CN110895065A - Heat exchanger, method for manufacturing heat exchanger, and air conditioner provided with heat exchanger - Google Patents

Heat exchanger, method for manufacturing heat exchanger, and air conditioner provided with heat exchanger Download PDF

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Publication number
CN110895065A
CN110895065A CN201910725513.1A CN201910725513A CN110895065A CN 110895065 A CN110895065 A CN 110895065A CN 201910725513 A CN201910725513 A CN 201910725513A CN 110895065 A CN110895065 A CN 110895065A
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CN
China
Prior art keywords
heat transfer
flat porous
porous heat
heat exchanger
flow path
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Pending
Application number
CN201910725513.1A
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Chinese (zh)
Inventor
山本尚毅
法福守
草野隆人
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Hitachi Johnson Controls Air Conditioning Inc
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Hitachi Johnson Controls Air Conditioning Inc
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Publication of CN110895065A publication Critical patent/CN110895065A/en
Pending legal-status Critical Current

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    • 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
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
    • F28D1/05316—Assemblies of conduits connected to common headers, e.g. core type radiators
    • F28D1/05333—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits
    • 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
    • F25B39/02—Evaporators
    • 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
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
    • F28D1/0535—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight the conduits having a non-circular cross-section
    • F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
    • F28D1/05383—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits
    • 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
    • F25B39/04—Condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • F28F1/022—Tubular elements of cross-section which is non-circular with multiple channels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • F28F1/025—Tubular elements of cross-section which is non-circular with variable shape, e.g. with modified tube ends, with different geometrical features
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
    • F28F1/32—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely the means having portions engaging further tubular elements
    • F28F1/325—Fins with openings
    • 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
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0061—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for phase-change applications
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F21/00—Constructions of heat-exchange apparatus characterised by the selection of particular materials
    • F28F21/08—Constructions of heat-exchange apparatus characterised by the selection of particular materials of metal
    • F28F21/081—Heat exchange elements made from metals or metal alloys
    • F28F21/084—Heat exchange elements made from metals or metal alloys from aluminium or aluminium alloys
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2245/00—Coatings; Surface treatments
    • F28F2245/02—Coatings; Surface treatments hydrophilic
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2255/00—Heat exchanger elements made of materials having special features or resulting from particular manufacturing processes
    • F28F2255/10—Heat exchanger elements made of materials having special features or resulting from particular manufacturing processes made by hydroforming
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2275/00—Fastening; Joining
    • F28F2275/12—Fastening; Joining by methods involving deformation of the elements
    • F28F2275/125—Fastening; Joining by methods involving deformation of the elements by bringing elements together and expanding

Abstract

The invention provides a heat exchanger realizing high heat exchange performance or an air conditioner comprising the heat exchanger. The heat exchanger of the present invention comprises: a flat porous heat transfer tube (1) having a refrigerant flow path (2) divided by at least four partition walls (3) in the tube in the width direction and substantially parallel thereto; a fin (10) having an insertion hole (11) for enlarging and engaging the flat porous heat transfer pipe; and headers that communicate with the refrigerant flow paths at respective ends of the flat porous heat transfer tubes, wherein partition walls are arranged so that the flow path width at both ends in the width direction of the flat porous heat transfer tubes is wider than the flow path width at other portions. The air conditioner of the present invention is provided with the heat exchanger.

Description

Heat exchanger, method for manufacturing heat exchanger, and air conditioner provided with heat exchanger
Technical Field
The present invention relates to a heat exchanger in which a refrigerant flow path is formed by a flat porous heat transfer tube, and an air conditioner provided with the heat exchanger.
Background
In refrigeration cycle apparatuses such as air conditioners, it is a mainstream to use pipe members made of copper or a copper alloy for heat transfer pipes constituting heat exchangers and refrigerant pipes connecting the heat exchangers. However, in recent years, from the viewpoint of weight reduction and cost reduction, a heat exchanger using a heat transfer pipe made of aluminum or an aluminum alloy in addition to a fin has been proposed.
