CN216049292U - Heat exchanger and multi-system air conditioning unit - Google Patents

Abstract

The application discloses heat exchanger and multi-system air conditioning unit, wherein, this heat exchanger includes first pipe, second pipe, third pipe, fourth pipe, heat exchange tube and fin, and the heat exchange tube includes first heat exchange tube and second heat exchange tube, and first heat exchange tube and second heat exchange tube arrange along the length direction of first pipe in turn, and the ratio of the hydraulic diameter of first pipe and second pipe is greater than 1 and less than or equal to 6, and/or the ratio of the width size of first heat exchange tube and second heat exchange tube is greater than 1 and less than or equal to 5. This application is through the relation of the water conservancy diameter of adjusting first pipe and second pipe to and the relation of first heat exchange tube and second heat exchange tube width size, can make two refrigerating system of heat exchanger have different heat transfer performance, with the demand of the different load operating mode of matching unit.

Description

Heat exchanger and multi-system air conditioning unit

Technical Field

The application relates to the technical field of air conditioner refrigeration, in particular to a heat exchanger and a multi-system air conditioning unit.

Background

In the related art, a multi-refrigeration system air conditioning unit includes a plurality of refrigeration systems capable of operating independently to meet different operating requirements, several systems share one or more heat exchangers, and several systems are isolated from each other and can operate independently. Taking a double-system heat exchanger as an example, the used multi-channel heat exchanger is commonly used for two systems, and the heat exchange units used for the two systems are often designed to have the same heat exchange capacity and are difficult to match various different operation conditions according to the environmental requirements.

SUMMERY OF THE UTILITY MODEL

The application provides a heat exchanger and multi-system air conditioning unit, can improve the adaptability of heat exchanger to multi-refrigerating system air conditioning unit when partial load operation, is favorable to improving the heat transfer performance under the partial load operation condition.

A first aspect of the present application provides a heat exchanger, comprising: a first assembly including a first tube and a second tube, a second assembly including a third tube and a fourth tube, a plurality of heat exchange tubes which are microchannel flat tubes, the heat exchange tubes including a plurality of channels provided along a length direction thereof, the plurality of channels being provided at intervals in a width direction of the heat exchange tubes, the heat exchange tubes including a first heat exchange tube and a second heat exchange tube, the first heat exchange tube communicating with the first tube and the third tube, the second heat exchange tube communicating with the second tube and the fourth tube, the first heat exchange tube and the second heat exchange tube being provided at intervals along a length direction of the first tube, the first tube and the second tube not communicating with each other, the third tube and the fourth tube not communicating with each other, a part of the fins being connected to one of the first heat exchange tubes, the other part of the fins being connected to one of the second heat exchange tubes, the first heat exchange tube, the fin and the second heat exchange tube are arranged along the length direction of the first tube, the number of the fins is multiple, the first hydraulic diameter of the first tube is D1, the second hydraulic diameter of the second tube is D2, the ratio of the first hydraulic diameter D1 to the second hydraulic diameter D2 is greater than 1 and less than or equal to 6, and/or the width dimension of the first heat exchange tube is Tw1, the width dimension of the second heat exchange tube is Tw2, and the ratio of the width dimension Tw1 of the first heat exchange tube to the width dimension Tw2 of the second heat exchange tube is greater than 1 and less than or equal to 5.

In some embodiments, the first heat exchange tube has a thickness dimension HT1 that is not equal to the second heat exchange tube thickness dimension HT 2.

In some embodiments, the width dimension of the first heat exchange tube and the width dimension of the second heat exchange tube satisfy the following condition: 0.2< D1 × Tw2/Tw1 × D2 ≤ 6.

In some embodiments, the ratio of the first hydraulic diameter D1 to the second hydraulic diameter D2 is greater than 1 and equal to or less than 4, and the ratio of the width dimension Tw1 of the first heat exchange tube to the width dimension Tw2 of the second heat exchange tube is greater than 1 and equal to or less than 3.

