CN116972454A

CN116972454A - Heat exchange system

Info

Publication number: CN116972454A
Application number: CN202210424255.5A
Authority: CN
Inventors: 金俊峰; 高强; 蒋建龙; 杨永龙
Original assignee: Sanhua Hangzhou Micro Channel Heat Exchanger Co Ltd
Current assignee: Sanhua Hangzhou Micro Channel Heat Exchanger Co Ltd
Priority date: 2022-04-21
Filing date: 2022-04-21
Publication date: 2023-10-31

Abstract

The application discloses a heat exchange system, which comprises a compressor, a throttling assembly, a pipeline, a fan, a heat exchanger and a refrigerant, wherein the heat exchanger comprises a first pipe and a second pipe; the heat exchange tube comprises a plurality of heat exchange channels, and the heat exchange tube comprises a first heat exchange tube and a second heat exchange tube; the first piece comprises a first cavity which is communicated with the heat exchange channels of the plurality of first heat exchange tubes, and the first cavity is communicated with the heat exchange channels of the plurality of second heat exchange tubes; the heat exchanger also comprises a plurality of inlet and outlet pipes, at least one inlet and outlet pipe is directly or indirectly connected with the first piece, and the inlet and outlet pipe comprises an inlet and outlet channel which is communicated with the first cavity.

Description

Heat exchange system

Technical Field

The application relates to the technical field of heat exchange, in particular to a heat exchange system.

Background

Microchannel heat exchangers have been commonly used in air conditioning systems as condensers or evaporators, and generally include a plurality of heat exchange tubes, an inlet header and an outlet header, and when the air conditioning system is in operation, refrigerant flows into the inlet header and then flows to each heat exchange tube, and when the header is vertically placed, after the refrigerant in gas-liquid two phases flows into the inlet header, the liquid refrigerant is easily accumulated under the header under the action of gravity, and the gaseous refrigerant is accumulated above the header, so that the maldistribution of the refrigerant in each heat exchange tube is easily caused, and the heat exchange performance of the heat exchanger is reduced.

Disclosure of Invention

The application provides a heat exchange system which is beneficial to adjusting the distribution of a refrigerant and improving the heat exchange performance of a heat exchanger.

According to an embodiment of the application, a heat exchange system comprises a compressor, a throttling assembly, a pipeline, a fan, a heat exchanger and a refrigerant, wherein the compressor is connected with the heat exchanger, the heat exchanger is connected with the throttling assembly, and the fan is suitable for accelerating the gas flow on the surface of the heat exchanger, wherein:

the heat exchanger includes:

a first tube and a second tube;

the heat exchange tube comprises a plurality of heat exchange channels, the heat exchange tube comprises a first heat exchange tube and a second heat exchange tube, one first heat exchange tube comprises a first tube section, a first bending section and a second tube section, the number of the first heat exchange tubes is multiple, the number of the second heat exchange tubes is multiple, and the number of the second heat exchange tubes is multiple;

the first pipe section is directly or indirectly connected with the first pipe, the other end of the first pipe section is directly or indirectly connected with one end of the first bending section, the one end of the second pipe section is directly or indirectly connected with the first piece, and the other end of the second pipe section is directly or indirectly connected with the other end of the first bending section;

one end of the second heat exchange tube is directly or indirectly connected with the second tube, and the other end of the second heat exchange tube is directly or indirectly connected with the first member;

the first piece comprises a first cavity which is communicated with the heat exchange channels of the plurality of first heat exchange pipes, and the first cavity is communicated with the heat exchange channels of the plurality of second heat exchange pipes;

the heat exchanger further comprises a plurality of inlet and outlet pipes, at least one inlet and outlet pipe is directly or indirectly connected with the first piece, the inlet and outlet pipe comprises an inlet and outlet channel, and the inlet and outlet channel is communicated with the first cavity;

when the heat exchange system works, in the gravity direction, the first bending section of the heat exchanger is lower than the first piece, the first piece is lower than the second pipe and higher than the first bending section, after the refrigerant enters the first piece, part of the refrigerant flows through the first heat exchange pipe and flows out of the first pipe, and the other part of the refrigerant flows through the second heat exchange pipe and flows out of the second pipe.

According to the technical scheme provided by the embodiment of the application, the first cavity is arranged in the heat exchanger of the heat exchange system, so that the uniformity of the refrigerant flowing into the heat exchange pipe is improved, and the distribution of the refrigerant is regulated, so that the heat exchange performance of the heat exchanger is improved.

