WO2018074344A1

WO2018074344A1 - Heat exchanger and refrigeration device using same

Info

Publication number: WO2018074344A1
Application number: PCT/JP2017/037131
Authority: WO
Inventors: 健二名越; 憲昭山本; 崇裕大城; 拓也奥村; 一彦丸本
Original assignee: パナソニックＩｐマネジメント株式会社
Priority date: 2016-10-21
Filing date: 2017-10-13
Publication date: 2018-04-26
Also published as: MY195919A; CN109416229B; JP2018066532A; JP6767621B2; CN109416229A

Abstract

In the present invention, a plurality of protrusions (12) are provided to a flowpath region (P) that connects the inlet side header flowpath (10) and the outlet side header flowpath (14) of the plate fins (2a), and the protrusions (12) come into contact with the surface of the adjoining plate fins, forming a raised shape and opening the direction of flow of a second fluid that flows between the layers of the plate fins (2a). As a result of this configuration, by means of the protrusions (12) it is possible to eliminate variation in the gaps between the layers of plate fins (2a), and it is possible to generate a leading edge effect at the raised edge part of the protrusions (12), thereby making it possible to improve heat exchange efficiency. Furthermore, the protrusions (12) eliminate the need to take thickness from the indented flat surfaces between flowpaths, making it possible to make the indented flat surfaces narrower, and to reduce the size of the heat exchanger by a corresponding amount.

Description

Heat exchanger and refrigeration apparatus using the same

The present invention relates to a heat exchanger and a refrigeration apparatus using the same, and more particularly to a plate fin stacked type heat exchanger configured by stacking plate-like plate fins through which a refrigerant flows and a refrigeration apparatus using the same.

In general, a refrigeration apparatus typified by an air conditioner or a refrigerator circulates a refrigerant compressed by a compressor through a heat exchanger typified by a condenser or an evaporator to exchange heat with a second fluid for cooling or heating. . However, the performance and energy saving performance as a refrigeration apparatus are greatly influenced by the heat exchange efficiency of the heat exchanger. Therefore, high efficiency is strongly demanded for heat exchangers.

Under such circumstances, the heat exchanger of the refrigeration apparatus generally uses a finned tube type heat exchanger configured by penetrating the heat transfer tube through the fin group, and the heat transfer tube is reduced in diameter. Therefore, improvement of heat exchange efficiency and downsizing are being promoted.

However, since there is a limit to reducing the diameter of such a heat transfer tube, improvement in heat exchange efficiency and downsizing are approaching the limits.

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

This plate fin laminated heat exchanger performs heat exchange between a first fluid that is a refrigerant that flows through a flow path formed in the plate fin and a second fluid that flows between the laminated plate fins. It is widely used in vehicle air conditioners (see, for example, Patent Document 1).

31 and 32 show a plate fin stacked heat exchanger described in Patent Document 1, and this heat exchanger 100 is configured by stacking plate fins 102 having flow paths 101 through which a refrigerant flows to form a plate fin stacked body 103. To do. Then, end plates 104 are stacked on both sides of the plate fin laminate 103, and an inlet-side header channel 105 and an outlet-side header channel 106 are formed on both left and right ends of the channel 101 to constitute the heat exchanger 100. ing.

Utility Model Registration No. 3192719

In the plate fin laminated heat exchanger described in Patent Document 1, the channel 101 is formed by press-molding a concave groove in the plate fin 102, and therefore the cross-sectional area of the channel 101 is used for the fin tube heat exchanger. It can be made smaller than the heat transfer tube, and the heat exchange efficiency can be increased.

However, the plate fin stacked heat exchanger as described in Patent Document 1 is formed at both ends of the plate fin 102 in order to form the inlet-side header channel 105 and the outlet-side header channel 106 at the left and right ends. The stacking interval between the plate fins 102 is maintained by abutting the annular protrusions 107 together. For this reason, there is a tendency that the stacking interval of the plate fins 102 between the inlet-side header channel 105 and the outlet-side header channel 106 varies.

Therefore, by providing a plurality of protrusions in the flow path 101 region connecting the inlet-side header flow path 105 and the outlet-side header flow path 106 of the plate fin 102 and bringing the protrusions into contact with the adjacent plate fins 102, Variations in the stacking interval between 102 can be prevented, and variations in the plate fin stacking interval through which the second fluid flows can be eliminated.

However, if a plurality of protrusions are provided in the flow path 101 region connecting the inlet-side header flow path 105 and the outlet-side header flow path 106, a dead water area is formed on the downstream side of the protrusion, and heat exchange performance is reduced. There was a problem that it would end up.

Further, the protrusions are formed on the recess plane between the concave grooves to be the flow path 101, but the meat is stealed from the recess plane portion around the protrusion at the time of the press molding. For this reason, a recessed plane having a certain dimension or more is required around the protrusion where the protrusion is provided, and the gap between the flow paths 101 must be widened, and the plate fin 102 becomes larger by that amount. In addition, the heat exchanger is also increased in size.

The present invention provides a small, high-performance heat exchanger and a refrigeration apparatus using the same, eliminating variations in the plate fin stacking interval without enlarging the plate fins or reducing the heat exchange performance.

The present invention provides a plurality of protrusions in the flow path region connecting the inlet-side header flow path and the outlet-side header flow path of the plate fin, the protrusions abut against the surface of the adjacent plate fin, and between the plate fin stacks. The cut and raised shape is such that the flow direction of the flowing second fluid is open.

Thereby, the variation in the interval between the plate fin stacks where the second fluid flows by the protrusion can be eliminated, and the protrusion has a cut-and-raised shape in which the flow direction of the second fluid is opened. The dead water area formed on the side can be cut and raised to produce the leading edge effect at the edge portion, and the heat exchange efficiency can be improved while suppressing the flow path resistance. In addition, since the protrusion is cut and raised so that the flow direction of the second fluid flowing through the plate fin laminated tube is opened, the first fluid flows in the first direction in the direction in which the fluid to be exchanged flows, that is, the direction intersecting the first fluid flow path. There is no need to steal meat from the recessed plane between the fluid flow paths. Therefore, it is not necessary to widen the hollow plane between the first fluid flow paths, and the plate fin, in other words, the heat exchanger can be reduced in size. By using such a heat exchanger, it is possible to provide a high-performance refrigeration apparatus that is compact and energy-saving.

