JP2018066531A - Heat exchanger and refrigeration system using the same - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a heat exchanger which has achieved both reduction in diameter of a flow passage and improvement in heat exchange efficiency by equalizing divided flows, and to provide a refrigeration system using the same.SOLUTION: A first fluid flow passage 11 group is formed by providing concave grooves at a plate fin 2a for constituting a heat exchanger, and also, a divided flow control pipe 24 is provided at a header opening 8b on an outlet side connected to the first fluid flow passage group. Thereby, reduction in diameter of a flow passage cross sectional area of the first fluid flow passage is achieved and heat exchange efficiency can be improved, and the first fluid can be divided into each first fluid flow passage surely as designed. The heat exchange efficiency can be made to be high as the heat exchange efficiency improvement is added by equalization of divided flows.SELECTED DRAWING: Figure 14

Description

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

  In general, in a refrigeration system such as an air conditioner or a refrigerator, a refrigerant compressed by a compressor is circulated to a heat exchanger such as a condenser or an evaporator to exchange heat with a second fluid for cooling or heating. System performance and energy saving are greatly affected by the heat exchange efficiency of the exchanger. Therefore, high efficiency is strongly demanded for the heat exchanger.

  One of the methods for improving the efficiency of this heat exchanger is to reduce the diameter of the heat transfer tubes through which the heat exchange fluid flows. As another method, for example, the refrigerant that is divided into each heat transfer tube is uniformly distributed. May be diverted to

  Under such circumstances, a heat exchanger of a refrigeration system generally uses a finned tube heat exchanger configured by passing a heat transfer tube through a fin group, and the heat transfer tube is reduced in diameter. Thus, improvement of heat exchange efficiency and downsizing are being promoted (see, for example, Patent Document 1).

  On the other hand, in order to improve the heat exchange efficiency, the heat exchange fluid is divided into a header flow path that guides the heat exchange fluid to each heat transfer tube, and the refrigerant flow to each heat transfer tube is made uniform to make the heat exchange efficiency uniform. (For example, refer patent document 2).

  FIG. 29 shows a heat exchanger described in the above-mentioned Patent Document 1. This heat exchanger 100 is configured by passing a heat transfer tube 102 through a fin group 101, and a flow dividing control tube is connected to the refrigerant inlet side header tube 103. 104 is provided. A plurality of refrigerant distribution openings 105 are arranged in the diversion control pipe 104, and the refrigerant distribution openings 105 are reduced in size as they move away from the refrigerant inlet, so that the refrigerant flowing through the heat transfer pipes 102 is evenly divided. It is like that.

  In this heat exchanger, since the refrigerant is divided at the inlet side of the refrigerant, the refrigerant is diverted to each heat transfer tube while suppressing an increase in the refrigerant temperature due to an increase in pressure loss. The heat exchange efficiency can be improved (if the refrigerant is diverted on the refrigerant outlet side, the pressure loss (hereinafter referred to as pressure loss) increases and the refrigerant temperature increases. The temperature difference with the second fluid to be heat exchange is reduced, offsetting the effect of improving the heat exchange efficiency due to the uniform flow, and conversely reducing the heat exchange efficiency, so that the refrigerant is divided at the refrigerant inlet side) .

JP 2010-78289 A JP 2012-207912 A

  However, the fin-tube heat exchanger described in Patent Document 1 has a limit in reducing the diameter because the heat transfer tube is a tube, and the improvement in heat exchange efficiency due to the decrease in the diameter of the heat transfer tube is approaching the limit. is there.

  However, this heat transfer tube can be easily reduced in diameter if it is a plate fin laminated heat exchanger. That is, the plate fin laminated heat exchanger is formed by pressing a concave groove on the plate fin to form a flow path corresponding to the heat transfer tube, so it is easy to reduce the cross-sectional area of the flow path, The flow path can be made even smaller than the heat transfer tube of the fin tube type heat exchanger.

  Therefore, the applicant studied to improve the heat exchange efficiency by combining the plate fin laminated heat exchanger configured by laminating the plate fins having flow paths with the shunt control pipe described in Patent Document 2.

  However, even if a shunt control pipe is incorporated in the header flow path of the plate fin laminated heat exchanger, the shunt effect by the shunt control pipe is not fully exhibited, and it has been found that there is a big problem in improving the heat exchange efficiency by the shunt. .

  The present invention has been intensively studied in view of the above points, and achieves both a reduction in the diameter of the flow path and an improvement in heat exchange efficiency due to the diversion effect, and a high-efficiency heat exchanger and a high-performance refrigeration using the heat exchanger. The purpose is to provide a system.

In the present invention, in order to achieve the above object, the heat exchanger causes the second fluid to flow between the plate fin stacks of the plate fin stack having the flow path through which the first fluid flows, so that the first fluid and the first fluid A heat exchanger for exchanging heat between two fluids,
The plate fins of the plate fin stack include a flow path region having a plurality of first fluid flow paths through which the first fluid flows in parallel, and an inlet-side header flow communicating with each first fluid flow path in the flow path area. A header region having a path and an outlet-side header channel, and the first fluid channel is formed by providing a concave groove in the plate fin,
And it is set as the structure which provided the shunt control pipe | tube in the said exit side header flow path used as the evaporation exit of a 1st fluid.