In some embodiments, one of the inlet and outlet pipes is in communication with the second pipe, and a shut-off valve is provided on the inlet and outlet pipe, and the shut-off valve is turned on when the heat exchanger operates as an evaporator of the refrigerant.

In some embodiments, one of the inlet and outlet pipes is in communication with the second pipe, and a shut-off valve is provided on the one of the inlet and outlet pipes, the shut-off valve being closed when the heat exchanger is operated as a condenser for refrigerant.

In some embodiments, the length direction of the first pipe section is at an angle to the length direction of the second pipe section, the first cavity comprises a first subchamber and a second subchamber, the first subchamber and the second subchamber are communicated, the first piece comprises a first wall and a second wall, the wall surrounding the first subchamber comprises a first wall, the wall surrounding the second subchamber comprises a second wall, a part of the first wall is directly connected or indirectly connected with the first heat exchange pipe, a part of the second wall is directly connected or indirectly connected with the second heat exchange pipe, the heat exchange channels of a plurality of the first heat exchange pipes are communicated with the first subchamber, the heat exchange channels of a plurality of the second heat exchange pipes are communicated with the second subchamber, and the inlet and outlet channels are communicated with the first subchamber or the second subchamber.

In some embodiments, the heat exchanger further comprises a third tube, at least a portion of the third tube being located within the first cavity, the third tube comprising a third channel, a tube wall surrounding the third channel comprising a plurality of through holes extending through the tube wall of the third tube, the inlet and outlet tube being directly or indirectly connected to the third tube, the inlet and outlet channel being in communication with the third channel.

In some embodiments, the heat exchanger further comprises a first fin and a second fin, wherein the first fin and the second fin are provided with a plurality of louvers arranged along the width direction of the heat exchange tubes, at least part of the first fin is positioned between two adjacent first heat exchange tubes in the length direction of the first tube, and at least part of the second fin is positioned between two adjacent second heat exchange tubes in the length direction of the second tube; the heat exchange capacity of the first fin is larger than that of the second fin.

In some embodiments, the heat exchange channels of the first heat exchange tube include a plurality of first channels, the plurality of first channels are disposed adjacent to each other in a width direction of the first heat exchange tube, the heat exchange channels of the second heat exchange tube include a plurality of second channels, the plurality of second channels are disposed adjacent to each other in the width direction of the second heat exchange tube, and a sum of channel cross-sectional areas of the heat exchange channels of the first heat exchange tube is greater than a sum of channel cross-sectional areas of the heat exchange channels of the second heat exchange tube.

In some embodiments, the heat exchange channels of the first heat exchange tube and the heat exchange channels of the second heat exchange tube each include the plurality of first channels and the plurality of second channels, the plurality of first channels are arranged at intervals in a width direction of the heat exchange tube, the plurality of second channels are arranged at intervals in the width direction of the heat exchange tube, a cross-sectional area of the first channels is larger than a cross-sectional area of the second channels, and the first channels are closer to a windward side of the heat exchange channels than the second channels.

In some embodiments, the heat exchange capacity of the first heat exchange tube is greater than the heat exchange capacity of the second heat exchange tube; the thickness dimension of the first heat exchange tube and the thickness dimension of the second heat exchange tube are different, and/or the width dimension of the first heat exchange tube and the width dimension of the second heat exchange tube are different.

In some embodiments, at least a portion of the third tube is located within the first subchamber, the inner volume of the first subchamber comprising the inner volume of the third channel, the inner volume of the first subchamber being greater than the inner volume of the second subchamber.

In some embodiments, the ratio of the internal volume of the first subchamber to the internal volume of the second subchamber is less than 30.

In some embodiments, the heat exchanger further comprises at least one second piece comprising a number of first flow channels extending through the second piece, the first flow channels communicating the first subchamber with the second subchamber.

In some embodiments, the sum of the channel cross-sectional areas of the first plurality of flow channels is S, wherein S satisfies the condition that 0.8+.D1+.D2/S+.16, wherein the equivalent diameter of the first subchamber is D1 and the equivalent diameter of the second subchamber is D2.

The foregoing description is only an overview of the present application, and is intended to be implemented in accordance with the teachings of the present application in order that the same may be more clearly understood and to make the same and other objects, features and advantages of the present application more readily apparent.