The heat exchanger is manufactured by attaching brazing filler metal made of aluminum alloy and brazing the plate-like fins and the flat porous heat conductive pipes, thereby achieving high heat exchange performance. However, this manufacturing method has a problem that the brazing of the plate-shaped fins of the heat exchanger needs to be performed with hydrophilic treatment.
As a manufacturing method of a heat exchanger instead of brazing, there is a method of mechanically joining a plate-like fin and a flat porous heat conductive pipe.
For example, patent document 1 describes the following method: the flat heat transfer tubes are attached so as to penetrate the plate-like fins, and the heat transfer tubes and the fins are joined to each other by increasing the internal pressure of the flat heat transfer tubes with a fluid to expand the heat transfer tubes. In the flat porous heat transfer pipe of patent document 1, the partition walls in the heat transfer pipe are bent or curved, and the heat transfer pipe is enlarged by linearly extending the partition walls.
Further, patent document 2 describes the following method: a flat porous heat transfer tube provided with partition walls having a substantially "く" shape is attached to plate-like fins having polygonal insertion holes so as to penetrate therethrough, and the flat tube is plastically deformed by water pressure or the like to be mechanically joined to the fins.
Documents of the prior art
Patent document 1: japanese patent No. 4109444
Patent document 2: japanese patent laid-open publication No. 2004-353954
Disclosure of Invention
Problems to be solved by the invention
According to patent documents 1 and 2, since the fins and the flat porous heat transfer tubes can be mechanically joined, hydrophilic coating treatment of the fins is performed in advance, and thus it is not necessary to perform hydrophilic coating treatment of the manufactured heat exchanger.
However, the shape of the flat porous heat transfer pipe causes uneven contact surface pressure between the expanded fins and the heat transfer pipe, and increases thermal contact resistance between the fins and the flat porous heat transfer pipe, thereby causing a problem that high heat exchange performance cannot be achieved.
The present invention has been made to solve the above-described problems, and an object of the present invention is to provide a heat exchanger that achieves high heat exchange performance, or an air conditioner including the heat exchanger.
Means for solving the problems
In order to achieve the above object, a heat exchanger according to the present invention includes: a flat porous heat transfer pipe having a refrigerant flow path divided by at least four partition walls in the width direction and substantially parallel to each other; a fin having an insertion hole to which the flat porous heat transfer pipe is joined by expansion; and a header that communicates with the refrigerant flow paths at respective ends of the flat porous heat transfer tubes, wherein the partition walls are arranged so that the flow path width at both ends in the width direction of the flat porous heat transfer tubes is wider than the flow path width at other portions.
The air conditioner of the present invention includes the heat exchanger.
Further, the heat exchanger of the present invention includes: a flat porous heat transfer pipe having a refrigerant flow path divided by at least four partition walls in the width direction and substantially parallel to each other; a fin having an insertion hole to which the flat porous heat transfer pipe is joined by expansion; and a header that communicates with the refrigerant flow paths at respective ends of the flat porous heat transfer tubes, wherein the partition walls are arranged so that the flow path width at both ends in the width direction of the flat porous heat transfer tubes is wider than the average flow path width at other portions.
Further, the heat exchanger of the present invention includes: a flat porous heat transfer pipe having a refrigerant flow path divided by at least four partition walls in the width direction and substantially parallel to each other; a fin having an insertion hole to which the flat porous heat transfer pipe is joined by expansion; and a header that communicates with the refrigerant flow paths at respective ends of the flat porous heat transfer tubes, wherein the partition walls are arranged so that the flow path width at the center in the width direction of the flat porous heat transfer tubes is narrower than the average flow path width at other portions of the flat porous heat transfer tubes.
The effects of the invention are as follows.
According to the present invention, since the contact thermal resistance after the flat porous heat transfer pipe is expanded to join the fins and the flat porous heat transfer pipe can be improved, a heat exchanger having high heat exchange performance can be provided.
