JP7365635B2 - Heat exchanger - Google Patents

Description

The present disclosure relates to a heat exchanger, and particularly relates to a stacked plate fin heat exchanger configured by stacking plate-like plate fins through which a refrigerant flows.

Heat exchangers, which are used to exchange thermal energy between fluids with different thermal energies, are used in many devices, especially laminated plate fin heat exchangers, for example in household and vehicle applications. It is widely used in air conditioners, computers, and various electrical equipment.

A stacked plate fin heat exchanger exchanges heat between the fluid (refrigerant) flowing through the flow path formed in the plate-shaped plate fins and the fluid (air) flowing between the stacked plate fins. This is a form of doing this.

In the field of laminated plate fin heat exchangers as described above, various configurations have been proposed for the purpose of reducing weight, size, and efficiency of heat exchange (for example, see Patent Document 1 and Patent Document 2). ).

Patent No. 3965901 Utility model registration No. 3192719 Patent No. 6504367

In the field of laminated plate fin heat exchangers, the plate fins are made of a thin material with high thermal conductivity, and the thickness of the plate fins is reduced to reduce the weight, size, and efficiency of heat exchange. It is being considered to flow fluid (refrigerant) at a higher pressure through the flow path than in conventional heat exchangers.

In a laminated plate fin heat exchanger, if a high-pressure refrigerant is flowed through the flow channels provided in the plate fins, the flow channels will be deformed, causing variations in the flow rate and flow velocity of the refrigerant, making it difficult to use as a heat exchanger. There was a risk that the performance of In a heat exchanger configured by stacking a plurality of plate fins, rigidity is provided at both ends in the stacking direction to prevent deformation and distortion in the stacking direction due to refrigerant flowing through the flow path. A tall and thick metal member was provided as an end plate (see Patent Document 3).

However, even in the laminated plate fin heat exchanger constructed in this way, it is important to reduce the weight and size as well as to further improve the efficiency of heat exchange.

An object of the present disclosure is to provide a highly reliable heat exchanger that is lighter in weight, smaller in size, and more efficient in heat exchange, and capable of flowing high-pressure refrigerant through a flow path.

A heat exchanger according to one embodiment of the present disclosure includes:
A plate fin laminate in which plate fins are stacked, each having a flow path through which a first fluid flows;
A supply/discharge pipe for supplying or discharging the first fluid flowing into the flow path of the plate fins of each layer in the plate fin stack,
A heat exchanger that flows a second fluid between each layer of the plate-fin laminate to exchange heat between the first fluid and the second fluid flowing through the flow path,
The plate fin is
a header opening into which the first fluid from the supply pipe is supplied when the supply/discharge pipe functions as a supply pipe;
a header flow path formed around the header opening;
a plate fin flow path through which the first fluid from the header flow path flows and exchanges heat with the second fluid;
The flow path between the header flow path and the plate fin flow path is configured to have a path that moves in the stacking direction.

According to the present disclosure, it is possible to provide a heat exchanger that is lightweight, compact, and efficient, and has high reliability even in a configuration in which a high-pressure refrigerant flows.

A perspective view showing the appearance of a laminated plate-fin heat exchanger according to Embodiment 1 of the present disclosure A plan view showing a first fin member and a second fin member of the plate fin in Embodiment 1. An exploded perspective view showing a stacked state of plate fins in Embodiment 1. A perspective view showing a part of the plate fin laminate in Embodiment 1 A perspective view showing the vicinity of the header flow path in the plate-fin laminate in Embodiment 1. A perspective view showing a cross section of the plate fin laminate according to Embodiment 1 taken along the line VI-VI shown in FIG. 2. Cross-sectional view showing the vicinity of the header opening of the plate-fin stack sandwiched between end plates A vertical cross-sectional view showing a longitudinal cross-sectional view perpendicular to the vertical cross-sectional view shown in FIG. A vertical cross-sectional view showing the first fin member in FIG. 7 A vertical cross-sectional view showing the second fin member in FIG. 7 A vertical cross-sectional view showing the first fin member in FIG. 8 A vertical cross-sectional view showing the second fin member in FIG. 8 A perspective view showing a longitudinal section of the plate-fin laminate in the first embodiment cut in the longitudinal direction. An end view cut in the longitudinal direction of the plate fin laminate in Embodiment 1 A perspective view showing a vertical cross section of the plate fin laminate in Embodiment 1. An end view of the plate-fin laminate showing the longitudinal section of FIG. 15 In the configuration of Embodiment 1, an exploded perspective view showing the first fin member in contact with the second end plate and the plate fins stacked thereon. An exploded perspective view showing the second fin member in contact with the first end plate and the plate fins stacked thereunder in the configuration of the first embodiment. A vertical cross-sectional view schematically showing a modification of the configuration of Embodiment 1 A perspective view showing a plate-fin laminate in a heat exchanger according to Embodiment 2 of the present disclosure Cross-sectional view of a region where a header flow path is formed in a plate-fin laminate in Embodiment 2 A perspective view showing a part of a plate fin laminate in a heat exchanger according to Embodiment 3 of the present disclosure A plan view showing a first fin member and a second fin member of a plate fin in Embodiment 3. A perspective view showing a longitudinal cross section of the plate fin laminate of Embodiment 3 taken along the longitudinal direction. An end view cut along the longitudinal direction of the plate-fin laminate in Embodiment 3

The heat exchanger of the first aspect according to the present disclosure includes:
A plate fin laminate in which plate fins are stacked, each having a flow path through which a first fluid flows;
A supply/discharge pipe for supplying or discharging the first fluid flowing into the flow path of the plate fins of each layer in the plate fin stack,
A heat exchanger that flows a second fluid between each layer of the plate-fin laminate to exchange heat between the first fluid and the second fluid flowing through the flow path,
The plate fin is
a header opening into which the first fluid from the supply pipe is supplied when the supply/discharge pipe functions as a supply pipe;
a header flow path formed around the header opening;
a plate fin flow path through which the first fluid from the header flow path flows and exchanges heat with the second fluid;
The flow path between the header flow path and the plate fin flow path has a path that moves in the stacking direction.

In the heat exchanger according to a second aspect of the present disclosure, in the first aspect, the plate fin has a configuration in which a first fin member and a second fin member are joined to form a flow path. ,
the first fin member has a recess for forming the header flow path and the plate fin flow path;
The second fin member may have a recess that forms a delivery channel that communicates the header channel and the plate fin channel of the first fin member.

In the heat exchanger according to a third aspect of the present disclosure, in the second aspect, the first fin member has a plurality of recesses for forming the plate fin flow path,
The recess of the delivery flow path of the second fin member in the plate fin communicates a plurality of recesses formed in the first fin member, and serves as a path for the plate fin flow path to move in the stacking direction. Good too.

