening 8a. , Flows to the refrigerant flow path 11 group via the connecting flow path 10b and the multi-branch flow path 10c. The refrigerant flowing into the refrigerant flow path 11 group of each plate fin 2a is turned back from the outward path side flow path portion 11a to the return path side flow path portion 11b, and passes through the outlet side header flow path 14 and the outlet side header opening 8b. It flows from the outflow pipe 5 to the refrigerant circuit of the refrigeration system.

Then, when flowing through the refrigerant flow path 11, the refrigerant exchanges heat with the air passing between the plate fins 2a laminates of the core laminates 2.

At this time, a strong pressure of the refrigerant is applied to the header region H where the header flow paths 10 and 14 on the inlet side and the outlet side of each of the core laminates 2 are located, as shown by the white arrows in FIG. The header region portion of one end plate 3a (first end plate 3a, 3a located on the outermost side of each core laminated body 2 laminated back to back in FIG. 8) tends to expand and deform.

However, in the heat exchanger of the present embodiment, the core laminates 2 and 2 laminated back to back are sandwiched by the reinforcing plates 16a and 16b whose both end portions including the header region corresponding portion are connected by the connecting means 9. Therefore, it is possible to suppress expansion and deformation in the extrapolation direction.

That is, the reinforcing plates 16a and 16b provided on the outer surface of the header region corresponding portion of the end plates 3a and 3a are connected by the connecting means 9 so that the end plates 3a and 3a are pressed against the core laminate 2 from the outside. Therefore, expansion of the end plates 3a and 3a is prevented. Moreover, since the strength of the header region-corresponding portion of the end plates 3a and 3a is strengthened by the rigidity of the reinforcing plates 16a and 16b themselves, the expansion and deformation of the header region-corresponding portion can be suppressed more strongly.

On the other hand, in the back-to-back second end plate 3b of the core laminate 2 corresponding to the header region, the outward refrigerant pressure acting on the header region corresponding portion is opposite to each other as the direction of the pressure is shown by the gray arrow. Because it becomes, it is offset. Therefore, the portion corresponding to the header region of the back-to-back portion can also be prevented from expanding and deforming without the reinforcing plates 16a and 16b.

In this way, in this heat exchanger, the core laminates 2 and 2 are laminated back to back to prevent expansion and deformation of the core laminates 2 and 2. Then, the size can be reduced by the amount that the reinforcing plates 16a and 16b are eliminated.

Moreover, since this heat exchanger constitutes the plate fin laminate 200 by combining the core laminates 2 and 2 as described above, the dimensional width of the entire plate fin laminate 200 in the plate fin stacking direction can be increased. That is, it is possible to obtain a long heat exchanger suitable for home air conditioners, commercial air conditioners, etc. while suppressing expansion and deformation.

Further, by providing the reinforcing plates 16a and 16b, even if the refrigerant flow path 11 group has a U-shaped flow path configuration exemplified in the present embodiment, expansion and deformation of the header region corresponding portion can be reliably suppressed. it can. That is, in the core laminate 2 of the present embodiment, the refrigerant flow path 11 provided in the plate fin 2a is U-turned in a substantially U shape, and the header flow path 10 on the inlet side and the header flow path 14 on the outlet side are made of the plate fin. Since it is gathered on one end side, the pressure on the inlet side and the outlet side is doubled on the portion. However, with the configuration shown in the present embodiment, even if such a double refrigerant pressure is applied, expansion deformation can be reliably prevented against this.

Furthermore, in the header region H of the core laminate 2, since the flow path area of the header flow path 10 is the largest, the refrigerant pressure in the header flow path 10 portion is the highest. However, since the header flow path 10 is brazed in contact with the adjacent header flow path 10, it is possible to effectively prevent the expansion and deformation of the header flow path 10, and more reliably prevent the expansion and deformation of the portion corresponding to the header region. be able to.

The connecting means 9 such as the bolt can be used as a guide pin (jig) when laminating the plate fins 2a, the first and second end plates 3a and 3b, and the reinforcing plates 16a and 16b. It is possible to improve the stacking accuracy and the productivity.

