CN109312993B - Heat exchanger and refrigerating apparatus using the same - Google Patents

Heat exchanger and refrigerating apparatus using the same Download PDF

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Publication number
CN109312993B
CN109312993B CN201780038952.4A CN201780038952A CN109312993B CN 109312993 B CN109312993 B CN 109312993B CN 201780038952 A CN201780038952 A CN 201780038952A CN 109312993 B CN109312993 B CN 109312993B
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flow path
fluid
heat exchanger
plate
header
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CN201780038952.4A
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CN109312993A (en
Inventor
名越健二
山本宪昭
大城崇裕
奥村拓也
丸本一彦
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Panasonic Intellectual Property Management Co Ltd
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Panasonic Intellectual Property Management Co Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F28F3/04—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element

Abstract

In the present invention, a fluid collision portion (17) is provided on the group 1 of fluid flow paths (11) side of a connection flow path (10b) connecting the inlet-side header flow path (10) and the group 1 of fluid flow paths (11), and a multi-branch flow path (10c) is provided which guides a fluid, which collides with the fluid collision portion (17) and is dispersed, to the group 1 of fluid flow paths (11). According to this configuration, the refrigerant from the connecting channel (10b) in the inlet-side header channel (10) collides with the fluid collision section (17) and is dispersed, flows from the multi-branch channel (10c) to the group of 1 st fluid channels (11), and is uniformly distributed to the 1 st fluid channels (11), thereby improving heat exchange efficiency, and a heat exchanger that is small and has high heat efficiency can be configured.

Description

Heat exchanger and refrigerating apparatus using the same
Technical Field
The present invention relates to a heat exchanger and a refrigeration apparatus 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 apparatus using the same.
Background
In general, a refrigeration apparatus, such as an air conditioner or a refrigerator, performs cooling or heating by circulating a refrigerant compressed by a compressor through a heat exchanger, such as a condenser or an evaporator, to exchange heat with indoor air. However, the performance and energy saving of the apparatus are greatly influenced by the heat exchange efficiency of the heat exchanger. Therefore, the heat exchanger is strongly required to have high efficiency.
Among these, a heat exchanger of a refrigeration apparatus generally uses a fin-tube type heat exchanger in which fin groups penetrate heat transfer tubes, and the heat transfer tubes are reduced in diameter to improve heat exchange efficiency and reduce the size.
However, since there is a limit to the reduction in the diameter of such a heat transfer pipe, the improvement in heat exchange efficiency and the reduction in size are approaching the limit.
On the other hand, as a heat exchanger for use in heating, a plate fin stacked type heat exchanger in which exchange plate fins having flow paths are stacked is known.
This plate-fin stacked heat exchanger exchanges heat between a 1 st fluid, which is a refrigerant flowing through flow passages formed in the plate fins, and a 2 nd fluid flowing between the stacked plate fins, and is widely used in an air conditioner for a vehicle (see, for example, patent document 1).
Fig. 31 and 32 show a plate-fin stacked heat exchanger 100 described in patent document 1, in which plate fins 102 having flow paths 101 through which a refrigerant flows are stacked to form a plate-fin stacked body 103. End plates 104 are stacked on both sides of the plate-fin stacked body 103, and an inlet-side header flow path 105 and an outlet-side header flow path 106 are formed on both right and left ends of the flow path 101, thereby configuring the heat exchanger 100.
Documents of the prior art
Patent document
Patent document 1: utility model registration No. 3192719
Disclosure of Invention
In the plate-fin stacked heat exchanger described in patent document 1, since the flow paths 101 are formed by press-forming concave grooves in the plate fins 102, the cross-sectional area of the flow paths 101 can be made smaller than that of the heat transfer tubes used in the fin-tube type heat exchanger, and the heat exchange efficiency can be improved.
However, the refrigerant of the plate-fin stacked heat exchanger as described in patent document 1 flows from the inlet-side header flow passage 105 to the flow passage 101 through the connecting flow passage 101 a. However, when the flow channels 101 of one plate fin 2a are divided into a plurality of flow channels 101, a large amount of refrigerant flows through the flow channels 101 near the extension line connecting the flow channels 101a, but the flow rate of the refrigerant flowing through the other flow channels 101 is reduced. Therefore, the flow rates flowing through the respective flow paths 101 are not uniform, which adversely affects the heat exchange efficiency, and there is room for improvement in the improvement of the heat exchange efficiency.
The invention provides a small-sized high-performance heat exchanger and a refrigerating device using the same, wherein the heat exchanger is used for homogenizing the fluid flow distribution of the 1 st fluid flowing from an inlet side header flow passage to improve the heat exchange efficiency.
A fluid collision part is provided on the 1 st fluid flow path group side of a connection flow path connecting an inlet side header flow path and the 1 st fluid flow path group, and a multi-branch flow path guiding a fluid, which collides with the fluid collision part and is dispersed, to the 1 st fluid flow path group is provided.
Thus, the refrigerant from the connecting channel of the inlet-side header channel collides with the fluid collision portion, is dispersed, flows from the multi-branch channel to the 1 st fluid channel group, and is uniformly distributed to the 1 st fluid channels, so that the heat exchange efficiency can be improved. In addition, the flow path cross-sectional area of the 1 st fluid flow path can be reduced in diameter, and the heat exchange efficiency can be improved by reducing the diameter of the flow path, so that a heat exchanger that is small in size and high in heat efficiency can be provided. By using such a heat exchanger, a high-performance refrigeration apparatus having a compact structure and high energy saving performance can be provided.
Drawings
Fig. 1 is a perspective view showing an external appearance of a heat exchanger according to embodiment 1 of the present invention.
Fig. 2 is an exploded perspective view showing the heat exchanger according to embodiment 1 of the present invention in a vertically separated state.
Fig. 3 is an exploded perspective view of the heat exchanger according to embodiment 1 of the present invention.
Fig. 4 is a side view showing a state in which plate fins are stacked in the plate fin stacked body of the heat exchanger according to embodiment 1 of the present invention.
Fig. 5 is a cross-sectional view of 5-5 of fig. 1.
Fig. 6 is a cross-sectional view 6-6 of fig. 1.
Fig. 7 is a cross-sectional view of fig. 2 taken along line 7-7.
Fig. 8 is a perspective view showing a connection portion between an inflow tube and an outflow tube and a header opening portion of a heat exchanger according to embodiment 1 of the present invention in a cut-off manner.
Fig. 9 is a perspective view showing a 1 st fluid flow path group portion of a plate fin laminated body of a heat exchanger according to embodiment 1 of the present invention in a broken state.
Fig. 10 is a perspective view showing a first fluid flow path group portion of a heat exchanger according to embodiment 1 of the present invention in a partially cut-off state.
Fig. 11 is a perspective view showing a heat exchanger according to embodiment 1 of the present invention, with pin holes for positioning the plate-fin stacked body cut off.
Fig. 12 is a perspective view showing a plate-fin stacked body according to embodiment 1 of the present invention with a header opening portion cut off.
Fig. 13 is a plan view of a plate fin constituting a plate fin stacked body of a heat exchanger according to embodiment 1 of the present invention.
Fig. 14 is an enlarged plan view showing a header region of plate fins of a heat exchanger according to embodiment 1 of the present invention.
Fig. 15 is an exploded perspective view partially showing an enlarged structure of a plate fin of a heat exchanger according to embodiment 1 of the present invention.
Fig. 16A is a plan view of the 1 st plate fin of the heat exchanger according to embodiment 1 of the present invention.
Fig. 16B is a plan view of the 2 nd plate fin of the heat exchanger according to embodiment 1 of the present invention.
Fig. 16C is a plan view for explaining a state in which the 1 st plate fin and the 2 nd plate fin of the heat exchanger according to embodiment 1 of the present invention are overlapped.
Fig. 17 is a diagram for explaining the refrigerant flow operation of the plate fins of the heat exchanger according to embodiment 1 of the present invention.
Fig. 18 is an enlarged perspective view showing a protrusion provided in a flow path region of a plate fin of a heat exchanger according to embodiment 1 of the present invention.
Fig. 19 is an enlarged perspective view showing a projection provided at the U-turn side end portion of the 1 st fluid flow path of the plate fin of the heat exchanger according to embodiment 1 of the present invention.
Fig. 20 is an exploded perspective view showing a plate-fin stacked heat exchanger as a heat exchanger according to embodiment 2 of the present invention in a vertically separated state.
Fig. 21 is a plan view of a plate fin constituting a plate fin stacked body of a heat exchanger according to embodiment 2 of the present invention.
Fig. 22 is an exploded perspective view partially showing an enlarged structure of a plate fin of a heat exchanger according to embodiment 2 of the present invention.
