JP6906130B2 - Heat exchanger and refrigeration system using it - Google Patents

Description

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

Generally, in a refrigerating system such as an air conditioner or a refrigerator, the refrigerant compressed by the compressor is circulated to a heat exchanger such as a condenser or an evaporator to exchange heat with the indoor air for cooling or heating. The heat exchange efficiency of the vessel 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 formed by laminating plate fins having a flow path is known.

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

31 and 32 show the plate fin laminated heat exchanger described in Patent Document 1, and the heat exchanger 100 is a plate fin laminated body formed by laminating plate fins 102 having a flow path 101 through which a refrigerant flows. The end plates 104 are laminated on both sides of the 103, and the inlet side header flow path 105 and the outlet side header flow path 106 are formed on the left and right end portions of the flow path 101.

Utility Model Registration No. 3192719

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

However, in the plate fin laminated heat exchanger having the above configuration, since the header regions such as the inlet side header flow path 105 and the outlet side header flow path 106 having a low heat exchange contribution are located at both ends of the plate fin 102, the fin tube. Although the heat exchange efficiency was improved as compared with the type heat exchanger, there was room for improvement.

Further, the plate fin laminated heat exchanger is short because the flow path 101 from the inlet side header flow path 105 to the outlet side header flow path 106 is linear, and the flow path size is large unless the plate fins are lengthened. Since it cannot be lengthened, there is also a problem that the heat exchanger becomes large.

Among the above problems, the latter problem of increasing the size of the heat exchanger can be solved because the length of the flow path can be secured while suppressing the increase in size of the plate fins by making the flow path 101 U-turn.

However, even in this case, although the area of the U-turn side end of the plate fin 102 is reduced by the amount that the header flow path is eliminated, a fin surface having a constant width and a low heat exchange contribution remains.

In particular, since the fin plate 102 is provided with boss holes for positioning pins at both ends in order to facilitate the laminated positioning at the time of manufacture, at least at the end of the plate fin 102 in which the flow path 101 makes a U-turn. The area of the boss hole was required, and although the width was not as wide as the end on the side where the inlet side header flow path 105 and the outlet side header flow path 106 were provided, a fin surface having a low heat exchange contribution was left. ..

Since the downstream portion of the boss hole at the end on the U-turn side becomes a dead water area, the fin surface of the downstream portion of the boss hole has almost no heat exchange function, and its heat exchange contribution is extremely low. It was a thing.

The present invention has been made in view of these points, and an object of the present invention is to provide a compact and high-performance heat exchanger and a refrigeration system using the same by improving the heat exchange contribution of the end portion of the plate fin. It was done.

In order to achieve the above object, the present invention has a configuration in which a plurality of protrusions are provided at the header region formed at the end of the plate fin or the end on the U-turn side of the flow path.

As a result, the heat exchange contribution of the end portion of the plate fin can be increased, and the heat exchange efficiency of the entire rate fin can be increased. Moreover, it is possible to improve the heat exchange efficiency by reducing the diameter of the flow path by promoting the reduction of the diameter of the flow path cross-sectional area of the first fluid flow path. Therefore, it is possible to obtain a heat exchanger that is small in size and has high heat exchange efficiency. Then, by using such a heat exchanger, it is possible to provide a high-performance refrigeration system that is compact and has high energy saving.