In some embodiments, along the length direction of the first tube, the minimum distance between two adjacent first heat exchange tubes is Tp1, the minimum distance between two adjacent second heat exchange tubes is Tp2, the Tp1 is not equal to the Tp2, the hydraulic diameter D1 of the first tube and the hydraulic diameter D2 of the second tube satisfy the following conditions:

0.2<D1×Tp2/Tp1×D2≤30；

0.2<Tp2/TP1≤5。

in some embodiments, the first tube comprises a peripheral wall and a main channel surrounded by the peripheral wall, a finless zone is formed between the peripheral wall of the first tube and a part of the fins along the length direction of the first heat exchange tube, a side of the heat exchanger located upstream in the wind direction during operation is defined as a windward side, a side of the heat exchanger located downstream in the wind direction is defined as a leeward side, and at least a part of the second tube is located on the windward side or leeward side of the finless zone.

In some embodiments, a first distribution pipe is located within the main channel of the first pipe, the first distribution pipe extends a distance along the length direction of the first pipe, the second pipe comprises a peripheral wall and a main channel surrounded by the peripheral wall, a second distribution pipe is located within the main channel of the second pipe, the second distribution pipe extends a distance along the length direction of the second pipe, the hydraulic diameter of the first distribution pipe is D3, the hydraulic diameter of the second distribution pipe is D4, and the following conditions are satisfied: D3/D4 is more than or equal to 1 and less than or equal to 4.

In some embodiments, the fin has a width dimension Fw, the first heat exchange tube has a width dimension Tw1, and the second heat exchange tube has a width dimension Tw2, satisfying the following conditions: tw2< Fw ≦ Tw1+ Tw2

The second aspect of the present application also provides a multi-system air conditioning unit, wherein, includes the heat exchanger that the first aspect of the present application provided.

The third aspect of this application still provides a multi-system air conditioning unit, wherein, includes the heat exchanger that provides in the first aspect of this application, multi-system air conditioning unit includes first system and second system, first system includes first compressor unit, first system with the first pipe and the third pipe intercommunication of heat exchanger, the second system includes second compressor unit, the second system with the second pipe and the fourth pipe intercommunication of heat exchanger, the output of first compressor unit with the output of second compressor unit's ratio is greater than 1.5 and less than or equal to 5.

The technical scheme provided by the application can achieve the following beneficial effects:

the application provides a heat exchanger and multi-system air conditioning unit, through the relation of the hydraulic diameter of adjusting first pipe and second pipe to and the relation of first heat exchange tube and second heat exchange tube width size, can make two refrigerating system of heat exchanger have different heat transfer performance, with the demand of the different load operating mode of matching unit.

It is to be understood that both the foregoing general description and the following detailed description are exemplary and explanatory only and are not restrictive of the application.

Drawings

FIG. 1 is a schematic structural diagram of a heat exchanger provided in an embodiment of the present application;

FIG. 2 is a top view of the heat exchanger shown in FIG. 1;

FIG. 3 is a schematic cross-sectional view of a portion of the heat exchanger shown in FIG. 1;

FIG. 4 is a schematic cross-sectional view of a portion of the heat exchanger shown in FIG. 1;

FIG. 5 is a schematic diagram of a heat exchanger according to another embodiment of the present application;

FIG. 6 is a bottom view of the heat exchanger shown in FIG. 5;

FIG. 7 is a schematic structural diagram of a heat exchanger according to yet another embodiment of the present application;

FIG. 8 is a bottom view of the heat exchanger shown in FIG. 7;

FIG. 9 is a schematic structural diagram of a heat exchanger according to yet another embodiment of the present application;

FIG. 10 is a bottom view of the heat exchanger of FIG. 9;

FIG. 11 is a schematic structural diagram of a heat exchanger according to yet another embodiment of the present application;

FIG. 12 is a bottom view of the heat exchanger shown in FIG. 11;

FIG. 13 is a schematic diagram of a multi-system air conditioning unit configuration.

Reference numerals:

1-a heat exchanger; 11-a first heat exchange tube; 121-a first tube; 122-a third tube; 13-a second heat exchange tube; 141-a second tube; 142-a fourth tube; 16-a fin; 17-a finless zone section; 18-a first distribution pipe; 19-a second distribution pipe; 2-a first compressor train; 3-a second compressor train; l1-distance; l2-distance.

Detailed Description

In order to make the objects, technical solutions and advantages of the present application more apparent, the present application is described in further detail below with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are merely illustrative of the present application and are not intended to limit the present application.

In the description of the present application, unless explicitly stated or limited otherwise, the terms "first", "second", and the like are used for descriptive purposes only and are not to be construed as indicating or implying relative importance; the term "plurality" means two or more unless specified or indicated otherwise; the terms "connected," "fixed," and the like are to be construed broadly and may, for example, be fixedly connected, detachably connected, integrally connected, or electrically connected; may be directly connected or indirectly connected through an intermediate. The specific meaning of the above terms in the present application can be understood by those of ordinary skill in the art as appropriate.