Fig. 23 is a perspective view showing a 1 st fluid flow path group portion of a plate fin laminated body of a heat exchanger according to embodiment 2 of the present invention in a broken state.
Fig. 24 is a perspective view showing the appearance of a plate-fin stacked heat exchanger as a heat exchanger according to embodiment 3 of the present invention.
Fig. 25 is an exploded perspective view showing a state where the flow distribution control pipe is removed from the heat exchanger according to embodiment 3 of the present invention.
Fig. 26 is a perspective view showing a flow distribution control tube insertion portion of the plate fin laminate of the heat exchanger according to embodiment 3 of the present invention.
Fig. 27 is a perspective view of a flow dividing control tube of a heat exchanger according to embodiment 3 of the present invention.
Fig. 28 is a sectional view showing a flow dividing control tube portion of a heat exchanger according to embodiment 3 of the present invention.
Fig. 29 is a refrigeration cycle diagram of an air-conditioning apparatus using any of the heat exchangers according to embodiments 1 to 3 of the present invention.
Fig. 30 is a schematic cross-sectional view of an air-conditioning apparatus using any of the heat exchangers according to embodiments 1 to 3 of the present invention.
Fig. 31 is a cross-sectional view of a conventional plate-fin laminated heat exchanger.
Fig. 32 is a plan view of a plate fin of a conventional plate fin laminated heat exchanger.
Detailed Description
Hereinafter, embodiments of the present invention will be described with reference to the drawings.
The heat exchanger according to the present invention is not limited to the structure of the plate-fin stacked heat exchanger described in the following embodiments, and may include a structure of a heat exchanger equivalent to the technical idea described in the following embodiments.
The embodiments described below are merely examples of the present invention, and the structures, functions, operations, and the like described in the embodiments are merely examples and are not intended to limit the present invention.
(embodiment 1)
A plate-fin stacked heat exchanger as a heat exchanger according to embodiment 1 of the present invention will be described below with reference to the drawings.
Fig. 1 is a perspective view showing an appearance of a plate-fin stacked heat exchanger as a heat exchanger according to the present embodiment. Fig. 2 is an exploded perspective view showing the heat exchanger of the present embodiment in a vertically separated state. Fig. 3 is an exploded perspective view of the heat exchanger of the present embodiment. Fig. 4 is a side view showing a state in which plate fins are stacked in the heat exchanger according to the present embodiment. Fig. 5 to 8 are sectional views of the heat exchanger according to the present embodiment.
As shown in fig. 1 to 8, a heat exchanger 1 as a heat exchanger of the present embodiment includes an inlet tube 4 as an inlet-side header passage into which a refrigerant as a 1 st fluid flows, a plate fin laminate 2 formed by laminating a plurality of plate fins 2a having a rectangular plate shape, and an outlet tube 5 as an outlet-side header passage through which the refrigerant as the 1 st fluid flowing through the plate fins 2a is discharged.
On both sides (upper and lower sides in fig. 1) in the stacking direction of the plate fin laminate 2, end plates 3a, 3b having substantially the same shape as the plate fins 2a in plan view are provided. The end plates 3a and 3b are formed of a rigid plate material, and are formed by, for example, grinding a metal material such as aluminum, an aluminum alloy, or stainless steel.
The end plates 3a and 3b and the plurality of plate fins 2a are integrally joined by brazing in a stacked state, but may be joined by other heat-resistant fixing methods, for example, chemical joining members.
In the present embodiment, the end plates 3a and 3b on both sides of the plate-fin laminated body 2 are fastened and fixed at both longitudinal end portions thereof by fastening means 9 such as bolts and nuts or rivet pins. That is, the end plates 3a and 3b on both sides of the plate-fin stacked body mechanically connect and fix the plate-fin stacked body 2 so as to sandwich the plate-fin stacked body 2.
In the present embodiment, the reinforcing plates 16a and 16b are further arranged at the header region corresponding portions of the one end portions (left end portions in fig. 1) in the longitudinal direction of the end plates 3a and 3b, and the reinforcing plates 16a and 16b are fastened and fixed by the fastening mechanism 9, whereby the end plates 3a and 3b are also included, and the plate-fin laminated body 2 is mechanically sandwiched.
The reinforcing plates 16a and 16b are also formed of a rigid plate material, for example, a metal material such as stainless steel or aluminum alloy, as in the case of the end plates 3a and 3b, but it is preferable that the reinforcing plates 16a and 16b be a material having higher rigidity or have a thicker plate thickness than the end plates 3a and 3 b.
The plate fins 2a have a plurality of parallel 1 st fluid flow path groups (the 1 st fluid flow path structure including the plate fins 2a of the 1 st fluid flow path group will be described later) in which the 1 st fluid refrigerant flows, the 1 st fluid flow path group being formed in a substantially U-shape, and the inlet tubes 4 and the outlet tubes 5 connected thereto are arranged so as to be concentrated on one end portion side (upper side in fig. 1) of the end plate 3a on one side of the plate fin laminate 2.
In the heat exchanger 1 configured as described above, the refrigerant flowing in from the inflow tube 4 flows in parallel in the longitudinal direction through the plurality of flow path groups formed inside the respective plate fins 2a constituting the plate fin stacked body 2, makes a U-turn, and is discharged from the return flow outlet tube 5. On the other hand, air as the 2 nd fluid passes through gaps formed between the stacked layers of the plate fins 2a constituting the plate fin stacked body 2. Thereby, heat exchange between the refrigerant as the 1 st fluid and the air as the 2 nd fluid is performed.
Next, a plate fin laminate 2 as a main body of the heat exchanger 1 and plate fins 2a constituting the plate fin laminate 2 will be described with reference to fig. 9 to 19.
Fig. 9 is a perspective view showing a 1 st fluid flow path group portion of the plate fin laminated body of the heat exchanger according to the present embodiment in a broken state. Fig. 10 is a perspective view showing a first fluid flow path group portion of the heat exchanger according to the present embodiment in a broken state. Fig. 11 is a perspective view showing a pin hole portion for positioning the plate fin laminate of the heat exchanger according to the present embodiment in a broken state. Fig. 12 is a perspective view showing a header opening portion of the plate-fin stacked body of the heat exchanger according to the present embodiment in a cut-off manner. Fig. 13 is a plan view of a plate fin constituting the plate fin stacked body of the heat exchanger according to the present embodiment. Fig. 14 is an enlarged plan view showing a header region of the plate fin of the heat exchanger according to the present embodiment. Fig. 15 is an exploded perspective view partially showing an enlarged structure of a plate fin of the heat exchanger according to the present embodiment. Fig. 16A is a plan view of the 1 st plate fin of the heat exchanger of the present embodiment. Fig. 16B is a plan view of the 2 nd plate fin of the heat exchanger according to the present embodiment. Fig. 16C is a plan view for explaining a state in which the 1 st plate fin and the 2 nd plate fin of the heat exchanger of the present embodiment are overlapped. Fig. 17 is a diagram for explaining the refrigerant flow operation of the plate fins of the heat exchanger according to the present embodiment. Fig. 18 is an enlarged perspective view showing protrusions provided in the flow path regions of the plate fins of the heat exchanger of the present embodiment. Fig. 19 is an enlarged perspective view showing a protrusion provided at the U-turn side end portion of the 1 st fluid flow path of the plate fin of the heat exchanger of the present embodiment.
As shown in fig. 9, the plate fins 2a of the heat exchanger of the present embodiment are configured by stacking the 1 st plate fins 6 and the 2 nd plate fins 7 having different flow path structures.
As shown in FIG. 15, the 1 st plate fin 6 of the plate fins 2a is formed by brazing a 1 st plate-like member 6a, which is press-formed with a 1 st fluid flow passage structure described later in detail, to a 2 nd plate-like member 6b having the same structure as the 1 st plate-like member in a face-to-face manner. Although not shown, the 2 nd plate fins 7 are also configured by brazing 2 plate-like members face to face in the same manner as the 1 st plate fins 6. The 1 st plate-like member 6a and the 2 nd plate-like member 6b are made of a thin metal plate such as aluminum, an aluminum alloy, or stainless steel.
The flow path structure formed in the plate fin 2a will be described below.
The 1 st plate fins 6 and the 2 nd plate fins 7 of the plate fins 2a have the same configuration except for the position shift from the 1 st fluid flow passages 11 described later, and therefore only the 1 st plate fins 6 will be illustrated in fig. 13 to 15.
As shown in fig. 13 showing the 1 st plate fin 6, the plate fin 2a (the 1 st plate fin 6, the 2 nd plate fin 7) has a header region H formed at one end (the left side in fig. 13) in the longitudinal direction, and the other region is a flow path region P. In the header region H, an inlet-side header opening 8a and an outlet-side header opening 8b are both formed, and an inflow pipe 4 and an outflow pipe 5 are connected thereto (see fig. 8).