Further, the strong pressure of the refrigerant applied to the header region H of each of the core laminates 2 and 2 may press and deform the outer peripheral flow path 10a cross-sectional area of the header flow path 10 in the header region H, but the header flow path 10 Since the top surface of the outer wall of the outer peripheral flow path 10a is in contact with the outer peripheral flow path 10a of the other header flow path 10 adjacent in the stacking direction in the stacking direction and is in a brazing state, it is not deformed and is reliable. It can be highly sexual.

As described above, even if this heat exchanger is a heat exchanger having a large amount of refrigerant as described above or an environment-friendly refrigerant having a high compression ratio, the core laminates 2 and 2 are laminated. It is possible to prevent expansion and deformation of the header region portion of the plate fin laminate 200 constructed in the above manner. As a result, the pressure of the refrigerant can be used in a higher state, and a highly efficient heat exchanger can be obtained.

Moreover, in this heat exchanger, the cross-sectional area of the concave groove for the refrigerant flow path formed in the plate fin 2a is reduced to reduce the diameter of each flow path area of the refrigerant flow path 11 group, thereby improving the heat exchange efficiency. It can be improved and miniaturization can be promoted.

That is, the heat exchange efficiency is improved and the length is realized by reducing the diameter of the flow path cross-sectional area of the refrigerant flow path 11 while preventing expansion and deformation of the plate fin laminate 200 in the portion corresponding to the header region. can do.

As described above, this heat exchanger can prevent expansion and deformation due to the refrigerant pressure by connecting the two core laminates 2 with the end plates 3b of the core laminate 2 back to back, but also has the following effects. ..

That is, in the heat exchanger of the present embodiment, since the refrigerant flow path 11 group provided in the plate fin 2a is formed in a substantially U shape as described above and folded back, the plate fin 2a is not enlarged. The length of the refrigerant flow path can be lengthened, the heat exchange efficiency between the refrigerant and the air can be increased, and the refrigerant can be reliably overcooled to improve the efficiency of the refrigeration system. Moreover, the miniaturization of the heat exchanger can be promoted.

Further, in the present embodiment, the refrigerant that exchanges heat with the air flowing between the plate fin stacks of the core laminate 2 is a communication flow path 10b, a multi-branch flow path 10c, and a refrigerant flow from the header flow path 10 on the inlet side. Although it flows to the road 11 group, since the diversion collision wall 17 is provided on the downstream side of the connecting flow path 10b, the refrigerant collides with the diversion collision wall 17 and is split up and down, and each of them is separated from the multi-branch flow path 10c. It is diverted to the refrigerant flow path 11. Therefore, it is possible to prevent the refrigerant from being extremely biased to the flow path on the extension line of the connecting flow path 10b.

Further, when the refrigerant flow paths 11 groups are formed in a U shape and folded back as in this embodiment, as is clear from FIG. 18, the length of each flow path of the refrigerant flow paths 11 groups is set. The U-shaped outer circumference, in other words, the flow path 11a-2 side away from the slit 15, becomes longer, and a drift due to the difference in the flow path length occurs.

However, in this heat exchanger, the connecting flow path 10b from the header flow path 10 is provided so as to be biased toward the repeating path flow path portion side from the center line O of the outward path side flow path portion 11a of the refrigerant flow path 11 group. , It is possible to suppress the drift and allow the refrigerant to flow substantially uniformly in each flow path.

That is, in this heat exchanger, the flow 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 is configured by making the refrigerant flow path 11 group U-turn. Even if the path length is different and the flow path resistance is changed, the connecting flow path 10b from the header flow path 10 on the inlet side is biased toward the repeating path side flow path portion side of the outward path side flow path portion 11a. Therefore, the length of the branch flow path from the connecting flow path 10b to each outward path side flow path portion 11a becomes longer as it gets closer to the return path side flow path portion 11b, and offsets the refrigerant flow path 11 groups. It can be uniformly divided into each flow path.

Therefore, it is possible to make the heat exchanger with higher heat exchange efficiency while promoting the miniaturization of the heat exchanger by the synergistic effect of the U-turn of the refrigerant flow path 11 group and the equalization of the diversion by the diversion collision wall 17.

