Heat exchanger, cabinet air conditioner and air conditioning system

Abstract

The utility model provides a heat exchanger, a cabinet air conditioner and an air conditioning system, the heat exchanger comprises a temperature control heat exchange part and a dehumidification heat exchange part which are arranged side by side, a first throttling element is connected in series between a first side port of the temperature control heat exchange part and a first side port of the dehumidification heat exchange part, the windward heat exchange area of the temperature control heat exchange part is S1, and the windward heat exchange area of the dehumidification heat exchange part is S2. The windward heat exchange area of the dehumidification heat exchange part is S2, and S1: S2 = 0.34-0.62. According to the utility model, the temperature control and dehumidification energy efficiency can be improved while the cooling and heating performance of the air conditioner applying the air conditioner is ensured.

Description

TECHNICAL FIELD

[0001] The utility model belongs to air conditioning technology field, concretely relates to a heat exchanger, cabinet type air conditioner, air conditioning system. BACKGROUND

[0002] Household variable frequency heat pump air conditioners have been widely popularized in China, providing cooling and dehumidification functions in summer and heating services in winter. In order to ensure the dehumidification effect, the evaporating temperature of the air conditioner must be lower than the dew point temperature of the return air, and at the same time, in order to maintain the comfort of the indoor environment, the return air temperature should not be too low. However, in the low load cooling mode, the evaporating temperature of the household variable frequency air conditioner is usually high, in order to achieve effective dehumidification, the air volume of the indoor unit needs to be reduced, which will lead to the decrease of the evaporating temperature, and further affect the cooling efficiency and dehumidification capacity.

[0003] Especially in the middle and lower reaches of the Yangtze River basin and the areas south of it, the relative humidity in the transition season (i.e. the period when neither cooling nor heating is needed) is very high, especially during the "Meiyu season" and "Back to the South", the problem of indoor air humidity is particularly serious, not only affecting the comfort of living, but also possibly having adverse effects on health. When the conventional household variable frequency air conditioner dehumidifies in the transition season, with the gradual decrease of the indoor return air temperature and the dew point temperature, the indoor relative humidity may no longer continue to decrease, and even rebound, resulting in a cold and dry indoor environment. In addition, with the decrease of the evaporating temperature and the dew point temperature of the return air, the unit energy consumption of the air conditioner will also decrease significantly, which means that the dehumidification efficiency is low and the energy consumption is increased.

[0004] In view of the fact that about half of the population in China lives in the middle and lower reaches of the Yangtze River basin and the areas south of it, the duration of cooling demand in summer and humid weather in the transition season in these areas is very long, therefore, the demand for cooling and dehumidification is very large. In order to solve the problem of poor comfort and high energy consumption of the conventional household variable frequency air conditioner in the transition season humid weather, a series of reheat dehumidification technical scheme is proposed in the related technology. This technical scheme connects the indoor heat exchanger through the dehumidification valve, in the reheat dehumidification mode, the dehumidification valve plays the role of throttling, so that the heat exchanger upstream of the dehumidification valve is in a high temperature state, heating the indoor return air; while the heat exchanger downstream of the dehumidification valve is in a low temperature and low pressure state, cooling and dehumidifying the indoor return air, finally, the mixed air of the two parts of the heat exchanger is sent into the room, thus improving the dehumidification efficiency and ensuring the comfort of the indoor environment.

[0005] In order to reduce the size, the household cabinet heat exchanger usually has the characteristics of single U tube length, multiple U tube quantity, multiple shunt quantity and the like, when the heat exchanger is applied to a series reheating dehumidification system, the area ratio of the reheating section heat exchanger before the indoor heat exchanger dehumidification valve and the evaporating section heat exchanger after the dehumidification valve will affect the system refrigeration / heating energy efficiency and the reheating dehumidification SMER (unit energy consumption dehumidification quantity), and reasonable heat exchanger area ratio and reheating dehumidification heat exchange part flow path need to be designed to consider the system conventional refrigeration / heating operation performance and the reheating dehumidification operation energy efficiency. Utility model content

[0006] Therefore, the utility model provides a kind of heat exchanger, cabinet air conditioner, air conditioning system, can overcome the technical problem of the area ratio of two heat exchange parts of heat exchanger with series reheating dehumidification heat exchange part in relevant technology is not reasonable enough, cannot consider conventional refrigeration / heating operation performance and reheating dehumidification operation energy efficiency.