FIG. 1 is a perspective view showing the appearance of the heat exchanger in the first embodiment of the present invention. FIG. 2 is an exploded perspective view showing the heat exchanger according to the first embodiment of the present invention in a state where the heat exchanger is vertically separated. FIG. 3 is an exploded perspective view of the heat exchanger according to the first embodiment of the present invention. FIG. 4 is a side view showing a plate fin laminated state of the plate fin laminated body of the heat exchanger according to the first embodiment of the present invention. FIG. 5 is a sectional view taken along line 5-5 of FIG. 6 is a cross-sectional view taken along the line 6-6 in FIG. 7 is a cross-sectional view taken along the line 7-7 in FIG. FIG. 8 is a perspective view of the heat exchanger according to the first embodiment of the present invention, with the connection portion of the inflow pipe and the outflow pipe and the header opening portion cut away. FIG. 9 is a perspective view showing the first fluid flow path group portion of the plate fin laminate of the heat exchanger according to the first embodiment of the present invention. FIG. 10 is a perspective view showing the first fluid flow path group portion of the heat exchanger in the first embodiment of the present invention cut away. FIG. 11 is a perspective view showing the positioning boss hole portion of the plate fin laminate of the heat exchanger according to the first embodiment of the present invention. FIG. 12 is a perspective view showing the header opening portion of the plate fin laminate of the heat exchanger according to the first embodiment of the present invention cut away. FIG. 13 is a plan view of plate fins constituting the plate fin laminate of the heat exchanger according to the first embodiment of the present invention. FIG. 14 is an enlarged plan view showing the header region of the plate fin of the heat exchanger according to the first embodiment of the present invention. FIG. 15 is an exploded perspective view showing a part of the configuration of the plate fin of the heat exchanger according to the first embodiment of the present invention. FIG. 16A is a plan view of the first plate fin of the heat exchanger according to the first embodiment of the present invention. FIG. 16B is a plan view of the second plate fin of the heat exchanger according to the first embodiment of the present invention. FIG. 16C is a plan view for explaining a state in which the first plate fin and the second plate fin of the heat exchanger according to the first embodiment of the present invention are overlapped. FIG. 17 is a diagram for explaining the refrigerant flow operation of the plate fins of the heat exchanger according to the first embodiment of the present invention. FIG. 18 is an enlarged perspective view showing a protrusion provided in the flow path region of the plate fin of the heat exchanger according to the first embodiment of the present invention. FIG. 19 is an enlarged perspective view showing a protrusion provided on the U-turn side end of the first fluid flow path of the plate fin of the heat exchanger according to the first embodiment of the present invention. FIG. 20 is an exploded perspective view showing a plate fin stacked heat exchanger, which is a heat exchanger according to the second embodiment of the present invention, in a state where it is vertically separated. FIG. 21 is a plan view of plate fins constituting the plate fin laminate of the heat exchanger according to the second embodiment of the present invention. FIG. 22 is an exploded perspective view showing a part of the configuration of the plate fins of the heat exchanger according to the second embodiment of the present invention. FIG. 23 is a perspective view showing the first fluid flow path group portion of the plate fin laminate of the heat exchanger according to the second embodiment of the present invention. FIG. 24 is a perspective view showing an appearance of a plate fin stacked heat exchanger that is a heat exchanger according to the third embodiment of the present invention. FIG. 25 is an exploded perspective view showing a state in which the shunt control pipe is extracted from the heat exchanger according to the third embodiment of the present invention. FIG. 26 is a perspective view showing a branch flow control tube insertion portion in the plate fin laminate of the heat exchanger according to the third embodiment of the present invention. FIG. 27 is a perspective view of a shunt control tube of a heat exchanger according to the third embodiment of the present invention. FIG. 28 is a cross-sectional view showing a branch flow control pipe portion of the heat exchanger in the third embodiment of the present invention. FIG. 29 is a refrigeration cycle diagram of an air conditioner using any of the heat exchangers according to the first to third embodiments of the present invention. FIG. 30 is a schematic cross-sectional view of an air conditioner using any one of the heat exchangers according to the first to third embodiments of the present invention. FIG. 31 is a cross-sectional view of a conventional plate fin laminated heat exchanger. FIG. 32 is a plan view of a plate fin of a conventional plate fin laminated heat exchanger.

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

Note that the heat exchanger of the present disclosure is not limited to the configuration of the plate fin stacked heat exchanger described in the following embodiment, and heat equivalent to the technical idea described in the following embodiment. Includes the configuration of the exchanger.

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

(First embodiment)
Hereinafter, a plate fin laminated heat exchanger which is a heat exchanger according to a first embodiment of the present invention will be described with reference to the drawings.

FIG. 1 is a perspective view showing the appearance of a plate fin laminated heat exchanger which is a heat exchanger in the present embodiment. FIG. 2 is an exploded perspective view showing the heat exchanger according to this embodiment in a state where the heat exchanger is vertically separated. FIG. 3 is an exploded perspective view of the heat exchanger in the present embodiment. FIG. 4 is a side view showing a plate fin lamination state of the heat exchanger in the present embodiment. 5 to 8 are sectional views of the heat exchanger according to the present embodiment.

As shown in FIGS. 1 to 8, the heat exchanger 1 that is a heat exchanger in the present embodiment includes an inlet pipe 4 that is an inlet-side header channel into which a refrigerant that is a first fluid flows, and a rectangular plate. Plate fin laminate 2 configured by laminating a plurality of plate fins 2a, and an outflow which is an outlet-side header channel that discharges the refrigerant that is the first fluid that has flowed through the channel in plate fin 2a Tube 5.

Further,

end plates

3a and 3b having substantially the same shape in plan view as the plate fin 2a are provided on both sides (upper and lower sides in FIG. 1) of the plate fin laminate 2 in the stacking direction. The

end plates

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

The

end plates

3a and 3b and the plurality of plate fins 2a are integrally joined by brazing in a stacked state. However, the

end plates

3a and 3b and the plurality of plate fins 2a are joined using another heat-resistant fixing method, for example, a chemical joining member. It may be.

In the present embodiment, the

end plates

3a and 3b on both sides of the plate fin laminate 2 are fixed at both ends in the longitudinal direction by connecting means 9 such as bolts / nuts or caulking pin shafts. That is, the

end plates

3a and 3b on both sides of the plate fin laminate are in a form in which the plate fin laminate 2 is mechanically connected and fixed in a form sandwiching the plate fin laminate 2.

Further, in the present embodiment, the reinforcing

plates

16a and 16b are further arranged in the header region corresponding part of the longitudinal direction one end portion (the left end portion in FIG. 1) of the

end plates

3a and 3b, and the reinforcing

plates

16a and 16b are connected. The plate fin laminated body 2 including the

end plates

3a and 3b is mechanically clamped by being connected and fixed by fastening the means 9.

The reinforcing

plates

16a and 16b are also formed of a rigid plate material, for example, a metal material such as stainless steel or aluminum alloy, like the

end plates

3a and 3b. However, the reinforcing

plates

16a and 16b are more than the

end plates

3a and 3b. It is preferable to use a highly rigid material or a thick plate.

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

In the heat exchanger 1 configured as described above, the refrigerant flowing in from the inflow pipe 4 is parallel to the longitudinal direction in a plurality of flow path groups formed in the respective plate fins 2a constituting the plate fin laminate 2. Then, the U-turn is turned and is discharged from the return outlet pipe 5. On the other hand, the air that is the second fluid passes through the gap formed between the stacks of the plate fins 2 a constituting the plate fin stack 2. Thereby, 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 forms the main body of the heat exchanger 1 and the plate fins 2a constituting the same will be described with reference to FIGS.

FIG. 9 is a perspective view showing the first fluid flow path group portion of the plate fin laminate of the heat exchanger in the present embodiment by cutting. FIG. 10 is a perspective view showing the first fluid flow path group portion of the heat exchanger in the present embodiment by cutting. FIG. 11 is a perspective view showing the positioning boss hole portion of the plate fin laminate of the heat exchanger according to the present embodiment by cutting. FIG. 12 is a perspective view showing the header opening portion of the plate fin laminate of the heat exchanger in the present embodiment by cutting. FIG. 13 is a plan view of plate fins constituting the plate fin laminate of the heat exchanger in the present embodiment. FIG. 14 is an enlarged plan view showing the header region of the plate fin of the heat exchanger in the present embodiment. FIG. 15 is an exploded perspective view showing an enlarged part of the configuration of the plate fins of the heat exchanger in the present embodiment. FIG. 16A is a plan view of the first plate fin of the heat exchanger in the present embodiment. FIG. 16B is a plan view of the second plate fin of the heat exchanger in the present embodiment. FIG. 16C is a plan view for explaining a state in which the first plate fin and the second plate fin of the heat exchanger in the present embodiment are overlapped. FIG. 17 is a diagram for explaining the refrigerant flow operation of the plate fins of the heat exchanger in the present embodiment. FIG. 18 is an enlarged perspective view showing a protrusion provided in the flow path region of the plate fin of the heat exchanger in the present embodiment. FIG. 19 is an enlarged perspective view showing a protrusion provided at an end portion on the U-turn side of the first fluid flow path of the plate fin of the heat exchanger in the present embodiment.

As shown in FIG. 9, the plate fin 2a of the heat exchanger in the present embodiment is configured by laminating first plate fins 6 and second plate fins 7 having different flow path configurations.

As shown in FIG. 15, the first plate fin 6 of the plate fin 2a includes a first plate member 6a in which a first fluid flow path configuration, which will be described in detail later, is press-molded, and a second plate shape having the same configuration as the first plate member 6a. It is constituted by brazing and joining the member 6b. Although not shown, the second plate fin 7 is also configured by brazing and joining two plate-like members in the same manner as the first plate fin 6. In addition, the 1st plate-shaped member 6a and the 2nd plate-shaped member 6b consist of metal thin plates, such as aluminum, aluminum alloy, and stainless steel.