In the heat exchanger according to a fourth aspect of the present disclosure, in the first or second aspect, a recess for forming the header flow path in the first fin member and the plate fin flow path are formed. It has a flat delivery area between the recess and
The recess of the delivery flow path in the second fin member is in a region opposite to the delivery area of the first fin member,
The plate fin may be configured such that a recess for forming the header flow path and a recess for forming the plate fin flow path are continuous.

A heat exchanger according to a fifth aspect of the present disclosure, in any one of the second to fourth aspects, includes end plates provided to sandwich both ends of the plate-fin laminate in the stacking direction. Equipped with
In the plate fin laminate, the first fin member or the second fin member constituting the plate fin may be provided at a position in contact with the end plate.

In the heat exchanger according to a sixth aspect of the present disclosure, in the fifth aspect, the plate fin is configured by joining the flat surfaces of the first fin member and the second fin member, and A flat joint surface between the first fin member and the second fin member may be configured to contact the end plate.

In the heat exchanger according to a seventh aspect of the present disclosure, in any one of the second to sixth aspects, a plurality of recesses for forming the plate fin flow path in the first fin member are provided. is arranged on a meandering line,
The recess for forming the delivery flow path in the second fin member may meander by communicating with the recess of the plate fin flow path in the first fin member in the plate fin.

Hereinafter, as an embodiment of the heat exchanger of the present disclosure, a laminated plate-fin heat exchanger 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 laminated plate-fin heat exchanger described in the following embodiments, but may have a configuration equivalent to the technical idea described in the following embodiments. It includes a heat exchanger having a The embodiment described below shows an example of the present invention, and the configuration, function, operation, etc. shown in the embodiment are illustrative and do not limit the present disclosure. Among the constituent elements in the following embodiments, constituent elements that are not described in the independent claims indicating the most significant concept will be described as arbitrary constituent elements.

《Embodiment 1》
FIG. 1 is a perspective view showing the appearance of a laminated plate-fin heat exchanger (hereinafter simply referred to as a heat exchanger) 1 according to the first embodiment. As shown in FIG. 1, the heat exchanger 1 according to the first embodiment has an inlet pipe 4 into which a refrigerant as the first fluid A is supplied, and a plurality of plate fins 2a each having a rectangular plate shape. The plate fin stack 2 includes a plate fin stack 2 and a discharge pipe 5 for discharging the refrigerant that has flowed through the flow path formed in the plate fin 2a.

In the heat exchanger 1 of Embodiment 1, the supply pipe 4 and the discharge pipe 5 have substantially the same configuration, and the function corresponding to the operation at that time is used as the name. In the present disclosure, the supply pipe 4 and the discharge pipe 5 are collectively referred to as supply and discharge pipes (4, 5).

End plates 3 (3a, 3b) are arranged at both ends of the plate fin laminate 2 in the stacking direction, and the end plates 3 (3a, 3b) have substantially the same shape in plan view as the rectangular plate fin 2a. . An inlet pipe 4 or an outlet pipe 5 is connected to both longitudinal ends of one end plate 3 (3a). In addition, in the configuration of Embodiment 1, a configuration will be described in which the supply pipe 4 or the discharge pipe 5 is joined to both ends of one end plate 3a, but depending on the specifications of the device in which the heat exchanger 1 is used, A configuration may also be adopted in which the inlet pipe 4 is joined to one end plate 3a and the discharge pipe 5 is joined to the other end plate 3b.

In the following embodiments, the stacking direction of the plate-fin laminate 2 in the heat exchanger 1 shown in FIG. , the position of the other end plate 3b will be explained below. However, when the heat exchanger 1 is installed in a device (for example, an air conditioner), the stacking direction is not specified as the vertical direction (vertical direction).

The end plates 3 (3a, 3b) disposed at both ends of the plate-fin stack 2 in the stacking direction are fixed to each other at a predetermined interval by positioning means (for example, positioning bolts), and the plate-fin stack Body 2 is pinched. The positioning means for maintaining and fixing the end plates 3 (3a, 3b) at both ends at a predetermined interval has a function of positioning each of the stacked plate fins 2. The end plate 3 is made of a plate made of a metal material such as aluminum, aluminum alloy, or stainless steel.

In the heat exchanger 1 of the first embodiment, the refrigerant, which is the first fluid A, is configured to flow through channels (plate fin channels 13) formed in each plate fin 2a of the plate fin stack 2. On the other hand, air, which is the second fluid B, passes through gaps formed between the plate fins 2a in the plate fin stack 2. In the heat exchanger 1 configured in this way, heat exchange is performed between the first fluid A and the second fluid B in the plate-fin stack 2.

Each of the plurality of plate fins 2a constituting the plate fin laminate 2 in the heat exchanger 1 of the first embodiment has a first fin member 10 and a second fin member 20, which are two plate materials, facing each other. They are pasted together and bonded (brazed) to form a flow path. A plurality of plate fins 2a configured in this manner are bonded (brazed) under pressure and heat in a stacked state, thereby forming a plate fin stack 2.

FIG. 2 is a plan view showing the first fin member 10 and the second fin member 20 that constitute the plate fin 2a. In FIG. 2, (a) is a plan view of the first fin member 10, and (b) is a plan view of the second fin member 20. The first fin member 10 and the second fin member 20 are made of a metal plate material such as aluminum, aluminum alloy, or stainless steel, and have at least a brazing material layer in the core material of the metal plate material. Further, the first fin member 10 and the second fin member 20 are processed into a predetermined shape using a thin plate material having a thickness of, for example, 0.2 mm. The first fin member 10 and the second fin member 20, which have been processed into a predetermined shape, are pressurized and heated so that they come into close contact with each other at a predetermined position, thereby ensuring that the opposing flat predetermined regions are joined (waxed) to each other. attached).

The first fin member 10 shown in FIG. Formed on both ends. The header flow path 11 in the first fin member 10 is formed by an annular recess configured to protrude toward the front side of the page in FIG. 2(a). A header communication channel 12 is formed extending a predetermined distance from one location on the outer circumferential portion of the header channel 11 . An end portion of a plate fin channel 13 formed in the heat exchange region C of the plate fin 2a is arranged on the extension line of the header communication channel 12 in the lead-out direction.

