CN112066599A

CN112066599A - Heat exchanger and air conditioner

Info

Publication number: CN112066599A
Application number: CN201910502417.0A
Authority: CN
Inventors: 山田贤一; 何哲旺; 武滔; 李成恩
Original assignee: Midea Group Co Ltd; GD Midea Air Conditioning Equipment Co Ltd
Current assignee: Midea Group Co Ltd; GD Midea Air Conditioning Equipment Co Ltd
Priority date: 2019-06-11
Filing date: 2019-06-11
Publication date: 2020-12-11

Abstract

The invention provides a heat exchanger and an air conditioner, wherein the heat exchanger comprises: the fin structure is provided with a fluid channel and a flow collecting port, the flow collecting port comprises at least one inlet flow collecting port and at least one outlet flow collecting port, and the at least one inlet flow collecting port and the at least one outlet flow collecting port are communicated through the fluid channel. The application provides a heat exchanger, the refrigerant flows into the fin structure by at least one import current collector, flow out by at least one export current collector behind fluid passage, in order to realize the heat transfer of refrigerant and fin, at least one import current collector and at least one export current collector are linked together through fluid passage, and then make the fin structure have multiple form, can make up according to actual conditions, when making up a plurality of fin structures, the reposition of redundant personnel of refrigerant can be realized to at least one import pressure manifold and at least one export pressure manifold, promote the heat transfer effect of heat exchanger.

Description

Heat exchanger and air conditioner

Technical Field

The invention relates to the technical field of household appliances, in particular to a heat exchanger and an air conditioner.

Background

At present, the heat exchanger among the correlation technique contains finned tube heat exchanger and microchannel heat exchanger, and finned tube heat exchanger's pipe and fin pass through the expand tube and combine, and thermal contact resistance is bigger, and microchannel heat exchanger's flat pipe and fin pass through the welded connection, and wherein the radical of heat pipe is many, has the uneven problem of refrigerant distribution, is unfavorable for the heat transfer of heat exchanger.

Disclosure of Invention

The present invention is directed to solving at least one of the problems of the prior art or the related art.

To this end, a first aspect of the invention provides a heat exchanger.

The second aspect of the invention also provides an air conditioner.

In view of the above, a first aspect of the present invention provides a heat exchanger, including: the fin structure is provided with a fluid channel and a flow collecting port, the flow collecting port comprises at least one inlet flow collecting port and at least one outlet flow collecting port, and the at least one inlet flow collecting port and the at least one outlet flow collecting port are communicated through the fluid channel.

The heat exchanger provided by the invention comprises at least one fin structure, wherein the fin structure is provided with a fluid channel and a flow collecting port, a refrigerant flows into the fin structure from at least one inlet flow collecting port and flows out from at least one outlet flow collecting port after passing through the fluid channel so as to realize heat exchange between the refrigerant and the fin structure, the at least one inlet flow collecting port and the at least one outlet flow collecting port are communicated through the fluid channel, so that the fin structure has multiple forms and can be combined according to actual conditions, when a plurality of fin structures are combined, the at least one inlet flow collecting port and the at least one outlet flow collecting port can realize flow distribution of the refrigerant, and the heat exchange effect of the heat exchanger is improved. In addition, in the related art, the fins and the tubes are expanded and then combined together, thermal contact resistance between the tubes and the fins is large, and heat exchange efficiency of the fins is low, so that efficiency of the heat exchanger is reduced.

According to the heat exchanger provided by the invention, the following additional technical characteristics can be provided:

in the above technical solution, preferably, the number of the inlet manifold ports is at least two, and the fin structure further includes an inlet throttling channel, and the at least two inlet manifold ports are communicated through the inlet throttling channel.