According to the above configuration, the present invention can increase the heat exchange contribution of the end portion of the plate fin to increase the heat exchange efficiency of the entire plate fin, and is a compact and highly heat exchange efficient heat exchanger and energy saving using the same. It is possible to provide a highly efficient and 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. An exploded perspective view showing the plate fin laminated heat exchanger separated into upper and lower parts. An exploded perspective view of the plate fin laminated heat exchanger Side view showing the plate fin laminated state of the plate fin laminated body in the plate fin laminated type heat exchanger AA cross-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 / outflow pipe and the header opening portion in the plate fin laminated heat exchanger according to the first embodiment of the present invention. The perspective view which shows by cutting the refrigerant flow path group part of the plate fin laminated body in the plate fin laminated type heat exchanger. 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. Plan view 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. A perspective view showing the appearance of the plate fin laminated heat exchanger according to the second embodiment of the present invention. Top view of the plate fins constituting the plate fin laminate of the plate fin laminate type heat exchanger Exploded view showing a part of the structure of the plate fins in the plate fin laminated heat exchanger The perspective view which shows by cutting the refrigerant flow path group part of the plate fin laminated body in the plate fin laminated type heat exchanger. A perspective view showing the appearance of the plate fin laminated heat exchanger according to the third embodiment of the present invention. A perspective view showing a state in which the diversion control tube is pulled out from the plate fin laminated heat exchanger. A perspective view showing a flow dividing control pipe insertion portion in the plate fin laminated body of the plate fin laminated heat exchanger. Perspective view of the diversion control tube in the plate fin laminated heat exchanger A cross-sectional view showing a divergence control tube portion of the plate fin laminated heat exchanger. 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, in which a second fluid is allowed to flow between each plate fin laminate of a plate fin laminate having a flow path through which the first fluid flows, and the first fluid and the above are described. A heat exchanger that exchanges heat with the second fluid.
The plate fins of the plate fin laminate have a flow path region having a plurality of first fluid flow paths through which the first fluid flows in parallel, and a header on the inlet side communicating with each first fluid flow path in the flow path region. A header region having a flow path and a header flow path on the outlet side is provided, and the first fluid flow path is formed by providing a concave groove in the plate fin.
Moreover, a plurality of protrusions are provided in the header flow path of the plate fin.

As a result, the heat exchange contribution of the end portion of the plate fin can be increased, and the heat exchange efficiency of the entire rate fin can be increased. Moreover, it is possible to improve the heat exchange efficiency by reducing the diameter of the flow path by promoting the reduction of the diameter of the flow path cross-sectional area of the heat exchange flow path. Therefore, it is possible to obtain a heat exchanger that is small in size and has high heat exchange efficiency. Then, by using such a heat exchanger, it is possible to provide a high-performance refrigeration system that is compact and has high energy saving.

The second invention is a heat exchanger, in which a second fluid is allowed to flow between each plate fin laminate of a plate fin laminate having a flow path through which the first fluid flows, and the first fluid and the above are described. A heat exchanger that exchanges heat with the second fluid.
The plate fins of the plate fin laminate have a flow path region having a plurality of first fluid flow paths through which the first fluid flows in parallel, and a header on the inlet side communicating with each first fluid flow path in the flow path region. A header region having a flow path and a header flow path on the outlet side is provided, and the first fluid flow path is formed by providing a concave groove in the plate fin.
Further, the first fluid flow path formed in the plate fin is U-turned in a substantially U-shape so that the header flow path on the inlet side and the header flow path on the outlet side communicating with the first fluid flow path are formed at one end of the plate fin. The structure is such that the heat exchange flow path is gathered on the side and a protrusion is provided on the other end side of the plate fin where the heat exchange flow path makes a U-turn.

As a result, the flow path size of the first fluid flow path is lengthened without lengthening the plate fins to promote miniaturization of the heat exchanger and improvement of heat exchange efficiency, and a header flow path having a low heat exchange contribution. The heat exchange efficiency is improved by limiting the portion to only one end side of the plate fin, and the heat exchange function on the other end side of the plate fin through which the first fluid flow path makes a U-turn is improved by protrusions to improve the heat exchange function of the entire plate fin. The heat exchange efficiency can be increased. On top of that, it is possible to promote the reduction of the diameter of the flow path cross-sectional area of the first fluid flow path and improve the heat exchange efficiency by reducing the diameter of the flow path. Therefore, it is possible to obtain a heat exchanger that is small in size and has high heat exchange efficiency. Then, by using such a heat exchanger, it is possible to provide a high-performance refrigeration system that is compact and has high energy saving.

In the third invention, in the first or second invention, the protrusion is cut and formed, and the cut and raised edge of the raised protrusion faces the flow of the second fluid.

As a result, the front edge effect can be generated at the cut-up edge portion, and the heat exchange efficiency can be improved accordingly.

In the fourth aspect of the invention, in the first to third inventions, the protrusion is provided on the downstream side of the header flow path or the positioning through hole, and the flow on the downstream side of the header flow path or the positioning through hole is contracted. be.