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

The first plate fin 6 and the second plate fin 7 of the plate fin 2a have the same configuration except that the position of a first fluid flow path 11 described later is shifted, so the first plate fin 6 in FIGS. Only a figure number is given and explained.

As shown in FIG. 13 showing the first plate fin 6, the plate fin 2 a (first plate fin 6, second plate fin 7) has a header region H at one end in the longitudinal direction (left side in FIG. 13). The other region is a flow channel region P. Then, both the header opening 8a on the inlet 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 (see FIG. 8).

Further, a plurality of first fluid flow paths 11 that are first fluid flow paths through which a refrigerant that is the first fluid from the header opening 8a flows are formed in parallel in the flow path region P, and this first fluid flow path 11 group. Is folded at the other end (near the right end in FIG. 13) of the plate fin 2a (first plate fin 6, second plate fin 7) and connected to the header opening 8b on the outlet side. More specifically, the first fluid flow channel 11 group is composed of an outward flow channel portion 11a connected to the inlet header opening 8a and a return flow channel portion 11b connected to the outlet header opening 8b. It is shaped like a letter. Then, the refrigerant from the inlet-side header opening 8a makes a U-turn from the forward path side flow path portion 11a to the return path side flow path portion 11b and flows to the outlet side header opening 8b.

In addition, an inlet-side header flow path 10 through which the refrigerant from the header opening 8a flows to the first fluid flow path 11 group is formed around the inlet-side header opening 8a as shown in an enlarged view in FIG. Yes. The inlet-side header flow path 10 has an outer peripheral flow path 10a formed so as to swell from the outer periphery of the header opening 8a, and one communication flow extending toward the first fluid flow path 11 group side of the outer peripheral flow path 10a. The channel 10b and a multi-branch channel 10c connecting the communication channel 10b to each channel of the first fluid channel 11 group.

In addition, the outer peripheral flow path 10a, the communication flow path 10b, and the multi-branch flow path 10c in the inlet side header flow path 10 are formed wider than the first fluid flow paths 11 arranged in parallel in the flow path region P. The vertical cross-sectional shape orthogonal to the flow direction has a rectangular shape.

The opening shape of the header opening 8a on the inlet side has a larger diameter than the opening shape of the header opening 8b on the outlet side. This is a case where this heat exchanger is used as a condenser. In this case, the volume of the refrigerant after heat exchange is reduced.

Further, the number of the return-side flow passage portions 11b connected to the outlet-side header opening 8b is set to be smaller than the number of the forward-passage flow passage portions 11a into which the refrigerant flows from the inlet-side header opening 8a. This is the same reason that the diameters of the

header openings

8a and 8b are different, because the volume of the refrigerant after heat exchange is reduced.

In the present embodiment, the number of the forward path side flow path portions 11a is seven and the number of the return path side flow path portions 11b is two, but the present invention is not limited to this.

In addition, when this heat exchanger is used as an evaporator, the entrance and exit of the refrigerant is the reverse of the configuration described so far.

Further, in this plate fin 2a (first plate fin 6, second plate fin 7), an area in which the forward flow path portion 11a into which refrigerant flows from the header opening 8a on the inlet side is formed and the header on the outlet side are formed. Reduces heat conduction between refrigerants in the plate fins 2a (first plate fins 6 and second plate fins 7) between the region where the return-side flow path portion 11b flowing to the opening 8b is formed (heat insulation). For this purpose, a slit 15 is formed.

The connecting flow path 10b of the inlet-side header flow path 10 is provided so as to be biased toward a portion closer to the opposite side of the return path side flow path section 11b of the forward path side flow path section 11a. That is, as shown in FIG. 17, the width from the center line O of the connecting flow path 10b connected to the forward flow path section 11a through the multi-branch flow path 10c to the flow path 11aa at the end on the return path flow path section 11b side. V is configured to be larger than the width W from the center line O to the flow path 11ab at the end opposite to the return flow path section 11b. A shunting collision wall 17 is formed at the end of the communication flow path 10b on the header opening 8a side, that is, the opening connected to the forward flow path section 11a, and the forward flow path on the extension line of the communication flow path 10b. The portion is a non-flow channel portion 18. Therefore, the refrigerant from the communication flow path 10b collides with the flow dividing collision wall 17 and is divided (in the vertical direction in FIG. 17), and flows through the multi-flow path 10c on the downstream side of the communication flow path 10b in the non-flow path portion 18. It flows to each of the upper and lower flow path groups of the separated forward flow path section 11a.

An outlet-side header channel 14 is also formed in the outlet-side header opening 8b, and this outlet-side header channel 14 is provided in the inlet-side header opening 8a only without the shunting collision wall 17. It is basically formed in the same shape as the inlet-side header flow path 10. In this embodiment, since the number of the return-side flow path portions 11b of the first fluid flow path 11 group is as small as two, the communication flow path 10b is provided on a substantially center line of the return-side flow path portion 11b group. .

In the plate fin 2a (first plate fin 6 and second plate fin 7) configured as described above, in this example, the first plate fin 6 is provided with its flow path region P ( In FIG. 13, a plurality of protrusions 12 (first protrusions 12a, 12aa, second protrusions 12b) are formed at predetermined intervals in the longitudinal direction.

FIG. 16A is a plan view of the first plate fin 6. FIG. 16B is a plan view of the second plate fin 7. FIG. 6C is a plan view showing a state in which the first plate fin 6 and the second plate fin 7 are overlapped.

As shown in FIGS. 16A to 16C, the first protrusions 12a and 12aa are formed on the planar end 19a of the plate fin long side edge (the long side edges on the left and right sides in FIGS. 16A and 16C) and the side edges of the slit 15. Formed on the planar end 19b of each part. Then, as shown in FIG. 10, the first protrusion 12a abuts against the planar end 19a of the long side edge of the second plate fin 7 that is adjacent to and opposite to the first plate fin 6 in the stacking direction. The protrusion 12aa abuts on the planar end 19b on both side edges of the slit 15, and defines the interlaminar distance between the first plate fin 6 and the second plate fin 7 to a predetermined length. The first protrusions 12a are formed so as to be located on the inner side, for example, 1 mm or more inner side (first fluid flow path 11 side) from the end edge of each long side edge.

As shown in FIG. 16A, the second protrusions 12b are formed at predetermined intervals between the flow paths of the first fluid flow path 11 group, and in this example, the recessed flat surface portion 20 that becomes the non-flow path portion 18. The second protrusion 12b abuts on the concave flat surface portion 20 of the second plate fin 7 adjacent to the first plate fin 6 in the stacking direction shown in FIG. 16B, and the first plate fin 6 is similar to the first protrusion 12a. The interlaminar distance between the second plate fins 7 is defined as a predetermined length.

Further, as shown in FIG. 18, the protrusions 12 (first protrusions 12a, 12aa, and second protrusion 12b) cut up part of the

planar end portions

19a, 19b and the recessed planar portion 20 of the first plate fin 6. It is formed by. The raised edge Y of the protrusion 12 (first protrusion 12a, 12aa, second protrusion 12b) faces the flow direction indicated by the arrow of the second fluid flowing between the stacks of the plate fins 2a, and the raised edge Z is raised and raised. It is designed to follow the flow of two fluids. In the present embodiment, it is cut and raised in a substantially U-shaped cross section that opens in the flow direction of the second fluid.

And each protrusion 12 (1st protrusion 12a, 12aa, 2nd protrusion 12b) is brazing of each plate fin 2a (1st plate fin 6, 2nd plate fin 7) and end plate 3 (3a, 3b). Each top surface is fixed to the adjacent plate fins 2a (first plate fins 6, second plate fins 7) at the time of attachment, and each plate fin 2a (first plate fins 6, second plate fins 7) is integrated. It is linked to.