[0007] In order to solve the above problems, the utility model provides a kind of heat exchanger, including temperature control heat exchange part and dehumidification heat exchange part arranged side by side, first throttling element is connected in series between the first side port of temperature control heat exchange part and the first side port of dehumidification heat exchange part, the windward heat exchange area of temperature control heat exchange part is S1, the windward heat exchange area of dehumidification heat exchange part is S2, S1:S2=0.34~0.62.

[0008] In some embodiments, S1:S2=0.34~0.52.

[0009] In some embodiments, the temperature control heat exchange part and the dehumidification heat exchange part are both of tube-fin heat exchange structure, and the number of U tubes in the temperature control heat exchange part is m, the number of U tubes in the dehumidification heat exchange part is n, the ratio of m and n is within the ratio range of S1 and S2.

[0010] In some embodiments, a plurality of U tube groups are arranged in the temperature control heat exchange part, the first ports of the U tube groups are communicated by a first branch pipe and a first flow divider, the communication port of the first flow divider is the first side port, a plurality of U tube groups are arranged in the dehumidification heat exchange part, the first ports of the U tube groups are communicated by a second branch pipe and a second flow divider, the communication port of the second flow divider is the second side port, a is 3~5, and b is 3~5.

[0011] In some embodiments, the connection pipe between the communication port of the first flow divider and the first throttling element is a first connection pipe, the connection pipe between the communication port after the second flow divider and the first throttling element is a second connection pipe, and the flow passage inner diameter of the first connection pipe and the second connection pipe is greater than the flow passage inner diameter of each U tube and the first branch pipe and the second branch pipe.

[0012] In some embodiments, the flow-through inner diameter of each U-tube and the first branch pipe and the second branch pipe in the heat exchanger is one of 5 mm, 6 mm, 7 mm; and / or the flow-through inner diameter of the first connecting pipe and the second connecting pipe is one of 9 mm, 9.52 mm, 12 mm.

[0013] In some embodiments, the temperature control heat exchange part and the dehumidification heat exchange part are arranged from top to bottom along the height direction.

[0014] The utility model also provides a cabinet type air conditioner which comprises the heat exchanger.

[0015] The utility model also provides an air conditioning system which comprises the indoor heat exchanger, and the indoor heat exchanger is the heat exchanger.

[0016] The heat exchanger, the cabinet type air conditioner and the air conditioning system have the following beneficial effects:

[0017] The ratio of the windward heat exchange area of the temperature control heat exchange part 1 to the windward heat exchange area of the dehumidification heat exchange part 2 is limited to 0.34 to 0.62, which can ensure the cooling and heating performance of the air conditioner and improve the temperature control and dehumidification energy efficiency. BRIEF DESCRIPTION OF DRAWINGS

[0018] In order to more clearly illustrate the embodiments of the utility model or the technical solutions in the prior art, the following will briefly introduce the drawings needed to be used in the embodiment or the prior art description. The drawings in the following description are only exemplary, and for those skilled in the art, other implementation drawings can be obtained according to the provided drawings without creative labor.

[0019] Figure 1 It is the structure schematic view of the heat exchanger in the utility model embodiment 1 (in the temperature control and dehumidification mode);

[0020] Figure 2 It is the structure schematic view of the heat exchanger in the utility model embodiment 2 (in the temperature control and dehumidification mode);

[0021] Figure 3 It is the principle schematic view of the air conditioning system in another embodiment of the utility model (the circulating flow path in the operation temperature control and dehumidification mode);

[0022] Figure 4 It is the simulation calculation result of the temperature control and dehumidification performance of different temperature control and dehumidification flow paths;

[0023] Figure 5 It is the simulation calculation result of the influence of the saturation temperature drop of the temperature control heat exchange part and the dehumidification heat exchange part in different temperature control and dehumidification flow paths on the rated refrigeration performance.