Drawings
Fig. 1 is a diagram showing a main part of a heat exchanger of an embodiment.
Fig. 2 is a view showing a cross section of the flat porous heat transfer pipe in the longitudinal direction.
Fig. 3 is a view showing an appearance of a plate-like fin.
Fig. 4 is a diagram showing a manufacturing flow of the heat exchanger according to the embodiment.
Fig. 5 is a view showing a cross section of the flat porous heat transfer pipe.
Fig. 6 is a view showing the flatness and bondability of the flat porous heat transfer tube with different distances between the partition walls.
Fig. 7 is a sectional view of the flat porous heat transfer pipe of comparative example 1.
Fig. 8 is a sectional view of the flat porous heat transfer pipe of comparative example 2.
Fig. 9 is a sectional view of the flat porous heat transfer pipe of example 4.
Fig. 10 is a cross-sectional view of a flat porous heat transfer tube having heat dissipation fins formed in the refrigerant flow paths.
Fig. 11 is a cross-sectional view of a flat porous heat transfer tube in which heat dissipation fins are formed in the refrigerant flow paths excluding the central portion.
In the figure:
1-flat porous heat transfer pipe, 2-refrigerant flow path, 3-bulkhead, 4-pipe wall, 10-plate fin, 11-insertion hole, 12-fin sleeve.
Detailed Description
Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.
Fig. 1 is a diagram showing a main part of a heat exchanger of an embodiment. The heat exchanger according to the embodiment functions as a condenser or an evaporator of an air conditioner, and is used as either an indoor heat exchanger or an outdoor heat exchanger.
The heat exchanger is composed of the following components: a flat porous heat transfer pipe 1 through which a refrigerant flows; a plate-like fin 10 provided with a plurality of insertion holes 11 for expanding and engaging the flat porous heat transfer tubes 1; and headers (not shown) that communicate with the flat porous heat transfer tube 1 at both ends of the flat porous heat transfer tube 1, respectively.
The refrigerant flowing into one of the headers is distributed to the plurality of flat porous heat transfer tubes 1, and flows through the tubes of the flat porous heat transfer tubes 1. At this time, the latent heat and sensible heat of the refrigerant are transferred to the plate-like fins 10 joined to the flat porous heat transfer tubes 1. The thermal contact resistance between the flat porous heat conductive pipes 1 and the plate-like fins 10 affects the heat exchange performance of the heat exchanger, which will be described in detail later. Therefore, in the heat exchanger of the embodiment, the contact surface pressure of the joint portion between the flat porous heat transfer pipe 1 and the plate-like fin 10 is made appropriate to reduce the contact thermal resistance, thereby improving the heat exchange performance of the heat exchanger.
The flat porous heat transfer pipe 1 will be described in detail with reference to fig. 2.
Fig. 2 shows a longitudinal cross section of the flat porous heat transfer pipe 1.
The flat porous heat transfer pipe 1 is made of aluminum or an aluminum alloy, and is provided with a plurality of refrigerant flow paths 2 divided by a plurality of partition walls 3 provided along the longitudinal direction of the pipe cross section (the width direction of the pipe). In the manufacturing process, a compressed fluid of high pressure is supplied to the refrigerant flow path 2 enclosed by the bent or curved partition wall 3 and the tube wall 4, and the partition wall 3 is deformed so as to be elongated, thereby expanding the flat porous heat transfer tube 1 in the short axis direction of the tube cross section (the thickness direction of the tube), which will be described in detail later.
Next, the plate-like fin 10 will be described in detail with reference to fig. 3.
Fig. 3 is a view showing the appearance of the plate-like fin 10.
The plate-like fins 10 are made of aluminum or an aluminum alloy, and have a hydrophilic coating treatment applied to the outer surface thereof.
