JP2018066534A - Heat exchanger and refrigeration system - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a small-sized and high-performance heat exchanger in which heat exchange efficiency is improved by equalizing a fluid branched flow rate to a first fluid flow passage from a header flow passage on an inlet side, and a refrigeration system using the same.SOLUTION: A fluid collision part 17 is provided on a first fluid flow passage group side of a connection flow passage 10b for connecting a header flow passage 10 on an inlet side and a first fluid flow passage 11 group, and a multiple-branching flow passage 10c is provided for guiding the fluid dispersed by colliding with the fluid collision part to the first fluid flow passage group. Thereby, a refrigerant from the connection flow passage of the header flow passage on the inlet side collides with the fluid collision part and disperses, and flows to the first fluid flow passage group from the multiple-branching flow passage, it is branched uniformly in each of the first fluid flow passages and heat exchange efficiency improves. Thus, a small-sized heat exchanger with high heat efficiency can be achieved.SELECTED DRAWING: Figure 17

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

  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. Therefore, improvement of heat exchange efficiency and downsizing are being promoted.

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

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

  This plate fin laminated heat exchanger performs heat exchange between a fluid flowing through a flow path formed in the plate fin and a second fluid flowing between the laminated plate fins. It is used for the air conditioner etc. (refer patent document 1).

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

Utility Model Registration No. 3192719

  In the plate fin laminated heat exchanger described in Patent Document 1, since the groove 101 is press-formed on the plate fin 102 to form the flow path 101, the cross-sectional area of the flow path 101 is set to a fin tube type heat transfer tube. The heat exchange efficiency can be increased.

  However, in the plate fin laminated heat exchanger having the above-described configuration, the refrigerant flows from the header-side flow path 105 on the inlet side to the flow path 101 via the communication flow path 106. However, the flow path 101 is divided into a plurality of lines. In the case where the flow path 101 is near the extension line of the communication flow path 106, a large flow rate flows, but the flow rates flowing in the other flow paths 101 are reduced, and the flow rates flowing through the flow paths 101 are biased, resulting in heat exchange efficiency. There was still room for improvement in improving heat exchange efficiency.

  The present invention has been made in view of the above points, and is a compact and high-performance heat exchanger that improves the heat exchange efficiency by equalizing the fluid flow rate from the inlet side header flow path to the first fluid flow path. And a refrigeration system using the same.

  In order to achieve the above object, the present invention provides a fluid collision part on the first fluid channel group side of the communication channel connecting the header channel on the inlet side and the first fluid channel group, and the fluid collision part. A multi-branch channel that guides the fluid that collides with the first fluid channel to the first fluid channel group is provided.

  Thereby, the refrigerant from the communication channel of the header channel on the inlet side collides and disperses in the fluid collision part, flows from the multi-branch channel to the first fluid channel group, and is evenly divided to each first fluid channel. This improves the heat exchange efficiency. Moreover, it is possible to improve the heat exchange efficiency by reducing the diameter of the flow path cross-sectional area of the first fluid flow path, and to make the heat exchanger small and highly heat efficient. be able to. And by using such a heat exchanger, it can be set as a compact and highly efficient refrigeration system with high energy-saving property.

  According to the above configuration, the present invention can provide a small heat exchanger with high heat exchange efficiency and a high-performance refrigeration system with high energy saving using the heat exchanger.

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 side view which shows the plate fin lamination | stacking state of the plate fin laminated body in the plate fin lamination type 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 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 The figure for demonstrating the refrigerant | coolant flow operation | movement of the plate fin 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 The perspective view which shows the external appearance of the plate fin lamination type heat exchanger in Embodiment 3 of this invention The perspective view which shows the state which extracted the shunt control pipe from the plate fin lamination type 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 Refrigeration cycle diagram of an air conditioner using the plate laminated heat exchanger of the present invention Schematic sectional view of the air conditioner Sectional view of a conventional plate fin stacked heat exchanger Plan view of plate fins in the conventional plate fin laminated 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 fin of the plate fin laminate includes 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 communicating with each first fluid flow path in the flow path area. A header region having a flow path and an outlet-side header flow path, and the first fluid flow path is formed by providing a concave groove in the plate fin,
In addition, a fluid collision part is provided on the first fluid channel side of the communication channel that connects the header channel on the inlet side and the first fluid channel group, and the fluid that collides with the fluid collision part and disperses the first fluid channel. A multi-branch channel that guides one fluid channel group is provided.