[0024] The reference signs are:

[0025] 1, temperature control heat exchange part; 2, dehumidification heat exchange part; 3, first throttling element; 41, first flow divider; 42, second flow divider; 43, third flow divider; 51, distribution pipe; 52, gas collecting pipe; 100, indoor heat exchanger; 101, outdoor heat exchanger; 102, second throttling element; 103, compressor; 104, four-way reversing valve. DETAILED DESCRIPTION

[0026] The technical solutions in the embodiments of the present application will be clearly and completely described below with reference to the drawings in the embodiments of the present application. Obviously, the described embodiments are only part of the embodiments of the present application, rather than all the embodiments. The description of the at least one exemplary embodiment is actually only illustrative, but not as any limitation on the present application and its application or use. Based on the embodiments in the present application, all other embodiments obtained by those skilled in the art without creative labor fall within the scope of protection of the present application.

[0027] In the description of the present application, it should be understood that the orientation words such as "front, back, up, down, left, right", "horizontal, vertical, perpendicular, horizontal" and "top, bottom" and the like indicate the orientation or positional relationship shown in the drawings, and are only for the convenience of describing the present application and simplifying the description, and in the absence of the opposite description, these orientation words do not indicate and imply that the indicated device or element must have a specific orientation or be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation on the scope of protection of the present application; the orientation words "inner, outer" refer to the inner and outer of the contour of each component itself.

[0028] For the convenience of description, spatial relative terms such as "on", "above", "upper surface", "upper" and the like can be used herein to describe the spatial positional relationship of one device or feature with respect to other devices or features as shown in the drawings. It should be understood that the spatial relative terms are intended to include different orientations in use or operation in addition to the orientation of the device described in the drawings. For example, if the device in the drawings is inverted, the device described as "above" or "on" other devices or structures will be positioned "below" or "under" other devices or structures. Thus, the exemplary term "above" can include both "above" and "below" orientations. The device can also be positioned in other different ways (rotated 90° or in other orientations), and the spatial relative descriptions used herein are interpreted accordingly.

[0029] In addition, it should be noted that the use of the terms "first", "second", etc. to define parts is merely for the convenience of distinguishing the corresponding parts, and the above terms have no special meaning unless otherwise stated, and therefore cannot be understood as limiting the scope of protection of the utility model.

[0030] Referring to Figures 1 to 5 As shown in the drawings, according to the embodiment of the utility model, a heat exchanger is provided, which comprises a temperature control heat exchange part 1 and a dehumidification heat exchange part 2 arranged side by side, the side-by-side arrangement means that the incoming air flow flows to the windward area of the temperature control heat exchange part 1 and the dehumidification heat exchange part 2 simultaneously in parallel, so that part of the incoming air flow can be heated and warmed by the temperature control heat exchange part 1, and the other part of the incoming air flow is condensed and dehumidified by the dehumidification heat exchange part 2, and the air flows after heat exchange with the temperature control heat exchange part 1 and the dehumidification heat exchange part 2 are mixed and then sent out, thereby achieving the purpose of temperature control and dehumidification of the incoming air flow, and the temperature control heat exchange part 1 and the dehumidification heat exchange part 2 do not have a front and back overlapping arrangement part, a first throttling element 3 is connected in series between the first side port of the temperature control heat exchange part 1 and the first side port of the dehumidification heat exchange part 2, the windward heat exchange area of the temperature control heat exchange part 1 is S1, the windward heat exchange area of the dehumidification heat exchange part 2 is S2, and S1:S2 = 0.34-0.62.

[0031] In the technical scheme, the ratio of the windward heat exchange area of the temperature control heat exchange part 1 to the windward heat exchange area of the dehumidification heat exchange part 2 is limited to 0.34-0.62, which can ensure the cooling and heating performance of the air conditioner and improve the temperature control and dehumidification energy efficiency at the same time.

[0032] As a more preferred embodiment, S1:S2 = 0.34-0.52, which can further improve the cooling and heating performance of the air conditioner and the temperature control and dehumidification energy efficiency.

[0033] It can be understood that the first throttling element 3 can be referred to as a dehumidification valve, which divides the heat exchanger into the temperature control heat exchange part 1 at the upstream and the dehumidification heat exchange part 2 at the downstream, the surface temperature of the temperature control heat exchange part 1 is higher than the incoming air temperature in the reheating and dehumidification mode, the indoor return air is heated to compensate for the sensible heat of the dehumidification process of the dehumidification heat exchange part 2; the surface temperature of the dehumidification heat exchange part 2 is lower than the dew point temperature of the return air, the indoor return air is cooled and dehumidified, and the two air flows are mixed before being sent out, forming a supply air state with low moisture content and temperature close to the incoming air temperature, thereby improving the dehumidification comfort in the transition season.