Moreover, since a slit 15 is formed between the outward path side flow path portion 11a and the return path side flow path portion 11b of the refrigerant flow path 11 group and is thermally divided, the refrigerant flow path 11 group The heat transfer from the outward path side flow path portion 11a to the return path side flow path portion 11b can be prevented to efficiently supercool the refrigerant, and the heat exchange efficiency can be further improved.

Further, in the heat exchanger of this embodiment, a plurality of cut-up protrusions 12 (12a, 12aa, 12b) are provided in the flow path region P of the core laminate 2, and the heat exchange efficiency in the flow path region P is improved. Can be made to. More specifically, the cut-up protrusions 12 (12a, 12aa, 12b) are formed so that the cut-up edge Y faces the flow direction of the second fluid flowing between the laminated plates of the plate fins 2a. At the same time as making the distance between the fin laminates constant, the dead water area that tends to occur on the downstream side of the cut-up protrusions 12 (12a, 12aa, 12b) is minimized, and the leading edge effect is generated at the cut-up edge Y portion. be able to. Moreover, since it is cut and formed so as to face the flow direction of the second fluid, the flow resistance to the second fluid can be made small. Therefore, it is possible to greatly improve the heat exchange efficiency while suppressing the increase in the flow path resistance in the flow path region P of the core laminate 2.

Regarding the arrangement configuration of the cut-up protrusions 12, the cut-up protrusions 12 (12a, 12aa, 12b) provided on the plate fins 2a are arranged in a staggered manner with respect to the second fluid, and the leeward side is formed more than the windward side. Can present various configurations, but the optimum configuration for improving the heat transfer coefficient may be selected according to the specifications and configurations of the heat exchanger and the user's request.

Further, since each of the raised protrusions 12 (12a, 12aa, 12b) is cut and formed so that the flow direction of the air flowing through the gap of the core laminate 2 is opened, the direction in which the air flows, that is, the refrigerant flow. It is not necessary to steal meat from the recessed plane 20 between the refrigerant flow paths in the direction intersecting the road. Therefore, the recessed plane 20 between the refrigerant flow paths can be made narrower by the amount that the meat stealing dimension is unnecessary, as compared with the one formed by raising the cut-up protrusion 12b like a columnar protrusion or the like. The width of the plate fin 2a, in other words, the heat exchanger can be miniaturized.

In addition, the plate fin 2a has a narrow plane 20a and a wide plane 20b due to the alternating positional deviation arrangement of the refrigerant flow paths 11 (see FIG. 7) at the end edge of the long side portion thereof, and the wide plane 20b.
Since the cut-up protrusion 12a is formed on the side and the top surface thereof is fixed to the narrow plane 20a of the adjacent plate fin 2a, it is not necessary to widen the width on the narrow plane 20a side for forming the protrusion. Will also get better. That is, by using the wide flat surface 20b to provide a protrusion on the wide flat surface side and abutting and fixing to the narrow flat surface 20a, the width of the long side portion of the plate fin on the narrow flat surface side is not widened. The narrow flat surface can be left as it is, and the miniaturization of the heat exchanger can be promoted accordingly.

Further, since the cut-up protrusions 12 (12a, 12aa, 12b) are fixed to the adjacent plate fins 2a at the time of brazing joining of the plate fins 2a and the end plates 3a and 3b, each plate. It also serves to integrally connect the fins 2a, and can improve the rigidity of the core laminate 2.

In particular, in the present embodiment, the portion on the extension line of the connecting flow path 10b of the refrigerant flow path 11 group is a non-flow path portion 18, and the non-flow path portion 18 is used to form a part of the protrusions 12 (12a, 12b). That is, since the second cut-up protrusion 12b is provided, the fin plate stacking interval in the refrigerant flow path 11 group portion can be reliably maintained. As a result, the heat exchange efficiency can be improved by making the air flow in the refrigerant flow path 11 group portion stable without variation.

