WO2021057543A1

WO2021057543A1 - Multi-channel heat exchanger and air conditioning refrigeration system

Info

Publication number: WO2021057543A1
Application number: PCT/CN2020/115229
Authority: WO
Inventors: 赵磊; 蒋建龙; 高强; 蒋皓波; 黄宁杰
Original assignee: 杭州三花微通道换热器有限公司
Priority date: 2019-09-29
Filing date: 2020-09-15
Publication date: 2021-04-01
Also published as: CN210689278U; US20220333833A1

Abstract

A multi-channel heat exchanger and an air conditioning refrigeration system. The multi-channel heat exchanger comprises a plurality of flat tubes (30); each flat tube (30) comprises a first flat tube part, a second flat tube part, a third flat tube part, and a fourth flat tube part which are distributed along the direction from an airflow inlet side to an airflow outlet side; each group of flat tube parts comprises at least two circulation channels; the flat tubes (30) have cross sections intersecting in the thickness direction of the flat tubes (30) and the width direction of the flat tubes (30); the cross section comprises a circulation section; the total area of the circulation sections of the first flat tube part is A1,…, the total area of the circulation sections of the fourth flat tube part is A4, and the total area A1 of the circulation sections of the first flat tube part is 1.05-1.4 times of the total area A4 of the circulation sections of the fourth flat tube part. The flat tube (30) can improve heat exchange efficiency of the heat exchanger on an air facing side, and enhance heat exchange capability of the heat exchanger.

Description

Multi-channel heat exchanger and air conditioning refrigeration system

Cross-references to related applications

This application requires the priority and rights of a Chinese patent application with an application number of 201921648808.5 and an application date of September 29, 2019. The entire content of the above Chinese patent application is hereby incorporated into this application by reference.

Technical field

The embodiments of the present application belong to the technical field of heat exchange equipment, and specifically relate to a multi-channel heat exchanger and an air conditioning refrigeration system having the multi-channel heat exchanger.

Background technique

As an alternative technology for copper tube fin heat exchangers, multi-channel heat exchangers have attracted more and more attention in the field of air conditioning technology, and have developed rapidly in recent years. Along the flow direction of the refrigerant, the refrigerant evaporates or condenses at different positions in the side-by-side flow channels, resulting in a mismatch between the flow distribution of the refrigerant in the flow channel and the heat exchange temperature difference. Obvious signs appear on the cross section of the flat tube near the windward side and the leeward side. Due to the temperature difference, an obvious supercooling or superheating temperature gradient is formed on the flat tube section near the outlet of the heat exchanger, and the temperature difference on the windward side cannot be better utilized.

Summary of the invention

For this reason, the embodiment of the present application proposes a multi-channel heat exchanger, which can improve the flow distribution of the refrigerant in the flow channel and the matching of the heat exchange temperature difference, and improve the heat exchange efficiency on the windward side of the heat exchanger , Improve the heat exchange capacity of the heat exchanger.

The multi-channel heat exchanger according to the embodiment of the present application includes: a plurality of flat tubes, the plurality of flat tubes are arranged at intervals along the thickness direction of the flat tubes, and the flat tubes are mutually arranged along the thickness direction of the flat tubes. Opposite and parallel first longitudinal side and second longitudinal side, and third longitudinal side and fourth longitudinal side opposite to each other along the width direction of the flat tube, between the first longitudinal side and the second longitudinal side The distance is smaller than the distance between the third longitudinal side surface and the fourth longitudinal side surface, and the flat tube is divided into four parts of equal width along the width direction of the flat tube, including the distance from the inlet side of the air flow to the air flow. The first flat tube portion, the second flat tube portion, the third flat tube portion, and the fourth flat tube portion distributed in the direction of the outlet side, each group of the flat tube portion includes at least two flow channels, the flow channels along the The length direction of the flat tube extends, and each of the circulation channels is arranged at intervals along the width direction of the flat tube, and the flat tube has a cross section that intersects along the thickness direction of the flat tube and the width direction of the flat tube. Including the flow cross section, the total area of the flow cross section of the first flat tube portion is A ₁ ..., the total area of the flow cross section of the fourth flat tube portion is A ₄ , and the flow of the first flat tube portion The total area A ₁ of the cross section is 1.05 to 1.4 times _{the total area A 4} of the flow cross section of the fourth flat tube portion.

According to the flat tube of the embodiment of the present application, the circulation cross-sectional area of the four-part circulation channel is set to decrease sequentially from the air inlet side to the air outlet side, so that the heat exchange on the windward side and the windward side of the multi-channel heat exchanger can be achieved. The heat exchange can reasonably match the heat exchange demand of the air flow on the air inlet side and on the air outlet side, improve the heat exchange efficiency on the windward side, and then improve the heat exchange performance of the multi-channel heat exchanger.

In some embodiments, the distance between the circulation channel of any one of the four flat tube portions and the two adjacent circulation channels is equal.