Further, a plurality of 1 st fluid flow paths 11 through which the refrigerant as the 1 st fluid flows from the header openings 8a are formed in parallel in the flow path region P, and the 1 st fluid flow paths 11 are folded back at the other end portions (the vicinity of the right-side end portion in fig. 13) of the plate fins 2a (the 1 st plate fins 6, the 2 nd plate fins 7) and connected to the header openings 8b on the outlet side. Specifically, the 1 st fluid flow path 11 group is formed by a forward flow path portion 11a connected to the inlet-side header opening 8a and a return flow path portion 11b connected to the outlet-side header opening 8b, and is folded back in a U-shape. The refrigerant from the inlet-side header opening 8a then turns from the outward flow path portion 11a to the return flow path portion 11b U and flows toward the outlet-side header opening 8 b.
Further, around the inlet-side header opening 8a, as shown enlarged in fig. 14, an inlet-side header passage 10 is formed through which the refrigerant from the header opening 8a flows to the 1 st fluid passage 11 group. The inlet-side header passage 10 includes an outer peripheral passage 10a formed so as to bulge from the outer periphery of the header opening 8a, one connection passage 10b extending toward the 1 st fluid passage 11 group side of the outer peripheral passage 10a, and a multi-branch passage 10c connecting the connection passage 10b and each of the 1 st fluid passage 11 groups.
The outer peripheral flow path 10a, the connecting flow path 10b, and the multi-branch flow path 10c of the inlet-side header flow path 10 are formed wider than the respective 1 st fluid flow paths 11 arranged in parallel in the flow path region P, and have a rectangular shape in a vertical cross-sectional shape perpendicular to the flow direction.
Further, the opening shape of the inlet-side header opening 8a is larger in diameter than the outlet-side header opening 8 b. This is because this is the case where the heat exchanger is used as a condenser, and in this case, the volume of the refrigerant after heat exchange becomes small.
The number of return-side flow path portions 11b connected to the outlet-side header opening 8b is set to be smaller than the number of outward-side flow path portions 11a into which the refrigerant flows from the inlet-side header opening 8 a. This is because the volume of the refrigerant after heat exchange is reduced for the same reason as the difference in the diameters of the header openings 8a and 8 b.
In the present embodiment, the number of the forward flow path portions 11a is 7 and the number of the return flow path portions 11b is 2, but the present invention is not limited thereto.
In addition, when this heat exchanger is used as an evaporator, the inlet and outlet for the refrigerant is configured in reverse to the configuration described above.
In the plate fins 2a (the 1 st plate fins 6, the 2 nd plate fins 7), slits 15 are formed between a region where the outward flow path side flow path portion 11a into which the refrigerant from the inlet side header opening 8a flows and a region where the return flow path side flow path portion 11b to the outlet side header opening 8b is formed, in order to reduce (insulate) the heat conduction between the refrigerants in the plate fins 2a (the 1 st plate fins 6, the 2 nd plate fins 7).
The connection channel 10b of the inlet-side header channel 10 is provided in a portion of the outward-side channel 11a that is offset from the return-side channel 11 b. That is, as shown in fig. 17, the width V of the flow path 11aa from the center line O of the connecting flow path 10b connected to the forward flow path portion 11a via the multi-branch flow path 10c to the end on the return flow path portion 11b side is larger than the width W of the flow path 11ab from the center line O to the end on the opposite side to the return flow path portion 11 b. A fluid collision wall 17 as a fluid collision portion is formed at the end of the connection channel 10b on the header opening 8a side, that is, at the opening portion connected to the forward channel portion 11a, and the forward channel portion located on the extension of the connection channel 10b becomes a non-channel portion 18. Therefore, the refrigerant from the connecting channel 10b collides with the fluid collision wall 17 and is split (split vertically in fig. 17), and flows through the multi-branch channel 10c on the downstream side of the connecting channel 10b to the respective channel groups above and below the outward channel 11a divided by the non-channel 18.
In addition, an outlet-side header passage 14 is also formed in the outlet-side header opening 8b, and the outlet-side header passage 14 is formed in substantially the same shape as the inlet-side header passage 10 provided in the inlet-side header opening 8a except that the fluid collision wall 17 is not provided. In this embodiment, since the number of the return-side channel parts 11b of the 1 st fluid channel 11 group is as small as two, the connection channel 10b is provided substantially on the center line of the return-side channel part 11b group.
In the case of the above-structured 2a (1 st plate fin 6, 2 nd plate fin 7), in the present embodiment, as shown in fig. 16a, the 1 st plate fin 6 has a plurality of projections 12(1 st projections 12a, 12aa, 2 nd projections 12b) formed at predetermined intervals in the longitudinal direction in the flow passage region P (see fig. 13).
Fig. 16A is a plan view of the 1 st plate fin 6. Fig. 16B is a plan view of the 2 nd plate fin 7. Fig. 16C is a plan view showing a state where the 1 st plate fins 6 and the 2 nd plate fins 7 are overlapped.
As shown in fig. 16A to 16C, the 1 st projections 12a, 12aa are formed on the flat end portions 19a of the long side edge portions of the plate fins (the long side edge portions on both the left and right sides in fig. 16A and 16C) and the flat end portions 19b of both side edge portions of the slit 15, respectively. As shown in fig. 10, the 1 st projection 12a abuts on the flat end 19a of the long side edge of the 2 nd plate fin 7 adjacent to and facing the 1 st plate fin 6 in the stacking direction, and although not shown, the 1 st projection 12aa does not abut on the flat end 19b of both side edges of the slit 15, and the stacking distance between the 1 st plate fin 6 and the 2 nd plate fin 7 is defined to be a predetermined length. The 1 st projection 12a is formed so as to be located inward from the end edge of each long-side edge portion, for example, 1mm or more (the 1 st fluid channel 11 side) inward from the end edge.
As shown in fig. 16A, the 2 nd projections 12b are formed at predetermined intervals between the channels of the 1 st fluid channel 11 group, in this example, recessed flat portions 20 serving as the non-channel portions 18. As shown in fig. 16B, the 2 nd protrusions 12B abut on the recessed planar portions 20 of the 2 nd plate fins 7 adjacent to the 1 st plate fins 6 in the stacking direction, and the stacking distance between the 1 st plate fins 6 and the 2 nd plate fins 7 is defined to be a predetermined length, as with the 1 st protrusions 12 a.
Further, as shown in fig. 18, the projections 12 (the 1 st projections 12a, 12aa and the 2 nd projections 12b) are formed by cutting out the planar end portions 19a, 19b of the 1 st plate fin 6 and a part of the recessed planar portion 20. The cut-formed end edges Y of the projections 12 (the 1 st projections 12a, 12aa, the 2 nd projections 12b) face the flow direction indicated by the arrow of the 2 nd fluid flowing between the stacked layers of the plate fins 2a, and the cut-formed raised pieces Z are along the flow direction of the 2 nd fluid. In the present embodiment, the cross section of the opening in the flow direction of the 2 nd fluid is cut into a substantially コ shape.
The respective projections 12(1 st projections 12a, 12aa, 2 nd projections 12b) are configured to integrally connect the respective plate fins 2a (1 st plate fins 6, 2 nd plate fins 7) by fixing the top surfaces thereof to the adjacent plate fins 2a (1 st plate fins 6, 2 nd plate fins 7) at the time of brazing the respective plate fins 2a (1 st plate fins 6, 2 nd plate fins 7) and the end plates 3(3a, 3 b).
The 1 st projections 12a, 12aa and the 2 nd projections 12b may be arranged linearly along the flow direction of the 2 nd fluid (air), or may be arranged in a staggered manner.
Further, as shown in fig. 19, the plate fin 2a (6) is further formed with a plurality of projections 22 (3 rd projection 22a, 4 th projection 22b) on the fin flat surface portion 21 at the end portion on the turn-back side of the flow path region P in which the 1 st fluid flow path 11 group is U-turned. The projections 22 (the 3 rd projection 22a and the 4 th projection 22b) are also formed by cutting the fin flat surface portion 21. The cut-formed edges Y of the projections 22 (the 3 rd projection 22a and the 4 th projection 22b) face the flow of the 2 nd fluid. The projections 22 (the 3 rd projection 22a, the 4 th projection 22b) are provided on the downstream side of the positioning pin hole 13, and the 3 rd projection 22a nearest to the downstream side of the positioning pin hole 13 is cut out in a shape contracting the fluid flow on the downstream side of the positioning pin hole 13, for example, in a form opened in an ハ -shape in the 2 nd fluid flow direction. The 4 th projections 22b on the downstream side of the 3 rd projection 22a are arranged alternately so that the center line thereof is shifted from the center line of the next 4 th projection 22b on the downstream side.