  Thereby, the refrigerant from the communication channel of the header channel on the inlet side collides and disperses in the fluid collision part, flows from the multi-branch channel to the first fluid channel group, and is evenly divided to each first fluid channel. This improves the heat exchange efficiency. Moreover, it is possible to improve the heat exchange efficiency by reducing the diameter of the flow path cross-sectional area of the first fluid flow path, and to make the heat exchanger small and highly heat efficient. be able to. And by using such a heat exchanger, it can be set as a compact and highly efficient refrigeration system with high energy-saving property.

  According to a second invention, in the first invention, the first fluid flow path formed in the plate fin is U-turned into a substantially U shape so as to be divided into an outward flow path section and a return flow path section. A header channel and a header channel on the outlet side are collectively arranged on one end side of the plate fin, and a communication channel connecting the forward channel portion of the first fluid channel group and the header channel on the inlet side Is provided so as to be deviated from the center of the forward flow path section toward the repetitive path flow path section, and a fluid collision section is provided in the communication flow path, and the fluid that collides with the fluid collision section and is dispersed is supplied to the first fluid flow path. The multi-branch flow path for guiding the road group is provided.

  Accordingly, the first fluid flow path can be lengthened without increasing the plate fin, heat exchange of the first fluid can be performed, and the heat exchange efficiency can be improved, and the first fluid flow path can be U-turned. As a result, even if the length from the header channel on the inlet side to the header channel on the outlet side of each channel of the first fluid channel group is different and the channel resistance is changed, the header channel on the inlet side is changed. Since the connecting flow path from the communication flow path is biased to the opposite side portion of the forward flow path section away from the return flow path section, the length of the branch flow path from the communication flow path to each forward flow path section is It becomes a shape that becomes longer as it gets closer to the path and cancels out, and can be evenly divided into each flow path of the first fluid flow path group. Therefore, it is possible to obtain a heat exchanger with higher heat exchange efficiency while promoting the downsizing of the heat exchanger by the synergistic effect by the U-turn of the first fluid flow path group and the uniform flow. Moreover, by making the first fluid flow path group U-turned, the first fluid flow path is lengthened without lengthening the plate fins, and the first fluid flow path from the forward path side flow path section to the return path side flow path section. The heat transfer can be prevented and the refrigerant can be efficiently subcooled, and the heat exchanger can be reduced in size while further improving the heat exchange efficiency.

  According to a third aspect of the present invention, in the first or second aspect of the present invention, the extended line portion of the communication flow path of the forward flow path portion of the first fluid flow path group is a non-flow path portion, and a protrusion is formed on the non-flow path portion. It is provided and the top part is made to contact the surface of the adjacent fin plate, and the lamination gap between fin plates is held.

  This makes it possible to maintain the stacking gap between the fin plates through which the second fluid flows using the uniform distribution structure of the refrigerant to the first fluid flow path group, and to stabilize the stacking gap between the fin plates without variation. As a result, the heat exchange efficiency can be further improved.

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

  As a result, this refrigeration system can be a high-performance refrigeration system with high energy savings because the heat exchanger is small and highly efficient.

  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. FIG. 3 is an exploded perspective view of the plate fin laminated heat exchanger, FIG. 4 is a side view showing the plate fin laminated state of the plate fin laminated body, and FIGS. 5 to 8 are views of the plate fin laminated heat exchanger. It is sectional drawing.

  As shown in FIGS. 1 to 8, the heat exchanger 1 of the present embodiment includes an inflow pipe (inlet header) 4 into which a refrigerant that is a first fluid flows, and a plurality of plate fins 2 a having a rectangular plate shape. It has the plate fin laminated body 2 comprised by laminating | stacking, and the outflow pipe | tube (outlet header) 5 which discharges | emits the refrigerant | coolant which flowed through the flow path in the plate fin 2a.

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. 9-19.

  9 to 12 are perspective views showing a part of the plate fin laminate cut away, and FIGS. 13 to 19 are views showing the structure of the plate fins.

  As shown in FIG. 9, the plate fin laminate 2 is configured by laminating plate fins 2 a (first plate fins 6 and second plate fins 7) having two types of flow path configurations.