  As a result, the diameter of the cross-sectional area of the first fluid channel can be reduced to improve the heat exchange efficiency, and the first fluid can be reliably diverted to each first fluid channel as designed. In addition, the heat exchange efficiency is improved by the uniform flow, and the heat exchange efficiency can be increased. That is, in this plate fin laminated heat exchanger, the first fluid flow path is reduced in diameter, so that the pressure loss of the first fluid is several times larger on the header outlet side than on the header flow path side. On the other hand, the shunt flow of the first fluid is greatly influenced by the distribution of pressure loss. For this reason, as described above, this plate fin laminated heat exchanger has the same pressure loss as the outlet header flow path several times even if the flow dividing control pipe is provided in the inlet header flow path, which is common sense in the past. Since the first fluid flowing through one fluid flow path depends on the pressure loss of the outlet header flow path, it could not be divided as designed. However, in the present invention, since the shunt control pipe is provided in the outlet-side header flow path having a high pressure loss based on the understanding of the magnitude of the pressure-loss difference in the inlet / outlet-side header flow path and the pressure loss distribution situation, it has a great influence on the flow split. Thus, the distribution of pressure loss in the outlet-side header channel, which is several times higher, can be controlled to make the flow distribution uniform, and the heat exchange efficiency can be improved by making the flow distribution uniform.

  The present invention provides a heat exchanger having a high heat exchange efficiency and a high-performance refrigeration system using the same, which achieves both a reduction in the diameter of the flow path and a uniform flow distribution by the above configuration. it can.

The perspective view which shows the external appearance of the plate fin lamination type heat exchanger in Embodiment 1 of this invention The exploded perspective view which shows the state which separated the plate fin lamination type heat exchanger up and down Exploded perspective view of the plate fin laminated heat exchanger The perspective view which shows the state which extracted the shunt control pipe from the plate fin lamination type heat exchanger Side view showing the header region of the plate fin laminated heat exchanger AA sectional view of FIG. BB sectional view of FIG. CC sectional view of FIG. The perspective view which cut | disconnects and shows the connection part and header opening part of the inflow / outflow pipe | tube in the plate fin lamination type heat exchanger in Embodiment 1 of this invention. The perspective view which cut | disconnects and shows the refrigerant | coolant flow path group part of the plate fin laminated body in the plate fin laminated heat exchanger The perspective view which cut | disconnects and shows the refrigerant | coolant flow path group part in the plate fin lamination type heat exchanger The perspective view which cut | disconnects and shows the positioning boss hole part of the plate fin laminated body in the same plate fin laminated heat exchanger The perspective view which cut | disconnects and shows the header opening part of the plate fin laminated body in the plate fin laminated heat exchanger The perspective view which shows the shunt control pipe insertion part in the plate fin laminated body of the same plate fin laminated heat exchanger A perspective view of a flow dividing control pipe in the plate fin laminated heat exchanger Sectional drawing which shows the shunt control pipe part of the plate fin lamination type heat exchanger Plan view of plate fins constituting plate fin laminate of same plate fin laminate type heat exchanger An enlarged plan view showing the header area of the plate fin Exploded view showing part of the configuration of the plate fin It is a top view of the plate fin, (a) is a plan view of the first plate fin, (b) is a plan view of the second plate fin, (c) is a state when the first and second fin plates are overlapped Plan view for explaining An enlarged perspective view showing a protrusion provided in a flow path region of the plate fin The expansion perspective view which shows the protrusion provided in the refrigerant | coolant flow path U-turn side edge part of the plate fin The perspective view which shows the external appearance of the plate fin lamination type heat exchanger in Embodiment 2 of this invention Plan view of plate fins constituting plate fin laminate of same plate fin laminate type heat exchanger An exploded view showing a part of the configuration of the plate fins in the plate fin laminated heat exchanger The perspective view which cut | disconnects and shows the refrigerant | coolant flow path group part of the plate fin laminated body in the plate fin laminated heat exchanger Refrigeration cycle diagram of an air conditioner using the plate laminated heat exchanger of the present invention Schematic sectional view of the air conditioner Cross section of conventional heat exchanger

1st invention is a heat exchanger, This heat exchanger flows the 2nd fluid between each plate fin lamination | stacking of the plate fin laminated body which has a flow path through which a 1st fluid flows, The said 1st fluid and the said A heat exchanger for exchanging heat with a second fluid,
The plate fins of the plate fin stack include a flow path region having a plurality of first fluid flow paths through which the first fluid flows in parallel, and an inlet-side header flow communicating with each first fluid flow path in the flow path area. A header region having a path and an outlet-side header channel, and the first fluid channel is formed by providing a concave groove in the plate fin,
And it is set as the structure which provided the shunt control pipe | tube in the said exit side header flow path used as the evaporation exit of a 1st fluid.

  As a result, the diameter of the cross-sectional area of the first fluid channel can be reduced to improve the heat exchange efficiency, and the first fluid can be reliably diverted to each first fluid channel as designed. In addition, the heat exchange efficiency is improved by the uniform flow, and the heat exchange efficiency can be increased. That is, in this plate fin laminated heat exchanger, the first fluid flow path is reduced in diameter, so that the pressure loss of the first fluid is several times larger on the header outlet side than on the header flow path side. On the other hand, the shunt flow of the first fluid is greatly influenced by the distribution of pressure loss. For this reason, as described above, this plate fin laminated heat exchanger has the same pressure loss as the outlet header flow path several times even if the flow dividing control pipe is provided in the inlet header flow path, which is common sense in the past. Since the first fluid flowing through one fluid flow path depends on the pressure loss of the outlet header flow path, it could not be divided as designed. However, in the present invention, since the shunt control pipe is provided in the outlet-side header channel having a high pressure loss based on the understanding of the magnitude of the pressure-loss difference in the inlet-outlet-side header channel and the pressure-loss distribution state, the shunt flow is greatly affected. By controlling the pressure loss distribution in the outlet header flow path that is several times as high as that given, the flow can be made uniform, and the heat exchange efficiency can be improved by making the flow even.