In the first fin member 10, the plate fin channel 13 formed on the extension line of the header communication channel 12 in the lead-out direction is formed by a recess similarly to the header communication channel 12. The plate fin channel 13 is formed to meander throughout the heat exchange area C of the plate fin 2a. The plate fin flow path 13 includes a first plate fin flow path 13a formed of a linear recess, and a second plate fin flow path 13b formed of an arcuate recess. In the configuration of the first embodiment, a plurality (for example, three) of linear first plate fin channels 13a extend in parallel in the longitudinal direction in the heat exchange region C of the plate fin 2a. A meandering flow path is formed by connecting the arcuate second plate fin flow path 13b between these ends. Further, the heat exchange area C in the plate fin 2a is an area other than the header area where the header flow path 11 is formed.

As described above, header channels 11 that communicate with the supply pipe 4 or the discharge pipe 5 are formed at both ends of the first fin member 10 in the longitudinal direction. In the first fin member 10, each of the header passages 11, header communication passages 12, and plate fin passages 13 is point symmetrical with respect to the center point of the first fin member 10 in a plan view. It is arranged so that.

In the first fin member 10, a heat transfer blocking slit 6, which is a missing portion (gap), is formed between the meandering plate fin channels 13. By forming the heat transfer blocking slit 6 which is the missing portion (gap) in this way, the heat transfer effect between the adjacent plate fin channels 13 is suppressed. Further, in the first fin member 10, positioning pin openings 9 for inserting positioning pins (not shown) are formed at a plurality of locations (three locations) so as to surround the header channel 11. The heat transfer cutoff slit 6 and the positioning pin opening 9 are arranged with the center point of the first fin member 10 in plan view as the center of symmetry, similarly to each flow path (header flow path 11, plate fin flow path 13). It is formed symmetrically.

Further, as shown in FIG. 2(a), in the first fin member 10, the header communication channel 12 leading out from the header channel 11 is connected to the plate fin channel 13 formed on the extension line in the leading direction. are not connected in a direct product manner, and a flat channel transfer area 16 is formed between them. That is, in the first fin member 10, the recess of the header communication passage 12 and the recess of the first plate fin passage 13a are not connected.

On the other hand, in the second fin member 20, as shown in FIG. 2B, a delivery channel 21 is formed at a position facing the channel delivery region 16 of the first fin member 10. In FIG. 2(b), the delivery channel 21 is formed by a recess that protrudes to the back side of the page. As a result, in the plate fin 2a where the first fin member 10 and the second fin member 20 are joined, the header communication channel 12 and the plate fin channel 13 are in communication via the delivery channel 21. . As a result, the refrigerant supplied from the supply pipe 4 flows through the header flow path 11, header communication flow path 12, delivery flow path 21, plate fin flow path 13, delivery flow path 21, header communication flow path 12, and header flow path. 11 and is discharged from the discharge pipe 5.

In the second fin member 20, a plate fin convex region 22 is formed in a region of the first fin member 10 that faces the linear first plate fin channel 13a (see the cross-sectional view of FIG. 16, which will be described later). This plate fin convex region 22 is combined and joined with the first plate fin flow path 13a, ensuring the flow path shape of the straight portion of the plate fin flow path 13, and deforming the cross-sectional shape perpendicular to the flow direction of the refrigerant. is suppressed.

In addition, in the second fin member 20, a similar heat transfer blocking slit 6 is formed between the plate fin convex regions 22 at a position corresponding to the heat transfer blocking slit 6 formed in the first fin member 10. ing. By forming the heat transfer blocking slits 6 in this manner, the heat transfer effect between adjacent plate fin channels 13 is suppressed, thereby increasing the heat exchange efficiency.

Further, in the configuration of the first embodiment, the second fin member 20 is provided with a plurality of interval defining protrusions 7 for defining the gaps between the laminated plate fins 2a at a constant interval. Note that these spacing regulating protrusions 7 maintain a constant spacing between the plate fins 2a adjacent in the stacking direction, so the spacing regulating protrusions 7 maintain a constant spacing between the plate fins 2a adjacent to each other in the stacking direction. The fin 2a may be provided on the surface opposite to the surface on which the first fin member 10 and the second fin member 20 are brazed) or on the outer surface of both, and the location thereof is determined by the flow path to be formed. It is set as appropriate depending on the position.

In the second fin member 20 configured as described above, similarly to the first fin member 10, each element ( A heat transfer blocking slit 6, a spacing defining protrusion 7, and a positioning pin opening 9) are provided.

FIG. 3 is an exploded perspective view showing a state in which two sets of plate fins 2a (first fin member 10 and second fin member 20) are stacked, and shows the vicinity of the header flow path 11. As shown in FIG. 3, in the first fin member 10, a header flow passage opening 8, which is a notch, is formed on the inner peripheral side of the annular recess that forms the header flow passage 11. The header passage ports 8 are formed at a plurality of locations on the inner peripheral side of the annular header passage 11 . In the configuration of the first embodiment, the header channel ports 8 (8a, 8b) are formed, for example, at opposing positions on the inner peripheral side of the header channel 11. In the first embodiment, the header flow passage ports 8 (8a, 8b) are formed at opposite positions of the header flow passage 11 on the center line extending in the longitudinal direction of the plate fin 2a passing through the center of the annular header flow passage 11. (See FIG. 2(a)).

Note that the formation positions of the plurality of header flow passage ports 8 in the header flow passage 11 are the upper and lower positions in the vertical direction when a device (for example, an air conditioner) equipped with the heat exchanger 1 is installed. Preferably included.

FIG. 4 is a perspective view showing a part of the plate-fin laminate 2 in the first embodiment. Although FIG. 4 shows a plate fin laminate 2 in which a plurality of plate fins 2a are stacked, the number of plate fins 2a to be stacked is appropriately set according to the specifications of the heat exchanger 1. In the plate-fin laminate 2 shown in FIG. 4, the end plates 3 (3a, 3b) are removed, and no positioning pins are inserted into the positioning pin openings 9.

FIG. 5 is a perspective view showing the vicinity of the header channel 11 in the plate-fin laminate 2 shown in FIG. 4. FIG. FIG. 6 is a perspective view showing a cross section of the plate-fin laminate 2 shown in FIG. 4 taken along the line VI--VI shown in FIG. As shown in FIGS. 5 and 6, a header opening 11a is formed on the inner peripheral side of the header channel 11 in the plate-fin stack 2, penetrating in the stacking direction. The refrigerant from the supply pipe 4 to the header flow path 11 or the refrigerant from the header flow path 11 to the discharge pipe 4 flows through the header opening 11a.

In the plate-fin laminate 2, the inner peripheral side of the header flow path 11, which constitutes the inner surface side of the header opening 11a penetrating in the stacking direction, is continuously joined in the stacking direction by brazing. Further, on the outer peripheral side of the header flow path 11, they are joined so as to be continuous in the stacking direction. As a result, the inner circumferential side and the outer circumferential side of the header channel 11 in the plate-fin laminate 2 are securely joined in the stacking direction, and the rigidity of the header channel 11 is increased.