As a result, the dead water region having a low heat exchange contribution to be generated on the downstream side of the header flow path or the positioning through hole can be minimized, and the heat exchange efficiency can be further improved accordingly.

In the fifth aspect of the invention, in the first to fourth inventions, a plurality of auxiliary cut-up protrusions are further provided on the downstream side of the protrusions so as to meander with respect to the flow of the second fluid.

As a result, the heat exchange efficiency can be further improved by adding the heat exchange function by the auxiliary cut-up protrusion in addition to the heat exchange function by the protrusion near the downstream side of the header flow path or the positioning through hole.

A sixth aspect of the present invention is the first to fifth aspect of the invention, wherein the protrusion abuts the top thereof on the surface of an adjacent plate fin.

As a result, the plate fins can be connected and fixed in a laminated state by the protrusions, and the heat exchange efficiency can be improved and the rigidity of the plate fin laminated body can be increased.

The seventh invention is a freezing system, in which the heat exchanger constituting the freezing 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 small and highly efficient.

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 shows a state in which the plate fin laminated heat exchanger is separated into upper and lower parts. An exploded perspective view, FIG. 3 is an exploded perspective view of a plate fin laminated heat exchanger, FIG. 4 is a side view showing a plate fin laminated state of a plate fin laminated body, and FIGS. 5 to 8 are plate fin laminated heat exchangers. It is a cross-sectional view.

As shown in FIGS. 1 to 8, the heat exchanger 1 of the present embodiment has an inflow pipe (inlet header) 4 into which a refrigerant as a first fluid flows, and a plurality of rectangular plate-shaped plate fins 2a. It has a plate fin laminate 2 formed by laminating, and an outflow pipe (outlet header) 5 for discharging the refrigerant flowing through the flow path in the plate fin 2a.

Further, end plates 3a and 3b having substantially the same shape as the plate fins 2a in a plan view are provided on both sides (upper side and lower side in FIG. 1) of the plate fin laminated body 2 in the stacking direction. The end plates 3a and 3b are made of a rigid plate material, and are formed by metal processing a metal material such as aluminum, an aluminum alloy, or stainless steel by grinding.

The end plates 3a and 3b and the plurality of plate fins 2a are brazed and joined in a laminated state, but are joined using another heat-resistant fixing method, for example, a chemical joining member. It may have been done.

Further, in the present embodiment, both end plates 3a and 3b on both sides of the plate fin laminate 2 are connected and fixed at both ends in the longitudinal direction by connecting means 9 such as bolts and nuts or caulking pin shafts. That is, the end plates 3a and 3b on both sides of the plate fin laminate have a shape in which the plate fin laminate 2 is mechanically connected and fixed so as to sandwich the plate fin laminate 2.

Further, in the present embodiment, the reinforcing plates 16a and 16b are further arranged at the header region corresponding portion of one end portion in the longitudinal direction (the left end portion in FIG. 1) of the end plates 3a and 3b, and the reinforcing plates 16a and 16b are used as described above. The plate fin laminate 2 including the end plates 3a and 3b is mechanically sandwiched by connecting and fixing by fastening the connecting means 9.

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 (hereinafter, the inflow pipe 4 and the outflow pipe 5 are collectively referred to as an inflow / outflow pipe). Are collectively arranged on one end side of the end plate 3a on one side (upper side in FIG. 1) 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 through a plurality of flow paths inside each plate fin 2a of the plate fin laminate 2, makes a U-turn, and flows out. It is discharged from the pipe 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 plate fin 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 plate fin laminate 2 that is the main body of the heat exchanger 1 and the plate fins 2a that constitute the plate fin laminate 2 will be described with reference to FIGS. 9 to 19.

9 to 12 are perspective views showing a part of the plate fin laminated body cut out, and FIGS. 13 to 19 are views showing the configuration of the plate fins.

As shown in FIG. 9, the plate fin 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. 15, 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 structure so as to face each other. The first plate-shaped member 6a and the second plate-shaped member 6b are made of a thin metal plate such as aluminum, an aluminum alloy, or stainless steel.