  According to a second invention, in the first invention, the flow dividing control pipe has a plurality of first fluid branch ports, and the first fluid branch port has an opening area on the first fluid inlet side as a first fluid outlet. The opening area on the side is larger.

  Thereby, it is possible to equalize the first fluid amount by suppressing the deviation of the fluid flow rate generated between the first fluid channel near the first fluid inlet side and the first fluid channel near the first fluid outlet side. The efficiency can be further improved, and the pressure loss and the like at the first fluid outlet side portion can be controlled by a simple cylinder configuration that only opens the diversion port, so that the first fluid can be reliably diverted and provided at low cost. it can.

  According to a third invention, in the first or second invention, the first fluid flow path formed in the plate fin is U-turned in a substantially U shape to communicate with the first fluid flow path. It is set as the structure which put together the header flow path of the path | route and the exit side to the one end part side of a plate fin.

  This makes it possible to increase the heat exchange amount of the first fluid by elongating the first fluid flow path without lengthening the plate fins, improving the heat exchange efficiency, and promoting further downsizing of the heat exchanger. it can.

  4th invention is a refrigeration system, This refrigeration system uses the heat exchanger which comprises a refrigerating cycle as the heat exchanger as described in any one of said 1st-3rd invention.

  Thereby, since this refrigeration system has the high heat exchange efficiency of a heat exchanger, it can be set as the highly efficient refrigeration system with high energy saving property.

  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 embodiments, and is a heat exchanger equivalent to the technical idea described in the following embodiments. The configuration is included.

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

  FIG. 1 is a perspective view showing the external appearance of a plate fin laminated heat exchanger (hereinafter simply referred to as a heat exchanger) 1 according to the present embodiment, and FIG. 2 shows the plate fin laminated heat exchanger separated in the vertical direction. 3 is an exploded perspective view of the plate fin laminated heat exchanger, FIG. 4 is a perspective view showing a state in which the flow dividing control pipe is extracted from the plate fin laminated heat exchanger, and FIG. 5 is a plate fin laminated type. The side view which shows the header area | region part of a heat exchanger, FIGS. 6-8 is sectional drawing of a plate fin lamination type heat exchanger.

  As shown in FIGS. 1 to 9, the heat exchanger 1 of the present embodiment is a heat exchanger suitable for use as an evaporator, and includes an inflow pipe (inlet header) 4 into which a refrigerant that is a first fluid flows. A plate fin laminate 2 configured by laminating a plurality of plate fins 2a each having a rectangular plate shape, and an outflow pipe (outlet header) 5 for discharging the refrigerant that has flowed through the flow path in the plate fins 2a. Have.

  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) in the stacking direction of the plate fin stack 2. 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, but they are joined using another heat-resistant fixing method, for example, a chemical joining member. May be.

  In this embodiment, the end plates 3a and 3b on both sides of the plate fin laminate 2 are connected and fixed at both ends in the longitudinal direction by connecting means 9 such as bolts / 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 portions of the longitudinal end portions (the left end portion in FIG. 1) of the end plates 3a and 3b. The plate fin laminated body 2 including the end plates 3a and 3b is mechanically clamped by being connected and fixed by fastening the connecting means 9.

  The reinforcing plates 16a and 16b are also made of a rigid plate material like the end plates 3a and 3b, for example, a metal material such as stainless steel and aluminum alloy, but are more rigid than the end plates 3a and 3b. Alternatively, it is preferable to use a thick plate.

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

In the heat exchanger 1 of the present embodiment configured as described above, the refrigerant flows through the plurality of flow path groups inside the plate fins 2a of the plate fin laminate 2 in parallel in the longitudinal direction, makes a U-turn, and then flows out. It is discharged from the tube 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 laminated body 2 which makes the main body of the said heat exchanger 1, and the plate fin 2a which comprises this are demonstrated using FIGS. 10-13, FIGS. 17-22.

  10 to 13 are perspective views showing a part of the plate fin laminate cut away, and FIGS. 17 to 22 are views showing the structure of the plate fins.

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

  As shown in FIG. 19, the first plate fin 6 and the second plate fin 7 of the plate fin 2a are the same as the first plate-like member 6a formed by press-molding the refrigerant flow path configuration described in detail later. The second plate-like member 6b having the configuration is configured by facing and brazing. The said 1st plate-shaped member 6a and the 2nd plate-shaped member 6b consist of metal thin plates, such as aluminum, an aluminum alloy, and stainless steel.

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

  Since the first plate fin 6 and the second plate fin 7 of the plate fin 2a have the same configuration except that the position of the refrigerant flow path 11 described later is shifted, the first plate fin 6 of FIG. An explanation will be given with a case number assigned.

  As shown in FIG. 17, the plate fin 2 a (6, 7) has a header region H formed at one end in the longitudinal direction (left side in FIG. 17), and the other region is a flow channel region P. ing. In the header region H, both an inflow header opening 8a and an outlet header opening 8b are formed, and the inflow pipe 4 and the outflow pipe 5 are connected.