In the description of the present application, it should be understood that the terms "upper" and "lower" used in the description of the embodiments of the present application are used in a descriptive sense only and not for purposes of limitation. In addition, in this context, it will also be understood that when an element is referred to as being "on" or "under" another element, it can be directly on "or" under "the other element or be indirectly on" or "under" the other element via an intermediate element.

As shown in fig. 1 to 13, the present embodiment provides a heat exchanger 1 and a multi-system air conditioning unit, and the heat exchanger 1 is applied to the multi-system air conditioning unit. The heat exchanger 1 may be used as a condenser or an evaporator, and in the present embodiment, the heat exchanger 1 is preferably used as an evaporator.

The multi-system air conditioning unit comprises a compressor, a condenser, an expansion valve, a heat exchanger 1 serving as an evaporator and a fan system. In the working process of the multi-system air conditioning unit, low-pressure steam of a refrigerant is sucked by the compressor and compressed into high-temperature high-pressure steam which is then discharged to the condenser, and outdoor air sucked by the fan system flows through the condenser to take away heat emitted by the refrigerant, so that the high-pressure refrigerant steam is condensed into medium-temperature high-pressure liquid. The medium-temperature high-pressure liquid is converted into a low-temperature low-pressure gas-liquid mixed state through an expansion valve and sprayed into the heat exchanger 1, the low-temperature low-pressure gas-liquid mixed state is evaporated at corresponding low pressure, surrounding heat is absorbed, meanwhile, air continuously enters the heat exchanger 1 through a fan system for heat exchange, and the air which is cooled after heat release is sent to the indoor. Therefore, the indoor air continuously circulates and flows to achieve the purpose of refrigeration and temperature reduction. The refrigerant flowing out of the heat exchanger 1 is changed into low-temperature and low-pressure gas again by taking away heat (absorbing heat) in the air, and is sucked into the compressor again, and the cycle is repeated.

The heat exchanger 1 provided by the embodiment of the application comprises a first unit, a second unit, a plurality of heat exchange tubes and fins. Wherein the first assembly includes a first tube 121 and a second tube 141, and the second assembly includes a third tube and a fourth tube. The heat exchange tube is a microchannel flat tube, the heat exchange tube comprises a plurality of channels arranged along the length direction of the heat exchange tube, the channels are arranged at intervals in the width direction of the heat exchange tube, the heat exchange tube comprises a first heat exchange tube 11 and a second heat exchange tube 13, the first heat exchange tube 11 is communicated with a first tube 121 and a third tube 122, the second heat exchange tube 13 is communicated with a second tube 141 and a fourth tube 142, the first heat exchange tube 11 and the second heat exchange tube 13 are arranged at intervals in the length direction of the first tube 121, the first tube 121 is not communicated with the second tube 141, and the third tube 122 is not communicated with the fourth tube 142. A part of the fins is connected to one first heat exchange tube 11, the other part of the fins is connected to one second heat exchange tube 13, the first heat exchange tube 11, the fins and the second heat exchange tube 13 are arranged along the length direction of the first tube 121, and the number of the fins is plural. Therefore, the first heat exchange tube 11 and the second heat exchange tube 13 can share the fins 16, when the unit operates under partial load, the first heat exchange tube 11 or the second heat exchange tube 13 can exchange heat through all the fins 16, and the heat exchange efficiency can be improved.

In some embodiments, the first hydraulic diameter of the first tube 121 is D1, the second hydraulic diameter of the second tube 141 is D2, and the ratio of the first hydraulic diameter D1 to the second hydraulic diameter D2 is greater than 1 and less than or equal to 6, so that the amount of refrigerant that can flow through the second tube 141 is increased relative to the amount of refrigerant that can flow through the first tube 121, which is beneficial to heat exchange of refrigerant, and the heat exchange performance of a refrigeration system including the second tube 141 is improved. The ratio of the first hydraulic diameter D1 to the second hydraulic diameter D2 is adjusted, so that the two refrigeration systems have different heat exchange performances to meet the requirements of different load operation conditions of the unit.