As shown in FIG. 15, the first plate fin 6 and the second plate fin 7 of the plate fin 2 a are the same as the first plate-like member 6 a in which the refrigerant flow path configuration, which will be described in detail later, is press-molded. 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. 13, the plate fin 2 a (6, 7) has a header region H formed at one end in the longitudinal direction (left side in FIG. 13), 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 first fluid flow paths (hereinafter referred to as refrigerant flow paths) 11 through which the refrigerant that is the first fluid from the header opening 8a flows are formed in the flow path area P in parallel. Is folded at the other end of the first plate fin 2a (6, 7) (near the right end in FIG. 13) and connected to the header 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, as shown in an enlarged view in FIG. 14, a header flow path 10 through which the refrigerant from the header opening 8 a flows to the refrigerant flow path 11 group is formed around the header opening 8 a on the inflow side. The header flow path 10 includes an outer peripheral flow path 10a formed so as to bulge from the outer periphery of the header opening 8a, a single 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 that connects 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 8a on the inflow side is larger in diameter than the opening shape of the header opening 8b on the outlet side. This is a case where the heat exchanger is used as a condenser. In this case, the volume of the refrigerant after the heat exchange is reduced.

  In addition, the number of return-side flow passage portions 11b connected to the outlet-side header opening 8b is set to be smaller than the number of forward-passage flow passage portions 11a into which refrigerant flows from the inflow-side header opening 8a. This is the same reason that the diameters of the header openings 8a and 8b are different, because the volume of the refrigerant after heat exchange is reduced.

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

  In addition, when the said heat exchanger is used as an evaporator, the entrance and exit of a refrigerant | coolant becomes said reverse.

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 communication flow path 10b of the header flow path 10 is provided so as to be biased toward a portion of the forward path side flow path portion 11a opposite to the return path side flow path portion 11b. That is, as shown in FIG. 17, the width V from the center line O of the communication flow path 10b to the flow path 11a-1 at the end on the return path side flow path section 11b is opposite to the return path flow path section 11b. It is configured to be larger than the width W to the end flow path 11a-2. A shunting collision wall 17 is formed at the terminal end of the communication flow path 10b, that is, the opening connected to the forward flow path portion 11a, and the forward flow path portion on the extension line of the communication flow path 10b is non-flowing. It is a road 18. Therefore, the refrigerant from the communication flow path 10b collides with the flow dividing collision wall 17 and is divided (in the vertical direction in FIG. 17), and flows through the multi-flow path 10c on the downstream side of the communication flow path 10b in the non-flow path portion 18. It flows to each of the upper and lower flow path groups of the separated forward flow path section 11a.

  A header channel 14 is also formed in the header opening 8b on the outlet side, and this header channel 14 does not have the shunting collision wall 17, but the header channel provided in the header opening 8a on the inlet side. The shape is basically the same as 10. And in this embodiment, since the number of the return side flow path parts 11b of the refrigerant flow path 11 group is as few as two, the communication flow path 10b is provided on the approximate center line of the return path side flow path part 11b group.

  On the other hand, the plate fins 2a (6, 7) configured as described above are provided 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. 16A shows the first plate fin 6, FIG. 16B shows the second plate fin 7, and FIG. 16C shows the state when the two fin plates 2a (6, 7) are overlapped.

  As shown in FIG. 16, the first protrusions 12 a and 12 aa are formed on 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. 16A) and the side edges of the slit 15. As shown in FIG. 10, each of the planar end portions 19 b is in contact with the planar end portion 19 a of the long side edge portion of the second plate fin 7 that is adjacently opposed in the stacking direction. 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 apparent from FIG. 16A, the second protrusions 12b are formed at predetermined intervals between the flow paths of the refrigerant flow path 11 group, in this case, in the recessed flat surface portion 20 which becomes the non-flow path portion 18. 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. 16B, 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 projections 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. 19, the plate fin 2a (6) has a plurality of protrusions 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. 11, the plate fins 2a (6, 7) have positioning through holes (hereinafter referred to as positioning boss holes) 13 at the end portions 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 of this embodiment, the refrigerant that exchanges heat with the air flowing between the plate fin stacks of the plate fin stack 2 is connected from the header flow path 10 on the inlet side to the communication flow path 10b, the multi-branch flow path. 10c flows into the refrigerant flow path 11 group, but since the flow dividing collision wall 17 is provided on the downstream side of the communication flow path 10b, the refrigerant collides with the flow dividing collision wall 17 and splits up and down as shown in FIG. Then, the flow is diverted from the multi-branch channel 10c to each refrigerant channel 11. Therefore, it is possible to prevent the refrigerant from being extremely biased in the flow path on the extension line of the communication flow path 10b.