In the technical scheme, the number of the inlet collecting ports is at least two, the fin structure further comprises an inlet throttling channel, the at least two inlet collecting ports are communicated through the throttling channel, and then the refrigerant can flow into the other inlet collecting port from one of the at least two inlet collecting ports after being throttled by the inlet throttling channel and flows into the fluid channel to exchange heat with the fin structure, so that the heat exchange efficiency of the refrigerant and the fin structure is improved.

In any of the above technical solutions, preferably, the number of the outlet manifold ports is at least two, and the fin structure further includes an outlet throttling channel, and the at least two outlet manifold ports are communicated through the outlet throttling channel.

In the technical scheme, the number of the outlet collecting ports is at least two, the fin structure further comprises an outlet throttling channel, the at least two outlet collecting ports are communicated through the outlet throttling channel, so that the refrigerant can flow into the other outlet collecting port from one of the at least two outlet collecting ports after being throttled by the outlet throttling channel, and the heat exchange efficiency of the refrigerant and the fin structure is improved. Furthermore, when the heat exchanger is used for refrigerating, the refrigerant can enter the fin structure through the at least one inlet flow collecting port and flow out of the at least one outlet flow collecting port, when the heat exchanger is used for heating, the refrigerant can flow into the fin structure through the at least one outlet flow collecting port and flow out of the at least one inlet flow collecting port, and then the refrigerant can enter the fin structure after being throttled again during both refrigerating and heating, so that the heat exchange efficiency of the heat exchanger is improved.

Furthermore, the number of the inlet collecting ports is two, the number of the outlet collecting ports is two, the two inlet collecting ports are communicated through the inlet throttling channel, and the two outlet collecting ports are communicated through the outlet throttling channel.

In any of the above technical solutions, preferably, the fin structure further includes two fins, the fins are provided with fluid sub-channels and fluid collecting ports, and the two fins are oppositely disposed and attached to each other, so that central axes of the fluid collecting ports on the two fins are overlapped and the fluid sub-channels on the two fins form a fluid channel for fluid to flow.

In the technical scheme, the fin structure comprises two fins which are oppositely arranged and attached, namely the two fins are connected together in a reverse buckling manner, openings of the fluid sub-channels on the two fins are oppositely arranged, so that the fluid sub-channels on the two fins form the fluid channel for fluid to flow, and central axes of the collecting ports on the two fins are overlapped. Furthermore, the two fins are arranged in a mirror symmetry mode, and the projections of the two fins along the thickness direction of the fins are completely overlapped.

In any of the above solutions, preferably, the two fins are connected by welding.

In the technical scheme, the two fins are connected through welding, and further, the two fins are formed through inverse-buckling welding.

Further, the two fins may also be glued together.

In any of the above solutions, preferably, the fluid sub-channel is a groove formed on the fin, and the collecting port is a through hole formed on the fin.

In the technical scheme, the fluid sub-channels are grooves formed on the fins, the fluid sub-channels on the two fins form the fluid channels for fluid to pass through, the flow collecting ports are through holes formed on the fins, and when the fin structures are stacked, the fin structures are communicated with one another through the flow collecting ports, so that a refrigerant flows in the fin structures.

In any one of the above technical solutions, preferably, the number of the fin structures is at least two, and at least two fin structures are sequentially stacked along the central axis direction of the collecting port.

In the technical scheme, the number of the fin structures is at least two, the at least two fin structures are arranged in a stacking mode along the thickness direction of the fins, namely the at least two fin structures are arranged in a stacking mode along the central axis direction of the flow collecting port, and the refrigerant can flow into the at least two fin structures arranged in the stacking mode through the flow collecting port so as to fully exchange heat with the fin structures and improve the heat exchange efficiency of the heat exchanger.

In any of the above technical solutions, preferably, connecting pipes are arranged on two sides of the fin structures, and the connecting pipes connect the collecting ports of two adjacent fin structures.

In the technical scheme, connecting pipes are arranged on two sides of the fin structures and are communicated with the flow collecting port, and when at least two fin structures are stacked, two adjacent fin structures are communicated through the connecting pipes, so that the flow collecting ports of the two adjacent fin structures are communicated, and then the refrigerant can flow into the at least two fin structures through the flow collecting port and the connecting pipes and exchange heat with the fin structures.