Further, the first cut-up protrusion 12a provided on the long side portion of the core laminated body 2 is effective because it improves the strength of the long side edge portion of the core laminated body 2 which tends to be weak in strength. is there. In particular, the first cut-up protrusions 12aa provided on both side edge portions of the slit 15 of the core laminate 2 improve the strength of the slit edge portion which is divided by the provision of the slit 15 and the strength is lowered, so that the heat exchange efficiency is improved. It is effective because it can prevent deformation near the slit while improving the above.

The first cut-up protrusions 12aa provided on both side edges of the slit 15 may be one so as to straddle the slit 15, but in this case, the outbound side flow path portion 11a and the return path of the refrigerant flow path 11 group are used. There is a concern that heat conduction will occur between the side flow path portion 11b and the slit 15 will reduce the heat insulating effect. However, if the slits 15 are provided separately on both side edges as in the present embodiment, such a concern about heat conduction is eliminated and it is effective. Further, the first cut-up protrusion 12aa may be provided at a place away from the slit 15.

Further, since the first cut-up protrusions 12a and 12aa provided on the long side portion of the core laminate 2 and both side portions of the slit 15 are provided at positions away from the end edge of the plate fin long side of the core laminate 2. When dew condensation water is generated on the plate fins 2a of the core laminate 2 and the dew condensation water flows and is discharged along the edge of the plate fins 2a, the flow is caused by the first cut-up protrusions 12a and 12aa. It is possible to prevent various troubles from accumulating in the cut-and-press protrusions 12a and 12aa by being blocked, and it is possible to obtain a highly reliable heat exchanger.

Further, in the heat exchanger of the present embodiment, since the plate fins 2a are further provided with raised protrusions 22 (22a, 22b) at the U-turn side end of the refrigerant flow path, the plate without the refrigerant flow path 11 The heat exchange contribution of the U-turn side end of the fin 2a can be increased. Therefore, the heat exchange efficiency can be increased over the entire length of the flow path region of the plate fin 2a, and the heat efficiency of the heat exchanger can be improved.

In particular, the U-turn side end of the plate fin 2a has a positioning boss hole 13 and the downstream side thereof becomes a dead water area, so that the heat exchange contribution is extremely low. However, in this embodiment, the above Since a plurality of cut-up protrusions 22 (22a, 22b) are provided on the downstream side of the positioning boss hole 13, the heat exchange contribution of the entire area downstream of the positioning boss hole 13 can be improved.

Further, since the cut-up protrusion 22a provided near the downstream side of the positioning boss hole 13 has a shape that constricts the flow on the downstream side of the positioning boss hole 13, it occurs on the downstream side of the positioning viboss hole 13. The dead water region having a low heat exchange contribution can be minimized, and the heat exchange efficiency can be further improved accordingly.

In addition, each of the raised protrusions 22 (22a, 22b) is cut and formed in the same manner as the raised protrusions 12 (12a, 12aa, 12b) provided in the flow path region P, and the cut and raised edge Y is formed. Is formed to face the flow of the second fluid, so that the leading edge effect can be generated at the cut-up edge portion, and the heat exchange efficiency can be further improved by that amount.

Since the plurality of cutting protrusions 22 (22a, 22b) provided on the downstream side of the positioning boss hole 13 have a staggered arrangement that meanders with respect to the flow of the second fluid, all of them effectively exchange heat. It exerts its function and contributes to heat exchange.

Further, since the tops of the raised protrusions 22 (22a, 22b) are also fixed to the adjacent plate fins 2a and the short side portions of the plate fins 2a are connected and fixed in a laminated state, the core laminated body 2 Rigidity can also be increased.

In the present embodiment, the cut-up protrusion 22 provided near the downstream side of the positioning boss hole 13 is cut-up and formed into a cross-sectional shape that opens in a V shape in the flow direction of the second fluid. However, this may be formed by cutting up in a substantially L shape and provided in a pair facing each other, as long as it has a shape that constricts the flow on the downstream side of the positioning boss hole 13. It may be in any form.

(Embodiment 2)
As shown in FIGS. 21 to 24, the heat exchanger of the present embodiment is different from the heat exchanger of the first embodiment in the shape of the refrigerant flow path group and the installation position of the header opening. The same number is added to the part having the same function as the heat exchanger of No. 1, and different parts will be mainly described.