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

Since the first plate fins 6 and the second plate fins 7 of the plate fins 2a have the same configuration except that the positions of the refrigerant flow paths 11 described later are displaced, the first plate fins 6 are shown in FIGS. 13 to 15 and the like. A case number will be given for explanation.

As shown in FIG. 13, the plate fins 2a (6, 7) have a header region H formed at one end in the longitudinal direction (left side in FIG. 13), 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 first plate fins 2a (6, 7) (near the right end in FIG. 13) and is connected to the header opening 8b on the outlet side. More specifically, the refrigerant flow path 11 group includes an outward 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, and is substantially U. 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, as shown in an enlarged manner in FIG. 14, a header flow path 10 in which the refrigerant from the header opening 8a flows into the refrigerant flow path 11 group is formed around the header opening 8a on the inflow side. 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 peripheral flow path 10b. 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 5, 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.

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. A slit 15 is formed between the region and the region where the road portion 11b is formed for the purpose of reducing (insulating) the heat conduction between the refrigerants in the plate fins 2a (6, 7).

The connecting flow path 10b of the header flow path 10 is provided so as to be biased toward a portion of the outward path side flow path portion 11a opposite to the return path side flow path portion 11b. That is, as shown in FIG. 17, 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 diversion 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 connecting flow path 10b is non-flow. It is a road portion 18. Therefore, the refrigerant from the connecting flow path 10b collides with the diversion collision wall 17 and splits (splits vertically in FIG. 17), 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 diversion 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 are formed on the first plate fin 6 in this example in the flow path region P as shown in FIG. 16 (a). A plurality of protrusions 12 (first protrusions: 12a, 12aa, second protrusions: 12b) are formed at predetermined intervals in the longitudinal direction.

16 (a) and 16 (a) are the first plate fins 6, (b) are the second plate fins 7, and (c) are the states when both fin plates 2a (6, 7) are overlapped.

As shown in FIG. 16, 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. 16A) and the side edges of the slit 15. As shown in FIG. 10, they are formed on the flat end portions 19b, and as shown in FIG. 10, they come into contact with the flat end portions 19a of the long edge portions of the second plate fins 7 adjacent to each other in the stacking direction (the first protrusion 12aa is the slit 15). The distance between the layers is defined as a predetermined length by contacting the flat end portions 19b of both side edges (but not shown). 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 (refrigerant flow path 11 side) from the edge.

As is clear from FIG. 16A, 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. 16B, and is laminated with the second plate fin 7 in the same manner as the first protrusion 12a. The distance 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 surface portion 20 of the first plate fin 6, as shown in FIG. (Hereinafter, the 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. 19, 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 the center line thereof deviates from the center line of the protrusion 22b on the downstream side.

Similar to the raised protrusions 12 (first cut-up protrusions: 12a, 12aa, second cut-up protrusions: 12b), the cut-up protrusions 22 (22a, 22b) are plate fins whose top surfaces are adjacent to each other. 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. 11, 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. It is formed. The positioning boss holes 13 are also formed on 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. The connecting means 9 (see FIG. 3) such as bolts connecting the reinforcing plates 16a and 16b of the plate fin laminate 2 and the end plates 3a and 3b also serves 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. 11, 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 a header flow path 10 (10a, 10b, 10c) of both the inlet and the outlet formed in the header region H shown in FIG. ), And the other header flow path 10 facing the stacking direction and the outer peripheral portion 13a of the positioning boss hole are brazed and fixed, and the end portions of the plate fins 2a (6, 7) are integrally connected.

As the refrigerant flow path 11 in the present disclosure, for example, the cross-sectional shape orthogonal to the flow direction of the refrigerant is described as having a circular shape, but the refrigerant flow path 11 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 the plate fin 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 10 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 plate fin laminates 2.

Here, since the heat exchanger of this embodiment is provided with the raised protrusions 22 (22, a22b) at the U-turn side end of the refrigerant flow path of the plate fin 2a, the plate fin 2a without the refrigerant flow path 11 It is possible to increase the heat exchange contribution of the U-turn side end of the. 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. Since a plurality of cut-up protrusions 22 (22, a22b) 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-out protrusion 22 closest to 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, the heat exchange contribution generated on the downstream side of the positioning screw hole 13 The dead water region with a low temperature can be minimized, and the heat exchange efficiency can be further improved accordingly.