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

Further, as shown in FIG. 19, the plate fin 2a (6) has a plurality of protrusions 22 on the fin flat surface portion 21 at the end portion on the folded side of the flow path region P where the first fluid flow path 11 group makes a U-turn. (3rd protrusion 22a, 4th protrusion 22b) is formed. The protrusions 22 (third protrusion 22a and fourth protrusion 22b) are also formed by cutting and raising the fin plane portion 21. The cut and raised edges Y of the protrusions 22 (the third protrusion 22a and the fourth protrusion 22b) are opposed to the flow of the second fluid. The protrusions 22 (third protrusion 22 a and fourth protrusion 22 b) are provided downstream of the positioning boss hole 13, and the third protrusion 22 a immediately downstream of the positioning boss hole 13 is downstream of the positioning boss hole 13. It is formed by cutting and raising into a shape that contracts the flow of, for example, a shape that opens in the shape of a letter C toward the flow of the second fluid. The fourth protrusions 22b on the further downstream side than the third protrusions 22a are staggered so that the center line thereof is shifted from the center line of the fourth protrusion 22b on the downstream side.

Each projection 22 (third projection 22a, fourth projection 22b) is similar to the projection 12 (first projection 12a, 12aa, second projection 12b), and the top surface of each projection 22 is adjacent to the adjacent plate fin 2a (7). Abutting and fixing, the gap between adjacent plate fins 2a is defined to a predetermined length, and the plate fins 2a are connected to each other.

Further, as shown in FIG. 11, the plate fins 2a (first plate fins 6 and second plate fins 7) have positioning bosses which are positioning through holes at the end portions of the header region H and the flow channel region P. A hole 13 is formed. The positioning boss holes 13 are also formed in the

end plates

3a and 3b and the reinforcing

plates

16a and 16b stacked on both sides of the plate fins 2a (first plate fins 6 and second plate fins 7). The positioning boss hole 13 is provided with a positioning pin jig for laminating a plurality of plate fins 2a (first plate fins 6 and second plate fins 7), and highly precise lamination of the other plate fins 2a. In this embodiment, the connecting means 9 (see FIG. 3) such as bolts for connecting the reinforcing

plates

16a and 16b and the

end plates

3a and 3b of the plate fin laminate 2 also serves as a positioning pin jig. It has become.

Further, the outer peripheral portion of the positioning boss hole 13 provided at both ends of the plate fin 2a (the first plate fin 6 and the second plate fin 7) has a hole outer peripheral portion (hereinafter referred to as a positioning boss) bulging up and down. 13a) is formed. The positioning boss hole outer peripheral portion 13a forms a space different from the flow path through which the refrigerant flows. As shown in FIG. 11, the plate fins 2a (first plate fin 6, second plate fin adjacent to each other in the stacking direction are formed. 7), and a header region support portion that holds the stacking gap of the plate fins 2a.

And the positioning boss hole outer peripheral part 13a formed around the positioning boss hole 13 together with the inlet side header flow path 10 and the outlet side header flow path 14 formed in the header region H shown in FIG. The plate fins 2a (the first plate fin 6 and the second plate fin 7) are brazed and fixed to the inlet side header flow path 10, the outlet side header flow path 14 and the positioning boss hole outer peripheral portion 13a facing each other in the stacking direction. The end portions are connected together.

In addition, as the 1st fluid flow path 11 in this indication, although the cross-sectional shape orthogonal to the direction through which a refrigerant | coolant flows is demonstrated with the circular shape, rectangular shape etc. are included in addition to circular shape.

Further, in the present embodiment, the first fluid flow path 11 is described as having a shape protruding to both sides in the stacking direction, but is formed to protrude only on one side in the stacking direction. Also good. In the present disclosure, the circular shape includes a complex curve shape formed by a circle, an ellipse, and a closed curve.

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

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

The refrigerant flows from the inflow pipe 4 connected to one end portion side of the plate fin laminate 2 through the header opening 8a on the inlet side to each plate fin 2a inlet-side header flow path 10, that is, the outer peripheral flow around the header opening 8a. It flows to the first fluid channel 11 group through the channel 10a, the communication channel 10b, and the multi-branch channel 10c. The refrigerant that has flowed into the first fluid flow path 11 group of each plate fin 2a is folded back from the forward flow path section 11a to the return flow path section 11b, and the outlet side header flow path 14 and the outlet header opening 8b are formed. Through the outflow pipe 5 to the refrigerant circuit of the refrigeration apparatus.

And when flowing through the first fluid flow path 11, the refrigerant exchanges heat with the air passing between the plate fins 2 a of the plate fin laminate 2.

Here, in the heat exchanger of the present embodiment, a plurality of protrusions 12 (first protrusions 12a, 12aa, and second protrusions 12b) are provided in the flow path region P of the plate fin laminate 2, and the flow path region P The heat exchange efficiency in is improved. And the protrusion 12 (1st protrusion 12a, 12aa, 2nd protrusion 12b) is formed so that the cut-and-raised edge Y may oppose the flow direction of the 2nd fluid which flows between the lamination | stacking of the plate fin 2a. Therefore, the interval between the plate fins is made constant, and the dead water area that tends to occur on the downstream side of the projections 12 (first projections 12a, 12aa, second projections 12b) is minimized, and the cut edge Y portion Produces a leading edge effect. And since it cuts and raises so that it may oppose with the flow direction of a 2nd fluid, the flow resistance with respect to a 2nd fluid can also be made small. Therefore, the heat exchange efficiency can be greatly improved while suppressing an increase in flow resistance in the flow path region P of the plate fin laminate 2.

The protrusions 12 (the first protrusions 12a, 12aa, and the second protrusion 12b) provided on the plate fin 2a are linearly arranged with respect to the second fluid. It is more effective if many are formed, and an optimal configuration may be selected according to the specifications, configuration, and user's request of the heat exchanger.

Further, each of the protrusions 12 (first protrusions 12a, 12aa, and second protrusions 12b) is formed by cutting and raising the air flow direction that flows through the gap between the plate fin laminates 2 so that air flows. There is no need to steal meat from the recessed flat portion 20 between the first fluid flow paths in the direction, that is, the direction intersecting the first fluid flow paths. Therefore, the recessed flat surface portion 20 between the first fluid flow paths is narrower than that required for the meat stealing dimension, compared to the second protrusion 12b formed by cutting and raising, such as a cylindrical protrusion. Therefore, the width of the plate fin 2a, that is, the heat exchanger can be reduced in size.

In addition, the plate fin 2a has an edge of the long side portion thereof as a narrow plane 20a and a wide plane 20b due to the alternate positional displacement arrangement of the first fluid flow paths 11 (see FIG. 10), and on the wide plane 20b side. Since the first protrusion 12a is formed and its top surface is fixed to the narrow plane 20a of the adjacent plate fin 2a, the width on the narrow plane 20a side does not have to be increased to form the protrusion. . That is, the width of the long side portion of the plate fin on the narrow plane side is increased by providing a protrusion formed by cutting and raising on the wide plane side using the wide plane 20b. However, it is possible to keep the narrow plane as it is, and accordingly, downsizing of the heat exchanger can be promoted.

Further, the protrusions 12 (first protrusions 12a, 12aa, second protrusion 12b) are fixed to the adjacent plate fins 2a at the top surfaces of the plate fins 2a and the

end plates

3a, 3b when brazed. Therefore, the role which connects each plate fin 2a integrally is also played, and the rigidity of the plate fin laminated body 2 can be improved.

In particular, in the present embodiment, a portion on the extension line of the communication flow path 10b of the first fluid flow path 11 group is a non-flow path portion 18, and the projection 12 (first projection 12a, first Since the second projection 12b), that is, the second projection 12b is provided, the plate fin stacking gap in the first fluid flow path 11 group portion can be reliably maintained. As a result, it is possible to improve the heat exchange efficiency by making the air flow in the first fluid flow path 11 group portion stable without variation.

Further, the first protrusions 12a provided on the long side portion of the plate fin laminate 2 are effective because the strength of the long side edge portion of the plate fin laminate 2 that tends to be weak in strength is improved. . In particular, the first protrusions 12a provided on both side edge portions of the slit 15 of the plate fin laminate 2 improve the strength of the slit edge portion that is divided by the provision of the slit 15 and decreases its strength. While improving, it is possible to prevent deformation near the slit and is effective. The first protrusion 12aa may be provided at a location away from the slit 15.

The first protrusions 12a provided on both side edge portions of the slit 15 may be provided so as to straddle the slit 15. In this case, the forward-side flow path portion 11a and the return-side flow path of the first fluid flow path 11 group. There is a concern that heat conduction occurs between the portion 11b and the heat insulation effect due to the slit 15 is lowered. However, if the slits 15 are separately provided on both side edges as in the present embodiment, such a heat conduction concern is eliminated, which is effective.