  In addition, a plurality of refrigerant channels 11, which are first fluid channels through which the refrigerant from the header openings 8 a flows, are formed in the channel region P in parallel. In the vicinity of the right end portion in FIG. 13, it is folded back and connected to the outlet opening 8b on the outlet side. More specifically, the refrigerant 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. The refrigerant from the inflow side header opening 8a is U-turned from the forward path side flow path part 11a to the return path side flow path part 11b and flows to the outlet side header opening 8b. It has become.

  Further, around the header openings 8a and 8b on the inflow and outflow sides, as shown in an enlarged view in FIG. 18, header flow paths 10 and 14 connecting the header openings 8a and 8b and the refrigerant flow path 11 group are respectively provided. Is formed. The header flow path 10 includes an outer peripheral flow path 10a formed so as to swell from the outer peripheries of the header openings 8a and 8b, and a single communication flow path 10b extending to the refrigerant flow path 11 group side of the outer peripheral flow path 10a. The multi-branch flow path 10c connecting the communication flow path 10b to each flow path of the refrigerant flow path 11 group.

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

  The opening shape of the header opening 8b on the outlet side has a larger diameter than the opening shape of the header opening 8a on the inlet side. This is because since the heat exchanger is used as a condenser, the refrigerant gasifies on the outlet side and the volume increases.

  In addition, the number of the forward-side flow passage portions 11a connected to the header opening 8a on the inflow side is set to be smaller than the number of the return-side flow passage portions 11b through which the refrigerant flows to the header opening 8b on the outlet side. 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 round-trip channel portions 11a is two and the number of the forward-path channels 11b is five. However, the number is not limited to this.

  Further, in the plate fins 2a (6, 7), the region in which the forward flow path portion 11a into which the refrigerant flows from the header opening 8a on the inflow side is formed, and the return side flow that flows to the header opening 8b on the outlet side A slit 15 is formed between the region where the path portion 11b is formed in order to reduce (heat-insulate) the heat conduction between the refrigerants in the plate fins 2a (6, 7).

  The plate fin laminate 2 is configured by laminating the plate fins 2a (6, 7) having the above configuration. This heat exchanger mainly composed of the plate fin laminate 2 is shown in FIGS. As shown in FIG. 14, FIG. 16, etc., the refrigerant flow control pipe 24 is provided in the header flow path 14 on the outlet side.

  As shown in FIG. 14, the diversion control pipe 24 is inserted into the outlet opening 8b serving as the refrigerant evaporating outlet, that is, in the header flow path 14 on the outlet side. As shown, 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 tube 24 may have a configuration in which the tip is closed and brought into contact with 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 inner face of the header opening and the longitudinal direction thereof, that is, the lamination of the plate fins 2a. A plurality of flow dividing openings 26 are formed at substantially equal intervals in the direction.

  The plurality of branch openings 26 are formed so that the hole diameters become smaller in the direction in which the refrigerant flows, that is, toward the outlet opening 8b.

  The diversion control pipe 24 is attached to a reinforcing plate 16a as shown in FIG. 15, 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.

  The outflow pipe 5 is connected and fixed to the other surface of the reinforcing plate 16a to which the diversion control pipe 24 is attached.

  The heat exchanger configured as described above is further configured as follows in order to maintain the fin stack interval of the plate fin stack 2 and increase the rigidity, and will be described.

  That is, the plate fins 2a (6, 7) constituting the plate fin laminate 2 are, on the other hand, in the first plate fin 6 in this example, as shown in FIG. A plurality of protrusions 12 (first protrusions: 12a, 12aa, second protrusion: 12b) are formed at predetermined intervals in the longitudinal direction.

  FIG. 20A shows a state where the first plate fin 6, (b) shows the second plate fin 7, and (c) shows a state where the two fin plates 2 a (6, 7) are overlapped.

  As shown in FIG. 20, the first protrusions 12 a and 12 aa are formed at the planar end 19 a of the plate fin long side edge (the long side edge on both the left and right sides in FIG. 20A) and the side edge of the slit 15. As shown in FIG. 11, each flat end 19 b is in contact with the planar end 19 a of the long side edge of the second plate fin 7 that is adjacent to each other in the stacking direction as shown in FIG. 11. The distance between the two plate fins 7 is set to a predetermined length by contacting the flat end 19b of both side edges (not shown). The first protrusion 12a is formed so as to be located on the inner side, for example, 1 mm or more on the inner side (the refrigerant channel 11 side) from the end edge of each long side edge.

  As is clear from FIG. 20A, the second protrusions 12b are formed at predetermined intervals between the flow paths of the refrigerant flow path 11 group, that is, in the hollow flat surface portion 20 which is the non-flow path portion 18 in this example. Yes. The second protrusion 12b is in contact with the recessed flat portion 20 of the second plate fin 7 adjacent in the stacking direction shown in FIG. 20B, and is stacked between the second plate fin 7 similarly to the first protrusion 12a. The distance is defined as a predetermined length.

  Each of the protrusions 12 (12a, 12aa, 12b) is formed by cutting up part of the planar end portions 19a, 19b and the recessed planar portion 20 of the first plate fin 6 as shown in FIG. (Hereinafter, the protrusion 12 (12a, 12aa, 12b) is cut and raised) and the cut and raised edge Y is opposed to the flow direction indicated by the arrow of the second fluid flowing between the stacks of the plate fins 2a. The cut and raised piece Z follows the flow of the second fluid. 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.