Further, two adjacent fin structures are connected through connecting pipes in a welding mode.

Furthermore, the connecting pipes comprise a first connecting pipe and a second connecting pipe, and the first connecting pipe and the second connecting pipe are respectively communicated with the flow collecting port and are respectively positioned on two sides of the fin structure.

Furthermore, the pipe diameter of the first connecting pipe is larger than that of the second connecting pipe, and the outer diameter of the second connecting pipe is larger than or equal to the inner diameter of the flow collecting port.

In any of the above technical solutions, preferably, the fin structure has a symmetrical structure with a perpendicular plane as a symmetrical plane, the perpendicular plane being a connecting line between the center of the inlet collecting port and the center of the outlet collecting port.

In this technical scheme, the fin structure is symmetrical structure, and then can only realize the preparation of heat exchanger through one set of mould, practices thrift the cost, has promoted machining efficiency.

Furthermore, the fin structure takes a central axial plane of a connecting line between the center of the inlet collecting port directly connected with the end part of the fluid channel and the center of the outlet collecting port directly connected with the end part of the fluid channel as a symmetrical plane.

In any of the above solutions, preferably, the number of the fluid channels on the fin structure is at least one.

In the technical scheme, the number of the fluid channels on the fin structure is multiple, and the arrangement of the multiple fluid channels improves the heat exchange efficiency of fluid and fins.

Furthermore, the heat exchanger is vertically arranged, so that the length direction of the fins and the fluid channel are arranged in the vertical direction, and the central axis of the flow collecting port is arranged in the horizontal direction, so that the drainage performance of condensed water is excellent when the heat exchanger is used as an evaporator, the refrigerant distribution is not easily influenced by gravity, and the two-phase flow distribution is realized.

In any of the above technical solutions, preferably, the fin is integrally formed.

In the technical scheme, the fins are formed by integral forming, the heat exchange efficiency of the fins and the fluid channel is enhanced, the integral forming structure is simpler and more efficient to manufacture, the fins and the tubes are combined together after being expanded in the related technology, the thermal contact resistance between the tubes and the fins is larger, and the heat exchange efficiency of the fins is lower.

According to the second aspect of the present invention, there is also provided an air conditioner comprising: the heat exchanger provided by any one of the technical schemes.

The air conditioner provided by the second aspect of the invention has all the beneficial effects of the heat exchanger because the air conditioner comprises the heat exchanger in any one of the technical schemes.

Additional aspects and advantages of the invention will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of the invention.

Drawings

The above and/or additional aspects and advantages of the present invention will become apparent and readily appreciated from the following description of the embodiments, taken in conjunction with the accompanying drawings of which:

FIG. 1 shows a schematic structural view of a fin of one embodiment of the present invention;

FIG. 2 shows another schematic structural view of a fin of one embodiment of the present invention;

FIG. 3 shows a further structural schematic of a fin of one embodiment of the present invention;

FIG. 4 shows a schematic diagram of a heat exchanger according to an embodiment of the present invention;

FIG. 5 shows an enlarged schematic view of the structure at A in FIG. 4;

FIG. 6 is a further schematic diagram of the heat exchanger according to one embodiment of the present invention;

FIG. 7 shows an enlarged schematic view of the structure at B in FIG. 6;

FIG. 8 shows a schematic structural view of a fin of one embodiment of the present invention;

FIG. 9 shows a further structural schematic of a fin of one embodiment of the present invention;

FIG. 10 shows a partial structural schematic of a fin of one embodiment of the present invention;

FIG. 11 is a further partial structural schematic view of a fin according to an embodiment of the present invention;

FIG. 12 is an enlarged schematic view of the structure at C in FIG. 11;

FIG. 13 shows a partial structural schematic of a fin structure of one embodiment of the present invention;