[0034] In some embodiments, the temperature control heat exchange part 1 and the dehumidification heat exchange part 2 are both of the tube-fin heat exchange structure, that is, the temperature control heat exchange part 1 and the dehumidification heat exchange part 2 are respectively formed by a plurality of U-tubes connected in series, specifically, the number of U-tubes in the temperature control heat exchange part 1 is m, the number of U-tubes in the dehumidification heat exchange part 2 is n, and the ratio of m to n is within the ratio range of S1 to S2.

[0035] In the technical solution, by setting the number ratio of U tubes in the temperature control heat exchange part 1 and the dehumidification heat exchange part 2 to be within the area ratio range, the design difficulty of the heat exchanger can be simplified.

[0036] In some embodiments, a plurality of U tube groups are arranged in the temperature control heat exchange part 1, the first ports of the U tube groups are communicated with a first flow divider 41 via first branch pipes, the communication port of the first flow divider 41 is the first side port, a plurality of U tube groups are arranged in the dehumidification heat exchange part 2, the first ports of the U tube groups are communicated with a second flow divider 42 via second branch pipes, the communication port of the second flow divider 42 is the second side port, a is 3-5, and b is 3-5.

[0037] In the technical solution, by reasonably limiting the number of U tube groups arranged in the temperature control heat exchange part 1 and the dehumidification heat exchange part 2, that is, by reasonably limiting the number of branches of the heat exchangers, the heat exchange performance of the heat exchanger can be further improved.

[0038] In some embodiments, the connecting pipe between the communication port of the first flow divider 41 and the first throttling element 3 is a first connecting pipe, the connecting pipe between the communication port of the second flow divider 42 and the first throttling element 3 is a second connecting pipe, the flow diameters of the first connecting pipe and the second connecting pipe are greater than the flow diameters of the U tubes and the first branch pipes and the second branch pipes, specifically, the flow diameters of the U tubes, the first branch pipes and the second branch pipes in the heat exchanger are one of 5mm (φ5), 6mm (φ6) and 7mm (φ7), and the flow diameters of the first connecting pipe, the second connecting pipe, the first branch pipes and the second branch pipes are one of 9mm (φ9), 9.52mm (φ9.52) and 12mm (φ12), so as to reduce the pressure drop of the refrigerant in the refrigeration / heating mode as much as possible under the condition of meeting the installation process requirements.

[0039] In some embodiments, the temperature control heat exchange part 1 and the dehumidification heat exchange part 2 are arranged from top to bottom along the height direction.

[0040] In the technical solution, the temperature control heat exchange part 1 is arranged above the dehumidification heat exchange part 2, so that the phenomenon that the condensed water generated by the dehumidification heat exchange part 2 during operation flows to the temperature control heat exchange part 1 and causes poor temperature control effect of the temperature control heat exchange part 1 can be prevented when the dehumidification heat exchange part 2 is arranged above the temperature control heat exchange part 1.

[0041] For a better understanding of the present application, reference will be made to the following embodiments and drawings. Figure 4 and Figure 5 In order to prove the consistency of the area ratio and the design purpose of the present application, the inventors provide four different area flow paths as listed in Table 1, which are flow path a, flow path b, flow path c and flow path d (as shown in Figure 4 andFigure 5 Table 1 Heat exchanger different combination way

[0042] Table 1 Heat exchanger different combination way

[0043] Flow path type Area ratio Flow path a 0.28～0.34 Flow path b 0.34～0.41 Flow path c 0.41～0.52 Flow path d 0.52～0.62