  The cut and raised protrusions 12 (12a, 12aa, 12b) are adjacent to the plate fins 2a whose top surfaces are adjacent to each other when the plate fins 2a (6, 7) and the end plates 3 (3a, 3b) are brazed. (6, 7), and the plate fins 2a (6, 7) are connected together.

  The first cut-and-raised protrusions 12a and 12aa and the second cut-and-raised protrusion 12b are arranged in a straight line along the flow direction of the second fluid (air), but are arranged in a staggered arrangement. It may be provided.

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

Each of the cut and raised protrusions 22 (22a and 22b) is similar to the cut and raised protrusion 12 (first cut and raised protrusions: 12a and 12aa, second cut and raised protrusion: 12b). 2a (7) is abutted and fixed, defines a gap between adjacent plate fins 2a to a predetermined length, and connects the plate fins 2a to each other.

  Further, as shown in FIG. 12, the plate fins 2a (6, 7) have positioning through holes (hereinafter referred to as positioning boss holes) 13 at the ends of the header region H and the flow channel region P. Is formed. The positioning boss holes 13 are also formed in the end plates 3a, 3b and the reinforcing plates 16a, 16b stacked on both sides of the plate fins 2a (6, 7). The positioning boss hole 13 is equipped with a positioning pin jig for laminating a plurality of plate fins 2a (6, 7), and enables highly precise lamination of other plate fins 2a. Then, the connecting means 9 (refer to FIG. 3) such as bolts for connecting the reinforcing plates 16a and 16b and the end plates 3a and 3b of the plate fin laminated body 2 is also used as a positioning pin jig.

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

  The positioning boss hole outer peripheral portion 13a formed around the positioning boss hole 13 has both inlet and outlet header channels 10 (10a, 10b, 10c) formed in the header region H shown in FIG. In addition, the other end of the plate fins 2a (6, 7) is integrally connected by brazing to the other header flow path 10 and the positioning boss hole outer peripheral portion 13a facing each other in the stacking direction.

  In addition, as the refrigerant flow path 11 in the present disclosure, for example, the cross-sectional shape orthogonal to the direction in which the refrigerant flows is described as a circular shape, but includes a rectangular shape in addition to the circular shape.

  In the present embodiment, the refrigerant flow path 11 is described as having a shape protruding to both sides in the stacking direction, but may be formed to protrude only to one side in the stacking direction. 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 thereof 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 side of the plate fin laminate 2 through the header opening 8a on the inflow side to the header flow path 10 of each plate fin 2a, that is, the outer peripheral flow path 10a around the header opening 8a. Then, the refrigerant flows into the group of refrigerant channels 11 through the communication channel 10b and the multi-branch channel 10c. The refrigerant that has flowed into the refrigerant 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, via the outlet-side header flow path 10 and the outlet-side header opening 8b. It flows from the outflow pipe 5 to the refrigerant circuit of the refrigeration system.

  When the refrigerant flows through the refrigerant 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, the refrigerant gas flowing from the header opening 8a on the inlet side to the header channel 14 on the outlet side through the group of refrigerant channels 11 is the refrigerant as shown by the arrow in FIG. It flows into the diversion control pipe 24 through a plurality of diversion openings 26 formed in the pipe wall of the diversion control pipe 24 from the flow gap 25, and flows out from the outlet opening 8b on the outlet side to the outflow pipe 5.

  The diversion port 26 provided in the diversion control pipe 24 is formed so that its hole diameter decreases as it goes to the header opening 8b on the outlet side, so that the refrigerant flowing through each flow path of the refrigerant flow path 11 group. The amount will be equalized.

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

  However, in the heat exchanger according to the present embodiment, the branch flow control pipe 24 is provided in the outlet-side header flow path 14 having a high pressure loss, and thereby the outlet-side header flow path that is several times higher, which greatly affects the flow split. The pressure loss distribution in the axial direction in 14 can be controlled to be uniform. Therefore, it is possible to make uniform the flow rate of the refrigerant flowing through each flow path of the refrigerant flow path 11 group.

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

  At this time, due to the pressure loss generated in each flow path, the flow path of the plate fin farther from the flow-in pipe 4 than the flow path 11 of the plate fin (the flow path of the plate fin closer to the right in FIG. 16) The refrigerant flows more easily in the refrigerant flow path 11 of the plate fin closer to 4 (the auction flow path of the plate fin closer to the left in FIG. 16). In other words, the flow rate of the refrigerant may be uneven.

  However, the flow dividing control pipe 24 is inserted into the header opening 8b on the outlet side, and the opening area of the flow dividing opening 26a on the most outlet side is set to the outlet side of the flow dividing control pipe 24 (as shown in FIG. By making the diversion port 26a provided in the portion close to the left side smaller than the counter-exit side of the diversion control pipe 24 (the portion closer to the right side in FIG. 16), the pressure loss of the refrigerant passing through the diversion port is increased. Thus, the refrigerant flow in the first fluid channel 11 inside each plate fin can be equalized, and the heat exchange efficiency can be improved.

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

  Furthermore, the above-described uniform structure of refrigerant distribution by the flow dividing control pipe 24 is a simple structure in which the flow dividing port 26 is simply perforated in the flow dividing control pipe 24, so that it can be provided at low cost.

  Further, since the diversion control pipe 24 is provided integrally with the reinforcing plate 16a, the diversion control pipe 24 can be inserted into the header flow path 14 simply by mounting the reinforcing plate 16a. It is possible to prevent defective plate fin joining due to soldering at the plate fin brazed portion, which is a concern in the case of retrofitting, etc., and quality defects such as refrigerant leakage associated therewith, and a high quality and highly efficient heat exchanger can be obtained.