In some embodiments, the distance between any two adjacent circulation channels of the first flat tube portion is greater than the distance between any two adjacent circulation channels of the second flat tube portion distance.

In some embodiments, the sum of the cross-sectional areas of the circulation channels of the first flat tube part that are completely located in the first flat tube part is smaller than the sum of the cross-sectional areas of the second flat tube parts. The sum of the cross-sectional areas of the circulation channels that are completely located in the second flat tube portion in the circulation channel.

In some embodiments, it further includes a fin: the fin is arranged between the two flat tubes along the width direction of the flat tube and is connected to the two flat tubes respectively, and the fin includes a first 1 to nth group of fins, the first group of fins,..., the nth group of fins are distributed along the direction from the inlet side of the air flow to the outlet side of the air flow, where 1≤n, n is an integer, The air-side heat transfer coefficient of the n-th group of fins is smaller than the air-side heat transfer coefficient of the first group of fins.

In some embodiments, each of the first to nth groups of fins is provided with a plurality of shutters arranged along the width direction of the flat tube, and the number of shutters of the first group of fins is greater than that of the nth group of fins Number of.

In some embodiments, the multi-channel heat exchanger has at least one of the following characteristics: a. The opening width of the shutters of the first group of fins is greater than the opening width of the shutters of the nth group of fins; b; The opening angle of the shutters of the first group of fins is greater than the opening angle of the shutters of the nth group of fins; c. The opening length of the shutters of the first group of fins is greater than the opening length of the shutters of the nth group of fins .

In some embodiments, the distance between two adjacent fins in the first group of fins along the length of the flat tube is smaller than that of two adjacent fins in the nth group of fins along the length of the flat tube. The pitch of the fins.

In some embodiments, the flow cross-sectional area of each flow channel of each group of the flat tube portions is equal.

In some embodiments, the multi-channel heat exchanger has at least one of the following features: a. The cross-sectional area and shape of each of the flow channels in the same group of the flat tube portions are the same; b. The flat tube portion includes the same number of flow channels; c. Any two of the flow channels have the same length in the width direction of the flat tube, and the flow channels of the flat tube portions of different groups are along the flat tube. The length of the tube in the thickness direction is different; d. The length of any two of the flow channels along the thickness direction of the flat tube is the same, and the flow channels of the flat tube portions of different groups are along the width direction of the flat tube The length is different; e. At least part of the circulation channel is provided with internal ribs.

This application also proposes an air-conditioning refrigeration system.

The air conditioning and refrigeration system according to an embodiment of the present application includes the multi-channel heat exchanger, the second heat exchanger, the compressor, and the throttle valve described in any of the above embodiments, and the first set of the multi-channel heat exchanger One of the first ends of the flow tube and the second heat exchanger is connected to the inlet end of the compressor, and the first header of the multi-channel heat exchanger is connected to the first end of the second heat exchanger. The other one of the ends is connected to the outlet end of the compressor, and the throttle valve is connected between the second header of the multi-channel heat exchanger and the second end of the second heat exchanger .

The air-conditioning refrigeration system and the above-mentioned multi-channel heat exchanger have the same advantages over the prior art, which will not be repeated here.

The additional aspects and advantages of the present application will be partly given in the following description, and part of them will become obvious from the following description, or be understood through the practice of the present application.

Description of the drawings

The above and/or additional aspects and advantages of the present application will become obvious and easy to understand from the description of the embodiments in conjunction with the following drawings, in which:

Fig. 1 is a schematic structural diagram of a multi-channel heat exchanger according to an embodiment of the present application;

Figure 2 is a schematic side view of the multi-channel heat exchanger of the embodiment of the present application (the direction of the arrow is the air flow direction);

Fig. 3 is a schematic view of the structure of the fins of the multi-channel heat exchanger of the embodiment of the present application in one view;

Fig. 4 is a schematic view of the structure of the fins of the multi-channel heat exchanger of the embodiment of the present application from another perspective;

Fig. 5 is a schematic diagram of the fins of the multi-channel heat exchanger according to an embodiment of the present application;

Fig. 6 is a schematic diagram of the fins of the multi-channel heat exchanger according to an embodiment of the present application;

Figure 7 is a cross-sectional view of the flat tube of the multi-channel heat exchanger of the embodiment of the present application;

Fig. 8 is a cross-sectional view of a flat tube of a multi-channel heat exchanger according to an embodiment of the present application;

9 is a cross-sectional view of the flat tube of the multi-channel heat exchanger of the embodiment of the present application;

10 is a cross-sectional view of the flat tube of the multi-channel heat exchanger of the embodiment of the present application;

Figure 11 is a cross-sectional view of the flat tube of the multi-channel heat exchanger of the embodiment of the present application;

Fig. 12 is a cross-sectional view of a flat tube of a multi-channel heat exchanger according to an embodiment of the present application.