FIG. 14 is a further partial structural schematic view of the fin structure of one embodiment of the present invention;

FIG. 15 shows an enlarged schematic view of the structure at D in FIG. 14;

FIG. 16 is a schematic diagram showing the heat transfer capacity of a heat exchanger according to an embodiment of the present invention in a comparable case to a fin-and-tube heat exchanger and a microchannel heat exchanger of the related art;

FIG. 17 is a schematic diagram showing the air side heat transfer coefficient for a heat exchanger according to an embodiment of the present invention and a related art finned tube heat exchanger and microchannel heat exchanger under equivalent conditions;

fig. 18 shows a schematic view of the air side pressure loss of the heat exchanger according to an embodiment of the present invention in the same case as the fin tube heat exchanger and the microchannel heat exchanger of the related art.

Wherein, the correspondence between the reference numbers and the component names in fig. 1 to 18 is:

1 heat exchanger, 10 fin structures, 100 fins, 102 fluid channels, 103 fluid sub-channels, 104 inlet collecting ports, 106 outlet collecting ports, 108 inlet throttling channels, 109 outlet throttling channels, 12 first connecting pipes and 14 second connecting pipes.

Detailed Description

In order that the above objects, features and advantages of the present invention can be more clearly understood, a more particular description of the invention will be rendered by reference to the appended drawings. It should be noted that the embodiments and features of the embodiments of the present application may be combined with each other without conflict.

In the following description, numerous specific details are set forth in order to provide a thorough understanding of the present invention, however, the present invention may be practiced in other ways than those specifically described herein, and therefore the scope of the present invention is not limited by the specific embodiments disclosed below.

A heat exchanger 1 and an air conditioner according to some embodiments of the present invention will be described below with reference to fig. 1 to 18.

According to an embodiment of the first aspect of the invention, the invention proposes a heat exchanger 1 comprising: the fin structure 10 is provided with a fluid channel 102 and a plurality of collecting ports, the collecting ports comprise at least one inlet collecting port 104 and at least one outlet collecting port 106, and the at least one inlet collecting port 104 and the at least one outlet collecting port 106 are communicated through the fluid channel 102.

The heat exchanger 1 provided by the invention, as shown in fig. 1, includes at least one fin structure 10, the fin structure 10 is provided with a fluid channel 102 and a flow collecting port, a refrigerant flows into the fin structure 10 from at least one inlet flow collecting port 104, and flows out from at least one outlet flow collecting port 106 after passing through the fluid channel 102, so as to realize heat exchange between the refrigerant and the fin structure 10, the at least one inlet flow collecting port 104 and the at least one outlet flow collecting port 106 are communicated through the fluid channel 102, so that the fin structure 10 has various forms, and can be combined according to actual conditions, when a plurality of fin structures 10 are combined, the at least one inlet flow collecting port 104 and the at least one outlet flow collecting port 106 can realize flow distribution of the refrigerant, thereby improving the heat exchange effect of the heat exchanger 1. In addition, in the related art, the fins and the tubes are expanded and then combined together, thermal contact resistance between the tubes and the fins is large, and heat exchange efficiency of the fins is low, so that efficiency of the heat exchanger is reduced.

Specifically, as shown in fig. 1 and 2, the number of the inlet collecting ports 104 is two, and the number of the outlet collecting ports 106 is one, as shown in fig. 3, the number of the inlet collecting ports 104 and the number of the outlet collecting ports 106 are two, so that the heat exchanger 1 has various combinations.

In the above embodiment, preferably, the number of the inlet headers 104 is at least two, and the fin structure 10 further includes an inlet throttling passage 108, and at least two inlet headers 104 are communicated through the inlet throttling passage 108.