  Further, when the refrigerant flow passage 11 group is formed in a U shape and folded as in this embodiment, as is apparent from FIG. 17, each flow passage length of the refrigerant flow passage 11 group is: The U-shaped outer periphery, in other words, the longer the flow path side away from the slit 15, the longer the flow is, and a drift occurs due to the difference in flow path length.

  However, in this heat exchanger, the communication flow path 10b from the header flow path 10 is provided so as to be biased toward the repetitive flow path section side from the center line O of the forward flow path section 11a of the refrigerant flow path 11 group. Therefore, the drift can be suppressed and the refrigerant can be flowed substantially uniformly in each flow path.

  That is, in this heat exchanger, since the refrigerant flow passage 11 group is configured to make a U-turn, the flow from the header flow passage 10 on the inlet side to the header flow passage 14 on the outlet side of each flow passage in the refrigerant flow passage 11 group. Even if the flow path resistance changes due to different path lengths, the communication flow path 10b from the inlet-side header flow path 10 is biased to the repetitive path side flow path side of the forward path flow path section 11a. Therefore, the length of the branch flow path from the communication flow path 10b to each forward path side flow path part 11a becomes longer as it becomes closer to the return path side flow path part 11b, and cancels out. The flow can be evenly divided into each flow path.

  Therefore, it is possible to obtain a heat exchanger with higher heat exchange efficiency while promoting downsizing of the heat exchanger by a synergistic effect by making the U-turn of the refrigerant flow path 11 group and equalizing the flow distribution.

  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. Thus, heat transfer from the forward path side flow path portion to the return path side flow path portion can be prevented to efficiently exchange heat of the refrigerant, and further improvement in heat exchange efficiency can be achieved.

  As described above, this heat exchanger can improve the heat exchange efficiency by equalizing the fluid flow rate from the inlet side header flow path to the first fluid flow path, but also has the following effects. Is.

  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. 7, the high pressure of the refrigerant applied to the header flow path 10 tends to be deformed upward on the upper end plate 3a and downward on the lower end plate 3b. Since the upward expansion deformation force applied to the plate 3a is also received by the downward pressure from the refrigerant existing in the inflow pipe 4 connected to the upper end plate 3a, the upward expansion deformation force is offset by this force. Thus, outward expansion 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 as described above or an environment-friendly refrigerant with 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.

  Further, in the header region H of the plate fin laminate 2, since the flow passage area of the header flow passage 10 is the largest, the refrigerant pressure in the flow passage 10 portion is the highest. However, since the header flow path 10 is brazed in contact with the adjacent header flow path 10, the expansion deformation can be effectively prevented, and the expansion deformation of the header area corresponding portion can be more reliably prevented. be able to.

  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.

  In addition, although the strong pressure of the refrigerant | coolant added to the header area | region H of the said plate fin laminated body 2 may also deform | transform the cross section of the header flow path 10 in the header area | region H, the outer wall (flat surface) of the said header flow path 10 is Since the other header flow paths 10 adjacent in the stacking direction are in contact with each other in the stacking direction and are in a brazed state, the pressure generated by the refrigerant in each header flow path is canceled out and is not deformed. Can be high.

  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.

  Further, the refrigerant flow path 11 group is formed 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 combined on one end side, whereby the refrigerant pressure in the header region portion is doubled. Even if added, the header flow path corresponding portion connects the end plates 3a, 3b and further adds the reinforcing plates 16a, 16b to prevent deformation as described above. It can be surely prevented.

In the heat exchanger of this embodiment, a plurality of cut and raised protrusions 12 (12a, 12aa, 12b) are provided in the flow path region P of the plate fin laminate 2, and the heat exchange efficiency in the flow path region P is improved. Can be improved. More specifically, the cut and raised protrusions 12 (12a, 12aa, and 12b) are formed so that the cut and raised edges Y are opposed to the flow direction of the second fluid flowing between the stacks of the plate fins 2a. The spacing between the fin stacks is made constant, the dead water area that tends to occur on the downstream side of the cut-and-raised projections 12 (12a, 12aa, 12b) is minimized, and the leading edge effect is generated at the cut-and-raised edge Y portion. be able to. 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.

  It should be noted that the cut and raised protrusions 12 (12a, 12aa, and 12b) provided on the plate fins 2a are staggered with respect to the second fluid, or more of the leeward side 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 according to the specifications and configuration of the heat exchanger and the user's request.