The plate-like fins 10 are provided with a plurality of insertion holes 11 into which the flat porous heat exchanger tubes 1 are inserted at predetermined intervals. A fin collar 12 bent toward one surface side of the plate-like fins 10 is provided on the outer peripheral portion of the insertion hole 11, and is joined to the flat porous heat transfer pipe 1 inserted and expanded. By providing the fin collar 12, the thermal contact resistance at the joint between the plate-like fins 10 and the flat porous heat transfer tubes 1 can be reduced.
The insertion holes 11 are formed with a gap of about 0 to 150 μm for inserting the flat porous heat transfer pipe 1 before expansion.
The contact surface pressure of the joint between the plate-like fin 10 and the flat porous heat transfer pipe 1 is affected by the spring back caused by the deformation of the insertion hole 11. Therefore, the amount of expansion of the flat porous heat exchanger tube 1 is determined by the sum of the amount of deformation of the insertion hole 11 that generates the contact surface pressure and the gap of the insertion hole 11 into which the flat porous heat exchanger tube 1 is inserted.
At this time, it is desirable that the amount of expansion of the flat porous heat transfer pipe 1 is constant in the width direction so that the contact surface pressure of the joint portion in the width direction (long axis direction of the cross section) of the flat porous heat transfer pipe 1 becomes uniform. However, when the pressures are uniformly applied, the both end portions of the flat porous heat exchanger tube 1 are difficult to expand, and the expansion amount of the both end portions of the flat porous heat exchanger tube 1 is smaller than that of the central portion.
Therefore, it is considered that the amount of deformation of the plate-like fins 10 is made constant by changing the hole width of the insertion holes 11 at the end portions and the central portion, but in this case, there is a possibility that a problem arises in the formation of the fin collars 12. Therefore, in the heat exchanger of the embodiment, the hole width of the insertion hole 11 is set constant, and the arrangement of the partition walls 3 of the flat porous heat transfer pipe 1 is changed to make the expansion amount of the flat porous heat transfer pipe 1 reasonable, which will be described in detail below.
Here, a method of manufacturing the heat exchanger according to the embodiment will be described with reference to fig. 4.
Fig. 4 is a diagram showing a manufacturing flow of the heat exchanger according to the embodiment.
In step S41, a hydrophilic coating treatment is applied to an aluminum plate made of aluminum or an aluminum alloy material, and in step S42, the plate-shaped fin 10 is manufactured by press working into a predetermined shape.
In step S43, the flat porous heat transfer tube 1 is manufactured by, for example, performing extrusion processing or drawing processing on an aluminum or aluminum alloy material and cutting the material into a predetermined size corresponding to the size of the heat exchanger of the embodiment.
Further, in step S44, a plurality of flat porous heat transfer pipes 1 are arranged at predetermined intervals.
In step S45, the plurality of flat porous heat transfer pipes 1 aligned in step S44 are inserted into the insertion holes 11 of the plate-like fins 10. At this time, there is no gap or a fine gap (0 to 150 μm) is formed between the outer periphery of the flat porous heat transfer tube 1 and the fin collar 12.
Next, in step S46, both ends of the flat porous heat transfer pipe 1 inserted into the insertion holes 11 of the plate-like fins 10 are inserted into engagement holes provided in the header. Also, both end portions of the flat porous heat conductive pipes 1 and the headers are joined by brazing or another suitable method.
In step S47, the compressed fluid is supplied to the flat porous heat transfer tubes 1 through the header to increase the internal pressure of the refrigerant flow paths 2, thereby pressurizing the flat porous heat transfer tubes 1 and expanding the flat porous heat transfer tubes 1, thereby joining the plate-like fins 10 and the flat porous heat transfer tubes 1.
In the heat exchanger of the embodiment, the flat porous heat transfer tube 1 having reduced contact thermal resistance described below is expanded by the above-described manufacturing method and mechanically joined to the plate-like fins 10, so that the hydrophilic coating treatment of the plate-like fins 10 can be performed in advance, and the heat exchanger can be easily manufactured.
Hereinafter, the arrangement of the partition walls 3 of the flat porous heat transfer pipe 1 in the heat exchanger according to the embodiment will be described in detail.