In addition, since each of the cut-up protrusions 22 (22, a22b) has a shape in which the cut-up end edge Y faces the flow of the second fluid, the front edge effect can be generated at the cut-up end edge portion. Therefore, the heat exchange efficiency can be further improved.

Since the plurality of cutting protrusions 22 (22, a22b) 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 (22, a22b) 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 plate fin laminated body 2 It is also possible to increase the rigidity of.

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 in a substantially U-shaped cross section so as to open in the flow direction of the second fluid. This may be in the form of facing each other as a pair of substantially L-shaped cuts, and may be in a shape that constricts the flow on the downstream side of the positioning boss hole 13.

Further, in the heat exchanger of this embodiment, a plurality of cut-up protrusions 12 (12a, 12aa, 12b) are also provided in the flow path region P of the plate fin laminate 2, and the heat exchange efficiency in the flow path region P can be improved. Can be improved. In particular, in the cut-up protrusions 12 (12a, 12aa, 12b), the cut-up edge Y faces the flow direction of the second fluid flowing between the stacks of the plate fins 2a as in the cut-up protrusions 22 (22, a22b). Since it is formed so as to be formed, the interval between the plate fin stacks is made constant, and the cut-up protrusion 12 (12a) is formed.
, 12aa, 12b), the dead water area that tends to occur on the downstream side is minimized, and the front edge effect is generated at the cut-up edge Y portion. 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 plate fin laminate 2.

The cut-up protrusions 12 (12a, 12aa, 12b) provided on the plate fin 2a are linearly arranged with respect to the second fluid, but they are arranged in a staggered manner or form more leeward side than the leeward side. It is more effective if it is used, and the optimum configuration may be selected according to the specifications and configuration 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 plate fin laminate 2 is opened, the direction in which the air flows, that is, the refrigerant. It is not necessary to steal meat from the recessed plane 20 between the refrigerant flow paths in the direction intersecting the flow paths. 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 end edge of the long side portion of the plate fin 2a has a narrow plane 20a and a wide plane 20b due to the alternating misalignment arrangement of the refrigerant flow paths 11 (see FIG. 10), and is cut to the wide plane 20b side. Since the raised protrusion 12a is formed 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. 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 plate fin 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 gap 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 plate fin laminated body 2 improves the strength of the long side edge portion of the plate fin laminated body 2 which tends to be weak in strength, which is effective. Is the target. In particular, the first cut-up protrusion 12a provided on both side edge portions of the slit 15 of the plate fin laminate 2 improves the strength of the slit edge portion which is divided by the provision of the slit 15 and the strength is lowered, so that heat exchange is performed. It is effective because it can prevent deformation near the slit while improving efficiency.

The first cut-up protrusion 12a provided on both side edge portions of the slit 15 may be provided so as to straddle the slit 15, but in this case, the outward path side flow path portion 11a and the return path side flow of the refrigerant flow path 11 group. There is a concern that heat conduction will occur between the road 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, the first cut-up protrusions 12a and 12aa provided on the long side portion of the plate fin laminate 2 and both side portions of the slit 15 are provided at positions separated from the edge of the plate fin long side of the plate fin laminate 2. Therefore, when dew condensation water is generated on the plate fins 2a of the plate fin laminate 2 and the dew condensation water flows and is discharged along the edge of the plate fins 2a, the first cut-up protrusions 12a and 12aa It is possible to prevent the flow from being blocked by the heat exchanger and accumulating in the cut-and-push projection 12a portion to cause various troubles, and it is possible to obtain a highly reliable heat exchanger.

As described above, this heat exchanger can increase the heat exchange contribution of the end portion of the plate fins to improve the heat exchange efficiency of the entire plate fins, but also has the following effects. be.

That is, in this type of heat exchanger, a strong pressure of the refrigerant is applied to the header region H of the plate fin laminate 2, and the header region H portion or the like where the header flow path 10 is located tends to expand and deform.