  Each of the cut and raised protrusions 12 (12a, 12aa, and 12b) is formed by cutting and raising so that the flow direction of the air flowing through the gap between the plate fin laminates 2 is open. There is no need to steal meat from the hollow plane 20 between the refrigerant flow paths in the direction intersecting the flow paths. 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 edge of the long side portion of the plate fin 2a is formed into a narrow plane 20a and a wide plane 20b due to the alternately displaced arrangement of the refrigerant flow path 11 (see FIG. 10), and is cut to the wide plane 20b side. Since the raised protrusion 12a is formed and its top surface is fixed to the narrow plane 20a of the adjacent plate fin 2a, the width on the narrow plane 20a side does not need to be increased for forming the protrusion. 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.

  Further, since the cut and raised protrusions 12 (12a, 12aa, 12b) are fixed to the adjacent plate fins 2a at the top surfaces thereof when the plate fins 2a and the end plates 3a, 3b are joined by brazing. The role which connects the fin 2a integrally can also be fulfilled, and the rigidity of the plate fin laminated body 2 can be improved.

  In particular, in the present embodiment, a portion on the extension line of the communication flow path 10b of the 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 protrusion 12b is provided, the fin plate stacking gap in the refrigerant flow path 11 group portion can be reliably maintained. As a result, the heat exchange efficiency can be improved by making the air flow in the refrigerant flow path 11 group portion stable without variation.

  Further, the first cut-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 projections 12a provided on both side edge portions of the slit 15 may be formed as a shape straddling the slit 15, but in this case, the forward-side flow path portion 11a of the refrigerant flow path 11 group and the return path There is a concern that heat conduction occurs between the side flow path portion 11b and the heat insulation effect by 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.

  The first cut and raised protrusions 12a and 12aa 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 edges of the plate fin long side of the plate fin laminate 2. Therefore, when the condensed water is generated in the plate fin 2a of the plate fin laminate 2 and the condensed water flows along the edge of the plate fin 2a and is discharged, the first cut and raised protrusions 12a and 12aa are provided. Therefore, it is possible to prevent various troubles from occurring due to the flow being blocked by the cut-off projections 12a and 12aa, and 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 end of the refrigerant flow path U-turn side, so that the projection 22 (22, a22b) is provided. The degree of contribution to heat exchange at the end of the U-turn side of the fin 2a can be increased. Therefore, the heat exchange efficiency can be increased over the entire flow path region of the plate fin 2a, and the heat efficiency of the heat exchanger can be improved.

  In particular, the U-turn side end of the plate fin 2a 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 (22, a22b) 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, the cut and raised protrusions 22 (22a and 22b) are cut and formed in the same manner as the cut and raised protrusions 12 (12a, 12aa and 12b) provided in the flow path region P, and the cut and raised edges Y are formed. Therefore, 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 protrusions 22 (22, a22b) 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 exchange heat. The function is demonstrated and the heat exchange contribution is high.

  Further, the top portions of the cut and raised protrusions 22 (22, a22b) are fixed to the adjacent plate fins 2a and the short sides of the plate fins 2a are connected and fixed in a laminated state. It is also possible to increase the rigidity.

  In the present embodiment, the cut-and-raised protrusion 22 provided in the immediate vicinity of the downstream side of the positioning boss hole 13 is cut and raised in a cross-sectional shape that opens in the shape of a square toward the flow direction of the second fluid. However, this may be formed by cutting and raising it into a substantially L shape and providing it in a pair facing each other, as long as the flow downstream of the positioning boss hole 13 is reduced. Any form is acceptable.

(Embodiment 2)
As shown in FIGS. 20 to 23, the heat exchanger of the present embodiment is different from the heat exchanger of the first embodiment in the shape of the refrigerant flow path group and the installation position of the header opening. 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. 20 is a perspective view showing the appearance of the heat exchanger according to the second embodiment, and FIG. 21 is a plan view of the plate fins constituting the plate fin laminate of the plate fin laminated heat exchanger. FIG. 22 is an exploded view showing a part of the configuration of the plate fin in the heat exchanger, and FIG. 23 is a perspective view showing a section of the refrigerant channel group of the plate fin laminate in the heat exchanger. FIG.

  20 to 23, in the heat exchanger of the present 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. And the shunt collision wall 17 is provided in the linear part of the connection flow path 10b, as shown in FIG.

  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, as in the case of the cut-and-raised protrusion 22 (22, a22b).

(Embodiment 3)
The heat exchanger of this embodiment is suitable for use as an evaporator in which the refrigerant inlet and outlet of the heat exchanger are reversed. As shown in FIGS. 14 is provided with a refrigerant diversion control tube 24.