Fig. 5 is a view showing a cross section of the flat porous heat transfer pipe 1.
The flat porous heat transfer tube 1 is a flat tube formed such that the upper and lower tube walls 4 are substantially parallel to each other, and the flat porous heat transfer tube 1 includes a plurality of partition walls 3, and the plurality of partition walls 3 are connected to the upper and lower tube walls 4 inside the flat porous heat transfer tube 1, and have a cross-sectional shape that is bent in a mountain shape (in a mirror image of "く" or "く" of hiragana, japanese) in the long axis direction of the cross-section of the flat porous heat transfer tube 1. The inside of the flat porous heat transfer pipe 1 is divided by the partition walls 3, and a plurality of refrigerant flow paths 2 are provided in parallel.
The solid line in fig. 5 shows the cross section of the flat porous heat transfer pipe 1 before expansion, and the broken line shows the cross section of the flat porous heat transfer pipe 1 after expansion. The cross section (broken line) of fig. 5 after the pipe expansion is described in an exaggerated state.
In the expansion of the flat porous heat transfer tube 1, the partition walls 3 bent in a mountain shape extend along straight lines, and the dimension in the short axis direction of the cross section (the thickness direction of the tube) increases. The dimension increase in the short axis direction (tube thickness direction) of the cross section is the tube expansion amount.
The amount of expansion is determined by the shape of the partition wall 3, but the expansion state differs depending on the difference between one side and the partition wall 3 in the refrigerant flow path 2 at both ends of the flat porous heat transfer tube 1. The refrigerant flow paths 2 adjacent to the refrigerant flow paths 2 at both ends of the flat porous heat transfer tube 1 are affected by the expansion of the end portions.
Therefore, when the partition walls 3 are equally spaced, the amount of expansion is distributed in the longitudinal direction of the cross section. Specifically, the expansion amount decreases toward the end of the flat porous heat transfer pipe 1.
Tension applied to the partition walls 3 during pipe expansion is generated by the pressure of the compressed fluid inside the pipe wall 4 sandwiched by the partition walls 3, and the tension applied to the partition walls 3 is proportional to the interval between the partition walls 3. In the flat porous heat transfer pipe 1 of the embodiment, the amount of expansion is adjusted by changing the intervals of the partition walls 3 based on this.
As described above, the end portions of the flat porous heat transfer tubes 1 are less likely to be expanded than the central portion, and it is desirable to expand the intervals between the partition walls 3 at the end portions, but the rigidity of the end portions in the longitudinal direction of the insertion holes 11 is high, so there is an upper limit to the amount of expansion in terms of obtaining a uniform contact surface pressure. That is, there is an upper limit to the length of the interval of the partition walls 3 at the end portions of the flat porous heat conductive pipes 1.
Further, since the partition walls 3 are deformed so as to extend in the shape of "く", the intervals between the partition walls 3 do not change before and after the tube expansion.
Next, the relationship between the difference between the intervals between the partition walls 3 of the flat porous heat exchanger tube 1 and the amount of expansion in the longitudinal direction of the cross section, and the adhesiveness at the insertion holes 11 will be described with reference to fig. 6 to 9.
FIG. 6 shows the interval (L) between the partitions 3 provided in the tubes of the flat porous heat transfer tube 1c、L1、L2、LT) The ratio of the interval between the end portion and the partition wall 3 in the center portion (L) in each example is differentT/Lc) Flatness (Δ Ymax- Δ Ymin) of the flat porous heat transfer tube 1, and bondability of the flat porous heat transfer tube 1 at the insertion hole 11.
Interval (L) of partition wall 3c、L1、L2、LT) Corresponding to the distance between the partitions of the partition wall 3 shown in fig. 5.
Interval LcThe distance between the partition walls of the flow channel closest to the center of the flat porous heat transfer pipe 1 (the length of the pipe wall 4) is shown.