The hydraulic diameters of the first tube 121 and the third tube 122 are the same, and the hydraulic diameters of the second tube 141 and the fourth tube 142 are the same. The first tube 121, the third tube 122 and the first heat exchange tube 11 may form a refrigeration circuit, the second tube 141, the fourth tube 142 and the second heat exchange tube 13 may form another refrigeration circuit, and the heat dissipation performance of the two refrigeration circuits may be the same or different.

In some embodiments, the width dimension of the first heat exchange tube 11 is Tw1, the width dimension of the second heat exchange tube 13 is Tw2, and the ratio of the width dimension Tw1 of the first heat exchange tube 11 to the width dimension Tw2 of the second heat exchange tube 13 is greater than 1 and less than or equal to 5. In this embodiment, the hydraulic diameters of the first tube 121, the second tube 141, the third tube 122 and the fourth tube 142 are the same, the width dimensions of the first heat exchange tube 11 and the second heat exchange tube 13 are different, and the heat exchange capacity of the heat exchange tube with a larger width dimension is relatively stronger, and by making the width dimensions of the first heat exchange tube 11 and the second heat exchange tube 13 different, the heat dissipation performance of the refrigeration circuit including the first heat exchange tube 11 and the heat dissipation performance of the refrigeration circuit including the second heat exchange tube 13 can be different, and specifically, by adjusting the ratio of the width dimension of the first heat exchange tube 11 to the width dimension of the second heat exchange tube 13 within the range of the ratio of 1-5, the different heat exchange performances of the two refrigeration circuits can be obtained, so that the requirements of different load operation conditions of the unit can be met.

In some embodiments, the hydraulic diameters of the first and second tubes 121 and 141 are different, and the width dimensions of the first and second heat exchange tubes 11 and 13 are also different. Specifically, the ratio of the first hydraulic diameter D1 to the second hydraulic diameter D2 is within the range of 1-6, and the ratio of the width dimensions of the first heat exchange tube 11 to the second heat exchange tube 13 is within the range of 1-5, so that the two refrigeration loops of the heat exchanger can obtain different heat exchange capacities more flexibly by simultaneously adjusting the hydraulic diameters of the first tube 121 and the second tube 141 and the width dimensions of the first heat exchange tube 11 and the second heat exchange tube 13, and the different load operation conditions of the unit can be more flexibly matched.

Further, the thickness HT1 of the first heat exchange tube 11 and the thickness HT2 of the second heat exchange tube 13 may not be equal, so that the thicknesses of the first heat exchange tube 11 and the second heat exchange tube 13 may be adjusted according to the operation condition of the unit, so as to obtain different heat exchange performances of the two refrigeration circuits of the heat exchanger.

Specifically, the width dimension of the first heat exchange tube 11 and the width dimension of the second heat exchange tube 13 satisfy the following condition: 0.2< D1 × Tw2/Tw1 × D2 ≤ 6. Wherein D1 is the hydraulic diameter of the first tube 121, D2 is the hydraulic diameter of the second tube 141, Tw1 is the width of the first heat exchange tube 11, and Tw2 is the width of the second heat exchange tube 13.

Under the conditions that the hydraulic diameters of the first pipe 121 and the second pipe 141 are different and the width dimensions of the first heat exchange pipe 11 and the second heat exchange pipe 13 are also different, by enabling the hydraulic diameters of the first pipe 121 and the second pipe 141 and the width dimensions of the first heat exchange pipe 11 and the second heat exchange pipe 13 to satisfy the above formula, the two refrigeration circuits of the heat exchanger can maintain sufficient system pressure, the refrigerant can be ensured to have sufficient flow velocity for oil return, and the system can be ensured to have optimal heat exchange performance.

Specifically, the hydraulic diameters of the first tube 121 and the second tube 141 are different, the ratio of the hydraulic diameter D1 of the first tube 121 to the hydraulic diameter D2 of the second tube 141 is greater than 1 and equal to or less than 4, and the ratio of the width Tw1 of the first heat exchange tube to the width Tw2 of the second heat exchange tube is greater than 1 and equal to or less than 3.

In some embodiments, under the conditions that the hydraulic diameters of the first tube 121 and the second tube 141 are different and the width dimensions of the first heat exchange tube 11 and the second heat exchange tube 13 are the same, the hydraulic diameters of the first tube 121 and the second tube 141 satisfy the above formula, so that the heat exchange capacity of the refrigerant in the first tube 121 with a larger hydraulic diameter can be enhanced, two refrigeration loops with different heat exchange capacities can be obtained, and matching of operating conditions of different loads of the unit is facilitated.