Further, the

first protrusions

12 a and 12 aa provided on the long side portion of the plate fin laminate 2 and both side portions of the slit 15 are provided at positions away from the edge of the plate fin long side of the plate fin laminate 2. Therefore, when dew condensation water is generated in the plate fins 2a of the plate fin laminate 2 and the dew condensation water flows and discharges along the edge of the plate fins 2a, the flow is caused by the first protrusions 12a and 12aa. It is possible to prevent the condensed water from accumulating in the portion where the first protrusions 12a and 12aa are blocked, and to prevent various troubles caused by the condensed water from occurring, and to provide a highly reliable heat exchanger. be able to.

Further, in the heat exchanger of the present embodiment, as shown in FIGS. 13 and 19, the protrusion 22 (the third protrusion 22a, the fourth protrusion) is also formed on the U-turn side end portion of the first fluid channel 11 of the plate fin 2a. A protrusion 22b) is provided. Therefore, the heat exchange contribution degree of the U-turn side end part of the plate fin 2a without the first fluid flow path 11 can be increased. Therefore, the heat exchange efficiency can be increased over the entire 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 is provided with a positioning boss hole 13, and its downstream side is a dead water area, so that the heat exchange contribution is extremely low. Since the plurality of protrusions 22 (third protrusion 22a and fourth protrusion 22b) are provided on the downstream side of the positioning boss hole 13, the degree of contribution to heat exchange in the entire downstream side of the positioning boss hole 13 can be improved.

In particular, the third protrusion 22a closest to the downstream side of the positioning boss hole 13 has a shape that contracts the flow on the downstream side of the positioning boss hole 13, so that the degree of heat exchange contribution generated on the downstream side of the positioning screw hole 13 is reduced. The low dead water area can be minimized, and the heat exchange efficiency can be further improved accordingly.

In addition, each projection 22 (third projection 22a, fourth projection 22b) is cut and raised in the same manner as the projection 12 (first projection 12a, 12aa, second projection 12b) provided in the flow path region P. . Since the cut and raised edge Y faces the flow of the second fluid, the leading edge effect can be produced at the cut and raised edge portion, and the heat exchange efficiency can be further improved.

Since the plurality of protrusions 22 (third protrusion 22a and fourth protrusion 22b) provided on the downstream side of the positioning boss hole 13 have a zigzag arrangement meandering with respect to the flow of the second fluid, all of them are effective. It exhibits a heat exchange function and has a high degree of heat exchange contribution.

Further, the tops of the respective protrusions 22 (the third protrusion 22a and the fourth protrusion 22b) are fixed to the adjacent plate fins 2a, and the short sides of the plate fins 2a are connected and fixed in a stacked state. The rigidity of the fin laminate 2 can also be increased.

Note that the third protrusion 22a provided in the immediate vicinity of the downstream side of the positioning boss hole 13 is cut and raised in a cross-sectional shape that opens in the shape of a letter toward the flow direction of the second fluid in the present embodiment. is there. However, this may be provided with a pair of facing projections cut and raised to have an L-shaped cross section, and any shape can be used as long as the downstream flow of the positioning boss hole 13 is reduced. Such a form may be sufficient.

As described above, this heat exchanger can make the gap between the plate fin stacks constant, and can reduce the flow resistance by minimizing the dead water area by the protrusion formed by cutting and raising and the leading edge effect at the edge of the cutting and raising. The heat exchange efficiency can be improved while suppressing the above. Moreover, it is possible to suppress an increase in the overall size of the heat exchanger due to meat theft due to the protrusion formed by cutting and raising, but the following effects are also obtained.

That is, in this type of heat exchanger, a strong pressure of the refrigerant is applied to the header region H (see FIG. 13) of the plate fin laminate 2, and the header region H portion where the inlet-side header channel 10 is located tends to expand and deform. To do.

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 portions of the

end plates

3 a and 3 b covering both sides of the plate fin laminate 2 are connected to the connecting means 9. The

end plates

3a and 3b are connected to each other. Therefore, it is possible to prevent the portions corresponding to the header regions 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 inlet-side header channel 10 tends to be deformed upward in the upper end plate 3a and downward in the lower end plate 3b. However, the upward expansion deformation force applied to the upper end plate 3a is also subjected to the downward pressure from the refrigerant existing in the inflow pipe 4 connected to the upper end plate 3a. The shape is canceled out, and the outward deformation of the portion corresponding to the header region of the upper end plate 3a can be prevented. The downward expansion 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, expansion deformation as a whole can be mitigated.

In particular, in the present embodiment, reinforcing

plates

16a and 16b are provided on the outer surfaces of the

end plate

3a and 3b corresponding to the header region, and the reinforcing

plates

16a and 16b are connected to each other by the connecting means 9 (see FIG. 3). 3a and 3b are pressed against the plate fin laminate 2 from the outside. Therefore, the strength of the portion corresponding to the header region of the

end plates

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

plates

16a, 16b itself, and the expansion deformation of the portion corresponding to the header region is strongly suppressed.

Further, by providing the reinforcing

plates

16a and 16b, the expansion deformation of the portion corresponding to the header region can be reliably suppressed even if the U-shaped flow path configuration exemplified in the present embodiment is used. That is, the plate fin laminated body 2 according to the present embodiment causes the first fluid flow path 11 provided in the plate fin 2a to be U-turned into a U shape so that the inlet side header flow path 10 and the outlet side header flow path 14 are plate fins. Therefore, the pressure on the inlet side and the outlet side is doubled on this part. However, with the configuration shown in this embodiment, even when such double refrigerant pressure is applied, expansion deformation can be reliably prevented against this.

Therefore, as described above, even when the heat exchanger has a large amount of refrigerant or is an environment-friendly refrigerant having a high compression ratio, expansion deformation of the header region portion of the plate fin laminate 2 can be prevented. As a result, it is possible to use a refrigerant in a high pressure state, such as an environmentally compatible refrigerant having a high compression ratio, and a highly efficient heat exchanger can be obtained.

In addition, in this heat exchanger, by reducing the cross-sectional area of the concave groove for the first fluid channel formed in the plate fin 2a, each channel area of the first fluid channel 11 group (see FIG. 6) is reduced. The diameter can be increased, the heat exchange efficiency can be improved, and the miniaturization can be promoted.

That is, by reducing the diameter of the cross-sectional area of the first fluid flow path 11 while preventing expansion deformation at the portion corresponding to the header region of the plate fin laminate 2, the heat exchange efficiency is improved and the miniaturization is promoted. be able to.

Since the reinforcing

plates

16a and 16b need only be provided in the header region corresponding portion, the increase in volume caused by the provision of the reinforcing

plates

16a and 16b can be minimized, and the heat exchanger can be downsized. It is possible to realize expansion deformation prevention and improvement in heat exchange efficiency without loss.

Further, in the header region H (see FIG. 13) of the plate fin laminate 2, since the flow area of the inlet header flow path 10 is the largest, the refrigerant pressure in the inlet header flow path 10 portion is the highest. However, since the inlet-side header flow path 10 is brazed in contact with the adjacent inlet-side header flow path 10, the expansion deformation can be effectively prevented, and the expansion deformation of the portion corresponding to the header region is more reliably performed. Can be prevented.

The connecting means 9 such as a bolt can be used as a guide pin (jig) when laminating the plate fins 2a,

end plates

3a, 3b, and reinforcing

plates

16a, 16b. Productivity can also be improved.

In addition, although the strong pressure of the refrigerant | coolant added to the header area | region H of the plate fin laminated body 2 may deform | transform the cross section of the inlet side header flow path 10 in the header area | region H, the outer wall (flat surface) of the inlet side header flow path 10 Are in contact with other inlet-side header channels 10 adjacent in the stacking direction in the stacking direction and are brazed, so that the pressure generated by the refrigerant in each header channel is offset and deformed. And can be highly reliable.