In this embodiment, as shown in fig. 2, the number of the inlet collecting ports 104 is at least two, the fin structure 10 further includes an inlet throttling channel 108, at least two inlet collecting ports 104 are communicated with each other through the throttling channel, so that the refrigerant can flow from one of the at least two inlet collecting ports 104 into the other inlet collecting port 104 after being throttled by the inlet throttling channel 108, and flow into the fluid channel 102 to exchange heat with the fin structure 10, thereby improving the heat exchange efficiency between the refrigerant and the fin structure 10.

In any of the above embodiments, preferably, the number of outlet headers 106 is at least two, and the fin structure 10 further includes an outlet throttling passage 109, and at least two outlet headers 106 are communicated through the outlet throttling passage 109.

In this embodiment, as shown in fig. 3, the number of the outlet collecting ports 106 is at least two, the fin structure 10 further includes an outlet throttling channel 109, and the at least two outlet collecting ports 106 are communicated with each other through the outlet throttling channel 109, so that the refrigerant can flow from one of the at least two outlet collecting ports 106 into the other outlet collecting port 106 after being throttled by the outlet throttling channel 109, thereby improving the heat exchange efficiency between the refrigerant and the fin structure 10. Further, when the heat exchanger 1 is used for cooling, the refrigerant can enter the fin structure 10 through the at least one inlet collecting port 104 and flow out through the at least one outlet collecting port 106, when the heat exchanger 1 is used for heating, the refrigerant can flow into the fin structure 10 through the at least one outlet collecting port 106 and flow out through the at least one inlet collecting port 104, and then the refrigerant can enter the fin structure 10 after being throttled again during both cooling and heating, so that the heat exchange efficiency of the heat exchanger 1 is improved.

Further, as shown in fig. 3, the number of the inlet manifold ports 104 is two, the number of the outlet manifold ports 106 is two, the two inlet manifold ports 104 are communicated through an inlet throttling channel 108, and the two outlet manifold ports 106 are communicated through an outlet throttling channel 109.

In any of the above embodiments, preferably, the fin structure 10 includes two fins 100, the fin 100 is provided with a fluid sub-channel 103 and a fluid collecting port, the two fins 100 are oppositely disposed and attached to each other, so that central axes of the fluid collecting ports on the two fins 100 coincide with each other, and the fluid sub-channels 103 on the two fins 100 form a fluid channel 102 for fluid to flow.

In this embodiment, as shown in fig. 14 and 15, the fin structure 10 includes two fins 100, two fins 100 are oppositely disposed and attached to each other, that is, the two fins 100 are connected together in an inverted manner, and openings of fluid sub-channels 103 on the two fins 100 are oppositely disposed, so that the fluid sub-channels 103 on the two fins 100 form a fluid channel 102 for fluid to flow, and central axes of collecting ports on the two fins 100 are coincident with each other. Further, the two fins 100 are arranged in mirror symmetry, and the projections of the two fins 100 along the thickness direction of the fins 100 are completely overlapped.

In any of the above embodiments, preferably, the two fins 100 are connected by welding.

In this embodiment, the two fins 100 are connected by welding, and further, the two fins 100 are formed by flip welding.

Further, the two fins 100 may also be adhered together.

In any of the above embodiments, preferably, the fluid sub-channels 103 are grooves formed on the fin 100, and the fluid collecting ports are through holes formed on the fin 100.

In this embodiment, as shown in fig. 11 and 12, the fluid sub-channels 103 are grooves formed on the fins 100, the fluid sub-channels 103 on two fins 100 form the fluid channels 102 for fluid to pass through, the collecting ports are through holes, and when the plurality of fin structures 10 are stacked, the plurality of fin structures 10 communicate with each other through the collecting ports, so that the refrigerant flows in the plurality of fin structures 10.

Further, as shown in FIG. 10, the two inlet manifolds 104 communicate with each other through an inlet throttling passage 108.

In any of the above embodiments, preferably, the number of the fin structures 10 is at least two, and at least two fin structures 10 are sequentially stacked along the central axis direction of the collecting port.