Drawings

Various other advantages and benefits will become apparent to those of ordinary skill in the art upon reading the following detailed description of the preferred embodiments. The drawings are only for purposes of illustrating the preferred embodiments and are not to be construed as limiting the application. Also, like reference numerals are used to designate like parts throughout the accompanying drawings. In the drawings:

FIG. 1 is a perspective view of a first construction of a heat exchanger according to an embodiment of the present application;

FIG. 2 is a side view of a first construction of a heat exchanger according to an embodiment of the present application;

FIG. 3 is a cross-sectional view taken along A-A of FIG. 2;

FIG. 4 is a schematic cross-sectional view of a heat exchange tube according to an embodiment of the present application;

FIG. 5 is a schematic view of a second construction of a heat exchanger according to an embodiment of the present application;

FIG. 6 is a cross-sectional view of a first fin according to an embodiment of the present application;

FIG. 7 is a schematic view of a third construction of a heat exchanger according to an embodiment of the present application;

fig. 8 is a block diagram of a heat exchange system according to an embodiment of the present application.

In the drawings, the drawings are not necessarily to scale.

Reference numerals in the specific embodiments are as follows:

the device comprises a 1-heat exchanger, a 2-compressor, a 3-throttling assembly, a 4-pipeline and a 5-fan;

10-a first tube;

20-a second tube;

30-heat exchange tubes, 31-first heat exchange tubes, 311-first tube sections, 312-second tube sections, 313-first curved sections, 3131-first torsion portions, 3132-first arc length portions, 32-second heat exchange tubes, 33-heat exchange channels, 331-first channels, 332-second channels;

40-first piece, 41-first chamber, 411-first subchamber, 412-first wall, 413-second subchamber, 414-second wall, 415-partition, 416-second flow channel;

50-third tube, 51-third channel;

60-a second piece, 61-a first flow channel;

70-first fins, 71-shutters;

80-second fins;

90-inlet and outlet pipes and 91-inlet and outlet channels.

Detailed Description

Embodiments of the technical scheme of the present application will be described in detail below with reference to the accompanying drawings. The following examples are only for more clearly illustrating the technical aspects of the present application, and thus are merely examples, and are not intended to limit the scope of the present application.

Unless defined otherwise, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this application belongs; the terminology used herein is for the purpose of describing particular embodiments only and is not intended to be limiting of the application; the terms "comprising" and "having" and any variations thereof in the description of the application and the claims and the description of the drawings above are intended to cover a non-exclusive inclusion.

In the description of embodiments of the present application, the technical terms "first," "second," and the like are used merely to distinguish between different objects and are not to be construed as indicating or implying a relative importance or implicitly indicating the number of technical features indicated, a particular order or a primary or secondary relationship. In the description of the embodiments of the present application, the meaning of "plurality" is two or more unless explicitly defined otherwise.

Reference herein to "an embodiment" means that a particular feature, structure, or characteristic described in connection with the embodiment may be included in at least one embodiment of the application. The appearances of such phrases in various places in the specification are not necessarily all referring to the same embodiment, nor are separate or alternative embodiments mutually exclusive of other embodiments. Those of skill in the art will explicitly and implicitly appreciate that the embodiments described herein may be combined with other embodiments.

In the description of the embodiments of the present application, the term "and/or" is merely an association relationship describing an association object, and indicates that three relationships may exist, for example, a and/or B may indicate: a exists alone, A and B exist together, and B exists alone. In addition, the character "/" herein generally indicates that the front and rear associated objects are an "or" relationship.

In the description of the embodiments of the present application, the term "plurality" means two or more (including two), and similarly, "plural sets" means two or more (including two), and "plural sheets" means two or more (including two).

In the description of the embodiments of the present application, the orientation or positional relationship indicated by the technical terms "center", "longitudinal", "transverse", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", "axial", "radial", "circumferential", etc. are based on the orientation or positional relationship shown in the drawings, and are merely for convenience of description and simplification of the description, and do not indicate or imply that the apparatus or element referred to must have a specific orientation, be configured and operated in a specific orientation, and therefore should not be construed as limiting the embodiments of the present application.

In the description of the embodiments of the present application, unless explicitly specified and limited otherwise, the terms "mounted," "connected," "secured" and the like should be construed broadly and may be, for example, fixedly connected, detachably connected, or integrally formed; or may be mechanically or electrically connected; can be directly connected or indirectly connected through an intermediate medium, and can be communicated with the inside of two elements or the interaction relationship of the two elements. The specific meaning of the above terms in the embodiments of the present application will be understood by those of ordinary skill in the art according to specific circumstances.