The refrigerant supplied from the supply pipe 4 is configured to flow through the header opening 11a and into the header flow path 11 through the header flow path ports 8 (8a, 8b) formed on the inner peripheral side of the header flow path 11. 5 and 6, one first header flow path port 8a of two header flow path ports 8 facing each other on the inner peripheral side of the header flow path 11 is shown. The first header flow path opening 8a and the second header flow path opening 8b are arranged at opposite positions on the center line extending in the longitudinal direction passing through the center of the header opening 11a, that is, on the center line extending in the longitudinal direction of the plate fin 2a. There is.

FIG. 7 is a cross-sectional view showing the vicinity of the header opening 11a in the plate-fin laminate 2 sandwiched between the end plates 3 (3a, 3b). The cross-sectional view in FIG. 7 is a vertical cross-sectional view taken along the line VI--VI shown in FIG. FIG. 8 is a longitudinal cross-sectional view showing a longitudinal cross-sectional view perpendicular to the cross-sectional view shown in FIG. 7. FIG. FIG. 8 shows the vicinity of the header opening 11a in the plate-fin laminate 2, and is a cross-sectional view including the first header flow path port 8a and the second header flow path port 8b.

As shown in FIG. 7, the plate fin laminate 2 is constructed by laminating a plurality of plate fins 2a formed by laminating a first fin member 10 and a second fin member 20 together. In the first fin member 10, a recess for forming a header flow path 11 is formed on the outer periphery of the header opening 11a. The header flow path 11 (dent) in the first fin member 10 includes a header flow path inner peripheral support portion 10a that constitutes the outer peripheral wall surface of the header opening 11a, a header flow path top portion 10b, and a header flow path outer peripheral support portion 10c. It is formed by That is, in the first fin member 10, the recess for forming the header flow path 11 has a header flow path top portion 10b having an annular top and a flat surface, and a header flow path top portion 10b stacked on the inner peripheral side. The header flow path inner circumferential support portion 10a serves as an inner circumferential wall that supports the header flow path top portion 10b in the stacking direction, and the header flow path outer circumferential support portion 10c serves as an outer circumferential wall that supports the header flow path top portion 10b in the stacking direction on the outer circumferential side.

On the other hand, the second fin member 20 is formed with an inner peripheral support portion 20a that is the outer edge portion of the outer periphery of the header opening 11a, and a flat portion 20b is formed following the inner peripheral support portion 20a. The flat portion 20b and the inner peripheral support portion 20a are bent and continuous. The inner circumferential support portion 20a of the second fin member 20 constitutes a wall surface on the outer circumferential side of the header opening 11a. The flat portion 20b of the second fin member 20 closes the recess formed by the header channel inner circumferential support portion 10a, the header channel top portion 10b, and the header channel outer circumferential support portion 10c of the first fin member 10, and This is a part of the annular header flow path 11 on the outer periphery of the header 11a.

As described above, in the first fin member 10 of the plate-fin laminate 2 in the first embodiment, the recess for forming the header flow path 11 is formed between the header flow path inner peripheral support portion 10a and the header flow path top portion 10b. and a header flow path outer peripheral support portion 10c. The header flow path is formed by joining the header flow path inner circumference support portion 10a and the header flow path outer circumference support portion 10c to the flat surface of the second fin member 20, and a part of the header flow path inner circumference support portion 10a is joined to the flat surface of the second fin member 20. A header channel opening 8 is formed.

Further, the second fin member 20 has a flat portion 20b having a flat surface, and an inner portion that is bent and continuous with the flat surface of the flat portion 20b and forms an outer edge portion of the header opening 11a on the inner peripheral side of the header flow path 11. It has a peripheral support part 20a. The inner periphery support part 20a of the second fin member 20 is joined to the first fin member 10 of another plate fin 2a adjacent in the stacking direction, so that the inner periphery side of the header channel 11 in the plate fin stack 2 is aligned in the stacking direction. It has a double wall surface extending to .

In addition, as shown in the longitudinal cross-sectional view of FIG. 8, opposing regions on the inner peripheral side of the header flow path 11 are formed by the first fin member 10 to form the header flow path opening 8 (8a, 8b). The inner peripheral support portion 10a of the header flow path is formed to have a short protrusion length from the top portion 10b of the header flow path. Similarly, the protruding length of the inner peripheral support portion 20a of the second fin member 20 is formed to be short. In this way, regions facing each other in the longitudinal direction of the header flow path inner peripheral support portion 10a and the inner peripheral support portion 20a are cut out, and header flow path ports 8 (8a, 8b) are formed on the inner peripheral side of the header flow path 11. is formed.

FIG. 9 is a longitudinal cross-sectional view of the first fin member 10 shown in FIG. 7, and shows the first fin member 10 in the vicinity of the header opening 11a. FIG. 10 is a longitudinal cross-sectional view showing the second fin member 20 shown in FIG. 7, and shows a portion joined to the first fin member 10 shown in FIG. 9. FIG. 11 is a longitudinal cross-sectional view of the first fin member 10 shown in FIG. 8, and shows the header channel openings 8 (8a, 8b) formed on the outer periphery of the header opening 11a. Similarly, FIG. 12 is a longitudinal cross-sectional view showing the second fin member 20 shown in FIG. 8, and shows a portion joined to the first fin member 10 shown in FIG. 11.

The first fin member 10 shown in FIG. 9 and the second fin member 20 shown in FIG. 10 are pasted and joined, and a header flow path 11 is formed around the outer periphery of the header opening 11a in one plate fin 2a. Ru. When the header flow path 11 is formed in this way, the header flow path inner peripheral support portion 10a of the first fin member 10 shown in FIG. 11 and the inner peripheral support portion 20a of the second fin member 20 shown in FIG. In this, header flow passage ports 8 (8a, 8b) in the header flow passage 11 are formed, and the header opening 11a communicates with the inside of the header flow passage 11 via the header flow passage ports 8 (8a, 8b).

As shown in FIG. 9, in the first fin member 10, the inner circumferential end of the header channel inner circumferential support portion 10a protrudes inward, forming a protruding end 10d. The inner circumferential end of the inner circumferential support portion 20a of the second fin member 20 in the plate fin 2a adjacent in the stacking direction is in contact with this protruding end 10d. Therefore, in the plate-fin laminate 2, the protruding end 10d of the first fin member 10 and the inner peripheral end of the inner peripheral support part 20a of the second fin member 20 are joined (see FIG. 7). ).