21 is a perspective view showing the appearance of the core laminate of the heat exchanger in the second embodiment, FIG. 22 is a plan view of the plate fins constituting the core laminate, and FIG. 23 is a partially enlarged configuration of the plate fins. FIG. 24 is a perspective view showing the refrigerant flow path group portion of the core laminated body cut out.

In FIGS. 21 to 24, in the heat exchanger of the present embodiment, the refrigerant flow paths 11 group provided in the plate fins 2a are linear, and the header opening 8a on the inlet side and the other end are on one end side thereof. A header opening 8b on the exit side is provided on the portion side. The inflow pipe 4 is connected to the header opening 8a on the inlet side, and the outflow pipe 5 is connected to the header opening 8b on the outlet side, and the refrigerant flows linearly from one end side to the other end side of the plate fin 2a and flows out. It is designed to do.

The header flow path 10 formed around the header opening 8a on the inlet side is composed of an outer peripheral flow path 10a, a connecting flow path 10b, and a multi-branched flow path 10c around the header opening, and the connecting flow path 10b is an outer peripheral flow path. After being formed so as to extend from 10a in the short side direction of the plate fin 2a, it is connected to the multi-branch flow path 10c, and the header flow path 14 on the outlet side is also configured in the same manner as the header flow path 10 on the inlet side. Both have a symmetrical shape.

Further, the end plates 3a and 3b on both sides of the core laminate 2 are connected by the connecting means 9 without using the reinforcing plates 16a and 16b to prevent expansion and deformation in the header regions H at both ends of the end plates 3a and 3b. ing.

The heat exchanger configured as described above is the same as the heat exchanger described in the first embodiment, including the detailed configuration and effects, except for the effect of forming the refrigerant flow path 11 group into a U shape. , The description is omitted.

In this example, the cut-up protrusion 22 provided at the U-turn side end portion of the plate fin 2a of the first embodiment may be appropriately provided in the header regions on both the inlet and outlet sides, and the U-turn side end portion may be appropriately provided. The same idea as the cut-up protrusions 22 (22a, 22b) provided in the above, for example, may be formed on the downstream side of the header flow path 10 which is a dead water area.

(Embodiment 3)
The heat exchanger of this embodiment is suitable for use as an evaporator in which the inlet and outlet of the refrigerant of the heat exchanger are reversed, and as shown in FIGS. 25 to 29, the header flow path on the outlet side. A refrigerant shunt control pipe 24 is provided in 14.

In this embodiment, a case where the heat exchanger having the configuration of the first embodiment is used as an evaporator will be described as an example.

FIG. 25 is a perspective view showing the appearance of the core laminate of the heat exchanger in the third embodiment, FIG. 26 is a perspective view showing a state in which the flow dividing control tube is extracted from the core laminate, and FIG. 27 is the core laminate. FIG. 28 is a perspective view showing a split flow control pipe insertion portion, FIG. 28 is a perspective view of the same split flow control pipe, and FIG. 29 is a cross-sectional view showing the current split control pipe portion of the core laminated body.

In FIGS. 25 to 29, the shunt control pipe 24 is inserted in the header opening 8b on the outlet side, which is the evaporation outlet of the refrigerant, that is, in the header flow path 14 on the outlet side, and the tip portion thereof is shown in FIG. 29. As described above, it extends to the end plate 3b on the side where the header opening is not provided, and is closed by the end plate 3b. The shunt control pipe 24 is composed of a pipe having a diameter smaller than the inner diameter of the header opening 8b and forms a refrigerant flow gap 25 with the inner surface of the header opening, and the longitudinal direction thereof, that is, stacking of plate fins 2a A plurality of shunt ports 26 are formed at substantially equal intervals in the direction.

The plurality of shunt ports 26 are formed so that their pore diameters decrease toward the direction in which the refrigerant flows, that is, toward the header opening 8b on the outlet side.

Further, the shunt control pipe 24 is attached to the reinforcing plate 16a as shown in FIGS. 26 and 28, and the reinforcing plate 16a is inserted into the header opening 8b by fastening the reinforcing plate 16a to the end plates 3a on both sides of the core laminate 2. It has become so.