Further, in the heat exchanger of the present embodiment, the first fluid flow path 11 group provided in the plate fin 2a is formed in a substantially U shape and folded so that the plate fin 2a is enlarged (length dimension). The first fluid flow path length can be increased without increasing the length).

This can increase the efficiency of heat exchange between the refrigerant and the air, and can reliably bring the refrigerant into a supercooled state, thereby improving the efficiency of the refrigeration apparatus. In addition, it is possible to reduce the size of the heat exchanger.

In addition, the first fluid flow path 11 group is formed in a U shape, and the inlet side header flow path 10 and the outlet side header flow path 14 are combined on one end side, whereby the refrigerant pressure in the header region H is increased. Even if double is added, the header flow path corresponding portion connects the

end plates

3a and 3b as described above, and the

reinforcement plates

16a and 16b are also added to prevent deformation, so that the corresponding portion of the header region H Can be reliably prevented.

In the present embodiment, the refrigerant that exchanges heat with the air flowing between the plate fin stacks of the plate fin stack 2 is connected from the inlet header flow path 10 to the communication flow path 10b, as shown in FIG. It flows to the channel 10c and the first fluid channel 11 group. Here, since the shunting collision wall 17 is provided on the downstream side of the connecting flow path 10b, the refrigerant collides with the shunting collision wall 17 and is split up and down as shown in FIG. The flow is diverted to the fluid flow path 11. Therefore, it is possible to prevent the refrigerant from being extremely biased in the flow path on the extension line of the communication flow path 10b.

Further, when the first fluid channel 11 group is formed in a U shape and folded as in the present embodiment, each channel of the first fluid channel 11 group is apparent from FIG. The length becomes longer toward the U-shaped outer periphery, in other words, the flow path side away from the slit 15, and a drift occurs due to the difference in the flow path length.

However, in this heat exchanger, as shown in FIG. 17, the communication flow path 10b from the inlet header flow path 10 is repeated from the center line (not shown) of the forward flow path portion 11a of the first fluid flow path 11 group. Since it is provided so as to be biased toward the road channel portion, it is possible to suppress the drift and flow the refrigerant substantially uniformly in each channel.

That is, in this heat exchanger, since the first fluid flow path 11 group is configured to make a U-turn, the inlet-side header flow path 10 to the outlet-side header flow path 14 of each flow path of the first fluid flow path 11 group. Even if the flow path resistance is changed due to the different flow path lengths, the communication flow path 10b from the inlet-side header flow path 10 is biased to the repetitive path side flow path side of the forward path side flow path section 11a. Yes. Therefore, the length of the branch flow path from the communication flow path 10b to each of the forward flow path portions 11a becomes longer as the return flow path portion 11b becomes closer to the first flow flow. The flow can be evenly divided into each flow path of the group of paths 11.

Therefore, the heat exchanger 1 with higher heat exchange efficiency can be obtained while promoting the downsizing by the synergistic effect by the U-turn of the first fluid flow path 11 group and the uniform flow.

Moreover, since the slit 15 is formed between the forward flow path portion 11a and the return flow path portion 11b of the first fluid flow path 11 group, the first fluid flow is formed. It is possible to further increase the heat exchange efficiency by preventing the heat transfer from the forward path side flow path portion 11a of the path 11 group to the return path side flow path portion 11b and increasing the heat exchange amount of the refrigerant.

(Second Embodiment)
As shown in FIGS. 20 to 23, the heat exchanger according to the second embodiment of the present invention has the shape of the first fluid flow path group and the installation position of the header opening according to the first embodiment. The parts having the same functions as those of the heat exchanger in the first embodiment are denoted by the same reference numerals, and the parts having different functions will be mainly described.

FIG. 20 is an exploded perspective view showing a plate fin laminated heat exchanger, which is a heat exchanger in the present embodiment, in a state of being vertically separated. FIG. 21 is a plan view of plate fins constituting the plate fin laminate of the heat exchanger in the present embodiment. FIG. 22 is an exploded perspective view showing a part of the configuration of the plate fins of the heat exchanger in the present embodiment in an enlarged manner. FIG. 23 is a perspective view showing the first fluid flow path group portion of the plate fin laminate of the heat exchanger in the present embodiment by cutting.

20 to 23, in the heat exchanger of the present embodiment, the first fluid flow path 11 group provided in the plate fin 2a is linear, and an inlet side header opening 8a is provided at one end thereof. And a header opening 8b on the outlet side is provided on the other end side. The inlet pipe 4 is connected to the header opening 8a on the inlet side, and the outlet pipe 5 is connected to the header opening 8b on the outlet side, and the refrigerant flows from the header opening 8a on one end side of the plate fin 2a to the other end side. The header opening 8b flows in a straight line.

The inlet-side header flow path 10 formed around the inlet-side header opening 8a includes an outer peripheral flow path 10a, a communication flow path 10b, and a multi-branch flow path 10c around the header opening 8a. The communication flow path 10b is formed so as to extend from the outer peripheral flow path 10a in the short side direction of the plate fin 2a, and is connected to the multi-branch flow path 10c. The outlet-side header flow path 14 is also connected to the inlet-side header flow path 10 The two are configured symmetrically.

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 shown in FIG. 3 showing the first embodiment, and the

end plates

3a and 3b are connected. The structure prevents the expansion deformation in the header regions H at both ends.

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 making the first fluid flow path 11 group U-shaped. It is the same and description is omitted.

The protrusions 22 (see FIG. 13) provided at the U-turn side end of the plate fin 2a of the first embodiment are appropriately provided in the header area H on the inlet side and the header area H on the outlet side in this example. That's fine. That is, the same idea as the protrusions 22 (22a, 22b) (see FIGS. 13 and 19) provided on the U-turn side end, for example, downstream of the inlet-side header channel 10 and the outlet-side header channel 14 that become dead water areas. It may be formed on the side.

(Third embodiment)
The heat exchanger according to the third embodiment of the present invention is suitable for use as an evaporator in which the refrigerant inlet and outlet of the heat exchanger are reversed. As shown in FIGS. The side header flow path 14 is provided with a refrigerant branch control pipe 24.

In the present 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 an appearance of a plate fin stacked heat exchanger that is a heat exchanger in the present embodiment. FIG. 25 is an exploded perspective view showing a state in which the shunt control pipe is extracted from the heat exchanger in the present embodiment. FIG. 26 is a perspective view showing a branch flow control tube insertion portion in the plate fin laminate of the heat exchanger in the present embodiment. FIG. 27 is a perspective view of a shunt control tube of the heat exchanger in the present embodiment. FIG. 28 is a cross-sectional view showing a branch flow control pipe portion of the heat exchanger in the present embodiment.

24 to 28, the flow dividing control pipe 24 is inserted into the outlet side header opening 8b serving as the refrigerant evaporating outlet, that is, the outlet side header flow path 14, and the tip thereof is as shown in FIG. Furthermore, 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 diversion control pipe 24 is constituted by a pipe having a diameter smaller than the inner diameter of the header opening 8b, and forms a refrigerant flow gap 25 between the header opening inner face and the longitudinal direction thereof, that is, the laminating direction of the plate fins 2a. A plurality of flow dividing openings 26 are formed at substantially equal intervals.

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

25 and 27, the diversion control pipe 24 is attached to the reinforcing plate 16a, and the reinforcing plate 16a is inserted into the header opening 8b by fastening to the end plates 3a on both sides of the plate fin laminate 2. It has become so.

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

In addition, the outflow pipe 5 is also connected and fixed to the reinforcing plate 16a. Further, the branch flow control pipe 24 may be configured such that its tip is closed and brought into 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 outlet side header flow path 14 via the first fluid flow path 11 group is indicated by an arrow in FIG. Then, the refrigerant flows from the refrigerant flow gap 25 into the flow dividing control pipe 24 through a plurality of flow dividing openings 26 formed in the wall of the flow dividing control pipe 24, and flows out from the header opening 8 b on the outlet side to the outflow pipe 5.

Here, the diversion port 26 provided in the diversion control pipe 24 is formed so that the hole diameter thereof becomes smaller toward the header opening 8b on the outlet side. The amount of flowing refrigerant can be equalized.