Further, the reinforcing plate 16a is connected to the flow dividing control pipe 24 and the reinforcing plate 16a, and the potential difference between the flow dividing pipe 5 and the outflow pipe 5 is directly connected between the flow dividing control pipe 24 and the outflow pipe 5. Since it is formed of a material that is smaller than the potential difference, it is possible to prevent the occurrence of dissimilar metal contact corrosion that occurs when the shunt control pipe 24 and the outflow pipe 5 are directly connected to each other. Can be improved. In particular, a remarkable effect can be expected and effective in a heat exchanger for an air conditioner, in which the inflow / outflow pipe is often formed of a copper pipe and the shunt control pipe 24 is often formed of stainless steel or the like.

  In this embodiment, the diversion control pipe 24 is provided on the reinforcing plate 16a. However, the diversion control pipe 24 may be provided on the end plate 3a side. In the case where the reinforcing plate 16a is not used, the diverting control pipe 24 is opposed to the end plate 3a. A diversion control pipe 24 and an outflow pipe 5 may be provided on the surface.

  Further, in this embodiment, it is assumed that the refrigerant flow path 11 group has a U-turn shape, but the same applies to a linear refrigerant flow path 11 group described in the second embodiment to be described later. Can be applied to.

  As described above, even if this heat exchanger is a plate fin laminated type, it is possible to make uniform the flow of refrigerant to each refrigerant flow path 11 and improve the heat exchange efficiency. It also has.

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

  However, in the heat exchanger shown in this embodiment, the portion corresponding to the header region of the plate fin laminate 2, that is, the header region corresponding portion of the end plates 3 a and 3 b covering both sides of the plate fin laminate 2 is connected to the connecting means 9. Since the end plates 3a and 3b are connected to each other, the header region corresponding portions of the end plates 3a and 3b can be prevented from expanding and deforming outward.

  That is, in FIG. 8, the high pressure of the refrigerant applied to the header region portion tends to be deformed upward in the upper end plate 3a and downward in the lower end plate 3b. Since the upward expansion deformation force applied to 3a also receives downward pressure from the refrigerant present in the inflow pipe 4 connected to the upper end plate 3a, the upward expansion deformation force is offset by this force. 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 surface 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 to remove the end plates 3a and 3b. Since the plate fin laminate 2 is pressed from the side, the strength of the portion corresponding to the header region of the end plates 3a and 3b is reinforced by the rigidity of the reinforcing plates 16a and 16b itself, and the expansion deformation of the portion corresponding to the header region is strengthened. It comes to suppress.

Moreover, even if it is set as the U-shaped flow path structure illustrated in this embodiment by providing the said reinforcement plates 16a and 16b, the expansion deformation | transformation of a header area | region corresponding part can be suppressed reliably. That is, the plate fin laminated body 2 of this embodiment makes the refrigerant flow path 11 provided in the plate fin 2a U-turn in a substantially U shape, and the header flow path 10 on the inlet side and the header flow path 14 on the outlet side are plate fins. Therefore, the pressure on the inlet side and the outlet side is doubled on the 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, even if it is a heat exchanger with a large amount of refrigerant or 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, the refrigerant can be used in a higher pressure state, and a highly efficient heat exchanger can be obtained.

  In addition, in this heat exchanger, by reducing the cross-sectional area of the concave grooves for the refrigerant flow passage formed in the plate fin 2a, the diameter of each flow passage area of the refrigerant flow passage 11 group is reduced, and the heat exchange efficiency is improved. It can improve and promote downsizing.

  In other words, the heat transfer efficiency is improved by reducing the diameter of the cross-sectional area of the refrigerant flow path 11 while preventing the expansion and deformation of the plate fin laminated body 2 at the portion corresponding to the header region, 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 providing the reinforcing plates 16a and 16b can be minimized, and the heat exchanger can be reduced in size. It is possible to prevent expansion deformation and improve heat exchange efficiency without impairing the process.

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

  Further, in the heat exchanger of the present embodiment, the refrigerant 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 (the length dimension is increased). ), The refrigerant flow path length can be increased.

  Thereby, the heat exchange efficiency of a refrigerant | coolant and air can be improved, a refrigerant | coolant can be reliably made into a supercooled state, and the efficiency of a refrigerating system can be improved. In addition, it is possible to reduce the size of the heat exchanger.

  In addition, since the slit 15 is formed between the forward flow path portion 11a and the return flow path portion 11b of the refrigerant flow channel 11 group, the refrigerant flow channel 11 group is formed. The refrigerant can be efficiently subcooled by preventing heat transfer from the forward path side flow path portion to the return path side flow path portion, and the heat exchange efficiency can be further improved.

  Further, in the heat exchanger of this embodiment, since the plurality of cut and raised protrusions 12 (12a, 12b) are provided in the flow channel region P of the plate fin laminate 2, the heat exchange efficiency in the flow channel region P is improved. Can be made. More specifically, the cut-and-raised protrusion 12 (12a, 12b) is formed so that the cut-and-raised edge Y faces the flow direction of the second fluid flowing between the laminated layers of the plate fins 2a. It is possible to make the interval between them constant, minimize the dead water area that tends to occur on the downstream side of the cut-and-raised projections 12 (12a, 12b), and cause the leading edge effect at the cut-and-raised edge Y portion. And since it cuts and raises so that it may oppose 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.