In this embodiment, as shown in fig. 4, the number of the fin structures 10 is at least two, at least two fin structures 10 are stacked in the thickness direction of the fin 100, that is, at least two fin structures 10 are stacked in the central axis direction of the flow collecting port, and the refrigerant can flow into the at least two stacked fin structures 10 through the flow collecting port, so that the refrigerant can fully exchange heat with the fin structures 10, and the heat exchange efficiency of the heat exchanger 1 is improved.

Specifically, the number of the fin structures 10 is plural, the two fins 100 in each fin structure 10 may be any one of the fins 100 of the embodiments shown in fig. 1, fig. 2 and fig. 3, so that the fin structure 10 has various forms, when a plurality of fin structures 10 are stacked, for example, the two fins 100 in the embodiment shown in fig. 1 constitute a first fin structure, the two fins 100 in the embodiment shown in fig. 2 constitute a second fin structure, and the two fins 100 in the embodiment shown in fig. 3 constitute a third fin structure, when the heat exchanger 1 includes a plurality of fin structures 10, the fin structure 10 may be any one of or a combination of the first fin structure, the second fin structure and the third fin structure, so that the heat exchanger 1 has various combinations, and after the first fin structure, the second fin structure and the third fin structure are combined, the heat exchanger has a good shunting effect, so that the refrigerant and the fin structure 10 can exchange heat better, and the heat exchange effect of the heat exchanger 1 is improved.

In any of the above embodiments, preferably, the fin structures 10 are provided with connecting pipes on two sides, and the connecting pipes connect the collecting ports of two adjacent fin structures 10.

In this embodiment, as shown in fig. 5, connecting pipes are disposed on two sides of the fin structures 10, the connecting pipes are communicated with the flow collecting ports, when at least two fin structures 10 are stacked, two adjacent fin structures 10 are communicated with each other through the connecting pipes, so that the flow collecting ports of two adjacent fin structures 10 are communicated with each other, and further, the refrigerant can flow into the at least two fin structures 10 through the flow collecting ports and the connecting pipes and exchange heat with the fin structures 10.

Further, two adjacent fin structures 10 are welded and connected by a connecting pipe.

Further, as shown in fig. 7, the connection pipes include a first connection pipe 12 and a second connection pipe 14, and the first connection pipe 12 and the second connection pipe 14 are respectively communicated with the collecting port and respectively located at both sides of the fin structure 10.

Further, the pipe diameter of the first connecting pipe 12 is larger than that of the second connecting pipe 14, and the outer diameter of the second connecting pipe 14 is larger than or equal to the inner diameter of the collecting port.

In any of the above embodiments, the fin structure 10 is preferably symmetrical about a mid-plane that is perpendicular to a line connecting the center of the inlet manifold 104 and the center of the outlet manifold 106.

In this embodiment, the fin structure 10 is a symmetrical structure, and then the heat exchanger 1 can be manufactured by only one set of mold, so that the cost is saved, and the processing efficiency is improved.

Further, the fin structure 10 is symmetrical about a mid-plane that is a line connecting the center of the inlet manifold 104 directly connected to the end of the fluid channel 102 and the center of the outlet manifold 106 directly connected to the end of the fluid channel 102.

Specifically, as shown in fig. 3, the number of the inlet collecting ports 104 and the number of the outlet collecting ports 106 are two, the two inlet collecting ports 104 are communicated with each other through the inlet throttling passage 108, and the two outlet collecting ports 106 are communicated with each other through the outlet throttling passage 109, so that the fin structure 10 is a symmetrical structure, and the production and the manufacture of the fin structure 10 are facilitated.

Further, as shown in fig. 3, when the fin structure 10 is a symmetrical structure and the heat exchanger 1 is used as an evaporator, only the outlet collecting port 106 directly connected to the fluid sub-passage 103 is used, and the outlet collecting port 106 communicating with the fluid sub-passage 103 through the outlet throttle passage 109 is not used.