Interval LTThe distance between the barrier walls of the end flow paths of the flat porous heat transfer tubes 1 and the straight line portions at the tube ends is shown.
Interval L1、L2The distance between the partition walls of the channels adjacent to each other from the channel adjacent to the central channel of the flat porous heat exchanger tube 1 toward the end is shown.
In this specification, the interval (L) between the partition walls 3 may be setc、L1、L2、LT) Referred to as the flow path width.
Δ Ymax and Δ Ymin show the maximum and minimum values of the expansion width of one side of the flat porous heat transfer tube 1, and the difference is taken as the flatness. And shows that the side with the smaller flatness is flat.
The flat porous heat transfer pipe 1 of comparative example 1 in FIG. 6 is L shown in FIG. 7c、L1、L2、LTAll holes of equal length of (2) are equal。
When the flat porous heat transfer pipe 1 of comparative example 1 is expanded, the pipe wall 4 of the central flow passage expands greatly, and the flatness increases.
Since high heat exchange performance is obtained by enlarging the flat porous heat transfer pipe 1 so that the outer surface of the pipe wall 4 is in close contact with the fin sleeve 12, it is not recommended that the outer surface of the pipe wall 4 be changed in a wavy or uneven manner by the enlargement, and the adhesiveness between the flat porous heat transfer pipe 1 and the fin sleeve 12 becomes insufficient (mark x).
The flat porous heat transfer pipe 1 of comparative example 2 in FIG. 6 is L shown in FIG. 8TLength ratio L ofc、L1、L2Is short.
In this case, the tube wall 4 of the expanded central flow passage expands largely, the flatness increases, and the adhesiveness between the flat porous heat transfer tube 1 and the fin collar 12 becomes insufficient (mark x).
The flat porous heat transfer pipe 1 of example 1 in FIG. 6 is LTLength ratio L ofc、L1、L2Is long.
In this case, after the expansion, the tube wall 4 of the refrigerant flow path 2 expands approximately uniformly, and the flatness becomes small, whereby the bondability of the flat porous heat transfer tube 1 to the fin tube 12 becomes excellent (reference ◎), and a heat exchanger with high heat exchange performance is obtained.
The flat porous heat transfer pipe 1 of example 2 in FIG. 6 is LTLength ratio L ofTL other than Lc、L1、L2Is long.
In this case, after expansion, the tube wall 4 of the refrigerant flow path 2 also expands approximately uniformly, and the flatness becomes small, whereby the bondability of the flat porous heat transfer tube 1 to the fin tube 12 becomes excellent (reference ◎), and a heat exchanger with high heat exchange performance is obtained.
The flat porous heat transfer pipe 1 of example 3 in FIG. 6 is LcLength ratio L of1、L2、LTIs short.
In this case, after expansion, the tube wall 4 of the refrigerant flow path 2 also expands approximately uniformly, and the flatness becomes small, whereby the bondability of the flat porous heat transfer tube 1 to the fin tube 12 becomes excellent (reference ◎), and a heat exchanger with high heat exchange performance is obtained.
The flat porous heat transfer pipe 1 of example 4 in FIG. 6 is L shown in FIG. 9cLength ratio L of1、L2、LTIs short.
In this case, the tube wall 4 of the expanded end flow passage expands, while the tube wall 4 of the center flow passage does not expand, whereby the flatness is reduced, and the bondability between the flat porous heat transfer tube 1 and the fin tube 12 becomes good (reference ○).
As shown in fig. 6, in the flat porous heat transfer tubes 1 of examples 1 to 4, the flat porous heat transfer tubes 1 and the fin collars 12 were excellent or superior in bondability, and a heat exchanger having high heat exchange performance was obtained. In contrast, in the flat porous heat transfer tubes 1 of comparative examples 1 to 2, the bondability between the flat porous heat transfer tube 1 and the fin collar 12 was insufficient. From this point of view, particularly, a condition that the adhesiveness becomes excellent is desired, and the flat porous heat transfer pipe 1 is formed so that the flow path width Lt at both ends in the width direction and the flow path width L at the center portion in the width direction are set to be equal to each othercBecomes 1.0 < (Lt/L)c) The partition walls 3 are arranged so as to be < 3.5.