In addition, like the projections 12 (the 1 st projections 12a, 12aa, and the 2 nd projections 12b), the respective projections 22 (the 3 rd projections 22a and the 4 th projections 22b) are also abutted and fixed to the adjacent plate fins 2a (7) so that the gaps between the adjacent plate fins 2a are defined to a constant length and the plate fins 2a are connected to each other.
As shown in fig. 11, in the plate fins 2a (the 1 st plate fin 6, the 2 nd plate fin 7), positioning pin holes 13 as positioning through-holes are formed at the end portions of the header region H and the flow path region P. The positioning pin holes 13 are also formed in the end plates 3a, 3b and the reinforcing plates 16a, 16b laminated on both sides of the plate fins 2a (the 1 st plate fin 6, the 2 nd plate fin 7). In addition, the positioning pin holes 13 allow a positioning pin jig to be attached when stacking a plurality of plate fins 2a (the 1 st plate fin 6, the 2 nd plate fin 7) to perform highly accurate stacking of the other plate fins 2a, and in this embodiment, a mode is adopted in which fastening means 9 (see fig. 3) such as bolts for fastening the reinforcing plates 16a, 16b and the end plates 3a, 3b of the plate fin stacked body 2 also serve as the positioning pin jig.
In the outer peripheral portions of the positioning pin holes 13 provided at both end portions of the plate fins 2a (the 1 st plate fin 6, the 2 nd plate fin 7), hole outer peripheral portions (hereinafter referred to as positioning pin hole outer peripheral portions) 13a that bulge out in the upper and lower directions are formed. The positioning pin hole outer peripheral portion 13a forms a space different from the flow path of the flowing refrigerant, and as shown in fig. 11, the adjacent plate fins 2a (the 1 st plate fin 6, the 2 nd plate fin 7) in the stacking direction abut against each other to serve as a header region support portion that holds the stacking gap of the plate fins 2 a.
The positioning pin hole outer peripheral portion 13a formed around the positioning pin hole 13 is brazed and fixed to the inlet-side header flow path 10, the outlet-side header flow path 14, and the positioning pin hole outer peripheral portion 13a facing each other in the stacking direction, together with the inlet-side header flow path 10 and the outlet-side header flow path 14 formed in the header region H shown in fig. 13, thereby integrally connecting the end portions of the plate fins 2a (the 1 st plate fin 6, the 2 nd plate fin 7).
The 1 st fluid flow path 11 according to the present invention is described, for example, as having a circular cross-sectional shape perpendicular to the direction in which the refrigerant flows, but includes a rectangular shape in addition to the circular shape.
In the present embodiment, the 1 st fluid channel 11 is described as having a shape protruding in both sides in the stacking direction, but may be formed so as to protrude only in one side in the stacking direction. In addition, in the present invention, the circular shape also includes a circle, an ellipse, and a compound curve shape formed by a closed curve.
The heat exchanger of the present embodiment is configured as described above, and its operational effects will be described below.
First, the flow of the refrigerant and the heat exchange action are explained.
The refrigerant flows from the inflow tubes 4 connected to one end portion side of the plate fin laminated body 2, through the inlet-side header opening 8a, and further through the outer peripheral flow paths 10a, the connecting flow paths 10b, and the multi-branch flow paths 10c around the header openings 8a, which are the header flow paths 10 of the respective plate fins 2a, to the group of the 1 st fluid flow paths 11. The refrigerant flowing through the 1 st fluid flow channel 11 group of the plate fins 2a is turned back from the outward flow channel 11a to the return flow channel 11b, and flows from the outlet pipe 5 to the refrigerant circuit of the refrigeration apparatus through the outlet-side header flow channel 14 and the outlet-side header opening 8 b.
When the refrigerant flows through the 1 st fluid flow path 11, the refrigerant exchanges heat with air passing through the stacked plate fins 2a of the plate fin stacked body 2.
Here, the heat exchanger of the present embodiment has the following structure: as shown in fig. 14, the refrigerant that exchanges heat with the air flowing between the stacked plate fins 2a of the plate fin stacked body 2 flows from the inlet-side header flow path 10 to the group of the connection flow path 10b, the multi-branch flow path 10c, and the 1 st fluid flow path 11. Here, since the fluid collision wall 17 is provided on the downstream side of the connection channel 10b, the refrigerant collides with the fluid collision wall 17, is split in the vertical direction shown in fig. 14, and is split from the multi-branch channel 10c to each of the 1 st fluid channels 11. This prevents the refrigerant from traveling extremely unevenly in the flow path at the portion on the extension line of the connecting flow path 10b connected to the inlet-side header flow path 10.
Further, when the 1 st fluid flow channel 11 group is folded back in a U-shape as in the present embodiment, as can be understood from fig. 17, the longer the flow channel length of each of the 1 st fluid flow channel 11 group is located away from the outer periphery of the U-shape, in other words, the longer the flow channel side of the slit 15, a drift due to the difference in the flow channel length occurs.
However, in this heat exchanger, as shown in fig. 17, since the connection channel 10b from the inlet-side header channel 10 is provided so as to be offset to the reverse return channel side with respect to the center line (not shown) of the outward channel side channel 11a of the group 1 of the fluid channels 11, the refrigerant can flow substantially uniformly through the respective channels while suppressing drift.
That is, in this heat exchanger, even if the flow path resistance varies depending on the flow path length from the inlet-side header flow path 10 to the outlet-side header flow path 14 of each flow path of the 1 st fluid flow path 11 group due to the structure in which the 1 st fluid flow path 11 group is U-turned, the connection flow path 10b from the inlet-side header flow path 10 is located at a position shifted to the return-side flow path side of the forward flow path 11 a. Therefore, the length of the branch path from the connection flow path 10b to each outward flow path portion 11a is longer as it approaches the return flow path portion 11b, so that the difference in resistance is offset, and the flow can be uniformly branched into the respective flow paths of the 1 st fluid flow path 11 group.
Therefore, the heat exchanger 1 having a higher heat exchange efficiency can be obtained while advancing miniaturization by the synergistic effect of the U-turn of the group 1 of the fluid flow paths 11 and the uniformization of the split flow.
Further, since the slit 15 is formed between the outward flow path portion 11a and the return flow path portion 11b of the 1 st fluid flow path 11 group to insulate them, heat transfer from the outward flow path portion 11a to the return flow path portion 11b of the 1 st fluid flow path 11 group can be effectively prevented, the heat exchange amount of the refrigerant can be increased, and the heat exchange efficiency can be further improved.
As described above, this heat exchanger can make the flow rate of the fluid distributed from the inlet-side header flow path 10 to the 1 st fluid flow path 11 uniform, and improve the heat exchange efficiency, and also has the following effects.
That is, in this heat exchanger, a strong pressure of the refrigerant is applied to the header region H (see fig. 13) of the plate-fin laminated body 2, and the portion of the header region H having the header flow channels 10 and the like are subjected to expansion deformation.
However, in the heat exchanger shown in the present embodiment, the header region corresponding portions of the plate fin laminated body 2, that is, the header region corresponding portions of the end plates 3a and 3b covering both side portions of the plate fin laminated body 2, are connected to each other by the connecting mechanism 9. Therefore, the header region corresponding portions of the end plates 3a, 3b can be prevented from being deformed by expansion outward.
That is, in fig. 7, the high pressure of the refrigerant applied to the inlet-side header flow path 10 is intended to deform the upper end plate 3a upward and to deform the lower end plate 3b downward. However, the upward expansion deformation force applied to the upper end plate 3a is also subjected to the downward pressure from the refrigerant present in the inflow pipe 4 connected to the upper end plate 3a, and therefore the upward expansion deformation force is offset by this force, and the outward expansion deformation of the header region corresponding portion of the upper end plate 3a can be prevented. Further, the downward expansion deformation force applied to the lower end plate 3b can be suppressed by connecting the end plate 3b and the upper end plate 3a as described above. As a result, the entire expansion deformation can be alleviated.
In particular, in the present embodiment, the reinforcing plates 16a, 16b are provided on the outer surfaces of the header region corresponding portions of the end plates 3a, 3b, the reinforcing plates 16a, 16b are connected to each other by the connecting mechanism 9 (see fig. 3), and the end plates 3a, 3b are pressed against the plate fin laminated body 2 from the outside. Therefore, the strength of the header region corresponding portions of the end plates 3a, 3b is reinforced by the rigidity of the reinforcing plates 16a, 16b themselves, and the expansion deformation of the header region corresponding portions can be strongly suppressed.