That is, in this type of heat exchanger, the first fluid flow path 11 is reduced in diameter, so that the refrigerant pressure loss is several times larger in the outlet header flow path 14 than in the inlet header flow path 10. . On the other hand, the flow of refrigerant is greatly affected by the distribution of pressure loss. Therefore, this type of heat exchanger has the first fluid flow path because the pressure loss of the outlet header flow path 14 is several times higher even if the branch flow control pipe 24 is provided in the conventional inlet header flow path 10. Since the refrigerant flowing through the outlet 11 depends on the pressure loss of the outlet-side header flow path 14, it cannot be divided as designed.

However, in the heat exchanger according to the present embodiment, the shunt control pipe 24 is provided in the outlet-side header flow path 14 having a high pressure loss, and thereby, in the outlet-side header flow path 14 that is several times higher, which greatly affects the flow split. The pressure loss distribution in the axial direction can be controlled to be uniform. Therefore, the refrigerant | coolant partial flow volume which flows through each flow path of the 1st fluid flow path 11 group can be equalize | homogenized.

Also, in this type of heat exchanger, the refrigerant flowing in from the inflow pipe 4 passes through the header openings 8a on the inlet side, is introduced into the first fluid flow paths 11 inside the respective plate fins 2a, and the header on the outlet side It flows into the opening 8b and flows out from the outflow pipe 5.

At this time, because of the pressure loss generated in each flow path, the first fluid flow path 11 of the plate fin 2a far from the inflow pipe 4 (the first fluid flow path of the plate fin 2a closer to the right in FIG. 28). ), The refrigerant flows more easily in the first fluid channel 11 of the plate fin 2a closer to the inflow pipe 4 (the first fluid channel of the plate fin 2a closer to the left in FIG. 28). In other words, the flow rate of the refrigerant may be uneven.

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 outlet 26a on the most outlet side is as shown in FIG. The flow outlet 26a provided in the portion close to the flow outlet is made smaller in diameter than the counter-outlet side of the flow dividing control pipe 24 (portion closer to the right side in FIG. 28), thereby increasing the pressure loss of the refrigerant passing through the flow outlet. As a result, the refrigerant flow does not drift, the amount of refrigerant in the first fluid flow path 11 inside each plate fin 2a can be equalized, and the heat exchange efficiency can be improved.

As a result, this heat exchanger improves the heat exchange efficiency in the first fluid flow path 11 group portion, and can be a heat exchanger with higher heat efficiency.

Furthermore, since the structure for equalizing the refrigerant flow by the flow dividing control pipe 24 is a simple structure in which the flow dividing port 26 is simply drilled in the flow dividing 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 outlet side header flow path 14 only by mounting the reinforcing plate 16a. For this reason, it is possible to prevent quality defects such as poor bonding of the plate fins 2a due to soldering of the brazed portion of the plate fins 2a, which is a concern when the diversion control pipe 24 is retrofitted by welding or the like, and accompanying refrigerant leakage, etc. And it can be set as a highly efficient heat exchanger.

Further, when the reinforcing plate 16a is connected to the flow dividing control pipe 24 and the reinforcing plate 16a, and the potential difference between the reinforcing pipe 16a and the outflow pipe 5 when used as an evaporator directly connects the flow dividing control pipe 24 and the outflow pipe 5 to each other. The material is smaller than the potential difference between the two. Therefore, it is possible to prevent the occurrence of different metal contact corrosion that occurs when the shunt control pipe 24 and the outflow pipe 5 are directly connected to each other, and the reliability in long-term use can be greatly improved. In particular, in the heat exchanger for an air conditioner, in which the inflow pipe 4 and the outflow pipe 5 are constituted by copper pipes, and the diversion control pipe 24 is often constituted by stainless steel, a remarkable effect can be expected and effective. .

In this embodiment, the flow dividing control pipe 24 is provided on the reinforcing plate 16a, but may be provided on the end plate 3a side. In the case of a type that does not use the reinforcing plate 16a, the shunt control pipe 24 faces the end plate 3a. A diversion control pipe 24 and an outflow pipe 5 may be provided on the surface.

In the present embodiment, the first fluid flow path 11 group is assumed to have a U-turn shape, but the linear first fluid flow path 11 group described in the second embodiment is used. However, it can be similarly applied.

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

(Fourth embodiment)
The fourth embodiment of the present invention is a refrigeration apparatus configured using one of the heat exchangers in each of the above-described embodiments.

In the present embodiment, an air conditioner will be described as an example of a refrigeration apparatus. FIG. 29 is a refrigeration cycle diagram of an air-conditioning apparatus that is a refrigeration apparatus in the present embodiment. FIG. 30 is a schematic cross-sectional view of an air conditioner that is a refrigeration apparatus in the present embodiment.

29 and 30, the air conditioner includes an outdoor unit 51 and an indoor unit 52 connected to the outdoor unit 51. The outdoor unit 51 includes a compressor 53 that compresses the refrigerant, a four-way valve 54 that switches a refrigerant circuit during the cooling and heating operation, an outdoor heat exchanger 55 that exchanges heat between the refrigerant and the outside air, and a decompressor 56 that decompresses the refrigerant. It is arranged. The indoor unit 52 is provided with an indoor heat exchanger 57 that exchanges heat between the refrigerant and the indoor air, and an indoor blower 58. The compressor 53, the four-way valve 54, the indoor heat exchanger 57, the decompressor 56, and the outdoor heat exchanger 55 are connected by a refrigerant circuit to form a heat pump refrigeration cycle.

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

The air conditioner shown in FIG. 29 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, the refrigerant 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 form a low-temperature and 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 becomes a low-temperature gas refrigerant. At this time, the room 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. Thereby, 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 room air, dissipates heat, and is cooled to become high-pressure liquid refrigerant. At this time, the room air is heated to heat the room. Thereafter, the refrigerant is sent to the decompressor 56, and is decompressed by the decompressor 56 to become a low-temperature and low-pressure two-phase refrigerant, sent to the outdoor heat exchanger 55, exchanges heat with the outside air, evaporates, and passes through the four-way valve 54. Then, it is returned to the compressor 53.

The air conditioner configured as described above uses any one of the heat exchangers in the first to third embodiments for the outdoor heat exchanger 55 or the indoor heat exchanger 57. Thus, the heat exchanger is small and highly efficient without expansion and deformation in the header region portion, so that a high-performance refrigeration apparatus with high energy saving performance can be obtained.

As described above, the first disclosure is a heat exchanger, and this heat exchanger has a second fluid between each plate fin stack of a plate fin stack having a heat exchange channel through which the first fluid flows. Is a heat exchanger that exchanges heat between the first fluid and the second fluid. The plate fins of the plate fin laminate include a flow path region having a plurality of heat exchange flow channels through which the first fluid flows in parallel, and an inlet header flow channel communicating with each of the heat exchange flow channels in the flow channel region. And a header region having an outlet-side header channel. The heat exchange flow path is formed by providing a concave groove in the plate fin, and between the heat exchange flow paths in the flow path region connecting the inlet side header flow path and the outlet side header flow path of the plate fin. Protrusions are provided on the recess plane. Furthermore, the protrusion has a cut-and-raised shape that abuts on the surface of the adjacent plate fin and opens the flow direction of the second fluid flowing between the plate fins.

With this configuration, it is possible to eliminate variations in the spacing between the plate fin stacks through which the second fluid flows, and the protrusion has a cut-and-raised shape in which the flow direction of the second fluid is open. The dead water area formed on the side can be cut and raised to produce the leading edge effect at the edge portion, and the heat exchange efficiency can be improved while suppressing the flow path resistance. Moreover, the protrusions are formed by cutting and raising the second fluid flowing between the plate fins so that the flow direction is open. With this configuration, there is no need to steal from the hollow plane between the heat exchange flow paths in the direction in which the fluid to be exchanged flows, that is, the direction intersecting the heat exchange flow path, and the hollow plane between the heat exchange flow paths is eliminated. The plate fin, that is, the heat exchanger can be downsized accordingly. And by using such a heat exchanger, it can be set as a compact and high-performance refrigeration apparatus with high energy saving.

The second disclosure is configured such that, in the first disclosure, the tops of the protrusions are brought into contact with the recessed planes of the adjacent plate fins.