The inflow pipe 4 is connected and fixed to the reinforcing plate 16a to which the shunt control pipe 24 is attached to the other surface facing the shunt control pipe 24.

The outflow pipe 5 is also connected and fixed to the reinforcing plate 16a. Further, the shunt control pipe 24 may be configured to close the tip portion thereof so as to be in contact with the end plate 3b.

In the heat exchanger configured as described above, the refrigerant gas flowing from the header opening 8a on the inlet side to the header flow path 14 on the outlet side via the refrigerant flow path 11 group is shown by the arrow in FIG. It flows from the refrigerant flow gap 25 through the plurality of diversion ports 26 formed on the pipe wall of the diversion control pipe 24 into the diversion control pipe 24, and flows out from the header opening 8b on the outlet side to the outflow pipe 5.

Here, since the shunt port 26 provided in the shunt control pipe 24 is formed so that the hole diameter becomes smaller toward the header opening 8b on the outlet side, the refrigerant flowing through each flow path of the refrigerant flow path 11 group. The amount can be equalized.

That is, in this heat exchanger, the pressure loss of the refrigerant is several times larger in the header flow path 14 on the outlet side than in the header flow path 10 on the inlet side due to the smaller diameter of the refrigerant flow path 11. On the other hand, the shunt flow of the refrigerant is greatly affected by the distribution of pressure loss. Therefore, in this heat exchanger, even if the flow dividing control pipe 24 is provided in the header flow path 10 on the inlet side, which is a conventional wisdom, the pressure loss of the header flow path 14 on the outlet side is several times higher, so that the refrigerant flow path 11 is used. Since the flowing refrigerant depends on the pressure loss of the header flow path 14 on the outlet side, the flow cannot be divided as designed.

However, in the heat exchanger of the present embodiment, the shunt control pipe 24 is provided in the header flow path 14 on the outlet side where the pressure loss is high, which has a large effect on the shunt flow and is several times higher than the header flow path on the outlet side. It is possible to control so that the pressure drop distribution in the axial direction in 14 becomes uniform. Therefore, it is possible to make the flow rate of the refrigerant flowing through each flow path of the refrigerant flow path 11 group uniform.

Further, in this heat exchanger, the refrigerant flowing from the inflow pipe 4 passes through the header opening 8a on the inlet side, is introduced into the refrigerant flow path 11 inside each plate fin, and flows into the header opening 8b on the outlet side. It flows out from the outflow pipe 5.

At this time, due to the pressure loss generated in each flow path, the inflow pipe is closer to the refrigerant flow path 11 of the plate fin farther from the inflow pipe 4 (the refrigerant flow path of the plate fin closer to the right in FIG. 29). Refrigerant flow is easier in the refrigerant flow path 11 of the plate fin closer to 4 (the refrigerant flow path of the plate fin closer to the left in FIG. 29). In other words, the flow rate of the refrigerant may be biased.

However, the flow dividing control pipe 24 is inserted inside the header opening 8b on the outlet side, and the opening area of the flow dividing port 26a on the most outlet side is measured on the outlet side of the flow dividing control pipe 24 (in FIG. 29, The diversion port 26a provided on the left side) has a smaller diameter than the counter-outlet side of the diversion control pipe 24 (the part closer to the right side in FIG. 29) to increase the pressure loss of the refrigerant passing through the diversion port. It is possible to equalize the amount of the refrigerant in the first fluid flow path 11 inside each plate fin and improve the heat exchange efficiency without causing the uneven flow rate of the refrigerant as in the above.

As a result, this heat exchanger can be made into a heat exchanger having improved heat exchange efficiency in the refrigerant flow path 11 group portion and further high heat efficiency.

Furthermore, since the above-mentioned uniform refrigerant shunt configuration is a simple configuration in which the shunt port 26 is simply drilled in the shunt control pipe 24, it can be provided at low cost.