As described above, in each plate fin 2a in the plate fin laminate 2, the header communication flow path 12 connected to the header flow path 11 is connected to the header communication flow path 12 via the delivery flow path 21 formed in the second fin member 20. This configuration is connected to the first plate fin channel 13a.

FIG. 13 is a perspective view showing a longitudinal section of the plate-fin laminate 2 taken along its longitudinal direction. FIG. 13 shows a cross section in which the header communication channel 12 and the first plate fin channel 13a communicate with each other via the delivery channel 21 in each plate fin 2a. FIG. 14 is an end view of the plate-fin laminate 2 cut along the longitudinal direction, showing the vicinity of the delivery channel 21. As shown in FIG.

As shown in FIGS. 13 and 14, in each plate fin 2a, the header communication channel 12 formed in the first fin member 10 is connected to the first fin member 20 via the delivery channel 21 formed in the second fin member 20. It communicates with a plate fin channel 13 formed in the fin member 10. Therefore, in the plate fin stack 2, for example, the refrigerant supplied from the supply pipe 4 flows into the header opening 11a, the header flow path 11, the header communication flow path 12, the delivery flow path 21, and the plate fin flow path 13. . At this time, in the configuration shown in FIG. 14, the refrigerant flows downward from the header communication passage 12 to the delivery passage 21, and the refrigerant flows upward from the delivery passage 21 to the plate fin passage 13. That is, the refrigerant moves in a undulating manner in the vertical direction (in the stacking direction) before and after the delivery flow path 21, and its path becomes longer than in a planar flow path.

FIG. 15 is a perspective view showing a longitudinal section of the plate-fin laminate 2 according to the first embodiment, taken along a plane orthogonal to the longitudinal direction thereof. FIG. 16 is an end view of the plate-fin laminate 2 showing the longitudinal section of FIG. 15. As shown in FIGS. 15 and 16, in the plate fin laminate 2 stacked between the end plates 3 (3a, 3b) at both ends, a second fin member 20, which is one of the plate fins 2a, is located at the upper end. A first fin member 10, which is the other one of the plate fins 2a, is provided at the lower end of the first fin member 10.

In the heat exchanger of the first embodiment, the lower surface of the upper first end plate 3a of the end plates 3 at both ends and the joint surface of the second fin member 20 disposed directly below are in full contact with each other. . Here, the bonding surface refers to a surface of the plate fin 2a where the first fin member 10 and the second fin member 20 are bonded.

On the other hand, the first fin member 10, which is the other one of the plate fins 2a, is disposed at the lower end of the plate fin stack 2, and the joint surface between the upper surface of the lower second end plate 3b and the first fin member 10 is disposed at the lower end of the plate fin stack 2. Fully in contact. This is because by arranging the bonding surface of the second fin member 20 that is bonded to the first fin member 10 to face the upper first end plate 3a, the flat surface becomes wider and the contact area becomes larger. . Similarly, by arranging the bonding surface of the first fin member 10 that is bonded to the second fin member 20 to face the lower second end plate 3b, the flat surface becomes wider and the contact area becomes larger.

FIG. 17 shows a plate composed of a first fin member 10 in contact with a lower second end plate 3b, and a second fin member 20 and a first fin member 10 stacked on top of the first fin member 10. It is an exploded perspective view showing fin 2a. FIG. 17 is a perspective view seen from below in the stacking direction. FIG. 18 shows a plate fin composed of a second fin member 20 that is in contact with the upper first end plate 3a, and a first fin member 10 and a second fin member 20 that are stacked under the second fin member 20. It is an exploded perspective view showing 2a. FIG. 18 is a perspective view seen from above in the stacking direction.

In FIGS. 17 and 18, areas where the respective fin members (10, 20) contact and are joined are shown by hatched areas. Note that the region where the first fin member 10 and the second fin member 20 that constitute the plate fin 2a come into contact becomes the region to be brazed. As shown in FIGS. 17 and 18, since the contact area between the end plate 3 (3a, 3b) and the first fin member 10 or the second fin member 20 is wide and overall, there is a special The plate-fin laminate 2 can be reliably joined to the first fin member 10 or the second fin member 20 without any special processing.

In addition, since the first fin member 10 and the second fin member 20 disposed at both ends of the plate-fin laminate 2 in the stacking direction are in contact with the end plate 3 as described above, the refrigerant from the supply pipe 4 flows into the header openings 11a of the first fin member 10 and the second fin member 20. However, in the first fin member 10 that is in contact with the second end plate 3b, the header communication channel 12 and the other end are closed, forming a flat channel delivery area 16. Therefore, the refrigerant does not flow into the plate fin flow path 13 in the first fin member 10 that is in contact with the second end plate 3b. On the other hand, the second fin member 20 that is in contact with the first end plate 3a has a structure in which only the delivery flow path 21 is formed as a flow path, and the header flow path 11 is not formed. There is no flow path into which the refrigerant 11a flows.

As described above, in the configuration of the heat exchanger 1 of the first embodiment, one of the members constituting the plate fin 2a is disposed at both ends of the plate fin laminate 2 in the stacking direction, so that the end plate 3 is It becomes possible to securely hold the plate-fin laminate 2 without performing any special processing. In the plate fin laminate 2 held by the end plate 3, the region between the header regions in which the header channels 11 provided on both sides of the plate fin 2a in the longitudinal direction are formed becomes a heat exchange region C, and the heat exchange A plate fin channel 13 having a desired shape is formed in region C. Between the heat exchange area C of the laminated plate fins 2a, air as the second fluid B contacts and flows with high efficiency to the plate fin flow path 13 formed in the heat exchange area C. has a predetermined gap. As described above, the gap between adjacent plate fins 2a in the stacking direction is determined by a plurality of spacing defining protrusions 7 (see FIG. 2(b)) provided on the first end plate 3a and/or the second end plate 3b. ).

In the heat exchanger 1 of the first embodiment configured as described above, the header flow path 11 is connected to the header flow path inner periphery support portion 10a of the first fin member 10, the header flow path top portion 10b, and the header flow path outer periphery. The header flow path formed in the inner peripheral support portion 10a is formed by a recess formed by the support portion 10c and a flat portion 20b formed by the substantially flat surface of the second fin member 20. This configuration is such that refrigerant is supplied from the supply pipe 4 through the passageway port 8 .

In the plate fin laminate 2 of the first embodiment, the header channel 11 formed on the outer periphery of the header opening 11a in each plate fin 2a is located on the inner periphery side of the header channel inner periphery support portion 10a of the first fin member 10. and are joined at the outer circumferential side of the header flow path outer circumferential support portion 10c. Further, in the stacked plate fins 2a, header channels adjacent in the stacking direction are joined. Therefore, the header flow path 11 in the first embodiment has a highly rigid configuration, and even when high-pressure refrigerant from the supply pipe 4 is supplied to the header flow path 11 from the header opening 11a through the header flow path port 8. This is a configuration in which deformation such as expansion of the header channel 11 is suppressed, and a desired shape of the channel is reliably maintained. Therefore, in the heat exchanger 1 of the first embodiment, highly efficient heat exchange can be performed with high reliability.