Referring to fig. 1 to 7, the applicant provides a heat exchange system comprising a compressor 2, a throttle assembly 3, a pipeline 4, a fan 5, a heat exchanger 1 and a refrigerant, the compressor 2 being connected to the heat exchanger 1, the heat exchanger 1 being connected to the throttle assembly 3, the fan 5 being adapted to accelerate the flow of gas at the surface of the heat exchanger 1, the heat exchanger 1 comprising:

the first tube 10 and the second tube 20 are preferably disposed opposite to each other with their axes extending in parallel.

The heat exchange tubes 30, the heat exchange tubes 30 comprise a plurality of heat exchange channels 33, the heat exchange tubes 30 comprise first heat exchange tubes 31 and second heat exchange tubes 32, one first heat exchange tube 31 comprises a first tube section 311, a first bending section 313 and a second tube section 312, the first heat exchange tubes 31 are a plurality of, the plurality of first heat exchange tubes 31 are arranged along the length direction of the first tube 10, first fins 70 are arranged between adjacent first heat exchange tubes 31, the plurality of second heat exchange tubes 32 are a plurality of, the plurality of second heat exchange tubes 32 are arranged along the length direction of the second tube 20, and second fins 80 are arranged between adjacent second heat exchange tubes 32.

And further comprises a first member 40, wherein one end of the first pipe section 311 is directly or indirectly connected with the first pipe 10, the other end of the first pipe section 311 is directly or indirectly connected with one end of the first bending section 313, one end of the second pipe section 312 is directly or indirectly connected with the first member 40, and the other end of the second pipe section 312 is directly or indirectly connected with the other end of the first bending section 313.

One end of the second heat exchange tube 32 is directly or indirectly connected to the second tube 20, and the other end of the second heat exchange tube 32 is directly or indirectly connected to the first member 40. Preferably, the connection of the first heat exchange tube 31 and the first member 40 is located below the connection of the second heat exchange tube 32 and the first member 40 in the gravitational direction.

The first member 40 includes a first cavity 41, the first cavity 41 is communicated with the heat exchange channels 33 of the plurality of first heat exchange tubes 31, the first cavity 41 is communicated with the heat exchange channels 33 of the plurality of second heat exchange tubes 32, the heat exchanger 1 further includes a plurality of inlet and outlet tubes 90, one inlet and outlet tube 90 is directly or indirectly connected with the first member 40 under the evaporation condition of the heat exchanger 1, the inlet and outlet tube 90 includes an inlet and outlet channel 91, the inlet and outlet channel 91 is communicated with the first cavity 41, and the refrigerant in gas-liquid two phases flows into the first cavity 41 through the inlet and outlet channel 91.

The compressor 2, the throttling assembly 3 and the heat exchanger 1 are communicated in sequence, and the fan 5 is positioned in the area between the first pipe 10 and the second pipe 20; in this embodiment, the heat exchanger 1 is used as an evaporator, the low-temperature low-pressure gaseous refrigerant is compressed by the compressor 2 to become a high-temperature high-pressure gaseous refrigerant, the high-temperature high-pressure gaseous refrigerant enters the condenser to be cooled to be a medium-temperature medium-pressure liquid refrigerant, the medium-temperature medium-pressure liquid refrigerant is throttled by the throttle component 3, the liquid refrigerant enters the heat exchanger 1 at a smaller flow, the low-temperature low-pressure gaseous refrigerant is fully expanded and evaporated in the heat exchanger 1 to be changed into the low-temperature low-pressure gaseous refrigerant, the circulation is completed, the fan 5 works during the circulation, and the air flow is sucked from the outer side to the inner side of the heat exchanger 1, so that the air flow temperature is reduced.

The heat exchanger operates as an evaporator for the refrigerant, the first curved section 313 of the heat exchanger 1 being located below the first member 40 in the direction of gravity, the first member 40 being located below the second tube 20 and above the first member 40, after the refrigerant has entered the first member 40, part of the refrigerant flowing through the first heat exchange tube 31 and out of the first tube 10, and the other part of the refrigerant flowing through the second heat exchange tube 32 and out of the second tube 20.

When the heat exchanger 1 is in operation in the evaporator, after the refrigerant in the gas-liquid two-phase state enters the first cavity 41 through the inlet and outlet pipe 90, the separation phenomenon of the gas-liquid two-phase refrigerant occurs in the first piece 40 under the action of gravity, the liquid refrigerant flows into the first heat exchange pipe 31 to exchange heat with air, the gaseous refrigerant flows into the second heat exchange pipe 32, the separation of the gas-liquid two-phase improves the uniformity of the liquid refrigerant flowing into the heat exchange pipes, and more liquid refrigerant can be better distributed to the first heat exchange pipe 31, so that the distribution of the refrigerant is regulated, and the heat exchange performance of the heat exchanger 1 is improved.