Reference signs:

Multi-channel heat exchanger 100,

The first header 10, the second header 20,

Flat tube 30, first longitudinal side 30a, second longitudinal side 30b, third longitudinal side 30c, fourth longitudinal side 30d, circulation channel 30e, first group of circulation channels 31, second group of circulation channels 32, and third group of circulation Channel 33, the fourth group of circulation channels 34, the fifth group of circulation channels 35, the sixth group of circulation channels 36, the seventh group of circulation channels 37, the inner rib 38,

The fin 40, the shutter 40a.

detailed description

The embodiments of the present application are described in detail below. Examples of the embodiments are shown in the accompanying drawings, in which the same or similar reference numerals denote the same or similar elements or elements with the same or similar functions. The embodiments described below with reference to the drawings are exemplary, and are only used to explain the present application, and should not be understood as a limitation to the present application.

Hereinafter, the multi-channel heat exchanger 100 of the embodiment of the present application will be described with reference to FIGS. 1 to 12.

As shown in FIGS. 1 and 2, the multi-channel heat exchanger 100 of the embodiment of the present application includes: a first header 10, a second header 20 and a plurality of flat tubes 30.

As shown in Figure 1, the axial direction of the first header 10 and the axial direction of the second header 20 can be parallel, the first header 10 and the second header 20 can be arranged in parallel and spaced apart from each other. The header 10 and the second header 20 are distributed along the length of the flat tube 30. The first header 10 can be used as the inlet header, and the second header 20 can be used as the outlet header, or the first header. The flow tube 10 can be used as an outlet header, and the second header 20 can be used as an inlet header.

As shown in FIG. 1, a plurality of flat tubes 30 are arranged at intervals along the thickness direction of the flat tubes 30, and the thickness direction of the flat tubes 30 may be parallel to the axial direction of the first header 10 and the axial direction of the second header 20, The plurality of flat tubes 30 may be spaced apart and arranged along the axial direction of the first header 10 and the axial direction of the second header 20. As shown in Figure 2, the first end of the flat tube 30 is connected to the first header 10, and the second end of the flat tube 30 is connected to the second header 20 to communicate the first header 10 and the second header. Flow tube 20, so that the heat exchange medium can be in the first header 10-flat tube 30-second header 20 or second header 20-flat tube 30-first header 10 Circulate between. The first header 10 may be provided with a first port, and the second header 20 may be provided with a second port. The first port and the second port are used to connect to an external pipeline to connect the heat exchanger to the entire In air conditioning systems or other heat exchange systems.

As shown in Figs. 7-12, the flat tube 30 has a first longitudinal side 30a, a second longitudinal side 30b, a third longitudinal side 30c, and a fourth longitudinal side 30d.

Wherein, the first longitudinal side 30a and the second longitudinal side 30b are opposite and parallel to each other along the thickness direction of the flat tube 30, the third longitudinal side 30c and the fourth longitudinal side 30d are opposite to each other along the width direction of the flat tube 30, and the first The distance between the longitudinal side 30a and the second longitudinal side 30b is smaller than the distance between the third longitudinal side 30c and the fourth longitudinal side 30d, that is, the thickness of the flat tube 30 is smaller than the width.

In the actual application of the multi-channel heat exchanger 100, air flows through the gap between the two flat tubes 30, that is, the air passes through the first longitudinal side 30a and the second longitudinal side 30b. The flat tube 30 of the present application In this case, the first longitudinal side 30a and the second longitudinal side 30b are arranged in parallel, that is, the thickness of the flat tube 30 is constant along the air inlet direction, so that the flat tube 30 itself has little influence on the fluidity of the air.

7-12, the flat tube 30 is divided into four parts of equal width along the width direction of the flat tube 30, and the four parts include the first distributed in the direction from the inlet side of the air flow to the outlet side of the air flow. 1 flat tube part, second flat tube part, third flat tube part and fourth flat tube part, and each flat tube part includes at least two circulation channels 30e, the circulation channels 30e extend along the length direction of the flat tube and have four parts The respective circulation channels 30e of the flat tube part are distributed at intervals along the width direction of the flat tube 30. The flat tube 30 has a cross section that intersects the thickness direction of the flat tube 30 and the width direction of the flat tube 30. The cross section includes a flow section. The first flat tube part The total area of the flow cross section of is A ₁ _{, the total area of the flow cross section of the fourth flat tube part is A 4} , and the total area of the flow cross section of the _{first flat tube part A 1} is the total area of the flow cross section of the fourth flat tube a _4-fold 1.4-fold -1.05, wherein a total cross-sectional flow area of the second portion of the flat tube a _2, the total cross-sectional flow area of the third portion of the flat tubes is a _3. It should be noted that the flat tube 30 of the present application is divided into four parts along its width direction, and the distribution of the circulation channel 30e has no direct correspondence with the separation of the flat tube. Therefore, the circulation channel 30e may be divided into four parts. At least a part is divided into the former flat tube part, and the remaining part is divided into the latter flat tube part. Therefore, the flow cross section of the flat tube part referred to in the present application includes the cross section of the complete flow channel and the cross section of the incomplete flow channel located in the flat tube part.