Further, since the flow dividing control pipe 24 is integrally provided with the reinforcing plate 16a, it can be inserted into the header flow path 14 simply by mounting the reinforcing plate 16a, and the flow dividing control pipe 24 can be inserted by welding or the like. It is possible to prevent poor quality such as plate fin bonding failure due to brazing of the plate fin brazed portion and accompanying refrigerant leakage, which may be a concern in the case of retrofitting, and it is possible to obtain a high quality and high efficiency heat exchanger.

Further, the reinforcing plate 16a is made of a material in which the potential difference between the flow dividing control pipe 24 and the outflow pipe 5 is smaller than the potential difference between the flow dividing control pipe 24 and the outflow pipe 5 when the flow dividing control pipe 24 and the outflow pipe 5 are directly connected. Since the plate 16a is made of stainless steel, the flow dividing control pipe 24 is made of aluminum, and the outflow pipe 5 is made of copper, it is possible to prevent the occurrence of contact corrosion of dissimilar metals that occurs when the flow dividing control pipe 24 and the outflow pipe 5 are directly connected to each other. This can greatly improve reliability in long-term use. In particular, a heat exchanger for an air conditioner in which the inflow / outflow pipe is made of a copper pipe and the shunt control pipe 24 is made of aluminum is expected to have a remarkable effect and is effective.

Although the shunt control pipe 24 is provided on the reinforcing plate 16a in this embodiment, it may be provided on the end plate 3a side, and in the case of a type in which the reinforcing plate 16a is not used, the end plate 3a faces each other. A shunt control pipe 24 and an outflow pipe 5 may be provided on the surface.

Further, in this embodiment, it is assumed that the refrigerant flow paths 11 groups make a U-turn, but the same applies to the linear refrigerant flow path 11 groups described in the second embodiment. can do.

(Embodiment 4)
The fourth embodiment is a refrigeration system configured by using one of the heat exchangers of each of the above-described embodiments.

In this 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, and FIG. 31 is a schematic cross-sectional view showing an indoor unit of the air conditioner.

In FIGS. 30 and 31, the air conditioner is composed of an outdoor unit 51 and an indoor unit 52 connected to the outdoor unit 51. The outdoor unit 51 includes a compressor 53 for compressing the refrigerant, a four-way valve 54 for switching the refrigerant circuit during cooling and heating operation, an outdoor heat exchanger 55 for exchanging heat between the refrigerant and the outside air, and a decompressor 56 for reducing the refrigerant. Has been done. Further, the indoor unit 52 is provided with an indoor heat exchanger 57 for exchanging heat between the refrigerant and the indoor air, and an indoor blower 58. Then, the compressor 53, the four-way valve 54, the indoor heat exchanger 57, the decompressor 56, and the outdoor heat exchanger 55 are connected by a refrigerant circuit to form a heat pump type refrigeration cycle.

In the refrigerant circuit according to the present embodiment, tetrafluoropropene or trifluoropropene is used as a base component, and difluoromethane or pentafluoroethane or tetrafluoroethane is preferably used so that the global warming potential is 5 or more and 750 or less. A refrigerant in which two components or three components are mixed so as to be 350 or less, more preferably 150 or less, respectively, is used.

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

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

In the air conditioner configured as described above, the heat exchanger is located in the header region portion by using the heat exchanger shown in each of the above embodiments for the outdoor heat exchanger 55 or the indoor heat exchanger 57. Since it is compact and highly efficient without expansion and deformation, it can be a high-performance refrigeration system with high energy saving.

In the present invention, the end plates of the core laminate are combined back to back, and the header region portion thereof is sandwiched between the reinforcing plates, so that even in a heat exchanger used for a household or commercial air conditioner, the header region portion can be used. It is possible to provide a long and highly efficient heat exchanger without expansion and deformation, and a high-performance refrigeration system with high energy saving using the heat exchanger. Therefore, it can be widely used in heat exchangers and various refrigeration equipment used for home and commercial air conditioners, and its industrial value is great.