However, in the heat exchanger shown in the present embodiment, the header region-corresponding portion of the plate fin laminate 2, that is, the header region-corresponding portion of the end plates 3a and 3b covering both side portions of the plate fin laminate 2, is connected to the connecting means 9. Since the end plates 3a and 3b are connected to each other, it is possible to prevent the portion corresponding to the header region of the end plates 3a and 3b from expanding and deforming outward.

That is, in FIG. 7, the high pressure of the refrigerant applied to the header flow path 10 tries to deform the upper end plate 3a upward and the lower end plate 3b downward, but the upper end. The upward expansion and deformation force applied to the plate 3a also receives a downward pressure from the refrigerant existing in the inflow pipe 4 connected to the upper end plate 3a, so that this force cancels out the upward expansion and deformation force. Therefore, it is possible to prevent outward expansion and deformation of the portion corresponding to the header region of the upper end plate 3a. The downward expansion and deformation force applied to the lower end plate 3b can be suppressed by connecting the end plate 3b to the upper end plate 3a as described above. As a result, the expansion deformation as a whole can be alleviated.

In particular, in the present embodiment, the reinforcing plates 16a and 16b are provided on the outer surface of the header region corresponding portion of the end plates 3a and 3b, and the reinforcing plates 16a and 16b are connected to each other by the connecting means 9 to remove the end plates 3a and 3b. Since the shape is pressed against the plate fin laminate 2 from the side, the strength of the header region-corresponding portion of the end plates 3a and 3b is strengthened by the rigidity of the reinforcing plates 16a and 16b themselves, and the expansion and deformation of the header region-corresponding portion is strongly strengthened. It comes to suppress.

Further, by providing the reinforcing plates 16a and 16b, even if the U-shaped flow path configuration illustrated in the present embodiment is provided, expansion and 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 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 plate fins. Since it is gathered on one end side of the above, 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.

Therefore, even in the case of a heat exchanger having a large amount of refrigerant or an environment-friendly refrigerant having a high compression ratio as described above, expansion and deformation of the header region portion of the plate fin laminate 2 can be prevented. 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, while preventing expansion and deformation of the plate fin laminate 2 in the portion corresponding to the header region, the diameter of the flow path cross-sectional area of the refrigerant flow path 11 is reduced to improve heat exchange efficiency and promote miniaturization. be able to.

Since the reinforcing plates 16a and 16b need only be provided in the portion corresponding to the header region, the volume increase increased by providing the reinforcing plates 16a and 16b can be minimized, and the heat exchanger can be made smaller. It is possible to prevent expansion and deformation and improve heat exchange efficiency without impairing the formation.

Further, in the header region H of the plate fin laminated body 2, since the flow path area of the header flow path 10 is the largest, the refrigerant pressure of 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.

Further, the connecting means 9 such as the bolt can be used as a guide pin (jig) when laminating the plate fins 2a, the end plates 3a and 3b, and the reinforcing plates 16a and 16b, thereby improving the laminating accuracy. , Productivity can also be improved.

The strong pressure of the refrigerant applied to the header region H of the plate fin laminate 2 may deform the cross section of the header flow path 10 in the header region H, but the outer wall (flat surface) of the header flow path 10 may be deformed. Since it is in contact with the other header flow path 10 adjacent in the stacking direction in the stacking direction and is in a rowing state, the pressure generated by the refrigerant in each header flow path is canceled out and is not deformed and is reliable. Can be high.

Further, 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 and folded back, the plate fin 2a is made large (the length dimension is made long). ), And the length of the refrigerant flow path can be lengthened.

As a result, the heat exchange efficiency between the refrigerant and the air can be increased, and the refrigerant can be reliably supercooled to improve the efficiency of the refrigerating system. Moreover, the heat exchanger can be miniaturized.

Further, by forming the refrigerant flow path 11 group into a substantially U shape and gathering the header flow path 10 on the inlet side and the header flow path 14 on the outlet side at one end side, the refrigerant pressure in the header region portion is doubled. Even if it is added, as described above, the header flow path corresponding portion connects the end plates 3a and 3b to each other, and the reinforcing plates 16a and 16b are also added to prevent deformation. It can be reliably prevented.