In any of the above embodiments, the number of fluid channels 102 on the fin structure 10 is preferably at least one.

In this embodiment, as shown in fig. 13, the number of the fluid channels 102 on the fin structure 10 is multiple, and the arrangement of the multiple fluid channels 102 improves the heat exchange efficiency between the fluid and the fin 100.

Further, as shown in fig. 8 and 9, the number of the fluid sub-channels 103 on the fin 100 is at least one, and the fluid sub-channels are symmetrical in the width direction of the fin 100.

In any of the above embodiments, the fin 100 is preferably integrally formed.

In this embodiment, the fins 100 are integrally formed, so that the heat exchange efficiency of the fins 100 and the fluid channels 102 is enhanced, and the integrally formed structure is simpler and more efficient to manufacture, while in the related art, the fins and the tubes are combined together after being expanded, so that the thermal contact resistance between the tubes and the fins is larger, and the heat exchange efficiency of the fins is lower.

Further, as shown in fig. 6, the heat exchanger 1 is vertically disposed to be consistent with the direction of gravity or to form a certain angle, so that the length direction of the fins 100 and the fluid channels 102 are disposed along the vertical direction, and the central axis of the collecting port is disposed along the horizontal direction, and further, when the heat exchanger 1 is used as an evaporator, the drainage performance of the condensed water is excellent, and the refrigerant distribution is not easily affected by gravity, thereby realizing two-phase flow distribution. In the related art, the heat exchangers of mass production comprise finned tube heat exchangers and microchannel heat exchangers, round tubes or flat tubes are arranged in the horizontal direction, meanwhile, in order to enlarge the heat conduction area outside the tubes, the fin parts are arranged in the vertical direction, so that condensate water is not smoothly discharged, air side pressure loss is large, the heat exchange tubes are placed in the horizontal direction and are easily influenced by gravity, and in addition, the number of heat conduction tubes is large, and the problem of difficult refrigerant distribution exists.

Specifically, according to the theory of heat transfer, the heat exchange amount Q is K · a₀Δ T, Total Heat transfer coefficient

Air side heat transfer coefficient h_o＝(Ap+η·Af)/A_o×h_aWherein, the specific meaning of the parameter in the above formula is: q: the amount of heat exchange; hw: conducting at the side of the refrigerant; ao: air side heat transfer area; and ho: an air-side thermal conductivity; ap: a tube heat conduction area; ha: fin portion air side conductivity; api: refrigerant side heat conduction area; af: the heat conducting area of the fin part; aco: the contact area of the fins with the tubes; eta: fin efficiency; and hc: contact conductivity of the fins to the tubes; Δ T: the temperature difference.

Specifically, the fin 100, the fluid channel 102, and the flow collecting port of the heat exchanger 1 of the present application are of an integrated structure, and have small thermal contact resistance, and can effectively improve fin efficiency η, improve total heat transfer coefficient, and finally improve heat transfer capacity, fig. 16 and 17 respectively compare the heat transfer capacity and the air side heat transfer coefficient under the same condition of the heat exchanger 1 of an embodiment of the present invention and a fin tube type heat exchanger and a micro-channel heat exchanger in the related art, as shown in fig. 16, a curve a shows the heat transfer capacity variation of the heat exchanger 1 provided by the present application under the same condition, a curve b shows the heat transfer capacity variation of the micro-channel heat exchanger in the related art under the same condition, a curve c shows the heat transfer capacity variation of the fin tube heat exchanger in the related art under the same condition, and as the wind speed increases, the heat transfer capacity of the heat exchanger 1 of the present application is better than the heat transfer capacities, as shown in fig. 17, a curve a represents a change of an air-side heat exchange coefficient of the heat exchanger 1 provided by the present application under the same condition, a curve b represents a change of an air-side heat exchange coefficient of the microchannel heat exchanger in the related art under the same condition, and a curve c represents a change of an air-side heat exchange coefficient of the finned tube heat exchanger in the related art under the same condition, and the air-side heat exchange coefficients of the heat exchanger 1 of the present application are better than those of the microchannel heat exchanger and the finned tube heat exchanger with an increase of wind speed, that is, the heat exchangers 1 have better heat exchange capacity.