Further, even when the U-shaped flow path structure exemplified in the present embodiment is configured by providing the reinforcing plates 16a and 16b, the expansion deformation of the portion corresponding to the header region can be reliably suppressed. That is, in the plate fin laminate 2 of the present embodiment, the 1 st fluid flow channels 11 provided in the plate fins 2a are U-turned in a U-shape to concentrate the inlet-side header flow channels 10 and the outlet-side header flow channels 14 on one end side of the plate fins, and therefore, double pressures on the inlet side and the outlet side are applied to these portions. However, with the structure shown in the present embodiment, even if such a double refrigerant pressure is applied, the expansion deformation can be reliably prevented against the pressure.
Therefore, even in the case of the heat exchanger having a large amount of refrigerant or the environment-compatible refrigerant having a high compression ratio as described above, the expansion deformation of the header region portion of the plate fin laminated body 2 can be prevented. As a result, for example, a refrigerant in a high-pressure state such as an environment-friendly refrigerant having a high compression ratio can be used, and a heat exchanger having high efficiency can be provided.
In this heat exchanger, the sectional area of the concave groove for the 1 st fluid flow path formed in the plate fin 2a can be reduced to reduce the diameter of each flow path area of the 1 st fluid flow path 11 group (see fig. 6), thereby improving heat exchange efficiency and promoting miniaturization.
That is, the flow channel cross-sectional area of the 1 st fluid flow channel 11 can be reduced in diameter while preventing the expansion deformation of the header region corresponding portion of the plate fin laminate 2, thereby improving the heat exchange efficiency and promoting the reduction in size.
Further, since the reinforcing plates 16a and 16b are only required to be provided at the header region corresponding portions, the increase in volume due to the provision of the reinforcing plates 16a and 16b can be minimized, and the prevention of expansion deformation and the improvement of heat exchange efficiency can be achieved without impairing the downsizing of the heat exchanger.
In the header region H (see fig. 13) of the plate-fin laminated body 2, the inlet-side header flow path 10 has the largest flow path area, and therefore the refrigerant pressure in the inlet-side header flow path 10 portion is also the highest. However, since the inlet-side header flow path 10 is connected to and brazed to the adjacent inlet-side header flow path 10, the expansion deformation thereof can be effectively prevented, and the expansion deformation of the header region corresponding portion can be more reliably prevented.
Further, the coupling mechanism 9 such as a bolt can be used as a guide pin (jig) when the plate fin 2a, the end plates 3a, 3b, and the reinforcing plates 16a, 16b are stacked, whereby the stacking accuracy can be improved and the productivity can be improved.
Further, although there is a problem that the strong pressure of the refrigerant applied to the header region H of the plate fin laminate 2 deforms the cross section of the inlet-side header flow paths 10 of the header region H, since the outer wall (flat surface) of the inlet-side header flow path 10 is in a state of being brought into contact with and brazed to another inlet-side header flow path 10 adjacent in the stacking direction, the pressure generated by the refrigerant in each header flow path is cancelled out, and a structure that is not deformed and has high reliability can be obtained.
In the heat exchanger of the present embodiment, the group of the 1 st fluid flow paths 11 provided in the plate fins 2a is formed in a substantially U shape and folded back, so that the length of the 1 st fluid flow path can be increased without increasing the size of the plate fins 2a (increasing the length dimension).
This improves the heat exchange efficiency between the refrigerant and the air, and reliably brings the refrigerant into an overcooled state, thereby improving the efficiency of the refrigeration apparatus. Further, the heat exchanger can be miniaturized.
Further, even if the refrigerant pressure in the portion of the header region H is doubly applied by forming the group of the 1 st fluid flow paths 11 in a substantially U-shape and concentrating the inlet-side header flow path 10 and the outlet-side header flow path 14 on the one end side, the header flow path corresponding portion connects the end plates 3a, 3b to each other as already described, and further increasing the reinforcement plates 16a, 16b prevents deformation, so that the expansion deformation of the corresponding portion of the header region H can be reliably prevented.
In the heat exchanger of the present embodiment, the plurality of projections 12 (the 1 st projections 12a, 12aa, the 2 nd projection 12b) are provided in the flow path region P of the plate-fin stacked body 2, and the heat exchange efficiency in the flow path region P is improved. The projections 12(1 st projection 12a, 12aa, 2 nd projection 12b) are formed such that the cut-off formed edge Y faces the flow direction of the 2 nd fluid flowing between the stacked layers of the plate fins 2 a. Therefore, the interval between the plate-fin stacked layers is fixed, the dead water region which may occur on the downstream side of the protrusions 12(12a, 12aa, 12b) is extremely small, and the leading edge effect occurs at the cut-formed end edge Y portion. Further, since the cutting is performed so as to face the flow direction of the 2 nd fluid, the flow resistance to the 2 nd fluid can also be made small. Therefore, the heat exchange efficiency of the plate fin stacked body 2 can be greatly improved while suppressing an increase in flow path resistance of the flow path region P.
The projections 12 (the 1 st projections 12a, 12aa, and the 2 nd projections 12b) provided on the plate fin 2a are arranged linearly with respect to the 2 nd fluid, but the projections 12 are more effective if they are staggered or formed more on the leeward side than on the windward side, and various configurations can be presented as the arrangement configuration of the projections 12, but an optimum configuration may be selected according to the specification and configuration of the heat exchanger and the desires of the user.
Further, since the respective projections 12 (the 1 st projections 12a, 12aa, the 2 nd projection 12b) are cut open in the flow direction of the air flowing through the gaps of the plate-fin laminated body 2, it is not necessary to make the recessed flat surface portion 20 between the 1 st fluid flow paths thin in the air flow direction, that is, in the direction intersecting the 1 st fluid flow paths. Therefore, compared to the case where the 2 nd projections 12b formed by the cut-and-raised formation are formed like cylindrical projections or the like, the recessed flat surface portion 20 between the 1 st fluid flow paths can be narrowed in accordance with the dimension that does not require thinning, and the width of the plate fin 2a, in other words, the heat exchanger can be downsized in accordance with this.
Furthermore, the edges of the long side portions of the plate fins 2a are formed with the narrow width flat surfaces 20a and the wide width flat surfaces 20b by the alternate offset arrangement of the 1 st fluid flow channels 11 (see fig. 10), the 1 st protrusions 12a are formed on the wide width flat surfaces 20b side, and the top surfaces thereof are fixed to the narrow width flat surfaces 20a of the adjacent plate fins 2a, so that it is not necessary to widen the width on the narrow width flat surfaces 20a side or the like in order to form the protrusions. That is, by providing the slit-shaped projections on the wide flat surface side by the wide flat surface 20b and bringing the projections into contact with the narrow flat surface 20a, the width of the long side portion of the plate fin on the narrow flat surface side can be made constant as the narrow flat surface without widening, and the heat exchanger can be downsized accordingly.
Further, the protrusions 12 (the 1 st protrusions 12a, 12aa, the 2 nd protrusions 12b) each have a top surface fixed to the adjacent plate fin 2a when the plate fins 2a and the end plates 3a, 3b are brazed, and therefore, also have a function of integrally connecting the plate fins 2a, and the rigidity of the plate-fin laminate 2 can be improved.
In particular, in the present embodiment, the portion above the extension line of the connection channel 10b of the 1 st fluid channel 11 group becomes the non-channel portion 18, and the 2 nd protrusion 12b, which is a part of the protrusion 12 (the 1 st protrusion 12a, the 2 nd protrusion 12b), is provided by the non-channel portion 18, so that the plate-fin laminated gap of the 1 st fluid channel 11 group portion can be reliably maintained. This makes it possible to stabilize the air flow uniformly in the group portion of the 1 st fluid flow path 11, thereby improving the heat exchange efficiency.
The 1 st protrusions 12a provided on the long side portions of the laminated plate fin body 2 are effective in improving the strength of the long side edge portions of the laminated plate fin body 2, which are likely to be weakened in strength. In particular, the 1 st projections 12a provided on both side edge portions of the slit 15 of the plate-fin laminated body 2 are effective in improving the strength of the slit edge portion which is divided by the provision of the slit 15 and has a reduced strength, and thus preventing deformation in the vicinity of the slit while improving the heat exchange efficiency. The 1 st projection 12aa may be provided at a position apart from the slit 15.
In addition, in the case where the 1 st projection 12a provided at the both side edge portions of the slit 15 is provided in a manner to straddle the slit 15, there is a problem that heat conduction occurs between the outward flow path portion 11a and the return flow path portion 11b of the 1 st fluid flow path 11 group, and the heat insulating effect of the slit 15 is lowered. However, if the slits 15 are provided separately at both side edge portions as in the present embodiment, such heat conduction is effectively eliminated. The 1 st projection 12aa may be provided at a position apart from the slit 15.