Further, an inlet/outlet pipe 90 is connected to the second pipe 20, and a shut-off valve (not shown) is provided in the inlet/outlet pipe 90, and is turned on when the heat exchanger 1 operates as an evaporator of the refrigerant, and is turned off when the heat exchanger 1 operates as a condenser of the refrigerant. The circulation amount of the refrigerant required during heating is small, the stop valve is conducted, the circulation amount of the refrigerant required during refrigeration cycle is large, the stop valve is closed, and the redundant refrigerant is stored in the second heat exchange tube 32 and the second tube 20 and is equivalent to a liquid storage tank, thereby solving the problem of unbalanced refrigerant filling amount during the circulation refrigeration/heating of the heat exchange system,

further, referring to fig. 1 to 3, the length direction of the first tube section 311 is angled with respect to the length direction of the second tube section 312, so that the heat exchanger 1 of this embodiment is generally V-shaped in configuration when the evaporator is in operation, the first chamber 41 includes a first sub-chamber 411 and a second sub-chamber 413, the first sub-chamber 411 and the second sub-chamber 413 communicate, at least a portion of the first sub-chamber 411 is located below the second sub-chamber 413 in the gravitational direction, the first member 40 includes a first wall 412 and a second wall 414, the wall surrounding the first sub-chamber 411 includes a first wall 412, the wall surrounding the second sub-chamber 413 includes a second wall 414, a portion of the first wall 412 is directly or indirectly connected with the first heat exchange tube 31, a portion of the second wall 414 is directly or indirectly connected with the second heat exchange tube 32, a plurality of heat exchange channels 33 of the first heat exchange tube 31 communicate with the first sub-chamber 411, a plurality of heat exchange channels 33 of the second heat exchange channels 33 of the inlet and outlet 91 communicate with the second sub-chamber 413, and the inlet and outlet 91 communicate with the first sub-chamber 413 or the second sub-chamber.

After the refrigerant in the gas-liquid two-phase state enters the first sub-chamber 411 or the second sub-chamber 413, the separation of the refrigerant in the gas-liquid two-phase state is easily generated due to the influence of gravity, because the first sub-chamber 411 is positioned below the second sub-chamber 413, the liquid refrigerant easily flows into the first sub-chamber 411 and then flows into the first heat exchange tube 31 to exchange heat with air, preferably, the connection point of the first heat exchange tube 31 and the first wall 412 is positioned at the lower part of the first wall 412 so as to be beneficial to the inflow of the liquid refrigerant, and the gaseous refrigerant enters the second sub-chamber 413, preferably, the connection point of the second heat exchange tube 32 and the second wall 414 is positioned at the upper part of the second wall 414 so as to be beneficial to the inflow of the gaseous refrigerant.

In some embodiments, the inlet and outlet channel 91 is communicated with the first subchamber 411, the refrigerant in the gas-liquid two-phase state firstly enters the first subchamber 411 in the first member 40, the upper half part of the first subchamber 411 is mostly gas, the lower half part of the first subchamber 411 is mostly liquid, the gaseous refrigerant rises into the second subchamber 413, and the gaseous refrigerant enters the second subchamber 413, so that the gas-liquid distribution of the refrigerant is regulated, and the heat exchange performance of the heat exchanger 1 is improved.

In some embodiments, the refrigerant in the gas-liquid two-phase state enters the first subchamber 411 from the inlet and outlet tube 90, and part of the refrigerant also accumulates in the inlet region of the first subchamber 411, resulting in uneven distribution of the refrigerant fluid in the first subchamber 411, and reducing the heat exchange capacity of the heat exchanger 1. For this purpose, the heat exchanger 1 further comprises a third tube 50, which third tube 50 may be a distribution tube, and referring to fig. 3, at least part of the third tube 50 is located in the first subchamber 411, the third tube 50 comprises a third channel 51, the wall surrounding the third channel 51 comprises a plurality of through holes penetrating the wall of the third tube 50, preferably the through holes are uniformly and axially distributed on the wall of the third tube 50, although other arrangements, such as increasing or decreasing proportionally, may be used, wherein the inlet and outlet tube 90 is directly or indirectly connected to the third tube 50, and the inlet and outlet channel 91 is in communication with the third channel 51. The refrigerant enters the third channel 51 of the third tube 50 through the inlet and outlet channels 91 of the inlet and outlet tube 90 and flows into the first subchamber 411 through the dispersed through holes, so that the refrigerant is dispersed and distributed, the uniform distribution of the refrigerant fluid in the first subchamber 411 is facilitated, the occurrence of the local accumulation condition of the refrigerant is reduced, and the heat exchange performance of the heat exchanger 1 is improved.