It should be noted that, generally, when the heat exchanger 1 is brazed in a brazing furnace based on the prior art, the first tube 121 is located above the second tube 141, but this may cause a difference in the parameters of the brazing furnace at the first tube 121 and the second tube 141. In order to ensure that the second tube 141 is welded well, the first tube 121 may be welded excessively, so that solder excessively enters the first tube 121, and thus there is a risk of blocking the nozzle of the first heat exchange tube 11, which may affect the heat exchange performance of the heat exchanger 1 if the nozzle of the first heat exchange tube 11 is blocked.

For this reason, in the present embodiment, as shown in fig. 3 and 4, the distance L1 between the inner wall of the first tube 121 and the first heat exchange tube 11 is made greater than the distance L2 between the inner wall of the second tube 141 and the second heat exchange tube 13. Therefore, the edge of the first heat exchange tube 11 is distant from the inner wall surface of the first tube, and even if the solder enters the first tube, the solder is accumulated between the first tube and the first heat exchange tube 11, and does not block the nozzle of the first heat exchange tube 11.

In some embodiments, as shown in fig. 3, the distance L1 between the inner wall of the first tube 121 and the first heat exchange tube 11 may be made greater than the distance L2 between the inner wall of the second tube 141 and the second heat exchange tube 13 by increasing the hydraulic diameter of the first tube 121. Meanwhile, the hydraulic diameter of the first pipe 121 is increased, so that heat exchange of the gas refrigerant is facilitated, and the heat exchange performance of the first heat exchange pipe 11 is improved.

Specifically, in the length direction of the first tube 121, the minimum distance between two adjacent first heat exchange tubes 11 is Tp1, the minimum distance between two adjacent second heat exchange tubes 13 is Tp2, Tp1 is not equal to Tp2, the hydraulic diameter D1 of the first tube 121 and the hydraulic diameter D2 of the second tube 141 satisfy the following conditions:

0.2<D1×Tp2/Tp1×D2≤30；

0.2<Tp2/TP1≤5。

it can be understood that the first heat exchange tubes 11 and the second heat exchange tubes 13 are respectively provided with a plurality of first heat exchange tubes 11 and a plurality of second heat exchange tubes 13, and the plurality of first heat exchange tubes 11 and the plurality of second heat exchange tubes 13 are alternately arranged, and specifically, at least one first heat exchange tube 11 is arranged between every two second heat exchange tubes 13, for example, two, three or more first heat exchange tubes 11 are arranged between every two second heat exchange tubes 13, so that the first heat exchange tubes 11 and the second heat exchange tubes 13 can be uniformly distributed, and the uniformity of the outlet air temperature is ensured. Of course, there may be at least one second heat exchange tube 13 between every two first heat exchange tubes 11.

Different tube pitches can realize differential matching of partial loads, for example, the number ratio of the first heat exchange tubes 11 to the second heat exchange tubes 13 can be 1:1, 2:1, 3:2 and the like, so that the operation conditions of the unit under different loads can be met.

Specifically, the first tubes 121 include a peripheral wall and a main channel surrounded by the peripheral wall, a finless zone section 17 is formed between the peripheral wall of the first tubes 121 and a part of the fins 16 along the length direction of the first heat exchange tubes 11, a side of the heat exchanger 1 located upstream in the wind direction during operation is defined as a windward side, a side of the heat exchanger 1 located downstream in the wind direction is defined as a leeward side, and at least a part of the second tubes 141 are located on the windward side or leeward side of the finless zone section 17, that is, a projection of the second tubes 141 is located between the fins 16 and the first tubes 121.

The finless area section 17 can ensure that the first heat exchange tube 11 and the second heat exchange tube 13 can be effectively welded and fixed with the fins 16. However, the wind passing through the finless zone section 17 cannot participate in heat exchange, and if the finless zone section 17 is too large, the wind is lost therefrom, resulting in a reduction in heat exchange performance. For this reason, in the present embodiment, by positioning at least part of the second tubes 141 on the windward side or the leeward side of the finless zone section 17, the wind blowing toward the finless zone section 17 can be brought into contact with the second tubes 141 to be able to exchange heat, and at the same time, the wind can be guided to the fins 16 to exchange heat by being blocked by the second tubes 141, thereby improving the heat exchange efficiency. In addition, when the heat exchanger 1 passes through the furnace, the brazing flux can be more conveniently brushed between the first heat exchange tube 11 and the first tube, so that the welding quality between the first heat exchange tube 11 and the first tube 121 is ensured.