As described above, in the heat exchanger 1 of the first embodiment, the laminated structure of the first fin member 10 and the second fin member 20 increases the strength of the header flow path in each plate fin 2a, and also increases the strength of the header flow path in each plate fin 2a. It becomes possible to achieve weight reduction, size reduction, and efficiency of heat exchange in the laminate 2. According to the configuration of the first embodiment, it is possible to provide a highly reliable heat exchanger that allows high-pressure refrigerant to flow through the flow path.

In the configuration of the first embodiment described above, the inner circumferential side of the header channel 11 of the plate fin 2a is connected to the inner circumferential support portion 10a of the header channel of the first fin member 10 and the inner circumferential side of the second fin member 20. It is composed of a wall surface having a double structure with the supporting portion 20a. As a result, in the heat exchanger 1 of the first embodiment, the strength of the inner peripheral side of the header flow path 11 to which refrigerant is supplied from the supply pipe 4 is increased, and it is possible to flow high-pressure refrigerant into the header flow path 11. This is a configuration that allows for

Further, in the configuration of the first embodiment, the joint surfaces of the first fin member 10 or the second fin member 20 constituting the plate fin 2a are brought into contact with the end plates 3 provided at both ends of the heat exchanger 1. It is configured as follows. Therefore, the plate-fin laminate 2 can be reliably sandwiched without performing any special processing on the end plate 3, and the first fin member 10 or the second fin member 20 in contact with the end plate 3 The structure is such that the flow of the refrigerant can be prevented without any special processing, and the refrigerant is prevented from leaking at the end plate 3.

[Modified example]
FIG. 19 is a longitudinal sectional view schematically showing a modification of the configuration of the first embodiment. FIG. 19 shows the vicinity of the header channel 11 in the first fin member 10A and the second fin member 20A. As shown in FIG. 19, the recess forming the header flow path 11 in the first fin member 10A has a header flow path top portion 10Ab that is formed in an annular shape and has a flat surface, and a header flow path top portion 10Ab that is connected to the inner circumference side and the outer circumference side. It is constituted by a header passage support part (header passage inner circumference support part 10Aa, header passage outer circumference support part 10Ac) formed so as to support in the stacking direction on both sides. Note that the flow path outer peripheral support portion 10Ac that supports the header flow path top portion 10Ab on the outer peripheral side is continuous with the heat exchange region C in which the plate fin flow path 13 is formed via a bent portion. As shown in the longitudinal cross-sectional view of FIG. 19, the recess for forming the header flow path 11 is formed between the header flow path inner peripheral support portion 10Aa, the header flow path top portion 10Ab, and the header flow path outer peripheral support portion 10Ac. is bent and continuous in a U-shape, and the cross section perpendicular to the flow path direction is a substantially rectangular flow path.

On the other hand, the second fin member 20A joined to the first fin member 10A has a header flow path inner peripheral support portion 10Aa, a header flow path inner peripheral support portion 10Aa, and a header flow path inner peripheral support portion 10Aa, as shown in FIG. It has a flat portion 20Ab that is a flat surface so as to cover the recess formed by the flow path top portion 10Ab and the header flow path outer peripheral support portion 10Ac. The second fin member 20A in the modified example shown in FIG. 19 is different from the inner peripheral support portion 20a of the second fin member 20 shown in FIG. It's not a good shape.

Therefore, in the plate fin laminate 2A of this modification, the inner peripheral side of the header flow path 11 is constituted by the header flow path inner peripheral support portion 10Aa of the first fin member 10A, and the header flow path 11 of the plate fin 2Aa is The inner peripheral side has a single layer structure. In FIG. 19, the lower end of the header channel inner peripheral support portion 10Aa is joined to the inner peripheral side tip portion of the second fin member 20A. The header flow path top portion 10Ab connected to the upper end of the header flow path inner peripheral support portion 10Aa is joined to the flat portion 20Ab of the second fin member 20A of the plate fin 2Aa adjacent in the stacking direction. That is, the inner circumferential side and the outer circumferential side of the header flow path 11 of the modified example shown in FIG. 19 are constituted by header flow path support portions that are joined vertically in the stacking direction and serve as connected wall surfaces.
As a result, in the plate-fin laminate 2A of the modified example, the header flow path 11 has a highly rigid structure even if the inner peripheral side has a single layer structure. Further, the inner peripheral side of the header flow path 11 in the laminated plate fins 2Aa has a single layer structure, but since each layer is continuously joined, a highly rigid refrigerant path is formed. In this refrigerant passage, a header flow passage port 8 is formed for each layer, so that a high-pressure refrigerant can be supplied to the header flow passage 11 of the plate fin 2Aa of each layer.

Note that other configurations (for example, header communication channel 12, plate fin channel 13, delivery channel 21, etc.) in the modification shown in FIG. 19 are the same as those described in the first embodiment.

《Embodiment 2》
Next, a laminated plate-fin heat exchanger (hereinafter simply referred to as a heat exchanger) according to a second embodiment of the present disclosure will be described. FIG. 20 is a perspective view showing a plate-fin laminate 100 in a heat exchanger according to the second embodiment. FIG. 21 is a cross-sectional view of a region in which header channels 130 are formed in plate-fin laminate 100 according to the second embodiment.

In FIGS. 20 and 21, elements having substantially the same functions and configurations as those of the first embodiment described above are given the same numbers. Furthermore, since the basic operation of the heat exchanger of the second embodiment is the same as that of the heat exchanger 1 of the first embodiment, the main differences in the second embodiment from the first embodiment are as follows. explain. The heat exchanger of the second embodiment differs greatly from the heat exchanger 1 of the first embodiment in the shape of the header flow path.

As shown in FIGS. 20 and 21, similarly to the configuration of Embodiment 1, the first fin member 110 and the second fin member 120 are joined (brazed) to form one plate fin 100a. Each of the first fin member 110 and the second fin member 120 in the second embodiment has an annular recess at an opposing position where the header channel 130 is formed. A header flow path 130 is formed by joining the first fin member 110 and the second fin member 120. Therefore, in the header flow path 130 in the second embodiment, the cross section perpendicular to the flow direction of the flow path is larger than that of the header flow path 11 in the first embodiment (for example, if a similar plate fin is used, (approximately twice the cross-sectional area perpendicular to) is formed.