Further, referring to fig. 1 and 6, in order to improve the turbulence capacity of the gas passing through the heat exchanger 1 and to improve the heat exchange performance of the heat exchanger 1, each of the first fin 70 and the second fin 80 is provided with a plurality of louvers 71 provided along the width direction of the heat exchange tube 30, at least part of the first fin 70 is located between two first heat exchange tubes 31 adjacent in the length direction of the first tube 10, at least part of the second fin 80 is located between two second heat exchange tubes 32 adjacent in the length direction of the second tube 20, and the gas can pass through the louvers 71 when passing through the first fin 70 and the second fin 80, so that the flow path of the gas can be prolonged and the heat exchange performance of the heat exchanger 1 can be improved.

Since the refrigerant in the first heat exchange tube 31 is in a liquid state and the refrigerant in the second heat exchange tube 32 is in a gaseous state, the heat exchange effect at the second heat exchange tube 32 is smaller than the heat exchange effect at the first heat exchange tube 31, and the heat exchange capacity of the first fin 70 is larger than the heat exchange capacity of the second fin 80, the heat transfer coefficient of the second fin 80 may be set smaller than that of the first fin 70, the FPI value of the first fin 70 is larger than that of the second fin 80, and/or the windowing angle of the louver 71 of the first fin 70 is larger than that of the louver 71 of the second fin 80, and/or the windowing length of the louver 71 of the first fin 70 is larger than that of the louver 71 of the second fin 80.

In some embodiments, the first fin 70 is disposed only between the adjacent first tube segment 311 and second tube segment 312, and referring to fig. 5, a heat exchanger 1 of a second structure is provided, and the first heat exchange tube 31 may further include a plurality of first curved segments 313, where the first curved segments 313 include two first torsion portions 3131 and one first arc length portion 3132, one end of the first arc length portion 3132 is connected to one first torsion portion 3131, the other end of the first arc length portion 3132 is connected to the other first torsion portion 3131, and a gap is provided between the first torsion portions 3131 of the adjacent two first heat exchange tubes 31 in the length direction of the first tube 10. It will be appreciated that the first curved sections 313 may be formed by twisting a flat tube, or may be formed by separately manufacturing other components, and that having a gap between adjacent twisted sections is beneficial to reducing the contact area between adjacent first curved sections 313, reducing dust accumulation, reducing corrosion of the heat exchanger 1, and improving reliability of the heat exchanger 1.

In some embodiments, referring to fig. 4, the plurality of heat exchange channels 33 includes a plurality of first channels 331 and a plurality of second channels 332, the plurality of first channels 331 includes a plurality of first channels 331 having a same channel cross-sectional area, the plurality of second channels 332 includes a plurality of second channels 332 having a same channel cross-sectional area, the plurality of first channels 331 and the plurality of second channels 332 are distributed along the air inlet side toward the outlet side in the air flow direction, the channel cross-sectional area of any one of the plurality of first channels 331 on the windward side is larger than the channel cross-sectional area of any one of the plurality of second channels 332, and in order to improve the heat exchange performance of the windward side of the heat exchange tube, the channel refrigerant flow area on the windward side of the heat exchange tube is larger than the refrigerant flow area of the other plurality of through holes of the heat exchange tube, and it is known to those skilled in the art that there may be more heat exchange channels 33 closer to the leeward side in the air flow direction, and the channel cross-sectional area in each heat exchange channel 33 is relatively smaller.

In some embodiments, since the refrigerant in the liquid state is in the first heat exchange tube 31 and the refrigerant in the gas state is in the second heat exchange tube 32, the heat exchange effect at the second heat exchange tube 32 is smaller than the heat exchange effect at the first heat exchange tube 31, so that the cross-sectional area of the heat exchange passage of the first heat exchange tube 31 is set to be larger than the cross-sectional area of the heat exchange passage of the second heat exchange tube 32.

In some embodiments, the first heat exchange tube 31 has a larger ruler-diameter than the second heat exchange tube 32, specifically, the ratio of the thickness dimensions of the first heat exchange tube 31 and the second heat exchange tube 32 is 1 or more and 3 or less, and/or the ratio of the width dimensions of the first heat exchange tube 31 and the second heat exchange tube 32 is 1 or more and 7 or less.