Specifically, the first distribution pipe 18 is located in the main channel of the first pipe 121, the first distribution pipe 18 extends for a certain distance along the length direction of the first pipe 121, the second pipe 141 includes a peripheral wall and a main channel surrounded by the peripheral wall, the second distribution pipe 19 is located in the main channel of the second pipe 141, the second distribution pipe 19 extends for a certain distance along the length direction of the second pipe 141, the hydraulic diameter of the first distribution pipe 18 is D3, the hydraulic diameter of the second distribution pipe 19 is D4, and the following conditions are satisfied: D3/D4 is more than or equal to 1 and less than or equal to 4, and the ratio can be 2 or 3, so that the gas-liquid two-phase refrigerant can uniformly flow into the corresponding tubes.

Specifically, the width dimension of the fin 16 is Fw, the width dimension of the first heat exchange tube 11 is Tw1, and the width dimension of the second heat exchange tube 13 is Tw2, which satisfies the following conditions: tw2< Fw ≦ Tw1+ Tw 2. Under the relation, the fin, the first heat exchange tube 11 and the second heat exchange tube 13 can be combined into an optimal configuration, and the heat exchange effectiveness of the heat exchanger is improved.

Another aspect of the present application further provides a multi-system air conditioning unit, which includes the heat exchanger 1 provided in any embodiment of the present application.

Another embodiment of the present application further provides a multi-system air conditioning unit, as shown in fig. 13, which includes the heat exchanger 1 provided in any embodiment of the present application, and the multi-system air conditioning unit includes a first system and a second system, the first system includes a first compressor unit 2, the first system is communicated with the first pipe 121 and the third pipe 122 of the heat exchanger, the second system includes a second compressor unit 3, the second system is communicated with the second pipe 141 and the fourth pipe 142 of the heat exchanger, and a ratio of output power of the first compressor unit 2 to output power of the second compressor unit 3 is greater than 1.5 and less than or equal to 5.

The multi-system air conditioning unit according to an embodiment of the present invention includes a plurality of refrigeration systems, at least two refrigeration systems in the multi-system air conditioning unit share at least one heat exchanger in any one of the above embodiments, as shown in fig. 13, the multi-system air conditioning unit 2 according to an embodiment of the present invention includes at least two refrigeration circuits, wherein, in one refrigeration circuit, the refrigerant flows out from the outlet of the first compressor 2 and enters the first pipe 121 of the heat exchanger 1, the first pipe 121 and the third pipe 131 communicate with each other through the first heat exchange tube 11, the refrigerant flows out from the third pipe 131 and returns to the inlet of the first compressor 2 to realize circulation of one refrigerant circuit, in another refrigeration circuit, the refrigerant flows out from the outlet of the second compressor 3 and enters the second pipe 141 of the heat exchanger 1, the second tube 141 and the fourth tube 142 are communicated through the second heat exchange tube 13, the refrigerant flows out of the second tube 141 and then enters the second tube 141 of another heat exchanger 1, the second tube 141 and the fourth tube 142 are communicated through the second heat exchange tube 13, the refrigerant flows out of the fourth tube 142 and then flows back to an inlet of the second compressor 3, circulation of a refrigerant loop is achieved, the heat exchanger can improve the utilization rate of a heat exchange area, and the improvement of the heat exchange performance of a system is facilitated.

The two systems can have different heat exchange capacities by enabling the two compressor sets to have different output powers, so that the operation working conditions of the sets with different loads can be matched, and the output powers of the two compressor sets can be adjusted within the range of more than 1.5 and less than or equal to 5, so that the adaptability of the heat exchanger to the multi-refrigerating-system air conditioning unit during partial load operation is improved.