Thus, total area A of the second flow cross-section of the flat tube portion ₂ may be the total area of flow cross-section of the third flat pipe portion is 1.3 times A _3, and the total area A of the third flow cross-section of the flat tube portion ₃ may be the total cross-sectional flow area of the flat tubes 4 is 1.2 times the section a _4, the flow cross-sectional area along the air inlet flow path 30e i.e. four portions of the flat side of the tube portion is gradually increased to the air outlet side. Of course, the number of circulation channels 30e is not limited to four parts, but can also be more groups, such as six groups, seven groups or eight groups. Among them, any one of the four-part flat tube portion 30e can be connected to the adjacent one. The distance between the two circulation channels 30e is set to be equal, so that each group of circulation channels 30e is evenly arranged.

It can be understood that when the air flows through the multi-channel heat exchanger 100, the temperature difference between the airflow on the windward side of the multi-channel heat exchanger 100 and the heat exchange medium is relatively large, and the outlet air of the multi-channel heat exchanger 100 The temperature difference between the airflow on the side and the heat exchange medium is small. In this way, the heat exchange demand of the airflow on the outlet side of the multi-channel heat exchanger 100 is smaller than the heat exchange demand of the airflow on the windward side of the multichannel heat exchanger 100, where the windward side of the multichannel heat exchanger 100 corresponds to the airflow On the inlet side, the air outlet side of the multi-channel heat exchanger 100 corresponds to the air outlet side.

In the related art, the cross-sectional area of the multiple circulation channels 30e from the windward side to the windward side of the multi-channel heat exchanger 100 is the same. Due to the heat transfer between the airflow and the heat exchange medium, each circulation channel 30e arranged side by side is along the wind flow direction. (Horizontal direction) The temperature of the heat exchange medium is different. Therefore, at a certain position, the heat exchange medium in the first group of flow passages on the windward side has been evaporated or condensed, while the heat exchange medium in the lateral rear flow passage has not yet evaporated or condensed.

In some embodiments, the distance between any two adjacent circulation channels 30e of the _{first flat tube portion is B 1} , and the distance between any two adjacent circulation channels 30e of the second flat tube portion is B ₂ , B _{1 is} greater than B ₂ , that is, the spacing of the circulation channels of each group of circulation channels 30 e from the inlet side of the air flow to the outlet side of the air flow in the plurality of sets of circulation channels 30 e gradually decreases.

In some embodiments, the sum of the cross-sectional areas of the circulation channels 30e of the first flat tube portion that are completely located in the first flat tube portion is C ₁ , and the flow channels 30e of the second flat tube portion are completely located in The sum of the cross-sectional area of the flow passage 30e of the second flat tube portion is C ₂ , and C _{2 is} greater than C ₁ , in other words, the cross-sectional area of the flow passage 30e of each flat tube portion from the inlet side of the air flow to the outlet side of the air flow Gradually increase. It should be noted that the flat tube 30 of the present application is divided into four parts along its width direction, and the distribution of the circulation channel 30e has no direct correspondence with the separation of the flat tube. Therefore, the circulation channel 30e may be divided into four parts. At least a part is divided into the former flat tube part, and the remaining part is divided into the latter flat tube part.

In this application, as shown in Figs. 7-12, the cross-sectional area of the circulation passage 30e corresponding to the multi-flat tube portion is set to decrease sequentially from the air inlet side to the air outlet side, so that the multi-flat tube portion The flow rate of the heat exchange medium in the air inlet side to the air outlet side decreases sequentially, that is, the heat exchange effect of the multi-channel heat exchanger 100 gradually weakens from the air inlet side to the air outlet side, thereby making the multi-channel heat exchanger The heat exchange on the windward side and the heat exchange on the outlet side of 100 can reasonably match the heat exchange demand of the airflow on the air inlet side and on the air outlet side, so that the heat exchange on both sides of the multi-channel heat exchanger 100 The effect more satisfies actual needs, balances the temperature difference between the windward side and the windward side of the multi-channel heat exchanger 100, prevents the multi-channel heat exchanger 100 from overcooling on one side and overheating on one side, and ensures the multi-channel heat exchanger 100 Use rationally and safely to improve the heat exchange performance of the multi-channel heat exchanger 100.

According to the flat tube 30 of the embodiment of the present application, the flow cross-sectional area of the flow passage of the four flat tube portions is set to decrease sequentially from the air inlet side to the air outlet side, which enables heat exchange on the windward side of the multi-channel heat exchanger 100 The amount of heat exchange and the heat exchange on the air outlet side can reasonably match the heat exchange requirements of the airflow on the air inlet side and the air outlet side, thereby effectively balancing the temperature difference of the refrigerant in the flat tube 30 on the windward and leeward sides, and optimizing the outlet flow. The degree of cold overheating further improves the heat exchange performance of the multi-channel heat exchanger 100.