The 1 st protrusions 12a, 12aa provided on the long side portions of the plate fin laminate 2 and on both side portions of the slit 15 are provided at positions away from the end edges of the long sides of the plate fins of the plate fin laminate 2. Therefore, when dew condensation water is generated in the plate fins 2a of the plate-fin stacked body 2 and flows along the end edges of the plate fins 2a to be discharged, the water flow is blocked by the 1 st projections 12a and 12aa, and the dew condensation water can be prevented from accumulating in the portions where the 1 st projections 12a and 12aa are provided, thereby preventing various problems caused by the dew condensation water from occurring, and providing a heat exchanger with high reliability.
In the heat exchanger of the present embodiment, as shown in fig. 13 and 19, the plate fins 2a are also provided with projections 22 (the 3 rd projections 22a, the 4 th projections 22b) at the U-turn side end portions of the 1 st fluid flow channels 11. Therefore, the degree of contribution of heat exchange at the U-turn side end portions of the plate fins 2a without the 1 st fluid flow channels 11 can be improved. Therefore, the heat exchange efficiency can be improved over the entire length of the flow path region of the plate fin 2a, and the heat efficiency of the heat exchanger can be improved.
In particular, since the U-turn side end portions of the plate fins 2a are provided with the positioning pin holes 13 and the downstream side thereof becomes the dead water region, the heat exchange contribution is extremely low, and in the present embodiment, since the plurality of projections 22 (the 3 rd projection 22a and the 4 th projection 22b) are provided on the downstream side of the positioning pin holes 13, the heat exchange contribution over the entire downstream side of the positioning pin holes 13 can be improved.
In particular, the 3 rd projection 22a closest to the downstream side of the positioning pin hole 13 is shaped to constrict the flow of the fluid on the downstream side of the positioning pin hole 13, so that the dead water region having a low heat exchange contribution degree generated on the downstream side of the positioning screw hole can be made extremely small, and the heat exchange efficiency can be further improved accordingly.
Furthermore, the respective projections 22 (the 3 rd projection 22a, the 4 th projection 22b) are cut and formed in the same manner as the projections 12 (the 1 st projections 12a, 12aa, the 2 nd projection 12b) provided in the flow path region P. Further, since the cut-formed edge Y faces the 2 nd fluid flow, a leading edge effect can be generated in the cut-formed edge portion, and the heat exchange efficiency can be further improved.
Further, since the plurality of projections 22 (the 3 rd projection 22a, the 4 th projection 22b) provided on the downstream side of the positioning pin hole 13 are arranged in a staggered manner with respect to the 2 nd fluid flow in a meandering manner, all of them can effectively exhibit the heat exchange function, and the heat exchange contribution can be improved.
Further, the respective protrusions 22 (the 3 rd protrusion 22a, the 4 th protrusion 22b) are also fixed to the adjacent plate fins 2a at the top portions thereof, and the short side portions of the plate fins 2a are connected and fixed in a stacked state, so that the rigidity of the plate fin stacked body 2 can be improved.
In the present embodiment, the 3 rd projection 22a provided on the nearest downstream side of the positioning pin hole 13 is cut and formed in a cross-sectional shape that opens like an ハ in the flow direction of the 2 nd fluid. However, the projections formed by cutting in an L-shaped cross section may be provided so as to face each other in pairs, and may have any shape as long as the shape of the fluid flow on the downstream side of the contraction positioning pin hole 13 is obtained.
(embodiment 2)
As shown in fig. 20 to 23, the heat exchanger according to embodiment 2 of the present invention differs from the heat exchanger according to embodiment 1 in the shape of the 1 st fluid flow path group and the installation position of the header opening, and portions having the same functions as those of the heat exchanger according to embodiment 1 are given the same reference numerals, and the description will be given centering on portions having different functions.
Fig. 20 is an exploded perspective view showing a plate-fin stacked heat exchanger as a heat exchanger according to the present embodiment in a vertically separated state. Fig. 21 is a plan view of a plate fin constituting a plate fin stacked body of the heat exchanger according to the present embodiment. Fig. 22 is an exploded perspective view showing a part of the structure of the plate fin of the heat exchanger according to the present embodiment in an enlarged manner. Fig. 23 is a perspective view showing a 1 st fluid flow path group portion of the plate fin laminated body of the heat exchanger according to the present embodiment in a broken state.
In fig. 20 to 23, the group of the 1 st fluid flow paths 11 provided in the plate fins 2a of the heat exchanger of the present embodiment is linear, and an inlet-side header opening 8a is provided on one end side thereof, and an outlet-side header opening 8b is provided on the other end side thereof. An inflow tube 4 is connected to the inlet-side header opening 8a, an outflow tube 5 is connected to the outlet-side header opening 8b, and the refrigerant flows linearly from the header opening 8a on one end side of the plate fin 2a to the header opening 8b on the other end side and flows out.
The inlet-side manifold flow path 10 formed around the inlet-side manifold opening 8a includes an outer peripheral flow path 10a around the manifold opening 8a, a connection flow path 10b, and a multi-branch flow path 10 c. The connection flow path 10b is formed to extend from the outer peripheral flow path 10a in the short side direction of the plate fin 2a, and then connected to the multi-branch flow path 10c, and the outlet-side header flow path 14 is also configured in the same manner as the inlet-side header flow path 10, and both are symmetrical in shape. As shown in fig. 22, the fluid collision wall 17 is provided in a linear portion of the connection channel 10 b.
The end plates 3a and 3b on both sides of the plate-fin stacked body 2 are connected by the connection mechanism 9 without using the reinforcing plates 16a and 16b shown in fig. 3 describing embodiment 1, and the expansion deformation of the header regions H at both ends of the end plates 3a and 3b is prevented.
The heat exchanger configured as described above is the same as the heat exchanger described in embodiment 1, including the configuration and effects of the detailed portions, except for the effect obtained by forming the 1 st fluid flow channel 11 group in a U-shape, and therefore, the description thereof is omitted.
The projections 22 (see fig. 13) provided at the U-turn side end portions of the plate fins 2a according to embodiment 1 may be provided in the inlet-side header region H and the outlet-side header region H as appropriate in this example. That is, the projections 22 (22a, 22b) provided at the U-turn side end portion (see fig. 13 and 19) may be formed on the downstream side of the inlet-side header flow path 10 and the outlet-side header flow path 14, which are dead water regions, for example.
(embodiment 3)
The heat exchanger according to embodiment 3 of the present invention is suitable for use as an evaporator in which the refrigerant inlet and the refrigerant outlet of the heat exchanger are reversed, and as shown in fig. 24 to 28, a refrigerant flow dividing control tube 24 is provided in the outlet-side header passage 14.
In this embodiment, a case where the heat exchanger having the structure of embodiment 1 is used as an evaporator will be described as an example.
Fig. 24 is a perspective view showing the appearance of a plate-fin stacked heat exchanger as a heat exchanger according to the present embodiment. Fig. 25 is an exploded perspective view showing a state in which the flow distribution control pipe is detached from the heat exchanger of the present embodiment. Fig. 26 is a perspective view showing a flow distribution control tube insertion portion of the plate fin laminate of the heat exchanger according to the present embodiment. Fig. 27 is a perspective view of the flow dividing control tube of the heat exchanger according to the present embodiment. Fig. 28 is a sectional view showing a flow dividing control tube portion of the heat exchanger according to the present embodiment.
In fig. 24 to 28, the flow dividing control tube 24 is inserted into the outlet-side header passage 14, which is the header opening 8b provided on the outlet side as the evaporation outlet of the refrigerant, and its tip portion is, as shown in fig. 28, extended to the end plate 3b on the side where the header opening is not provided, and is closed by the end plate 3 b. The flow distribution control tubes 24 are formed of tubes having a smaller diameter than the inner diameter of the header opening 8b, and have a refrigerant flow passage gap 25 formed between them and the header opening inner surface, and a plurality of flow distribution ports 26 formed at substantially equal intervals in the longitudinal direction thereof, that is, in the stacking direction of the plate fins 2 a.
The plurality of branch ports 26 are formed such that the hole diameters thereof become smaller as going toward the direction in which the refrigerant flows, i.e., the outlet-side header opening 8 b.
As shown in fig. 25 and 27, the flow distribution control tubes 24 are attached to the reinforcing plates 16a, and are inserted into the header openings 8b by fastening the reinforcing plates 16a to the end plates 3a on both sides of the plate-fin laminated body 2.
The inflow pipe 4 is connected and fixed to the other surface of the reinforcing plate 16a to which the flow distribution control pipe 24 is attached, the other surface facing the flow distribution control pipe 24.
The outlet pipe 5 is also connected and fixed to the reinforcing plate 16 a. The flow distribution control pipe 24 may be configured to close the distal end portion thereof and be in contact with the end plate 3 b.