Further, in the present embodiment, the refrigerant that exchanges heat with the air flowing between the plate fin laminates of the plate fin laminate 2 is a communication flow path 10b, a multi-branch flow path 10c, and a refrigerant from the header flow path 10 on the inlet side. Although it flows to the flow path 11 group, since the diversion collision wall 17 is provided on the downstream side of the communication flow path 10b, the refrigerant collides with the diversion collision wall 17 and is split up and down as shown in FIG. The flow is divided from the branch flow path 10c to each 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. 17, 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 side away from the slit 15, becomes longer, and a biased flow occurs due to the difference in the flow path length.

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 to make a U-turn of the refrigerant flow path 11 group. 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 to cancel each other out. 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 making the refrigerant flow path 11 groups U-turn and uniformizing the flow.

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 It is possible to prevent heat transfer from the outbound route side flow path portion to the return path side flow path portion to increase the amount of heat exchange of the refrigerant, and further improve the heat exchange efficiency.

(Embodiment 2)
As shown in FIGS. 20 to 23, 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.

FIG. 20 is a perspective view showing the appearance of the heat exchanger according to the second embodiment, and FIG. 21 is a plan view of the plate fins constituting the plate fin laminate of the plate fin laminated heat exchanger. A plan view, FIG. 22 is an exploded view showing a part of the configuration of the plate fins in the heat exchanger in an enlarged manner, and FIG. 23 is a perspective view showing the refrigerant flow path group portion of the plate fin laminate in the heat exchanger cut out. It is a figure.

In FIGS. 20 to 23, 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. 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 plate fin 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. It has become.

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.

The cut-up protrusions 22 (22, a22b) provided at the U-turn side end of the plate fin 2a of the first embodiment may be appropriately provided in the header regions on both the inlet and outlet sides in this example. The same idea as the raised protrusion 22 (22, a22b) provided at the end on the U-turn side, 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. 24 to 28, the header flow path on the outlet side. A refrigerant diversion 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. 24 is a perspective view showing the appearance of the heat exchanger according to the third embodiment, FIG. 25 is a perspective view showing a state in which the flow dividing control tube is pulled out in the heat exchanger, and FIG. 26 is a laminated plate fin of the heat exchanger. 27 is a perspective view showing the flow dividing control pipe insertion portion in the heat exchanger, FIG. 27 is a perspective view of the flow dividing control pipe in the heat exchanger, and FIG. 28 is a cross-sectional view showing the flow dividing control pipe portion of the heat exchanger.

In FIGS. 24 to 28, the flow dividing 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. 28. As described above, it extends to the end plate 3b on the side where the header opening is not provided, and is in a state of being blocked by the end plate 3b. The flow dividing 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 diversion ports 26 are formed at substantially equal intervals in the direction.

The plurality of diversion ports 26 are formed so that the pore diameter becomes smaller toward the direction in which the refrigerant flows, that is, toward the header opening 8b on the outlet side.

Further, the flow dividing control pipe 24 is attached to the reinforcing plate 16a as shown in FIGS. 25 and 27, 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 plate fin laminate 2. It is supposed to be done.

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

The outflow pipe 5 is also connected and fixed to the reinforcing plate 16a. Further, the flow dividing 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. 28. 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 diversion port 26 provided in the diversion 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 diversion 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, it cannot be divided as designed.

However, in the heat exchanger of the present embodiment, the diversion 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 diversion 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, the flow rate of the refrigerant flowing through each flow path of the refrigerant flow path 11 group can be made 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. 28). Refrigerant flows more easily in the refrigerant flow path 11 of the plate fin closer to 4 (the auction flow path of the plate fin closer to the left in FIG. 28). In other words, the flow rate of the refrigerant may be biased.

However, the flow divergence control pipe 24 is inserted inside the header opening 8b on the outlet side, and the opening area of the divergence port 26a on the most outlet side is determined on the outlet side of the flow divergence control pipe 24 (in FIG. 28, more 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. 28) 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 unbalanced 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 flow diversion configuration of the refrigerant by the diversion control pipe 24 is a simple configuration in which the diversion port 26 is simply drilled in the diversion control pipe 24, it can be provided at low cost.