In some embodiments, as shown in FIG. 3, the multi-channel heat exchanger 100 further includes fins 40. The fins 40 are arranged between the two flat tubes 30 along the width direction of the flat tubes 30, and the fins 40 are respectively Connected to two flat tubes 30, the fins include first to nth groups of fins 40.

Wherein, as shown in FIG. 4, each group includes at least one fin 40, and the first to nth groups of fins 40 are installed on the first longitudinal side 30a of one flat tube 30 and the second side of an adjacent flat tube 30. Between the longitudinal sides 30b, and the first to nth groups of fins 40 are arranged in sequence along the width direction of the flat tube 30, the first group of fins 40,..., the nth group of fins 40 along the air inlet side to the air outlet side , Where 1≤n, n is an integer.

Since the flat tube 30 is provided with a plurality of circulation channels 30e in the width direction, the plurality of circulation channels 30e can correspond to the n groups of fins 40, so that the heat of the heat exchange medium in the multi-channel heat exchanger 100 can be diffused to the fins. The fin 40 exchanges heat with the air flow, and the fin 40 has a large surface area, so that the air flow can exchange heat with the fin 40 sufficiently, so that the heat dissipation effect of each part of the multi-channel heat exchanger 100 can be maintained At a higher level.

Among them, the air-side heat transfer coefficient of the n-th group of fins 40 is smaller than the air-side heat transfer coefficient of the first group of fins 40, and the air-side heat transfer coefficient of the n-th group of fins 40 decreases sequentially from the first group to the n-th group. , And the heat transfer coefficient of the fin 40 near the air inlet side is greater than the heat transfer coefficient of the fin 40 near the air inlet side, so that the multiple sets of fins 40 can reasonably match the airflow on the air inlet side and the air outlet side. The heat exchange demand effectively balances the temperature difference of the refrigerant in the flat tubes 30 on the windward side and the leeward side, optimizes the degree of supercooling and superheat at the outlet, and thereby improves the heat exchange performance of the multi-channel heat exchanger 100.

In some embodiments, the first to nth groups of fins 40 are each provided with a plurality of louvers 40a arranged along the width direction of the flat tube 30, and the number of louvers 40a of the first group of fins 40 is Q ₁ ,..., The number of shutters 40a of the _k- th group of fins 40 is Q k ,..., the number of shutters 40a of the n-th group of fins 40 is Q _n , where it is satisfied that Q _{1 is} greater than Q _n , and when n is greater than 1, It is satisfied that Q _{k-1 is} greater than Q _k .

That is, as shown in FIG. 5, the number of louvers 40a from the first to the nth groups in the n groups of fins 40 is sequentially reduced, and the greater the number of louvers 40a, the better the heat exchange effect, so that the multi-channel exchange The heat exchange effect of the heat exchanger 100 on the air inlet side is greater than that on the air outlet side. In this way, the heat exchange effect of the multi-channel heat exchanger 100 can reasonably match the heat exchange demand of the air flow on the air inlet side and the air outlet side, optimize the outlet supercooling and superheating, and avoid unilateral overheating and unilateral overheating. In cold conditions, the rationality of the structural design of the multi-channel heat exchanger 100 is improved.

In some embodiments, the multi-channel heat exchanger 100 has at least one of the following features:

a. As shown in Figures 4 and 6, the opening width of the shutter 40a of the first group of fins 40 is W ₁ ,..., and the opening width of the shutter 40a of the kth group of fins 40 is W _k ,... , The window width of the shutter 40a of the n-th group of fins 40 is W _n , which satisfies: W _{1 is} greater than W _n , and when n is greater than 1, it is satisfied that W _{k-1 is} greater than W _k . As a result, the opening widths of the shutters 40a from the first group to the nth group of the n groups of fins 40 are sequentially reduced, and the larger the opening width of the shutters 40a, the better the heat transfer effect, so that the multi-channel heat exchanger The heat exchange effect of 100 on the air inlet side is greater than that on the air outlet side. In this way, the heat exchange effect of the multi-channel heat exchanger 100 can reasonably match the heat exchange demand of the air flow on the air inlet side and the air outlet side, and the heat exchange performance of the multi-channel heat exchanger 100 can be improved.

b. As shown in Figure 4, the opening angles of the shutters 40a of the first group of fins 40 are R ₁ ,..., and the opening angles of the shutters 40a of the kth group of fins 40 are R _k , ……, nth The window opening angle of the shutter 40a of the group of fins 40 is R _n , where R _{1 is} greater than R _n , and when n is greater than 1, R _{k-1 is} greater than R _k , so that the n group of fins 40 from The opening angles of the shutters 40a of the first to the nth groups are successively reduced, and the greater the opening angle of the shutters 40a, the better the heat exchange effect, so that the heat exchange effect of the multi-channel heat exchanger 100 from the air inlet side Greater than the heat exchange effect on the air outlet side. In this way, the heat exchange effect of the multi-channel heat exchanger 100 can reasonably match the heat exchange demand of the air flow on the air inlet side and the air outlet side, and the heat exchange performance of the multi-channel heat exchanger 100 can be improved.