According to the heat exchanger configured as described above, the refrigerant gas flowing from the inlet-side header opening 8a to the outlet-side header passage 14 through the group of the 1 st fluid passages 11 flows from the refrigerant flow common space 25 into the flow dividing control tubes 24 through the plurality of flow dividing ports 26 formed in the tube walls of the flow dividing control tubes 24, and flows from the outlet-side header opening 8b to the outflow tube 5, as indicated by arrows in fig. 28.
Here, the branch flow port 26 provided in the branch control pipe 24 is formed such that the diameter of the hole becomes smaller as going to the outlet-side header opening 8b, and therefore the amount of refrigerant flowing through each flow path of the 1 st fluid flow path 11 group can be made uniform.
That is, in this heat exchanger, the 1 st fluid flow path 11 is reduced in diameter, so that the pressure loss of the refrigerant is several times greater than that in the outlet-side header flow path 14 of the inlet-side header flow path 10. On the other hand, the refrigerant split flow is greatly affected by the distribution of pressure loss. Thus, in this heat exchanger, even if the flow dividing control tube 24 is provided in the inlet-side header passage 10, which is common in the prior art, the pressure loss of the outlet-side header passage 14 is several times higher, and therefore the refrigerant flowing through the 1 st fluid passage 11 depends on the pressure loss of the outlet-side header passage 14, and therefore the refrigerant cannot be divided as designed.
However, in the heat exchanger of the present embodiment, by providing the flow dividing control tubes 24 in the outlet-side header passage 14 having a high pressure loss, it is possible to control the pressure loss distribution in the axial direction in the outlet-side header passage 14 to be several times as high as the pressure loss distribution, which greatly affects the flow dividing. This makes it possible to equalize the flow rates of the refrigerant flowing through the respective flow paths of the 1 st fluid flow path 11 group.
In this heat exchanger, the refrigerant flowing in from the inflow tube 4 passes through the inlet-side header opening 8a, is introduced into the 1 st fluid flow path 11 inside each plate fin 2a, flows into the outlet-side header opening 8b, and flows out from the outflow tube 5.
At this time, due to the pressure loss generated in each flow path, the refrigerant flows more easily through the 1 st fluid flow paths 11 of the plate fins 2a close to the inlet tube 4 (the 1 st fluid flow paths of the plate fins 2a closer to the left in fig. 28) than through the 1 st fluid flow paths 11 of the plate fins 2a far from the inlet tube 4 (the 1 st fluid flow paths of the plate fins 2a closer to the right in fig. 28). In other words, there is a possibility that unevenness is generated in the flow rate of the refrigerant.
Then, the flow dividing control tube 24 is inserted into the header opening 8b on the outlet side, and the opening area of the flow dividing port 26a closest to the outlet side is made smaller as shown in fig. 28, and the flow dividing port 26a provided on the outlet side of the flow dividing control tube 24 (the portion closer to the left side in fig. 28) is made smaller than the flow dividing port 26a on the opposite outlet side of the flow dividing control tube 24 (the portion closer to the right side in fig. 28), whereby the pressure loss of the refrigerant passing through the flow dividing port is increased. This makes it possible to make the refrigerant amount in the 1 st fluid flow path 11 inside each plate fin 2a uniform without generating a drift in the refrigerant flow rate, and to improve the heat exchange efficiency.
As a result, the heat exchanger can improve the heat exchange efficiency in the group portion of the 1 st fluid flow path 11, and provide a heat exchanger with higher heat efficiency.
Further, the refrigerant flow distribution uniformizing structure by the flow distribution control tube 24 is a simple structure in which only the flow distribution port 26 is perforated in the flow distribution control tube 24, and therefore can be provided at low cost.
Furthermore, since the flow dividing control tube 24 is integrally provided in the reinforcing plate 16a, it can be inserted and provided in the outlet-side header passage 14 only by attaching the reinforcing plate 16 a. Therefore, poor joining of the plate fins 2a due to melting of the brazing filler metal at the brazing portions of the plate fins 2a, which is problematic in cases where the flow dividing control tubes 24 are additionally attached by welding or the like, and quality defects such as leakage of refrigerant that accompany the poor joining can be prevented, and a high-quality and high-efficiency heat exchanger can be provided.
Further, the reinforcing plate 16a is formed of a material having a smaller potential difference with the outlet pipe 5 when used as an evaporator by being connected to the flow dividing control pipe 24 and the reinforcing plate 16a than when the flow dividing control pipe 24 and the outlet pipe 5 are directly connected to each other. Therefore, the occurrence of dissimilar metal contact corrosion which occurs when the flow dividing control pipe 24 and the outflow pipe 5 are directly connected can be prevented, and the reliability in long-term use can be greatly improved. In particular, in the heat exchanger for an air conditioner in which the inflow pipe 4 and the outflow pipe 5 are often formed of copper pipes and the flow dividing control pipe 24 is formed of stainless steel or the like, significant effects can be expected and are effective.
In the present embodiment, the flow distribution control pipe 24 is provided on the reinforcing plate 16a, but may be provided on the end plate 3a side, or in the case of a type not using the reinforcing plate 16a, the flow distribution control pipe 24 and the outflow pipe 5 may be provided on the opposite surface of the end plate 3 a.
In addition, although the present embodiment assumes a U-turn shape of the 1 st fluid flow path 11 group, the 1 st fluid flow path 11 group having a straight line shape described in embodiment 2 can be similarly applied.
The structure and effect of the other details are the same as those of the heat exchanger described in embodiment 1, and the description thereof is omitted.
(embodiment 4)
Embodiment 4 of the present invention is a refrigeration apparatus configured using one of the heat exchangers of the respective embodiments described above.
In the present embodiment, an air-conditioning apparatus will be described as an example of a refrigeration apparatus. Fig. 29 is a refrigeration cycle diagram of an air-conditioning apparatus as a refrigeration apparatus of the present embodiment. Fig. 30 is a schematic sectional view of an air conditioning apparatus as a refrigeration apparatus according to the present embodiment.
In fig. 29 and 30, the air-conditioning apparatus is composed of an outdoor unit 51 and indoor units 52 connected to the outdoor unit 51. The outdoor unit 51 includes a compressor 53 that compresses a refrigerant, a four-way valve 54 that switches a refrigerant circuit during cooling and heating operation, an outdoor heat exchanger 55 that exchanges heat between the refrigerant and outside air, and a pressure reducer 56 that reduces the pressure of the refrigerant. Further, an indoor heat exchanger 57 and an indoor fan 58 for exchanging heat between the refrigerant and the indoor air are disposed in the indoor unit 52. 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 of the present embodiment, a refrigerant is used which is obtained by mixing 2 or 3 components, respectively, with tetrafluoropropene or trifluoropropene as a base component and difluoromethane, pentafluoroethane, or tetrafluoroethane so that the global warming potential becomes 5 or more and 750 or less, preferably 350 or less, and more preferably 150 or less.
In the air-conditioning apparatus shown in fig. 29, the four-way valve 54 is switched to communicate the discharge side of the compressor 53 with the outdoor heat exchanger 55 during the cooling operation. 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. The refrigerant exchanges heat with the outside air to dissipate heat, becomes a high-pressure liquid refrigerant, and is sent to the decompressor 56. The refrigerant is decompressed by the decompressor 56 to become a low-temperature low-pressure two-phase refrigerant, and is sent to the indoor unit 52. In the indoor unit 52, the refrigerant enters the indoor heat exchanger 57, exchanges heat with indoor air to absorb heat, evaporates and gasifies, and becomes a low-temperature gas refrigerant. At this time, the indoor air is cooled to cool the room. Further, the refrigerant returns to the outdoor unit 51 and returns to the compressor 53 via the four-way valve 54.
During the heating operation, the four-way valve 54 is switched to communicate the discharge side of the compressor 53 with the indoor unit 52. The refrigerant compressed by the compressor 53 becomes a high-temperature and high-pressure refrigerant, and is sent to the indoor unit 52 through the four-way valve 54. The high-temperature and high-pressure refrigerant enters the indoor heat exchanger 57, exchanges heat with indoor air to dissipate heat, and is cooled to become a high-pressure liquid refrigerant. At this time, the indoor air is heated to heat the room. Thereafter, the refrigerant is sent to the decompressor 56, decompressed at the decompressor 56 to become a low-temperature low-pressure two-phase refrigerant, sent to the outdoor heat exchanger 55, subjected to heat exchange with outside air, evaporated and gasified, and returned to the compressor 53 via the four-way valve 54.
In the air-conditioning apparatus configured as described above, by using any of the heat exchangers of embodiments 1 to 3 in the outdoor heat exchanger 55 or the indoor heat exchanger 57, expansion deformation of the heat exchanger in the header region portion is eliminated, and a high-performance refrigerating apparatus having high energy saving performance can be provided because the apparatus is small in size and high in efficiency.