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

  24 is a perspective view showing the external appearance of the heat exchanger according to the third embodiment, FIG. 25 is a perspective view showing a state in which the flow dividing control pipe is extracted from the heat exchanger, and FIG. 26 is a plate fin laminate of the heat exchanger. FIG. 27 is a perspective view of the diversion control pipe in the heat exchanger, and FIG. 28 is a cross-sectional view of the diversion control pipe portion of the heat exchanger.

24 to 28, the diversion control pipe 24 is inserted into the outlet-side header opening 8b serving as the refrigerant evaporating outlet, that is, the outlet-side header flow path 14, and the tip thereof is shown in FIG. Thus, it extends to the end plate 3b on the side where the header opening is not provided, and is closed by the end plate 3b. The diversion control pipe 24 is constituted by a pipe having a smaller diameter than the inner diameter of the header opening 8b, and the refrigerant flow gap 25 is provided between the header opening inner face and the inner face.
A plurality of flow outlets 26 are formed at substantially equal intervals in the longitudinal direction, that is, in the stacking direction of the plate fins 2a.

  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.

  25 and 27, the flow dividing control pipe 24 is attached to the reinforcing plate 16a. 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 come to be.

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

  The outflow pipe 5 is also connected and fixed to the reinforcing plate 16a. Further, the flow dividing control pipe 24 may be configured such that its tip is closed and brought into contact with the end plate 3b.

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

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

  That is, in this heat exchanger, the 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. 28) 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. 28). In other words, the flow rate of the refrigerant may be uneven.

However, the flow dividing control pipe 24 is inserted inside the header opening 8b on the outlet side, and the opening area of the flow outlet 26a on the most outlet side is as shown in FIG. By reducing the diameter of the diverting port 26a provided in the portion close to the outlet side of the diverting control pipe 24 (the portion closer to the right side in FIG. 28), the pressure loss of the refrigerant passing through the diverting port is increased. Such a drift of the refrigerant flow rate does not occur, the amount of refrigerant in the first fluid flow path 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.

  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 24 and the outflow pipe 5 is directly connected to the outflow pipe 5 when used as an evaporator. Since it is made of a material that is smaller than the potential difference between the two, 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 prevented, Reliability in long-term use can be greatly 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 refrigerant flow path 11 group is assumed to have a U-turn shape, but the linear refrigerant flow path 11 group described in the second embodiment is similarly applied. can do.

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

  In this embodiment, an air conditioner will be described as an example of a refrigeration system. FIG. 29 is a refrigeration cycle diagram of the air conditioner, and FIG. 30 is a schematic cross-sectional view showing the indoor unit of the air conditioner.

  In FIG. 29 and FIG. 30, 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 improve the heat exchange efficiency by uniformizing the fluid flow rate from the header flow path on the inlet side to the first fluid flow path, and to use a small and high heat exchange efficiency heat exchanger. A high-performance refrigeration system with high energy savings can be provided. 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, projection (first cut and raised projection)
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 Dividing collision part (dividing collision wall)
18 Non-flow-path part 19a, 19b Plane edge part 20 Indentation plane part 20a Narrow plane 20b Wide plane 21 Fin plane part 22 (22a, 22b) Protrusion (cut-and-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 laminate includes 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 communicating with each first fluid flow path in the flow path area. A header region having a flow path and an outlet-side header flow path, and the first fluid flow path is formed by providing a concave groove in the plate fin,
In addition, a fluid collision part is provided on the first fluid channel side of the communication channel that connects the header channel on the inlet side and the first fluid channel group, and the fluid that collides with the fluid collision part and disperses the first fluid channel. A heat exchanger provided with a multi-branch channel for guiding to one fluid channel group.   The first fluid flow path formed in the plate fin is U-turned into a substantially U shape to divide the forward flow path section and the return flow path section, and the header flow path on the inlet side and the header flow path on the outlet side are divided into plate fins. And the connecting flow path connecting the forward flow path portion of the first fluid flow path group and the header flow path on the inlet side is a repetitive flow path from the center of the forward flow path portion. In addition to providing a fluid collision part in the communication channel, a multi-branch channel for guiding fluid dispersed by colliding with the fluid collision part to the first fluid channel group is provided. The heat exchanger according to claim 1.   A portion on the extension line of the communication flow path of the forward flow path portion of the first fluid flow path group is a non-flow path portion, a projection is provided on the non-flow path portion, and the top portion is brought into contact with the surface of the adjacent fin plate. The heat exchanger according to claim 1 or 2, wherein a stacking gap between the plates is maintained.   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