c. As shown in Figure 4, the opening length of the shutter 40a of the first group of fins 40 is L ₁ ,..., the opening length of the shutter 40a of the kth group of fins 40 is L _k ,..., the nth The window length of the shutter 40a of the group fin 40 is L _n , where L _{1 is} greater than L _n , and when n is greater than 1, it is satisfied that L _{k-1 is} greater than L _k . In this way, the opening lengths of the shutters 40a from the first group to the nth group of the n groups of fins 40 are sequentially reduced, and the greater the opening length of the shutter 40a, the better the heat transfer effect, so that the multi-channel heat exchanger 100 The heat exchange effect on the air inlet side is greater than that on the air outlet side. In this way, the heat exchange effect of the multi-channel heat exchanger 100 can reasonably match the heat exchange demand of the air flow on the air inlet side and the air outlet side, and the heat exchange performance of the multi-channel heat exchanger 100 can be improved.

Therefore, when the multi-channel heat exchanger 100 of the present application satisfies at least one of the above characteristics, the air-side heat transfer coefficient or heat dissipation performance of the former group of fins 40 is better than that of the latter group of fins 40. The heat transfer coefficient, combined with the previous set of circulation channels 30e with a larger cross-sectional area, can further increase the heat exchange between the windward side fins 40 and the air, and increase the heat exchange between the refrigerant and the air, so as to exchange on the air outlet side. When it is hot, the heat exchange medium on the air outlet side can also exchange heat effectively, so that the heat exchange effects on both sides of the multi-channel heat exchanger 100 can be balanced.

In some embodiments, as shown in FIG. 3, the distance between two adjacent fins 40 along the length of the flat tube 30 in the first group of fins 40 is Fp ₁ ,..., the middle edge of the k-th group of fins 40 The distance between two adjacent fins 40 in the length direction of the flat tube 30 is Fp _k ,..., the distance between two adjacent fins 40 in the length direction of the flat tube 30 in the n-th group of fins 40 is Fp _n , which satisfies : Fp _{1 is} less than Fp _n , where, when n is greater than 1, Fp _{k-1 is} less than Fp _k . In other words, the distance between two adjacent fins 40 of the former group of fins 40 is smaller than the distance between two adjacent fins 40 of the latter group of fins 40, so that the air-side heat transfer coefficient of the former group of fins 40 In other words, the heat dissipation performance is better than the air-side heat transfer coefficient of the latter group of fins 40, and the latter group of circulation channels 30e with a larger circulation cross-sectional area can further increase the heat exchange between the windward-side fins 40 and the air. The heat exchange between the refrigerant and the air is increased, so that when heat is exchanged on the air outlet side, the heat exchange medium on the air outlet side can also exchange heat effectively, so that the heat exchange effects on both sides of the multi-channel heat exchanger 100 can be balanced.

Therefore, by combining the cross-sectional area of the internal circulation channel 30e of the flat tube 30 and the relevant parameters of the fin 40, the temperature gradient on the cross section of the flat tube 30 of the multi-channel heat exchanger 100 is effectively reduced, and the windward side and the leeward side are balanced. The temperature difference of the heat exchange medium inside the side optimizes the degree of supercooling and superheat at the outlet, thereby improving the heat exchange performance of the multi-channel heat exchanger 100.

Wherein, a boss can be provided on the fin 40, and the ratio of the number of bosses from the windward side to the leeward side of the fin 40 can be increased; or the ratio of the boss contact area from the windward side to the leeward side of the fin 40 can be increased ; Or reduce the flanging height on the windward side fin 40, increase the number of fins 40 from the windward side to the leeward side of the fin 40; adjust the distribution density of the fin 40, such as the fin 40 on the windward side The density is greater than the density of the fin 40 on the leeward side to balance the heat exchange effect on both sides of the multi-channel heat exchanger 100.

In some embodiments, as shown in FIGS. 8 and 9, each flat tube portion includes a plurality of flow channels 30e, and the flow cross-sectional area of each flow channel 30e of the same flat tube portion is equal, so that each flat tube portion The plurality of circulation passages 30e can circulate the heat exchange medium, which increases the overall heat exchange efficiency of the multi-channel heat exchanger 100.

a. As shown in Figures 8 and 9, the cross-sectional area of each circulation channel 30e of the same flat tube portion has the same shape, so that the flat tube 30 can be extruded.

b. As shown in Figures 8 and 9, each flat tube portion includes a plurality of circulation channels 30e, and each flat tube portion includes the same number of circulation channels 30e, so that the overall structure of the multi-channel heat exchanger 100 is more regular .

c. As shown in Figure 8, any two circulation channels 30e have the same length in the width direction of the flat tube 30, and the circulation channels 30e of different flat tube parts have different lengths in the thickness direction of the flat tube 30, but the length of the multi-flat tube part is different. The cross-sectional area of the circulation channel 30e still decreases from the windward side to the leeward side.

d. As shown in Figures 7 and 9, any two circulation channels 30e have the same length along the thickness direction of the flat tube 30, and the circulation channels 30e of different flat tube portions have different lengths along the width direction of the flat tube 30, but there are multiple groups The cross-sectional area of the circulation channel 30e still decreases from the windward side to the leeward side.

e. The outer contour of each circulation channel 30e is the same. For example, the outer contour of each circulation channel 30e can be one of rectangle, circle, hexagon and triangle, and at least part of the circulation channel 30e is provided with internal ribs. 38. Among them, the inner diameter is mainly provided in the circulation channel 30e near the leeward side, so as to reduce the cross-sectional area of the circulation channel 30e on the leeward side.