  Note that the cut and raised protrusions 12 (12a and 12b) provided on the plate fin 2a are arranged in a staggered manner with respect to the second fluid, and the arrangement structure of the cut and raised protrusions 12 is such that more leeward sides than the leeward side are formed. Various configurations can be presented, but it is only necessary to select an optimal configuration that improves the heat transfer coefficient in accordance with the specifications and configuration of the heat exchanger and the user's request.

  Further, since each of the cut and raised protrusions 12 (12a and 12b) is cut and raised so that the flow direction of the air flowing through the gap between the plate fin laminates 2 is opened, the flow direction of the air, that is, the refrigerant flow path. It is not necessary to steal the meat from the hollow plane 20 between the refrigerant flow paths in the direction intersecting with. Therefore, the hollow plane 20 between the refrigerant flow paths can be narrowed by an amount unnecessary for the meat stealing dimension as compared with the case where the cut and raised protrusion 12b is formed to be raised like a cylindrical protrusion or the like. The width of the plate fin 2a, in other words, the heat exchanger can be reduced in size.

  In addition, the plate fins 2a have narrow edges 20a and wide faces 20b at the edges of the long sides of the refrigerant flow passage 11 (see FIG. 11). Since the raised protrusion 12b is formed and its top surface is fixed to the narrow plane 20a of the adjacent plate fin 2a, it is not necessary to increase the width on the narrow plane 20a side. That is, by using the wide flat surface 20b to cut and raise on the wide flat surface side so as to be in contact with and fixed to the narrow flat surface 20a, the plate fin long side portion is not widened on the narrow flat surface side. The narrow plane can be left as it is, and the heat exchanger can be reduced in size accordingly.

  The cut and raised protrusions 12 (12a and 12b) are fixed to the adjacent plate fins 2a at the top surfaces of the plate fins 2a and the end plates 3a and 3b, respectively. The plate fin laminated body 2 can be improved in rigidity by also serving as a unitary connection.

  In particular, in the present embodiment, a portion on the extension line of the communication flow path 10b of the refrigerant flow path 11 group is a non-flow path portion 18, and a part of the protrusion 12 (12a, 12b) is utilized using the non-flow path portion 18, That is, since the second cut-and-raised projection 12b is provided, the stacking gap between the fin plates in the refrigerant flow path 11 group portion can be reliably maintained. As a result, the heat exchange efficiency can be improved by making the air flow in the refrigerant flow path 11 group portion stable without variation.

  Further, the first cut-and-raised protrusion 12a provided on the long side portion of the plate fin laminate 2 improves the strength of the long side edge portion of the plate fin laminate 2 which tends to be weak in strength. Is. In particular, the first cut-and-raised projections 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. It is possible to prevent deformation near the slit while improving the efficiency.

  The first cut-and-raised 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 of the refrigerant flow path 11 group There is a concern that heat conduction occurs between the path 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 edge portions as in the present embodiment, such a heat conduction concern is eliminated, which is effective. Further, the first cut and raised protrusion 12aa may be provided at a location away from the slit 15.

Further, the first cut and raised protrusions 12a provided on the long side portion of the plate fin laminate 2 and the 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. When the condensed water is generated in the plate fins 2a of the plate fin laminate 2 and the condensed water flows and is discharged along the edge of the plate fins 2a, the flow is blocked by the first cut-and-raised projections 12a. Therefore, it is possible to prevent various troubles from being accumulated in the cut-and-projection protrusion 12a, and to obtain a highly reliable heat exchanger.

  Further, in the heat exchanger of the present embodiment, the plate fin 2a is further cut and raised at the refrigerant flow path U-turn side end portion, so that the projection 22 (22a, 22b) is provided. It is possible to increase the heat exchange contribution at the end of the U-turn side of the fin 2a. 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 has 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 cut-and-raised protrusions 22 (22a, 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 cut-and-raised 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, and thus contributes to heat exchange that occurs downstream of the positioning screw hole 13 The dead water region having a low temperature can be minimized, and the heat exchange efficiency can be further improved accordingly.

  In addition, each of the cut and raised protrusions 22 (22a and 22b) is cut and formed in the same manner as the cut and raised protrusion 12 (12a and 12b) provided in the flow path region P, and the cut and raised edge Y is the first. Since the two fluids are opposed to each other, the leading edge effect can be produced at the cut and raised edge portion, and the heat exchange efficiency can be further improved accordingly.

  Since the plurality of cut-out projections 22 and 23 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 effectively exhibit a heat exchange function. In addition, the heat exchange contribution is high.

  Further, since each of the cut and raised protrusions 22 (22a, 22b) is fixed to the adjacent plate fin 2a and the short side portion of the plate fin 2a is connected and fixed in a laminated state, the plate fin laminate 2 It is also possible to increase the rigidity.

  In the present embodiment, the cut-and-raised projection 22 provided in the immediate vicinity of the downstream side of the positioning boss hole 13 is cut and raised in a substantially U-shaped cross section that opens in the flow direction of the second fluid. These may be configured to face each other as a pair of substantially L-shaped cuts and raised as long as the flow downstream of the positioning boss hole 13 is reduced.

(Embodiment 2)
As shown in FIGS. 23 to 26, the heat exchanger of the present embodiment is different from the heat exchanger of the first embodiment in the shape of the refrigerant flow path group and the installation position of the header opening. Parts having the same functions as those of the heat exchanger 1 are given the same reference numerals, and different parts will be mainly described.