A plurality of spacing defining protrusions 7 are formed on the surface side of the first fin member 110 in the second embodiment as a whole in order to ensure a distance between the plate fins 100a adjacent to each other in the stacking direction. As with the second fin member 20 in Embodiment 1 (see FIG. 2(b)), the distance between the adjacent plate fins 100a in the stacking direction is They are evenly distributed and arranged. Further, in the first fin member 110, positioning pin openings 9 are formed on both sides of the header channel 130, in line with the direction orthogonal to the longitudinal direction of the plate fin stack 100. That is, the header flow path 130 and the positioning pin opening 9 are arranged in a line in a direction perpendicular to the longitudinal direction of the plate-fin laminate 100, and are arranged in parallel to the flow direction of the air, which is the second fluid B. .

Similar to the first fin member 10 in Embodiment 1, the second fin member 120 in Embodiment 2 is formed with a header communication channel 12 and a plate fin channel 13 ((a in FIG. 2). )reference). Therefore, in order to communicate the header communication channel 12 of the second fin member 120 and the plate fin channel 13, a delivery channel 21 is formed in the first fin member 110 (see FIG. 20).

In the heat exchanger according to the second embodiment, similarly to the heat exchanger 1 according to the first embodiment, since the high-pressure refrigerant from the supply pipe 4 is supplied to the header flow path 130, the inner periphery of the header flow path 130 is A header channel opening 80 is formed on the side (see FIG. 21). The header channel opening 80 in the second embodiment is formed by cutting out a part of the inner peripheral end of the first fin member 110 that forms the header channel 130.

As shown in FIG. 21, in the first fin member 110 and the second fin member 120 that constitute one plate fin 100a, there is a region where the inner circumferential side and the outer circumferential side of the header flow path 130 are joined (brazed). Become. For this reason, the header flow path 130 has a configuration in which deformation of the header flow path is prevented in a configuration in which high-pressure refrigerant is sucked from the header flow path port 80, and has a highly reliable header flow path. .

In the configuration of the second embodiment, the header flow passage ports 80 are formed at opposing positions on the inner circumferential side of the header flow passage 130, and extend in the longitudinal direction of the plate fin 100a passing through the center of the annular header flow passage 130. It is formed at a position on the center line extending to . In this way, by forming the header flow path opening 80 to face the longitudinal position of the header flow path 130, when the heat exchanger is installed in a device (for example, an air conditioner), the plate fin stack Since the body 100 is inclined at a predetermined angle from the vertical line with respect to its longitudinal direction, for example, by 45 degrees, the opposing header flow passage ports 80 are located at upper and lower positions in the vertical direction. Therefore, when the refrigerant in the supply pipe 4 is flowing separately in a liquid phase and a gas phase, the liquid phase and gas phase refrigerant are supplied to the header passage ports 80 located at the upper and lower positions. As a result, the same refrigerant with a well-balanced liquid phase and gas phase is supplied to the plate fin channels 13 of each stacked layer in the heat exchange region, and the overall balance of the plate fin stack 100 is maintained. The configuration allows for highly efficient heat exchange.

《Embodiment 3》
Next, a laminated plate-fin heat exchanger (hereinafter simply referred to as a heat exchanger) according to a third embodiment of the present disclosure will be described. FIG. 22 is a perspective view showing a part of the plate-fin stack 200 in the heat exchanger according to the third embodiment. FIG. 23 is a plan view showing the first fin member 210 and the second fin member 220 in the plate fin 200a that constitutes the plate fin laminate 200 in the third embodiment. 23(a) shows the first fin member 210, and FIG. 23(b) shows the second fin member 220.

In Embodiment 3, elements having substantially the same functions and configurations as those in Embodiment 1 described above are given the same numbers and explained. Furthermore, since the basic operation of the heat exchanger in the third embodiment is the same as that of the heat exchanger 1 of the first embodiment, the main differences in the third embodiment from the first embodiment are as follows. explain. The heat exchanger of the third embodiment differs greatly from the heat exchanger 1 of the first embodiment in the shape of the plate fin flow path in the heat exchange region C. Note that in the configuration of Embodiment 3, the header flow path has the configuration described in Embodiment 1 and Embodiment 2.

In the plate fin 200a configured by joining the first fin member 210 and the second fin member 220 of Embodiment 3, the plate fin flow path 230 in the heat exchange area C moves in the stacking direction and undulates up and down. is formed. As shown in FIG. 23(a), the recesses constituting the plate fin channel 230 formed in the first fin member 210 are arranged such that the first plate fin channel 230a is linear and the second plate fin is arcuate. and a flow path 230b. In the first fin member 210 shown in FIG. 23(a), a plurality of first plate fin channels 230a are arranged in a straight line, and three rows of the first plate fin channels 230a on these straight lines are arranged in parallel. has been done. An arc-shaped second plate fin flow path 230b is arranged to connect two rows on both end sides of the first plate fin flow paths 230a arranged in three rows in parallel, and the plate fin flow path in the first fin member 210 is 230 are arranged in a meandering manner.

Further, as shown in FIG. 23(a), a flat channel transfer region 216 is formed between the plurality of first plate fin channels 230a arranged in a straight line in the first fin member 210. Therefore, the recesses forming the plate fin channel 230 in the first fin member 210 are in a divided state on a straight line.

On the other hand, as shown in FIG. 23(b), a plurality of delivery channels 240 are formed in the second fin member 220. These delivery channels 240 are recesses that face the channel delivery region 216 between the first plate fin channels 230a arranged in a straight line in the first fin members 210 to be joined. Therefore, the plate fin channel 230 on the straight line of the plate fin 200a is formed by the first plate fin channel 230a of the first fin member 210 and the delivery channel 240 of the second fin member 220, and is The refrigerant flows in a moving and undulating manner.

FIG. 24 is a perspective view showing a longitudinal section of the plate-fin laminate 200 of Embodiment 3 taken along its longitudinal direction. FIG. 24 shows a cross section in which the first plate fin channels 230a arranged in a straight line via the delivery channel 240 in each plate fin 200a communicate with each other while undulating up and down in the stacking direction. FIG. 25 is an end view of the plate-fin laminate 200 cut along the longitudinal direction, showing the vicinity of the delivery channel 240.

As shown in FIGS. 24 and 25, a flow path delivery area 216 is formed between a plurality of first plate fin flow paths 230a arranged in a straight line, and a stacking direction is formed with respect to these flow path delivery areas 216. A delivery channel 240 of the second fin member 220 is formed and stacked to face each other. Therefore, in each plate fin 200a in the plate fin stack 200 of the third embodiment, the first plate fin channels 230a arranged in a straight line communicate with each other via the delivery channel 240 while the channels undulate in the stacking direction. The configuration is as follows.