In some embodiments, the circulation channel 30e of the at least one second flat tube part is greater than or equal to the circulation channel 30e of any one of the third flat tube parts; the circulation channel 30e of the first flat tube part and the circulation channel 30e of the second flat tube part The cross-sectional areas of at least two of the passage 30e and the circulation passage 30e of the third flat tube part are equal; and the circulation passage 30e of the first flat tube part, the circulation passage 30e of the second flat tube part, and the third flat tube The number of flow channels 30e of the flow channels 30e of the first flat tube portion is set to be the same, or the number of flow channels 30e of the flow channel 30e of the first flat tube portion, the flow channel 30e of the second flat tube portion, and the flow channel 30e of the third flat tube portion is set To decrease sequentially.

In some embodiments, the shape of the flat tube 30 is circular, and a plurality of internal ribs 38 are provided in the flat tube 30, and the number of internal ribs 38 on the windward side is less than the number of internal ribs 38 on the leeward side. The flow resistance of the heat exchange medium on the leeward side is increased, and the flow resistance on the windward side is reduced. And as shown in FIG. 10, the portion of the flat tube 30 near the leeward side is provided with an inner rib 38.

As shown in FIG. 10, the flat tube 30 sequentially includes a flow channel 31 of a first flat tube part, a flow channel 32 of a second flat tube part, a flow channel 33 of a third flat tube part, and a flow channel 34 of a fourth flat tube part. , The circulation channel 35 of the fifth flat tube part, the circulation channel 36 of the sixth flat tube part, the circulation channel 37 of the seventh flat tube part, and the circulation channel 30e of the multi-flat tube part near the leeward side is provided with internal ribs 38 .

Or set the shape of the flat tube 30 to be elliptical or polygonal, as shown in Figures 7-12, the shape of the flat tube 30 is elliptical, and the number or area of the flow channels 30e on the windward side is greater than that on the leeward side; or The flat tube 30 adopts a wire tube, and along the direction from the windward side to the leeward side, the number of the windward side silk tube is more than the leeward side or the inner cross section of the silk tube is larger than the leeward side silk tube.

In this way, through the shape of the flat tube 30, the shape and arrangement of the circulation channel 30e, the heat exchange on the windward side and the heat exchange on the leeward side of the multi-channel heat exchanger 100 can match the actual heat exchange requirements. To effectively reduce the temperature gradient on the cross section of the flat tube 30 of the multi-channel heat exchanger 100, balance the temperature difference between the heat exchange medium on the windward side and the leeward side, optimize the outlet supercooling and superheat, and then improve the exchange rate of the multi-channel heat exchanger 100. Thermal performance.

This application also proposes an air-conditioning refrigeration system.

The air conditioning and refrigeration system according to the embodiment of the present application includes the multi-channel heat exchanger 100, the second heat exchanger, the compressor, the throttle valve, and the first header of the multi-channel heat exchanger 100 of any of the above embodiments 10 and one of the first ends of the second heat exchanger is connected to the inlet end of the compressor, and the other of the first header 10 and the first end of the second heat exchanger of the multi-channel heat exchanger 100 is connected with The outlet end of the compressor is connected, and the throttle valve is connected between the second header 20 of the multi-channel heat exchanger 100 and the second end of the second heat exchanger.

Therefore, by providing the above-mentioned multi-channel heat exchanger 100 in the air-conditioning and refrigeration system, the heat exchange medium in each flat tube of the air-conditioning and refrigeration system can effectively exchange heat to the air flow, without local insufficient heat exchange and The situation of local excess heat exchange improves the rationality of the structural design of the air-conditioning refrigeration system and the practicability of the air-conditioning refrigeration system.

In the description of this specification, the description with reference to the terms "one embodiment", "some embodiments", "exemplary embodiments", "examples", "specific examples", or "some examples" etc. means to incorporate the implementation The specific features, structures, materials, or characteristics described by the examples or examples are included in at least one embodiment or example of the present application. In this specification, the schematic representation of the above-mentioned terms does not necessarily refer to the same embodiment or example. Moreover, the described specific features, structures, materials or characteristics may be combined in any one or more embodiments or examples in a suitable manner.