1 Heat exchanger 2 Core laminate 2a Plate fins 3, 3a, 3b End plates 4 Inflow pipes 5 Outflow pipes 6 First plate fins 6a First plate-shaped members 6b Second plate-shaped members 7 Second plate fins 8, 8a, 8b Header opening 9 Connecting means (bolts and nuts)
10 Header flow path 10a Outer circumference flow path 10b Communication flow path 10c Multi-branch flow path 11 Refrigerant flow path (first fluid flow path)
11a Outward route side flow path 11b Return route side flow path 12 Cut-up protrusions 12a, 12aa Protrusions (first cut-up protrusion)
12b protrusion (second cut-up protrusion)
13 Through hole (boss hole for positioning)
13a Hole outer circumference (Positioning boss hole outer circumference)
14 Header flow path 15 Slit 16a, 16b Reinforcing plate 17 Divergence collision wall 18 Non-flow path part 19a, 19b Plane end 20 Depressed plane 20a Narrow plane 20b Wide plane 21 Fin plane 22 (22a, 22b) Slit)
24 Divergence control pipe 25 Refrigerant flow gap 26, 26a, 26b Divergence port 27 Hollow frame 51 Outdoor unit 52 Indoor unit 53 Compressor 54 Four-way valve 55 Outdoor heat exchanger 56 Decompressor 57 Indoor heat exchanger 58 Indoor blower 200 Plate Fin laminate

Claims (5)

A plate fin laminate having a flow path through which a first fluid such as a fluid flows is provided, and a second fluid is allowed to flow between the plate fin laminates of the plate fin laminate, and between the first fluid and the second fluid. The plate fin laminate is a core laminate configured by laminating a plurality of plate fins having a flow path through which a first fluid flows between a first end plate and a second end plate. The plate fins of the core laminated body are composed of a combination of bodies, and have a flow path region having a plurality of first fluid flow paths and each first of the flow path regions so that the first fluid flows in parallel. A header region having a header flow path communicating with the fluid flow path is provided, the first fluid flow path is formed by a concave groove provided in the plate fin, and the core laminate is a first fluid. The entrance opening and the exit opening, which are the entrances and exits of the fluid, are opened in the portion corresponding to the header region of the first end plate, and the second end plates are laminated back to back and combined to form a core laminate combined back to back. A reinforcing plate is arranged at least outside the portion corresponding to the header region of the first end plate, and the reinforcing plates are connected to each other by a connecting means to sandwich the header region of the core laminate combined back to back to correspond to the header region. The reinforcing plate arranged on the outside of the first end plate integrates a flow dividing control tube that rushes into the header flow path on the surface facing the header region corresponding portion while suppressing the expansion and deformation of the portion outward. In addition to being provided, the inflow pipe and outflow pipe of the first fluid are integrated into the inlet and outlet openings on the opposite outer surface, and the reinforcing plate has a diversion control pipe and the potential difference between the inflow pipe and the outflow pipe is the same as the diversion control pipe and the inflow pipe. Outflow pipe A heat exchanger made of a material that is smaller than the potential difference between the two when the supply and discharge pipes are directly connected . The first fluid flow path formed in the plate fin is U-turned in a substantially U shape, and the inlet side header flow path and the outlet side header flow path of the header flow path communicating with the first fluid flow path are on one end side of the plate fin. A claim that sandwiches the header area of the core laminated body in which the reinforcing plates of the header area corresponding portion provided together with the inlet side header flow path and the outlet side header flow path are connected by a connecting means and combined back to back. The heat exchanger according to 1. The header flow path provided in the header region of the core laminate includes an outer peripheral flow path around the header opening provided in the plate fin and a connecting flow path connecting the outer peripheral flow path and the plurality of first fluid flow paths. The heat exchanger according to any one of claims 1 or 2 , wherein the connecting means for connecting the reinforcing plate for preventing the expansion and deformation of the header region of the core laminate is formed through both side portions of the connecting flow path. The method according to any one of claims 1 to 3 , wherein the plate fins, the end plate, and the reinforcing plate are provided with through holes at appropriate positions on the peripheral edge of each header region corresponding portion, and the reinforcing plates are connected to each other through the through holes by fastening means. Heat exchanger. A refrigeration system in which the heat exchanger constituting the refrigeration cycle is the heat exchanger according to any one of claims 1 to 4 .

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