As described above, the configuration of the plate fin flow path 230 in the third embodiment is such that it meanders on a plane in the heat exchange region C and also moves and undulates in the stacking direction. As a result, in the heat exchanger of Embodiment 3, even if the shape (dimensions) of the plate-fin laminate is similar, the flow path is substantially smaller than that of a flow path configuration that merely meanders in a plane. This makes it possible to increase the heat exchange efficiency.

Note that in the configurations of Embodiments 1 to 3, the header flow path has been described as having an annular shape, but the present disclosure is not limited to this shape, and may be a simple annular shape. In addition, various shapes are included, such as a C-shape or a circular arc shape, which is a flow path shape that is not connected in an annular manner.

As described in Embodiments 1 to 3, the heat exchanger of the present disclosure has a configuration in which the header flow path is supplied with refrigerant from the inner circumferential side of the header flow path, and has a plate-fin stacked structure. The inner and outer circumferential sides of the header channels of each layer in the body are joined to form a highly rigid structure. In the heat exchanger configured in this manner, it becomes possible to supply a desired high-pressure refrigerant to the plate-fin stack, resulting in a configuration having a highly efficient heat exchange function.

In the plate fin laminate of the heat exchanger of the present disclosure, since the header flow path is constituted by the multilayer support portions (header flow path inner peripheral support portion, header flow path outer peripheral support portion) that are continuous in the stacking direction, the header flow path The pressure vulnerabilities in the header flow path have been significantly reduced, and the rigidity of the header flow path has been increased. As a result, in the heat exchanger of the present disclosure, stable operation can be maintained even when a refrigerant with a high pressure above a certain level is flowed.

Further, in the plate fin laminate of the heat exchanger of the present disclosure, the header flow path opening is formed in the support portion on the inner circumferential side of the header flow path, and this header flow path opening is the first communication point for the flow path of each plate fin. It's a mouth. The header flow path opening of the header flow path has a configuration that allows the opening shape and formation position to be set appropriately. It is a configuration that can be optimized for the current state) and further improve performance.

Furthermore, in the plate-fin laminate of the heat exchanger of the present disclosure, as explained in the heat exchanger of Embodiment 3, the plate-fin flow path formed in the heat exchange region has a meandering shape in a plane. In addition, since the flow path structure is such that it moves and undulates in the stacking direction, it becomes possible to configure the flow path path to be substantially long, resulting in a configuration that can improve heat exchange efficiency.

As described above, in the configuration of the heat exchanger according to the present disclosure, it is possible to achieve weight reduction, miniaturization, and high heat exchange efficiency, and at the same time, high-pressure refrigerant is applied to the plate fins of each layer in the plate fin stack. It is possible to provide a heat exchanger with high reliability and high heat exchange efficiency.

Although the present invention has been described in each embodiment with a certain degree of detail, these configurations are merely illustrative, and the contents disclosed in these embodiments may vary in the details of the configuration. In the present invention, substitutions, combinations, and changes in the order of elements in each embodiment can be realized without departing from the scope and spirit of the claimed invention.

The present disclosure can provide a highly reliable heat exchanger that can achieve weight reduction, miniaturization, and high heat exchange efficiency, and thus can construct air conditioning equipment with high market value.

1 Heat exchanger 2, 100, 200 Plate fin laminate 2a, 100a, 200a Plate fin 3 End plate 3a First end plate 3b Second end plate 4 Inlet pipe 4a Header opening 5 Discharge pipe 6 Heat transfer blocking slit 7 Spacing regulation Projections 8, 80 Header channel opening 8a First header channel opening 8b Second header channel opening 9 Positioning pin opening 10, 10A, 110, 210 First fin member 10a, 10Aa Header channel inner peripheral support portion 10b, 10Ab Header flow Top of channel 10c, 10Ac Header channel outer periphery support 10d Inner circumferential protruding end 11, 130 Header channel 11a Header opening 12 Header communication channel 13, 230 Plate fin channel 13a, 230a First plate fin channel ( linear)
13b, 230b Second plate fin channel (arc shape)
16, 216 Channel delivery area 20, 20A, 120, 220 Second fin member 20a Inner peripheral support portion 20b, 20Ab Flat portion 21, 240 Delivery channel

Claims (5)

A plate fin laminate in which plate fins are stacked, each having a flow path through which a first fluid flows;
A supply/discharge pipe for supplying or discharging the first fluid flowing into the flow path of the plate fins of each layer in the plate fin stack,
A heat exchanger that flows a second fluid between each layer of the plate-fin laminate to exchange heat between the first fluid and the second fluid flowing through the flow path,
The plate fin is
a header opening into which the first fluid from the supply pipe is supplied when the supply/discharge pipe functions as a supply pipe;
a header flow path formed around the header opening;
a plate fin flow path through which the first fluid from the header flow path flows and exchanges heat with the second fluid;
A flow path in the header flow path and the plate fin flow path is configured to have a path that moves in the stacking direction ,
The plate fin has a configuration in which a first fin member and a second fin member are joined to form a flow path,
the first fin member has a recess for forming the header flow path and the plate fin flow path;
The second fin member has a recess that forms a delivery channel that communicates the header channel and the plate fin channel of the first fin member,
having a flat transfer area between the recess for forming the header flow path and the recess for forming the plate fin flow path in the first fin member;
The recess of the delivery flow path in the second fin member is in a region opposite to the delivery area of the first fin member,
A heat exchanger, wherein in the plate fin, a recess for forming the header flow path and a recess for forming the plate fin flow path are continuous. The first fin member has a plurality of recesses for forming the plate fin flow path,
The recess of the delivery flow path of the second fin member in the plate fin communicates a plurality of recesses formed in the first fin member, and becomes a path for the plate fin flow path to move in the stacking direction. The heat exchanger according to claim 1 . comprising end plates provided to sandwich both ends of the plate-fin laminate in the stacking direction,
The heat exchanger according to claim 1 or 2 , wherein in the plate fin laminate, the first fin member or the second fin member constituting the plate fin is provided at a position in contact with the end plate. The plate fin is configured by joining flat surfaces of the first fin member and the second fin member, and the flat joining surfaces of the first fin member and the second fin member are in contact with the end plate. 4. A heat exchanger according to claim 3 , configured. A plurality of recesses for forming the plate fin flow path in the first fin member are arranged on a meandering line,
From claim 1, wherein the recess for forming the delivery flow path in the second fin member is configured to meander by communicating with the recess of the plate fin flow path in the first fin member in the plate fin. A heat exchanger according to any one of claims 4 to 5.

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