In some embodiments, referring to fig. 3, at least a portion of the third tube 50 is positioned within the first subchamber 411, the interior volume of the first subchamber 411 comprising the interior volume of the third passageway 51, the cross-sectional area of the first subchamber 411 being greater than 0.25 times the cross-sectional area of the second subchamber 413 and less than 5 times the cross-sectional area of the second subchamber 413. Experiments show that when the internal volume ratio of the first subchamber 411 to the second subchamber 413 is between 1 and 30, the gas-liquid two-phase liquid separation effect is better, and the gas is easier to enter the second subchamber 411, so that the gas-liquid distribution of the refrigerant is more favorably regulated.

In some embodiments, referring to fig. 1, 2 and 3, the heat exchanger 1 further includes a second member 60, where the second member 60 includes a first flow channel 61, the first wall 412 is a separate tube structure, the first subchamber 411 is located in the tube structure, preferably, the first subchamber 411 extends in a direction consistent with the extending direction of the tube structure, the second wall 414 is also a separate tube structure, the second subchamber 413 is located in the tube structure, preferably, the extending direction of the second subchamber 413 is consistent with the extending direction of the tube structure, the two tube structures are parallel, the first wall 412 is located below the second wall 414, the first subchamber 411 and the second subchamber 413 are communicated through the first communication channel 61, and because the inner diameter of the first flow channel 61 is smaller than the inner diameters of the first subchamber 411 and the second subchamber 413, the air is partially condensed back into the first subchamber 411 when passing through the first flow channel 61, so that the second subchamber is better to avoid the accumulation of the coolant in the second subchamber 413.

Further, referring to fig. 3, it will be understood by those skilled in the art that the number, size and distribution of the first flow channels 61 on each second member 60 may be modified according to practical situations, and is not limited herein, preferably the first flow channels 61 are plural, the sum of the channel sectional areas of the first flow channels 61 is S, S satisfies the condition that 0.8+.d1+.d2/s+.16, where the equivalent diameter of the first subchamber is D1, and the equivalent diameter of the second subchamber is D2, so as to control the flow rate of the refrigerant entering the second subchamber 413, if too large, the second heat exchange tube 32 will not boil too much liquid refrigerant, if too small, the entering of the gaseous refrigerant will be reduced, and the second heat exchange tube 32 loses the function of absorbing the gaseous refrigerant.

In some embodiments, referring to fig. 7, the first sub-chamber 411 and the second sub-chamber 413 are separated into two adjacent chambers by a partition 415, and a second flow channel 416 is penetrated through the partition 415, and two ends of the second flow channel 416 are respectively communicated with the first sub-chamber 411 and the second sub-chamber 413.

The first sub-cavity 411 and the second sub-cavity 413 are arranged in the same pipe body structure, the pipe body structure can be a regular square pipe, a round pipe, a triangular pipe or other pipe shapes, and also can be a special pipe, the special pipe is not limited in the arrangement, the first sub-cavity 411 is positioned below the second sub-cavity 413, after the refrigerant in the gas-liquid two-phase state enters the first sub-cavity 411 or the second sub-cavity 413, the separation of the refrigerant in the gas-liquid two-phase state is easy to generate due to the influence of gravity, and because the first sub-cavity 411 is positioned below the second sub-cavity 413, the liquid refrigerant easily flows into the first sub-cavity 411 and then flows into the first heat exchange pipe 31 to exchange heat with air, so the arrangement mode can be convenient for forming, parts are reduced, and meanwhile, the special pipe is also convenient to assemble and not easy to damage in the use process.

Finally, it should be noted that: the above embodiments are only for illustrating the technical solution of the present application, and not for limiting the same; although the application has been described in detail with reference to the foregoing embodiments, it will be understood by those of ordinary skill in the art that: the technical scheme described in the foregoing embodiments can be modified or some or all of the technical features thereof can be replaced by equivalents; such modifications and substitutions do not depart from the spirit of the application, and are intended to be included within the scope of the appended claims and description. In particular, the technical features mentioned in the respective embodiments may be combined in any manner as long as there is no structural conflict. The present application is not limited to the specific embodiments disclosed herein, but encompasses all technical solutions falling within the scope of the claims.