This configuration eliminates the need for the accuracy required to configure the tops of the protrusions to face each other, improving the degree of freedom, and quality due to misalignment between the tops that is a concern when the tops of the protrusions are in contact with each other. Defects can also be prevented.

The third disclosure is configured such that in the first disclosure or the second disclosure, the protrusion is provided at a position away from the edge of the long side of the plate fin.

With this configuration, condensed water is generated in the plate fins of the plate fin laminate, and when this condensed water flows and is discharged along the edge of the plate fin, the flow is blocked by the protrusions, and the condensed water accumulates in the protrusions. Various troubles can be prevented from occurring, and a highly reliable heat exchanger can be obtained.

According to a fourth disclosure, in any one of the first to third disclosures, the plate fin is configured by joining a plate provided with a concave groove serving as a heat exchange channel and facing each other. The flow paths are stacked so that the flow paths are alternately displaced in the stacking direction. In addition, the edge of the long side portion along the heat exchange flow path of the plate fin is used as a joint surface between the narrow plane and the wide plane due to the alternately-positioned arrangement of the heat exchange flow path, and further, there is a gap in the stacking direction of the plate fins. Protrusions are provided on the side of the wide flat surface, and the tops of the protrusions are brought into contact with the narrow planes of adjacent plate fins to join the plate fins.

With this configuration, the strength of the long side portion of the plate fin laminate can be improved to prevent deformation and the like, and a protrusion is provided on the wide plane side so as to contact and join the narrow plane. In other words, by using the wide plane to provide a projection on the wide plane side and abutting and joining to the narrow plane, there is no need to provide a projection on the narrow plane of the plate fin long side portion, and the narrow plane portion A width dimension can be narrowed and the size reduction of the heat exchanger can be promoted accordingly.

According to a fifth disclosure, in the first to fourth disclosures, an inlet-side header channel and an outlet side that communicate with the heat-exchange channel in a shape that turns the heat-exchange channel formed in the plate fin into a U shape The header flow path is collectively arranged on one end side of the plate fin, and a notch groove for heat insulation is formed between the forward flow path section and the return flow path section of the U-shaped heat exchange flow path. . Furthermore, a projection is provided on the groove edge portion of the forward-side channel portion and the return-side channel portion of the notch groove, and the plate fins are joined together by bringing the top of the projection into contact with the surface of the adjacent plate fin. Are connected.

With this configuration, it is possible to lengthen the heat exchange flow path without lengthening the plate fin and prevent heat transfer from the forward flow path section to the return flow path section to efficiently exchange heat of the first fluid. Thus, heat exchange efficiency can be improved while downsizing the heat exchanger. And while improving the heat exchange efficiency and downsizing, the strength of the groove edge portion, which is divided by the newly provided notch groove and decreases in strength, can be reinforced by the joining of the protrusion, and deformation near the groove edge can be achieved. In addition, the heat exchange efficiency can be improved.

The sixth disclosure is a refrigeration apparatus, and this refrigeration apparatus uses any one of the heat exchangers of the first to fifth disclosures as a heat exchanger constituting a refrigeration cycle.

With this configuration, the refrigeration apparatus can be a high-performance refrigeration apparatus with high energy saving because the heat exchanger is small and highly efficient.

In the present invention, a plurality of protrusions are provided in the flow path region and the protrusions are cut and raised so that the flow direction of the fluid is open, thereby eliminating variations in the plate fin stacking interval and reducing the size and efficiency of the heat. It is possible to provide an exchanger and a high-performance refrigeration apparatus using the same with high energy saving performance. Therefore, it can be widely used in heat exchangers and various refrigeration equipment used for home and commercial air conditioners, and has a great industrial value.

DESCRIPTION OF SYMBOLS 1,100 Heat exchanger 2,103 Plate fin laminated

body

2a, 102

Plate fin

3, 3a, 3b, 104 End plate 4 Inflow pipe 5 Outflow pipe 6 1st plate fin 6a 1st plate-shaped member 6b 2nd plate-shaped member 7

Second plate fin

8, 8a, 8b Header opening 9 Connection means (bolts and nuts)
10, 105 Inlet side header channel (header channel)
10a Peripheral flow path 10b Communication flow path 10c Multi-branch flow path 11 First fluid flow path 11a Outward flow path section 11b Return flow path section 12 Protrusion 12a, 12aa First protrusion (protrusion)
12b Second protrusion (protrusion)
13 Through hole (positioning boss hole)
13a hole outer peripheral part (positioning boss hole outer peripheral part)
14,106 Outlet side header channel (header channel)
15

slit

16a, 16b reinforcing plate 17 shunting collision wall 18

non-flow path part

19a, 19b plane end part 20 hollow plane part 20a narrow plane 20b wide plane 21 fin plane part 22 projection 22a third projection (projection)
22b Fourth protrusion (protrusion)
24 Branch flow control pipe 25

Refrigerant flow gap

26, 26a, 26b Branch 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

A heat exchanger that exchanges heat between the first fluid and the second fluid by causing the second fluid to flow between the plate fin laminates of the plate fin laminate having the heat exchange flow path through which the first fluid flows. Because
The plate fins of the plate fin laminate include a flow path region having a plurality of the heat exchange flow paths through which the first fluid flows in parallel, and an inlet communicating with each of the heat exchange flow paths in the flow path area. A header region having a side header channel and an outlet side header channel, and the heat exchange channel is formed by providing a concave groove in the plate fin,
And a protrusion is provided in the hollow plane between the flow paths for heat exchange in the flow path region connecting the inlet header flow path and the outlet header flow path of the plate fin, and the protrusion is adjacent to the plate. A heat exchanger having a cut-and-raised shape in contact with the surface of the fin and having an opening in the flow direction of the second fluid flowing between the plate fins.
The heat exchanger according to claim 1, wherein the top of the protrusion is brought into contact with a recessed plane of the adjacent plate fin.
The heat exchanger according to claim 1, wherein the protrusion is provided at a position away from an edge of a long side of the plate fin.
The heat exchanger according to claim 2, wherein the protrusion is provided at a position away from an edge of a long side of the plate fin.
The plate fins are configured by facing and connecting plates provided with concave grooves serving as the heat exchange flow paths, and the heat exchange flow paths of the plate fins are alternately displaced in the stacking direction. And the edge of the long side portion of the plate fin along the heat exchange channel is a joining surface of a narrow plane and a wide plane due to the alternating displacement of the heat exchange channel, and The projections are provided on the wide plane side intermittently positioned in the laminating direction of the plate fins, and the tops of the projections are brought into contact with the narrow planes of the adjacent plate fins to join the plate fins. The heat exchanger according to any one of 1 to 4.
The heat exchange flow path formed in the plate fin has a U-shaped shape, and the inlet header flow path and the outlet header flow path communicating with the heat exchange flow path are connected to one end of the plate fin. And a heat-insulating notch groove is formed between the forward-side channel portion and the return-side channel portion of the heat exchange channel, and the forward-side channel of the notched groove The plate fins are coupled to each other by providing the projection on the groove edge portion of the return portion and the return-side flow path portion, and bringing the top of the projection into contact with the surface of the adjacent plate fin and joining them together. The heat exchanger according to any one of 4.
The heat exchange flow path formed in the plate fin has a U-shaped shape, and the inlet header flow path and the outlet header flow path communicating with the heat exchange flow path are connected to one end of the plate fin. And a heat-insulating notch groove is formed between the forward-side channel portion and the return-side channel portion of the heat exchange channel, and the forward-side channel of the notched groove The plate fins are coupled to each other by providing the projections on the groove edge portion of the return-side flow path portion and joining the top portions of the projections in contact with the surfaces of the adjacent plate fins. The described heat exchanger.
A refrigeration apparatus comprising the heat exchanger constituting the refrigeration cycle as the heat exchanger according to any one of claims 1 to 4.
A refrigeration apparatus comprising the heat exchanger according to claim 5 as a heat exchanger constituting a refrigeration cycle.
A refrigeration apparatus comprising the heat exchanger according to claim 6 as a heat exchanger constituting a refrigeration cycle.
A refrigeration apparatus comprising a heat exchanger according to claim 7 as a heat exchanger constituting a refrigeration cycle.