As described above, the 1 st invention is a heat exchanger in which the 2 nd fluid flows between the stacked layers of the plate fins of the plate fin stacked body having the heat exchange flow path through which the 1 st fluid flows, and heat is exchanged between the 1 st fluid and the 2 nd fluid. Further, the plate fin of the plate fin laminate includes: a flow path region having a plurality of 1 st fluid flow paths through which the 1 st fluid flows in parallel; and a header region having an inlet-side header flow path and an outlet-side header flow path communicating with the respective 1 st fluid flow paths of the flow path region, and the 1 st fluid flow paths are formed by providing recessed grooves in the plate fins. Further, a fluid collision portion is provided on the 1 st fluid flow path side of the connection flow path connecting the inlet-side header flow path and the 1 st fluid flow path group, and a multi-branch flow path for guiding the 1 st fluid, which collides with the fluid collision portion and is dispersed, to the 1 st fluid flow path group is provided.
According to this configuration, the refrigerant from the connection channel of the inlet-side header channel collides with the fluid collision portion and is dispersed to flow from the branched channels to the 1 st fluid channel group, and is uniformly branched to each 1 st fluid channel, thereby improving the heat exchange efficiency. In addition, the flow path cross-sectional area of the 1 st fluid flow path can be reduced in diameter, and the heat exchange efficiency can be improved by reducing the diameter of the flow path, so that a heat exchanger that is small in size and high in heat efficiency can be provided. By using such a heat exchanger, a high-performance refrigeration apparatus having a compact structure and high energy saving performance can be provided.
The invention 2 is the invention according to claim 1 wherein the 1 st fluid flow path formed in the plate fin is divided into an outward flow path portion and a return flow path portion by U-turn, the inlet-side header flow path and the outlet-side header flow path are arranged concentrically on one end portion side of the plate fin, the outward flow path portion connecting the 1 st fluid flow path group is provided with a center offset to the opposite side of the return flow path portion from a connecting flow path of the inlet-side header flow path, a fluid collision portion is provided in the connecting flow path, and a multi-branch flow path for guiding the fluid dispersed by collision with the fluid collision portion to the 1 st fluid flow path group is provided.
Accordingly, the heat exchange of the 1 st fluid can be performed without providing the plate fins long and providing the 1 st fluid flow paths long, thereby improving the heat exchange efficiency, and even if the 1 st fluid flow paths 11 are configured to be U-turned, the connection flow paths from the inlet side header flow paths are located at positions deviated to the opposite side portions of the outward flow path portions from the return side flow path portions due to the difference in length from the inlet side header flow paths to the outlet side header flow paths of the respective flow paths of the 1 st fluid flow path group and the change in flow path resistance, and therefore, the lengths of the partial flow paths from the connection flow paths to the respective outward flow path portions become longer as they become closer to the return side flow path portions, thereby canceling the difference in resistance, and enabling the partial flow paths to be uniformly branched to the respective flow paths of the 1 st fluid flow path group. Therefore, the heat exchanger having a higher heat exchange efficiency can be obtained while advancing miniaturization by the synergistic effect of the U-turn and the flow distribution uniformization of the 1 st fluid flow path group. Further, by making the 1 st fluid flow path group U-turn, the 1 st fluid flow path can be made long without making the plate fins long, and heat transfer from the outward flow path portion to the return flow path portion of the 1 st fluid flow path can be prevented, the refrigerant can be supercooled efficiently, the heat exchange efficiency can be further improved, and the downsizing of the heat exchanger can be promoted.
The invention according to claim 3 is the fluid flow path set according to claim 1 or 2, wherein the extended line of the connection flow path of the outgoing flow path portion of the fluid flow path set 1 is a non-flow path portion, and the non-flow path portion is provided with a protrusion, the top of which abuts against the surface of the adjacent fin plate to maintain the lamination gap between the fin plates.
This allows the refrigerant to flow through the 1 st fluid flow path group in a uniform flow distribution manner, maintains the lamination gap between the fin plates through which the 2 nd fluid flows, provides a stable structure in which the lamination gap between the fin plates is not uneven, and further improves the heat exchange efficiency.
The 4 th invention is a refrigeration apparatus in which any one of the heat exchangers of the 1 st to 4 th inventions is used as a heat exchanger constituting a refrigeration cycle.
Accordingly, the heat exchanger of the refrigeration apparatus is small in size and high in efficiency, and therefore, the refrigeration apparatus can be made high in energy saving performance and high in performance.
Industrial applicability of the invention
The invention can make the fluid flow distribution of the 1 st fluid flow path of the inlet side header flow path uniform to improve the heat exchange efficiency, and can provide a small-sized and high-efficiency heat exchanger and a high-performance refrigerating device with high energy-saving performance using the same. This makes it possible to widely use the heat exchanger and various refrigeration equipment used in air conditioners for home use and business use, etc., and the industrial value thereof is high.
Description of the reference numerals
1. 100 heat exchanger
2. 103 plate fin laminate
2a, 102 plate fins
3. 3a, 3b, 104 end plate
4 inflow pipe
5 outflow pipe
6 st plate fin
6a 1 st plate-like member
6b 2 nd plate-like member
7 nd 2 nd plate fin
8. 8a, 8b header openings
9 connecting mechanism (bolt and nut)
10. 105 inlet side manifold flow path (manifold flow path)
10a peripheral flow path
10b, 101a connecting channel
10c multiple branch flow path
11 st fluid flow path
11a forward flow path part
11b return side channel part
12 protrusion
12a, 12aa 1 st projection (projection)
12b 2 nd projection (projection)
13 through hole (boss hole for positioning)
13a hole outer circumference (positioning pin hole outer circumference)
14. 106 outlet side manifold flow path (manifold flow path)
15 slit
16a, 16b reinforcing plate
17 fluid collision wall
18 non-flow path part
19a, 19b planar end portions
20 depressed plane part
20a narrow plane
20b broad width plane
21 fin plane part
22 projection
22a No. 3 projection (projection)
22b 4 th projection (projection)
24-flow dividing control tube
25 gap for refrigerant circulation
26. 26a, 26b branch-off opening
27 hollow frame
51 outdoor machine
52 indoor machine
53 compressor
54 four-way valve
55 outdoor heat exchanger
56 pressure reducer
57 indoor heat exchanger
58 indoor fan.

Claims (3)

1. A heat exchanger in which a 2 nd fluid flows between stacked plates of plate fins in a plate fin stacked body having a 1 st fluid-flowing heat exchange flow path, and heat exchange is performed between the 1 st fluid and the 2 nd fluid, the heat exchanger being characterized in that:
the plate fins of the plate fin laminate include: a flow path region having a plurality of 1 st fluid flow paths through which the 1 st fluid flows in parallel; and a header region having an inlet-side header flow path and an outlet-side header flow path communicating with the respective 1 st fluid flow paths of the flow path region, and the 1 st fluid flow paths are formed by providing the plate fins with concave grooves,
further, a fluid collision portion is provided on the 1 st fluid flow path side of a connection flow path connecting the inlet-side header flow path and a 1 st fluid flow path group composed of a plurality of the 1 st fluid flow paths, and a multi-branch flow path for guiding the 1 st fluid, which has collided and dispersed with the fluid collision portion, to the 1 st fluid flow path group is provided,
the 1 st fluid flow path formed in the plate fin is divided into an outward flow path portion and a return flow path portion by U-turn, and an inlet-side header flow path and an outlet-side header flow path are arranged to be concentrated on one end portion side of the plate fin, and the outward flow path portion connecting the 1 st fluid flow path group and the inlet-side header flow path are provided so that the center of the outward flow path portion is offset to the opposite side of the return flow path portion with respect to the connecting flow path connecting the inward flow path.
2. The heat exchanger of claim 1, wherein:
the upper portion of the extension line of the connection flow path of the outgoing flow path portion of the 1 st fluid flow path group is a non-flow path portion, and a protrusion is provided in the non-flow path portion so that the top thereof abuts against the surface of the adjacent plate fin to maintain the lamination gap between the plate fins.
3. A refrigeration device, characterized by:
the heat exchanger constituting the refrigeration cycle employs the heat exchanger according to claim 1 or 2.
CN201780038952.4A 2016-10-21 2017-10-13 Heat exchanger and refrigerating apparatus using the same Active CN109312993B (en)

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WO2020003412A1 (en) * 2018-06-27 2020-01-02 株式会社Ｗｅｌｃｏｎ Heat transport device and method for manufacturing same
JP6934608B2 (en) * 2019-04-15 2021-09-15 パナソニックＩｐマネジメント株式会社 Plate fin laminated heat exchanger and freezing system using it

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