As described above, according to the flat porous heat transfer tube 1 of the embodiment, since the irregularities on the outer surface of the tube during expansion are reduced, the contact thermal resistance is reduced, and a heat exchanger having high heat exchange performance can be provided.
Fig. 10 and 11 are cross-sectional views of the flat porous heat transfer pipe 1 of embodiment 1 to 4 of fig. 6, in which the heat exchange performance is further improved.
More specifically, the flat portions of the inner surfaces of the refrigerant flow paths 2 are formed with protrusions 13 that extend in the longitudinal direction of the flat porous heat exchanger tubes 1 and serve as heat dissipation fins, thereby increasing the heat transfer rate with the refrigerant and improving the heat exchange performance of the flat porous heat exchanger tubes 1.
As shown in fig. 11, the protrusion 13 may not be formed in the cooling flow path in the central portion. This can prevent a decrease in the flow path cross-sectional area, and can suppress a decrease in the refrigerant flow rate (an increase in pressure loss).
The cross-sectional shape of the protrusion 13 is not limited to a triangle, and may be an arc-shaped or a quadrangle.
As described above, the thickness of the tube wall 4 of the flat porous heat exchanger tube 1 is designed to be able to withstand the pressure generated by the fluid in the tube when used as a heat exchanger, and the tube wall thickness at both ends in the longitudinal direction of the tube cross section is larger in the cross section of the flat porous heat exchanger tube 1 than in the bent or curved partition walls arranged in the tube. Therefore, when the flat porous heat transfer pipe 1 is expanded, the both ends in the long axis direction of the pipe cross section are less elongated than the partition walls 2 in the short axis direction of the pipe cross section, and the pipe wall 4 of the flat porous heat transfer pipe 1 is in a state of being unevenly expanded.
When the flat porous heat transfer pipe 1 is expanded by the fluid pressure, the force of expansion in the short axis direction of the pipe cross section is proportional to the length of the flat portion in the porous pipe inner surface of each flow path between the partition walls. In the flat porous heat transfer pipe 1 of the embodiment, the length of the flat portion at the flow path at both ends in the long axis direction of the cross section is made longer than the length of the flat portion (distance between the partition walls) in the other flow path, thereby increasing the load applied to the flat portion of the flow path at both ends and expanding the pipe. As a result, the tube wall of the flat porous heat transfer tube 1 is uniformly expanded, and the adhesiveness between the fins and the heat transfer tube is improved.
The case where the flat porous heat transfer tube 1 of the embodiment is divided by six partition walls 3 and has seven refrigerant flow paths 2 has been described, but the number of partition walls 3 (refrigerant flow paths 2) is not limited to this. The flat porous heat transfer tube 1 may have at least five refrigerant flow paths 2.
According to the heat exchanger and the air conditioner using the flat porous heat transfer tube 1 of the embodiment, the heat exchange performance of the heat exchanger can be improved, and a heat exchanger having high hydrophilicity, corrosion resistance, deodorization, antibacterial properties, and mold resistance can be easily realized.

Claims (14)

1. A heat exchanger is provided with:
a flat porous heat transfer pipe having a refrigerant flow path divided by at least four partition walls in the width direction and substantially parallel to each other;
a fin having an insertion hole to which the flat porous heat transfer pipe is joined by expansion; and
a header that communicates with the refrigerant flow paths at each end of the flat porous heat transfer tubes,
the above-described heat exchanger is characterized in that,
the partition walls are arranged so that the flow channel width at both ends in the width direction is wider than the flow channel width at the other portions of the flat porous heat transfer pipe.
2. The heat exchanger of claim 1,
the flat porous heat transfer pipe has a flow path width Lt at both ends in the width direction and a flow path width L at the center in the width directioncBecomes 1.0 < (Lt/L)c) The partition walls are arranged so as to be less than 3.5.