Specifically, as shown in fig. 18, the air side pressure loss in the same case of the heat exchanger 1 according to one embodiment of the present invention and the fin tube heat exchanger and the micro-channel heat exchanger in the related art are compared, in which a curve a represents the air side pressure loss variation of the heat exchanger 1 provided in the present application in the same case, a curve b represents the air side pressure loss variation of the micro-channel heat exchanger in the related art in the same case, and a curve c represents the air side pressure loss variation of the fin tube heat exchanger in the related art in the same case, it can be seen that the air resistance performance of the heat exchanger 1 has a significant advantage compared with the fin tube heat exchanger, that is, the heat exchanger 1 of the present application is beneficial to reducing the air side pressure loss.

According to the second aspect of the present invention, there is also provided an air conditioner comprising: the heat exchanger 1 as set forth in any of the above embodiments.

The air conditioner provided by the second aspect of the invention comprises the heat exchanger 1 according to any one of the above embodiments, so that the air conditioner has all the advantages of the heat exchanger 1.

In the present invention, the term "plurality" means two or more unless explicitly defined otherwise. The terms "mounted," "connected," "fixed," and the like are to be construed broadly and include, for example, fixed connections, detachable connections, or integral connections; "coupled" may be direct or indirect through an intermediary. The specific meanings of the above terms in the present invention can be understood by those skilled in the art according to specific situations.

In the description herein, the description of the terms "one embodiment," "some embodiments," "specific embodiments," etc., means that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the invention. In this specification, the schematic representations of the terms used above do not necessarily refer to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples.

The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention, and various modifications and changes may be made by those skilled in the art. Any modification, equivalent replacement, or improvement made within the spirit and principle of the present invention should be included in the protection scope of the present invention.

Claims

1. A heat exchanger, comprising:

the fin structure is provided with a fluid channel and a flow collecting port, the flow collecting port comprises at least one inlet flow collecting port and at least one outlet flow collecting port, and the at least one inlet flow collecting port and the at least one outlet flow collecting port are communicated through the fluid channel.

2. The heat exchanger of claim 1,

the fin structure comprises at least two inlet collecting ports, and at least two inlet collecting ports are communicated through the inlet throttling channels.

3. The heat exchanger of claim 2,

the fin structure comprises at least two outlet collecting ports, and at least two outlet collecting ports are communicated through the outlet throttling channels.

4. The heat exchanger of any one of claims 1 to 3, wherein the fin structure further comprises:

the fin is provided with a fluid sub-channel and a flow collecting port, and the two fins are oppositely arranged and attached to each other, so that the central axes of the flow collecting ports on the two fins are overlapped, and the fluid sub-channels on the two fins form the fluid channel for fluid to flow.

5. The heat exchanger of claim 4,

the fluid sub-channels are grooves formed on the fins, and the flow collecting ports are through holes formed on the fins.

6. The heat exchanger according to any one of claims 1 to 3,

the number of the fin structures is at least two, and the at least two fin structures are sequentially stacked along the central axis direction of the flow collecting port.

7. The heat exchanger of claim 6,

connecting pipes are arranged on two sides of the fin structures and are used for communicating the flow collecting ports of two adjacent fin structures.

8. The heat exchanger according to any one of claims 1 to 3,

the fin structure takes a perpendicular plane connecting the center of the inlet flow collecting port and the center of the outlet flow collecting port as a symmetrical plane to form a symmetrical structure.

9. The heat exchanger of claim 4,

the number of the fluid channels on the fin structure is at least one; and/or

The fins are formed by integral molding.

10. An air conditioner, comprising:

a heat exchanger as claimed in any one of claims 1 to 9.