Although the embodiments of the present application have been shown and described, those of ordinary skill in the art can understand that various changes, modifications, substitutions, and modifications can be made to these embodiments without departing from the principle and purpose of the present application. The scope of the application is defined by the claims and their equivalents.

Claims

A multi-channel heat exchanger, characterized in that it comprises:

A plurality of flat tubes, the plurality of flat tubes are arranged at intervals along the thickness direction of the flat tube,

The flat tube has a first longitudinal side and a second longitudinal side opposite and parallel to each other in the thickness direction of the flat tube, and a third longitudinal side and a fourth longitudinal side opposite to each other in the width direction of the flat tube, so The distance between the first longitudinal side surface and the second longitudinal side surface is smaller than the distance between the third longitudinal side surface and the fourth longitudinal side surface, and the flat tube is divided into equal widths along the width direction of the flat tube The four parts, including the first flat tube part, the second flat tube part, the third flat tube part and the fourth flat tube part distributed along the direction from the inlet side of the air flow to the outlet side of the air flow, each group of the flat tube The pipe portion includes at least two circulation channels extending along the length direction of the flat tube, and each of the circulation channels is arranged at intervals along the width direction of the flat tube, and the flat tube has a length along the flat tube. A cross section where the thickness direction and the width direction of the flat tube intersect, the cross section includes a flow cross section, and the total area of the flow cross section of the first flat tube portion is A 1 , ..., the flow of the fourth flat tube portion The total area of the cross section is A 4 , and the total area A 1 of the flow cross section of the first flat tube portion is 1.05 to 1.4 times the total area A 4 of the flow cross section of the fourth flat tube portion.
The multi-channel heat exchanger according to claim 1, wherein the distance between any one of the four-part flat tube portions and the two adjacent ones of the circulation channels is equal.
The multi-channel heat exchanger according to claim 1, wherein the distance between any two adjacent circulation channels of the first flat tube portion is greater than any phase of the second flat tube portion The distance between two adjacent circulation channels.
The multi-channel heat exchanger according to claim 1, wherein the sum of the cross-sectional area of each of the circulation channels of the first flat tube portion that are completely located in the first flat tube portion It is smaller than the sum of the cross-sectional area of each of the circulation channels of the second flat tube portion that are completely located in the second flat tube portion.
The multi-channel heat exchanger according to any one of claims 1 to 4, further comprising fins, the fins being arranged between the two flat tubes along the width direction of the flat tubes And are respectively connected to the two flat tubes, the fins include the first to the nth group of fins, the first group of fins, ..., the nth group of fins along the inlet side of the airflow to the airflow The direction distribution on the outlet side of the fins, where 1≤n, n is an integer, and the air-side heat transfer coefficient of the nth group of fins is smaller than the air-side heat transfer coefficient of the first group of fins.
The multi-channel heat exchanger according to claim 5, wherein each of the first to nth groups of fins is provided with a plurality of louvers arranged along the width direction of the flat tube, and the first group of fins The number of shutters is greater than the number of shutters of the nth group of fins.
The multi-channel heat exchanger according to claim 6, wherein the multi-channel heat exchanger has at least one of the following characteristics:

a. The opening width of the shutters of the first group of fins is greater than the opening width of the shutters of the nth group of fins;

b. The opening angle of the shutters of the first group of fins is greater than the opening angle of the shutters of the nth group of fins;

c. The opening length of the shutters of the first group of fins is greater than the opening length of the shutters of the nth group of fins.
The multi-channel heat exchanger according to claim 6, wherein the distance between two adjacent fins in the first group of fins along the length of the flat tube is smaller than that of the middle edge of the nth group of fins. The distance between two adjacent fins in the length direction of the flat tube.
The multi-channel heat exchanger according to any one of claims 1-8, wherein the circulation cross-sectional area of each circulation channel of each group of the flat tube portions is equal.
The multi-channel heat exchanger according to claim 9, wherein the multi-channel heat exchanger has at least one of the following characteristics:

a. The cross-sectional area and shape of each of the circulation channels of the same group of the flat tube portions are the same;

b. Each group of the flat tube portion includes the same number of the circulation channels;

c. Any two of the flow channels have the same length in the width direction of the flat tube, and the flow channels of different groups of the flat tube portions have different lengths in the thickness direction of the flat tube;

d. Any two of the flow channels have the same length in the thickness direction of the flat tube, and the flow channels of different groups of the flat tube portions have different lengths in the width direction of the flat tube;

e. At least part of the circulation channels are provided with internal ribs.
An air-conditioning refrigeration system, comprising: the multi-channel heat exchanger, a second heat exchanger, a compressor, and a throttle valve according to any one of claims 1-10, and the multi-channel heat exchange One of the first header of the multi-channel heat exchanger and the first end of the second heat exchanger is connected to the inlet of the compressor, and the first header of the multi-channel heat exchanger is connected to the second The other of the first ends of the heat exchanger is connected to the outlet end of the compressor, and the throttle valve is connected to the second header of the multi-channel heat exchanger and the second heat exchanger. Between the second end.