Claims

1. A heat exchange system comprising a compressor, a throttling assembly, a conduit, a fan, a heat exchanger and a refrigerant, the compressor being connected to the heat exchanger, the heat exchanger being connected to the throttling assembly, the fan being adapted to accelerate the flow of gas over the surface of the heat exchanger, wherein the heat exchanger comprises:

a first tube and a second tube;

2. The heat exchange system as set forth in claim 1, wherein one of said inlet and outlet pipes is in communication with said second pipe, a shut-off valve being provided on said one of said inlet and outlet pipes, said shut-off valve being turned on when said heat exchanger is operated as an evaporator of refrigerant.

3. A heat exchange system according to claim 1 or 2, wherein one of said inlet and outlet pipes is in communication with said second pipe, and wherein one of said inlet and outlet pipes is provided with a shut-off valve, said shut-off valve being closed when said heat exchanger is operated as a condenser for refrigerant.

4. The heat exchange system of claim 1, wherein the length direction of the first tube segment is at an angle to the length direction of the second tube segment, the first chamber comprises a first subchamber and a second subchamber, the first subchamber and the second subchamber are in communication, the first member comprises a first wall and a second wall, the wall surrounding the first subchamber comprises a first wall, the wall surrounding the second subchamber comprises a second wall, a portion of the first wall is directly or indirectly connected to the first heat exchange tube, a portion of the second wall is directly or indirectly connected to the second heat exchange tube, a plurality of heat exchange channels of the first heat exchange tube are in communication with the first subchamber, a plurality of heat exchange channels of the second heat exchange tube are in communication with the second subchamber, and the inlet and outlet channels are in communication with the first subchamber or the second subchamber.

5. The heat exchange system of claim 1, wherein the heat exchanger further comprises a third tube, at least a portion of the third tube being located within the first chamber, the third tube comprising a third channel, a wall surrounding the third channel comprising a plurality of through holes extending through the wall of the third tube, the inlet and outlet tube being directly or indirectly connected to the third tube, the inlet and outlet channel being in communication with the third channel.

6. The heat exchange system according to claim 1, wherein the heat exchanger further comprises a first fin and a second fin each provided with a plurality of louvers provided in a width direction of the heat exchange tubes, at least a part of the first fin being located between two adjacent first heat exchange tubes in the first tube length direction, at least a part of the second fin being located between two adjacent second heat exchange tubes in the second tube length direction; the heat exchange capacity of the first fin is larger than that of the second fin.

7. The heat exchange system according to claim 6, wherein the heat exchange passage of the first heat exchange tube includes a plurality of first passages, the plurality of first passages being disposed adjacently in a width direction of the first heat exchange tube, the heat exchange passage of the second heat exchange tube includes a plurality of second passages, the plurality of second passages being disposed adjacently in the width direction of the second heat exchange tube, a sum of passage sectional areas of the heat exchange passages of the first heat exchange tube being larger than a sum of passage sectional areas of the heat exchange passages of the second heat exchange tube.

8. The heat exchange system according to claim 7, wherein the heat exchange channels of the first heat exchange tube and the heat exchange channels of the second heat exchange tube each include the plurality of the first channels and the plurality of the second channels, the plurality of the first channels being arranged at intervals in a width direction of the heat exchange tube, the plurality of the second channels being arranged at intervals in the width direction of the heat exchange tube, a cross-sectional area of the first channels being larger than a cross-sectional area of the second channels, the first channels being closer to a windward side of the heat exchange channels than the second channels.

9. The heat exchange system according to claim 1 or 7, wherein the heat exchange capacity of the first heat exchange tube is greater than the heat exchange capacity of the second heat exchange tube; the thickness dimension of the first heat exchange tube and the thickness dimension of the second heat exchange tube are different, and/or the width dimension of the first heat exchange tube and the width dimension of the second heat exchange tube are different.

10. The heat exchange system of claim 4 wherein at least a portion of the third tube is located within the first subchamber, the interior volume of the first subchamber comprising the interior volume of the third channel, the interior volume of the first subchamber being greater than the interior volume of the second subchamber.

11. The heat exchange system of claim 10, wherein a ratio of the interior volume of the first subchamber to the interior volume of the second subchamber is less than 30.

12. The heat exchange system according to claim 10 or 11, wherein the heat exchanger further comprises at least one second piece comprising a first flow channel, the first flow channel being a plurality of the first flow channels, the sum of the channel cross-sectional areas of the plurality of first flow channels being S, S satisfying the condition 0.8+.d1+.d2/s+.16, wherein the equivalent diameter of the first subchamber is D1 and the equivalent diameter of the second subchamber is D2.