3. A heat exchanger is provided with:
a flat porous heat transfer pipe having a refrigerant flow path divided by at least four partition walls in the width direction and substantially parallel to each other;
a fin having an insertion hole to which the flat porous heat transfer pipe is joined by expansion; and
a header that communicates with the refrigerant flow paths at each end of the flat porous heat transfer tubes,
the above-described heat exchanger is characterized in that,
the partition walls are arranged so that the flow path width at both ends in the width direction is wider than the average flow path width at the other portions.
4. The heat exchanger of claim 3,
the flat porous heat transfer pipe has a flow path width Lt at both ends in the width direction and a flow path width L at the center in the width directioncBecomes 1.0 < (Lt/L)c) Mode configuration of < 3.5The partition wall.
5. A heat exchanger is provided with:
a flat porous heat transfer pipe having a refrigerant flow path divided by at least four partition walls in the width direction and substantially parallel to each other;
a fin having an insertion hole to which the flat porous heat transfer pipe is joined by expansion; and
a header that communicates with the refrigerant flow paths at each end of the flat porous heat transfer tubes,
the above-described heat exchanger is characterized in that,
the partition walls are arranged so that the flow channel width at the center in the width direction is narrower than the average flow channel width at other portions of the flat porous heat transfer pipe.
6. The heat exchanger of claim 5,
the flat porous heat transfer pipe has a flow path width Lt at both ends in the width direction and a flow path width L at the center in the width directioncBecomes 1.0 < (Lt/L)c) The partition walls are arranged so as to be less than 3.5.
7. The heat exchanger according to any one of claims 1 to 6,
the partition walls have a bent or curved cross-sectional shape and are arranged to be axisymmetrical with respect to a vertical axis in the width direction of the flat porous heat transfer pipe.
8. The heat exchanger according to any one of claims 1 to 7,
the flat porous heat transfer pipe has a protrusion extending in the longitudinal direction of the pipe on the inner surface of the refrigerant flow path.
9. The heat exchanger of claim 8,
the projection is provided in the refrigerant flow path other than the central portion.
10. A heat exchanger is provided with:
a flat porous heat transfer pipe having a refrigerant flow path divided by six partition walls in the width direction and substantially parallel to each other;
a fin having an insertion hole to which the flat porous heat transfer pipe is joined by expansion; and
a header that communicates with the refrigerant flow paths at each end of the flat porous heat transfer tubes,
the above-described heat exchanger is characterized in that,
the flat porous heat transfer pipe has a flow path width Lt at both ends in the width direction and a flow path width L at the center in the width directioncBecomes 1.0 < (Lt/L)c) The partition walls are arranged so as to be less than 3.5.
11. The heat exchanger according to any one of claims 1 to 10,
the hole width of the insertion hole is constant.
12. The heat exchanger according to any one of claims 1 to 11,
the fin is made of aluminum or an aluminum alloy having a surface subjected to hydrophilic coating treatment,
the flat porous heat transfer pipe is made of aluminum or an aluminum alloy.
13. An air conditioner is characterized in that,
a heat exchanger according to any one of claims 1 to 12.
14. A method for manufacturing a heat exchanger according to any one of claims 1 to 12, comprising:
a step of forming plate-like fins from an aluminum plate material having a surface subjected to hydrophilic coating treatment;
inserting a plurality of the flat porous heat transfer tubes into the insertion holes of the plate-like fins;
joining headers to both ends of the flat porous heat transfer tube to communicate the flow paths of the flat porous heat transfer tube with the headers; and
and a step of joining the plate-like fins and the flat porous heat transfer tubes by supplying a compressed fluid to the header to expand the flat porous heat transfer tubes.
CN201910725513.1A 2018-09-13 2019-08-07 Heat exchanger, method for manufacturing heat exchanger, and air conditioner provided with heat exchanger Pending CN110895065A (en)

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