[0044] Table 1 lists the commonly used 2-row φ7 temperature control dehumidification indoor unit heat exchanger different combination way and its corresponding area ratio range, and the temperature control dehumidification performance of different flow paths and the simulation calculation of the influence of different flow path connection pipe pressure drop on the rated refrigeration performance, wherein the indoor unit (i.e. the indoor part of the air conditioner) branch number needs to ensure that the mass flow rate in the pipe is 150-250 kg / m 2 s under the rated refrigeration working condition (indoor 27 / 19℃, outdoor 35 / 24℃). According to this, the indoor unit heat exchanger branch number is estimated, while considering the symmetry of the flow path and the wind speed distribution and other factors. Taking the 2-row φ7 indoor unit heat exchanger R32 refrigerant as an example, the inlet specific enthalpy is determined by the condensation temperature 44℃, the condenser outlet temperature 38℃, the outlet specific enthalpy is determined by the pressure 1100kPa, and the superheat 1℃. With 7200W as the target refrigeration capacity, according to the appropriate mass flow rate range, the indoor unit branch number is estimated to be 3.1-5.1. Only for φ7 indoor unit heat exchanger, the branch design mainly selects 3-5. The temperature control condenser (i.e. the temperature control heat exchange part 1) and the dehumidification evaporator (i.e. the dehumidification heat exchange part 2) do not necessarily have to have the same number of branches. The saturation temperature drop of both needs to be considered comprehensively, and the appropriate branch number is selected in the design of the branch, for example, the temperature control condenser branch number is 3, and the dehumidification evaporator branch number is 4, while Figure 1 , respectively 4, 4. Figure 2

[0045] The simulation calculation results are shown in Figure 4 and Figure 5 , Figure 4 Under the typical temperature control dehumidification working condition indoor and outdoor 22℃ / 80%RH, the exhaust saturation temperature is given as 45℃ (Tc in Figure 4 ), the inlet saturation temperature difference of the outdoor condenser (i.e. the outdoor heat exchanger 101) and the temperature control condenser is 1℃ (△T in Figure 4 ), the dehumidification capacity and the indoor supply air volume are the same, and the temperature control dehumidification SMER (unit energy consumption dehumidification capacity) changes with the supply air temperature. From Figure 4 , it can be seen that with the increase of the area ratio, the highest supply air temperature that can be reached by the temperature control dehumidification mode increases, but when the area ratio increases to a certain extent, the temperature control dehumidification energy efficiency SMER significantly decreases; Figure 5 ​The trend of the rated refrigeration EER with the temperature drop between the temperature control section heat exchanger and the evaporating section heat exchanger at different area ratios is shown in the figure. It can be seen that the rated refrigeration performance decreases with the saturation temperature drop between the temperature control section heat exchanger and the evaporating section heat exchanger, and the decrease is higher with the increase of the area ratio. Therefore, when the area ratio is between 0.34 and 0.62 (i.e. flow path a, flow path b and flow path c), and further preferably between 0.34 and 0.52 (i.e. flow path b and flow path c), the system has better temperature control dehumidification performance and cooling and heating performance.

[0046] According to the embodiment of the utility model, further provide a kind of cabinet air conditioner, especially a kind of round cabinet machine, comprising the heat exchanger described above.

[0047] According to the embodiment of the utility model, further provide a kind of air conditioning system, comprising indoor heat exchanger 100, the indoor heat exchanger 100 is the heat exchanger described above. Specifically referring to Figure 3 As shown in the figure, it is the circulation schematic diagram of the series temperature control dehumidification air conditioning system using the heat exchanger of the utility model, mainly by compressor 103, indoor heat exchanger 100, four-way valve 104, outdoor heat exchanger 101 and second throttling element 102 and indoor and outdoor fan etc. In temperature control dehumidification mode, four-way valve is powered off;Refrigerant is discharged from the exhaust port of compressor 103 and enters outdoor heat exchanger 101 through the D pipe of four-way valve 104, and then is cooled to high-pressure high-temperature two-phase state through outdoor heat exchanger 101, and then passes through second throttling element 102, at this time, outdoor second throttling element 102 is in full open state, and is cooled to high-pressure supercooled liquid through temperature control heat exchange part 1 of indoor heat exchanger 100, and then is throttled to low-pressure two-phase state through first throttling element 3, and is cooled to low-pressure superheated gas through dehumidification heat exchange part 2 of indoor heat exchanger 100 and enters four-way valve 104 through E pipe, enters compressor 103 suction port, and is compressed to high-pressure high-temperature superheated gas, so as to complete the whole cycle.