FIG. 23 is a perspective view showing the appearance of the heat exchanger according to the second embodiment, and FIG. 24 is a plan view of the plate fins constituting the plate fin laminate of the plate fin laminated heat exchanger. FIG. 25 is an exploded view showing a part of the configuration of the plate fin in the heat exchanger, and FIG. 26 is a perspective view showing the refrigerant channel group part of the plate fin laminate in the heat exchanger in a cutaway view. FIG.

  23 to 26, in the heat exchanger of this embodiment, the refrigerant flow path 11 group provided in the plate fin 2a is linear, the header opening 8a on the inlet side on the one end side, and the other end. A header opening 8b on the outlet side is provided on the part side. An inlet pipe 4 is connected to the header opening 8a on the inlet side, and an outlet pipe 5 is connected to the header opening 8b on the outlet side, and the refrigerant flows out linearly from one end side to the other end side of the plate fin 2a. It is supposed to be.

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

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

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

  It should be noted that the cut-and-raised protrusions 22 provided on the U-turn side end of the plate fin 2a of the first embodiment may be appropriately provided in the header regions on both the inlet and outlet sides in this example. For example, it may be formed on the downstream side of the header flow path 10 serving as a dead water area, for example, in the same manner as the cut-and-raised protrusion 22 (22a, 22b).

(Embodiment 3)
The third embodiment is a refrigeration system configured using one of the heat exchangers of each of the embodiments described above.

  In this embodiment, an air conditioner will be described as an example of a refrigeration system. FIG. 27 is a refrigeration cycle diagram of the air conditioner, and FIG. 28 is a schematic cross-sectional view showing the indoor unit of the air conditioner.

  27 and 28, the air conditioner includes an outdoor unit 51 and an indoor unit 52 connected to the outdoor unit 51. The outdoor unit 51 is provided with a compressor 53 that compresses the refrigerant, a four-way valve 54 that switches the refrigerant circuit during the cooling and heating operation, an outdoor heat exchanger 55 that exchanges the heat of the refrigerant and the outside air, and a decompressor 56 that depressurizes the refrigerant. Has been. 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. A refrigerant in which two components or three components are mixed is used so that it is 350 or less, more desirably 150 or less.

During the cooling operation, the air conditioner switches the four-way valve 54 so that the discharge side of the compressor 53 and the outdoor heat exchanger 55 communicate with each other. 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, heat is exchanged with the outside air to dissipate the heat, and a high-pressure liquid refrigerant 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 the heat exchanger shown in each of the above embodiments for the outdoor heat exchanger 55 or the indoor heat exchanger 57, so that the heat exchanger is in the header region portion. Therefore, it is possible to provide a high-performance refrigeration system with high energy saving performance.

  The present invention makes it possible to make the diversion uniform by controlling the pressure loss distribution in the outlet header flow path, and to improve the heat exchange efficiency by equalizing the diversion and reducing the diameter of the flow path. It is possible to provide a high-performance refrigeration system with high energy saving performance using the same. 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 Heat exchanger 2 Plate fin laminated body 2a Plate fin 3, 3a, 3b End plate 4 Inflow pipe (inlet header)
5 Outflow pipe (outlet header)
6 1st plate fin 6a 1st plate-like member 6b 2nd plate-like member 7 2nd plate fin 8, 8a, 8b Header opening 9 Connection means (bolt and nut)
DESCRIPTION OF SYMBOLS 10 Header flow path 10a Peripheral flow path 10b Connection flow path 10c Multi-branch flow path 11 Refrigerant flow path (first fluid flow path)
11a Outward channel portion 11b Return channel portion 12 Cut and raised projections 12a and 12aa Projections (first cut and raised projections)
12b Protrusion (second cut and raised protrusion)
13 Through hole (positioning boss hole)
13a hole outer peripheral part (positioning boss hole outer peripheral part)
14 Header flow path 15 Slit 16a, 16b Reinforcement plate 17 Shunt collision wall 18 Non-flow path part 19a, 19b Plane end 20 Recessed flat part 20a Narrow plane 20b Wide plane 21 Fin flat part 22 (22a, 22b) Projection (cut) Raised protrusion)
24 Split flow control pipe 25 Refrigerant flow gap 26, 26a, 26b Split 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 (4)

A heat exchanger for causing a second fluid to flow between each plate fin stack of a plate fin stack having a flow path through which the first fluid flows, and exchanging heat between the first fluid and the second fluid,
The plate fin of the plate fin stack includes a flow channel region having a plurality of first fluid flow channels through which the first fluid flows in parallel, and a header flow channel communicating with each first fluid flow channel in the flow channel region. The first fluid flow path is formed by providing a concave groove in the plate fin, and the header flow path includes an inlet-side header flow path and an outlet-side header flow path. A heat exchanger in which a first fluid branch pipe that divides the first fluid into the first fluid channel is provided in the outlet-side header channel serving as an evaporation outlet of the first fluid.   The first fluid branch pipe includes a plurality of first fluid branch ports, and the first fluid branch port has an opening area on the first fluid inlet side larger than an opening area on the first fluid outlet side. The heat exchanger according to 1.   The heat according to claim 1 or 2, wherein the first fluid flow path formed in the plate fin is U-turned in a substantially U shape, and a header region communicating with the first fluid flow path is gathered on one end side of the plate fin. Exchanger.   The refrigeration system which used the heat exchanger which comprises a refrigerating cycle as the heat exchanger in any one of the said 1st-3rd.

Images