Further, since the flow dividing control pipe 24 is provided integrally 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 connected to the flow dividing control pipe 24 and the reinforcing plate 16a, and the potential difference between the outflow pipe 5 when used as an evaporator directly connects the flow dividing control pipe 24 and the outflow pipe 5. Since it is made of a material that is smaller than the potential difference between the two, it is possible to prevent the occurrence of galvanic corrosion that occurs when the diversion control pipe 24 and the outflow pipe 5 are directly connected. The reliability in long-term use can be greatly improved. In particular, a heat exchanger for an air conditioner in which the inflow / outflow pipe is made of a copper pipe and the flow dividing control pipe 24 is made of stainless steel or the like is expected to have a remarkable effect and is effective.

Although the flow dividing 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 the end plate 3a. A flow dividing 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.

Other detailed configurations and effects are the same as those of the heat exchanger described in the first embodiment, and the description thereof will be omitted.

(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.

INDUSTRIAL APPLICABILITY According to the present invention, the heat exchange contribution of the end portion of the plate fin can be increased to increase the heat exchange efficiency of the entire plate fin, and a compact heat exchanger having high heat exchange efficiency and high energy saving using the heat exchanger. A performance refrigeration system can be provided. Therefore, it can be widely used in heat exchangers and various refrigerating devices used for home and commercial air conditioners, and has great industrial value.

1 Heat exchanger 2 Plate fin laminate 2a Plate fins 3, 3a, 3b End plate 4 Inflow pipe (inlet header)
5 Outflow pipe (exit header)
6 1st plate fin 6a 1st plate-shaped member 6b 2nd plate-shaped member 7 2nd plate fin 8, 8a, 8b Header opening 9 Connecting means (bolts / nuts)
10 Header flow path 10a Outer peripheral 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 Peripheral part of hole (outer circumference of boss hole for positioning)
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) Protrusion (cutting) Raised protrusion)
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

Claims (6)

A heat exchanger in which a second fluid is allowed to flow between each plate fin laminate of a plate fin laminate having a flow path through which the first fluid flows, and heat is exchanged between the first fluid and the second fluid. The plate fins of the plate fin laminate have a flow path region having a plurality of first fluid flow paths through which the first fluid flows in parallel, and a header on the inlet side communicating with each first fluid flow path in the flow path region. A header region having a flow path and a header flow path on the outlet side is provided, and the first fluid flow path is formed by providing a concave groove in the plate fin, and the header flow path of the plate fin is formed. A heat exchanger in which a plurality of protrusions are provided , and the protrusions are provided on the downstream side of the header flow path or the positioning through hole to constrict the flow on the downstream side of the header flow path or the positioning through hole. A heat exchanger in which a second fluid is allowed to flow between each plate fin laminate of a plate fin laminate having a flow path through which the first fluid flows, and heat is exchanged between the first fluid and the second fluid. The plate fins of the plate fin laminate have a flow path region having a plurality of first fluid flow paths through which the first fluid flows in parallel, and a header on the inlet side communicating with each first fluid flow path in the flow path region. A header region having a flow path and a header flow path on the outlet side is provided, and the first fluid flow path is formed by providing a concave groove in the plate fin, and the first fluid formed in the plate fin. The inlet-side header flow path and the outlet-side header flow path that communicate with the first fluid flow path by making a U-turn in a substantially U-shape are gathered on one end side of the plate fin, and the first fluid flow flow is described. A protrusion is provided on the other end side of the plate fin where the path makes a U-turn, and the protrusion is provided on the downstream side of the header flow path or the positioning through hole to constrict the flow on the downstream side of the header flow path or the positioning through hole. heat exchangers. The heat exchanger according to claim 1 or 2, wherein the protrusions are cut and formed, and the cut and raised edges of the raised protrusions face the flow of the second fluid. The heat exchanger according to any one of claims 1 to 3 , further provided with a plurality of auxiliary cut-up protrusions on the downstream side of the protrusions so as to meander with respect to the flow of the second fluid. The heat exchanger according to any one of claims 1 to 4 , wherein the protrusion is in contact with the surface of an adjacent plate fin. A refrigeration system in which the heat exchanger constituting the refrigeration cycle is the heat exchanger according to any one of claims 1 to 5.

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