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

Claims (10)

1. A heat exchanger, comprising:

a first assembly comprising a first tube and a second tube;

a second assembly comprising a third tube and a fourth tube;

the heat exchange tubes are microchannel flat tubes, each heat exchange tube comprises a plurality of channels arranged along the length direction of the heat exchange tube, the channels are arranged at intervals in the width direction of the heat exchange tube, each heat exchange tube comprises a first heat exchange tube and a second heat exchange tube, the first heat exchange tube is communicated with the first tube and the third tube, the second heat exchange tube is communicated with the second tube and the fourth tube, the first heat exchange tube and the second heat exchange tube are arranged at intervals in the length direction of the first tube, the first tube is not communicated with the second tube, and the third tube is not communicated with the fourth tube;

the fins comprise first fins, part of the first fins are connected with one first heat exchange tube, the other part of the first fins are connected with one second heat exchange tube, the first heat exchange tubes, the first fins and the second heat exchange tubes are arranged along the length direction of the first tubes, and the number of the first fins is multiple;

the first hydraulic diameter of the first tube is D1, the second hydraulic diameter of the second tube is D2, the ratio of the first hydraulic diameter D1 to the second hydraulic diameter D2 is greater than 1 and less than or equal to 6, and/or the width dimension of the first heat exchange tube is Tw1, the width dimension of the second heat exchange tube is Tw2, and the ratio of the width dimension Tw1 of the first heat exchange tube to the width dimension Tw2 of the second heat exchange tube is greater than 1 and less than or equal to 5.

2. The heat exchanger of claim 1, wherein the first heat exchange tube has a thickness dimension HT1 that is not equal to the second heat exchange tube thickness dimension HT 2.

3. The heat exchanger according to claim 1, wherein the width dimension of the first heat exchange tube and the width dimension of the second heat exchange tube satisfy the following condition: 0.2< D1 × Tw2/Tw1 × D2 ≤ 6.

4. The heat exchanger of claim 1, wherein the ratio of the first hydraulic diameter D1 to the second hydraulic diameter D2 is greater than 1 and equal to or less than 4, and the ratio of the first heat exchange tube width dimension Tw1 to the second heat exchange tube width dimension Tw2 is greater than 1 and equal to or less than 3.

5. The heat exchanger according to any one of claims 1 to 4, wherein, along the length direction of the first tubes, the minimum distance between two adjacent first heat exchange tubes is Tp1, the minimum distance between two adjacent second heat exchange tubes is Tp2, the TP1 is not equal to the TP2, the hydraulic diameter D1 of the first tubes and the hydraulic diameter D2 of the second tubes satisfy the following conditions:

0.2<D1×Tp2/Tp1×D2≤30；

0.2<Tp2/TP1≤5。

6. a heat exchanger according to claim 5 wherein the first tubes comprise a peripheral wall and a primary channel bounded by the peripheral wall, a finless zone being formed between the peripheral wall of the first tubes and the fins along the length of the first heat exchange tubes, the side of the heat exchanger which is upstream in the direction of the wind in operation being defined as the windward side and the side of the heat exchanger which is downstream in the direction of the wind being defined as the leeward side, at least some of the second tubes being located on either the windward or leeward side of the finless zone.

7. The heat exchanger of claim 6, wherein a first distribution pipe is located in the main channel of the first pipe, the first distribution pipe extends for a certain distance along the length direction of the first pipe, the second pipe comprises a peripheral wall and a main channel surrounded by the peripheral wall, a second distribution pipe is located in the main channel of the second pipe, the second distribution pipe extends for a certain distance along the length direction of the second pipe, the hydraulic diameter of the first distribution pipe is D3, the hydraulic diameter of the second distribution pipe is D4, and the following conditions are satisfied: D3/D4 is more than or equal to 1 and less than or equal to 4.

8. The heat exchanger of claim 1, wherein the fin has a width dimension Fw, the first heat exchange tube has a width dimension Tw1, and the second heat exchange tube has a width dimension Tw2, wherein the following conditions are satisfied: tw2< Fw ≦ Tw1+ Tw 2.

9. A multi-system air conditioning unit comprising a heat exchanger as claimed in any one of claims 1 to 8, the air conditioning unit comprising a plurality of multi-system air conditioning units, at least two of the multi-system air conditioning units sharing the heat exchanger.

10. The multi-system air conditioning unit according to claim 9, comprising the heat exchanger of claim 9, wherein the multi-system air conditioning unit comprises a first system and a second system, wherein the first system comprises a first compressor unit, the first system is communicated with the first pipe and the third pipe of the heat exchanger, the second system comprises a second compressor unit, the second system is communicated with the second pipe and the fourth pipe of the heat exchanger, and the ratio of the output power of the first compressor unit to the output power of the second compressor unit is greater than 1.5 and less than or equal to 5.

Images