[0048] Example 1:

[0049] Figure 1The flow path schematic diagram of the heat exchanger in the structure arrangement form of the 2-row 58-U-tube φ7 indoor unit heat exchanger commonly used in the household cabinet machine, the heat exchanger area ratio of the temperature control condenser to the dehumidification evaporator is 0.38. When the temperature control dehumidification mode is operated, the refrigerant of the indoor unit heat exchanger (i.e. the indoor heat exchanger 100, the same below) successively passes through the liquid separation pipe 51, the third flow divider 43, the first flow divider 41, the first throttling element 3, the second flow divider 42 and the gas collection pipe 52. The third flow divider 43, the first flow divider 41 and the second flow divider 42 can be conventional brass flow dividers or impeller flow dividers, and the impeller separators are preferred to ensure uniform flow division. The gas collection pipe can reduce the pipeline pressure drop to reduce the influence on the system energy efficiency. The air simultaneously passes through the temperature control condenser and the dehumidification evaporator. The dehumidification evaporator cools and dehumidifies the air passing through it, and the temperature control condenser heats the air passing through it. The two air streams are mixed to form air close to the ambient temperature but with low humidity, thereby realizing the temperature control dehumidification function. In the temperature control dehumidification mode, the refrigerant from the outlet of the outdoor unit condenser (i.e. the outdoor heat exchanger 101, the same below) enters the pipeline liquid separation pipe 51, is divided into 3 paths through the third flow divider 43 (3-hole impeller flow divider), is heated and treated by the air passing through the temperature control condenser (at this time the refrigerant temperature is higher than the air temperature), is then combined into one path from the temperature control condenser, flows into the first throttling element 3, becomes low-temperature and low-pressure refrigerant, is divided into 4 paths through the second flow divider 42 (4-hole impeller flow divider), is cooled and dehumidified by the air passing through the dehumidification evaporator (at this time the refrigerant temperature is lower than the air dew point temperature), is then combined into one path from the dehumidification evaporator, enters the suction port of the compressor 103.

[0050] Due to the connection pipes, connection components and throttling devices between the temperature control condenser and the dehumidification evaporator of the temperature control dehumidification system, there is a pressure drop in the connection part. For the series temperature control dehumidification system, the greater the saturation temperature drop of the connection part, the more obvious the reduction of the refrigeration and heating energy efficiency. Therefore, for the connection part specifications between the temperature control condenser and the dehumidification evaporator of this flow path form: the front connection pipe of the first flow divider 41, the rear connection pipe of the second flow divider 42, the pipeline specifications are selected as 5mm, 6mm, 7mm, and 6mm and 7mm are preferred; the front and rear connection pipes of the first throttling element 3 are selected as 9mm, 9.52mm, 12mm, and 9mm and 9.52mm are preferred; the air flow when the first throttling element 3 is fully open is between 350-650L / min, and 400-500L / min is preferred.

[0051] This proposal gives the flow path structure form of the series temperature control system for the cabinet air conditioner indoor unit heat exchanger. It should be noted that the flow path given in the schematic diagram is only one flow path form under the given conditions of the number of U-tubes and the pipeline specifications of the indoor heat exchanger. For different models of U-tube number and heat exchanger length, the flow path form can also be adjusted appropriately under the area ratio given in the claims.

[0052] Embodiment 2:

[0053] Figure 2 The flow path schematic diagram of the heat exchanger in the structure arrangement form of the 2-row 58-U-tube φ7 indoor heat exchanger commonly used for the household cabinet machine, the heat exchanger area ratio of the temperature control condenser and the dehumidification evaporator is 0.45. When operating in the temperature control dehumidification mode, the refrigerant of the indoor heat exchanger passes through the liquid distribution pipe 51, the third flow divider 43, the first flow divider 41, the first throttling element 3, the second flow divider 42 and the gas collection pipe 52 in turn. The third flow divider 43, the first flow divider 41 and the second flow divider 42 can be conventional brass flow dividers or impeller flow dividers, and the impeller separators are preferred to ensure uniform distribution. The gas collection pipe can reduce the pressure drop of the pipeline to reduce the impact on the system energy efficiency. The air passes through the temperature control condenser and the dehumidification evaporator at the same time. The dehumidification evaporator cools and dehumidifies the air passing through it, and the temperature control condenser heats the air passing through it. The two air streams are mixed to form air with a temperature close to the ambient temperature but with low humidity, thereby realizing the temperature control dehumidification function. In the temperature control dehumidification mode, the refrigerant enters the pipeline liquid distribution pipe 51 from the outlet of the outdoor condenser (i.e. the outdoor heat exchanger 101, the same below), is divided into 4 paths through the third flow divider 43 (4-hole impeller flow divider), is heated and treated by the air passing through the temperature control condenser (at this time, the temperature of the refrigerant is higher than the temperature of the air), is then combined into one path from the temperature control condenser, flows into the first throttling element 3, becomes low-temperature and low-pressure refrigerant, is divided into 4 paths through the second flow divider 42 (4-hole impeller flow divider), is cooled and dehumidified by the air passing through the dehumidification evaporator (at this time, the temperature of the refrigerant is lower than the dew point temperature of the air), is then combined into one path from the dehumidification evaporator, and enters the suction port of the compressor 103.

[0054] Those skilled in the art can easily understand that the advantageous technical features of each of the above modes can be freely combined and superimposed without conflict.

[0055] The above only describes the preferred embodiments of the present application, and should not be used to limit the present application. Any modification, equivalent replacement and improvement made within the spirit and principle of the present application should be included in the protection scope of the present application. The above only describes the preferred embodiments of the present application, and should not be used to limit the present application. Any modification, equivalent replacement and improvement made within the spirit and principle of the present application should be included in the protection scope of the present application.

Claims

1. A heat exchanger comprising a temperature-controlled heat exchange part (1) and a dehumidifying heat exchange part (2) arranged side by side, a first throttling element (3) being connected in series between a first side port of the temperature-controlled heat exchange part (1) and a first side port of the dehumidifying heat exchange part (2), characterized in that, The windward heat exchange area of the temperature control heat exchange part (1) is S1, the windward heat exchange area of the dehumidification heat exchange part (2) is S2, and S1:S2=0.34-0.

62.

2. The heat exchanger of claim 1, wherein S1:S2=0.34-0.

52.

3. The heat exchanger of claim 1, wherein The temperature control heat exchange part (1) and the dehumidification heat exchange part (2) are both of the tube-fin heat exchange structure, and the number of U-tubes in the temperature control heat exchange part (1) is m, and the number of U-tubes in the dehumidification heat exchange part (2) is n, and the ratio of m to n is within the ratio range of S1 to S2.

4. The heat exchanger of claim 3, wherein The temperature control heat exchange part (1) is provided with a U-tube group, and the first port of the U-tube group is communicated with the first shunt (41) through a first branch pipe, and the converging port of the first shunt (41) is the first side port, and the dehumidification heat exchange part (2) is provided with a U-tube group, and the first port of the U-tube group is communicated with the second shunt (42) through a second branch pipe, and the converging port of the second shunt (42) is the second side port, and a is 3-5, and b is 3-5.

5. The heat exchanger of claim 4, wherein The connecting pipe between the converging port of the first shunt (41) and the first throttling element (3) is the first connecting pipe, the connecting pipe between the converging port of the second shunt (42) and the first throttling element (3) is the second connecting pipe, and the flow diameter of the first connecting pipe and the second connecting pipe is larger than the flow diameter of each U-tube and the first branch pipe and the second branch pipe.

6. The heat exchanger of claim 5, wherein The flow diameter of each U-tube and the first branch pipe and the second branch pipe in the heat exchanger is one of 5mm, 6mm and 7mm; and / or, the flow diameter of the first connecting pipe and the second connecting pipe is one of 9mm, 9.52mm and 12mm.

7. The heat exchanger of claim 1, wherein The temperature control heat exchange part (1) and the dehumidification heat exchange part (2) are arranged from top to bottom along the height direction.

8. A cabinet-type air conditioner, characterized by comprising: The heat exchanger comprises any one of claims 1-7.

9. An air conditioning system comprising an indoor heat exchanger (100), characterized by, The indoor heat exchanger (100) is the heat exchanger of any one of claims 1-7. The indoor heat exchanger (100) is the heat exchanger of any one of claims 1-7.

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