Heat exchange system and air conditioner

Abstract

The utility model belongs to the technical field of heat exchange systems, and discloses a heat exchange system and an air conditioner, the heat exchange system comprises an outdoor side assembly and an indoor side assembly, the outdoor side assembly comprises a first heat exchanger, and the indoor side assembly comprises a second heat exchanger, a third heat exchanger and a first expansion valve; the first end of the second heat exchanger is connected to the outdoor side assembly through a refrigerant pipeline, the second end of the second heat exchanger is connected to the first end of the first expansion valve through a refrigerant pipeline, and the second end of the first expansion valve is connected to the first end of the third heat exchanger through a refrigerant pipeline. The second end of the third heat exchanger is connected to the outdoor side assembly through a refrigerant pipeline, the ratio of the heat exchange area of the second heat exchanger to the heat exchange area of the third heat exchanger is 0.32-1.3, and in the reheating dehumidification mode, the first heat exchanger is a condenser, the second heat exchanger is a condenser, the third heat exchanger is an evaporator, and the second heat exchanger is a condenser. Therefore, the heat exchange system can enable the indoor environment to achieve the required comfort degree in various operation modes.

Description

Technical Field

[0001] The utility model relates to the technical field of heat exchange systems, in particular to a heat exchange system and an air conditioner. Background Art

[0002] Relative humidity is high during the transition season in the middle and lower reaches of the Yangtze River and areas south of it, particularly during the plum rain season and the return of the south wind. Indoor dehumidification is essential to address the comfort and health issues caused by damp air. Current air conditioning technologies used by household air conditioners during the transition season for cooling and dehumidification gradually decrease the indoor return air temperature and dew point. Once the indoor relative humidity reaches a certain level, it no longer decreases and may even increase. This results in a cold but not dry indoor environment, failing to meet the comfort requirements of dehumidification. Utility Model Content

[0003] The technical problem to be solved by the present invention is that when a household air conditioner is cooling and dehumidifying in the transition season, the indoor return air temperature and return air dew point gradually decrease, and the indoor relative humidity no longer decreases after dropping to a certain level or even increases, resulting in the indoor temperature being cold but not dry, which cannot meet the comfort requirements of dehumidification. A heat exchange system, an air conditioner and a control method are provided.

[0004] The utility model aims to provide a heat exchange system, comprising:

[0005] an outdoor side assembly, the outdoor side assembly comprising a first heat exchanger;

[0006] An indoor component, the indoor component including a second heat exchanger and a third heat exchanger refrigerant pipeline, connecting the outdoor component and the indoor component so that the indoor component and the outdoor component form a closed refrigerant circuit;

[0007] The second heat exchanger, the first expansion valve and the third heat exchanger are connected to the refrigerant pipeline in sequence, and the refrigerant flows into the second heat exchanger;

[0008] The ratio of the heat exchange area of ​​the second heat exchanger to the heat exchange area of ​​the third heat exchanger is 0.32 to 1.3;

[0009] Wherein, in the reheat dehumidification mode, the first heat exchanger is a condenser, the second heat exchanger is a condenser, and the third heat exchanger is an evaporator.

[0010] In some embodiments, the outdoor side assembly further comprises:

[0011] a compressor, wherein a first end of the compressor is connected to a second end of the third heat exchanger via a refrigerant pipeline, and a second end of the compressor is connected to a first end of the first heat exchanger via a refrigerant pipeline;

[0012] a second expansion valve, wherein a first end of the second expansion valve is connected to a second end of the first heat exchanger via a refrigerant pipeline; and a second end of the second expansion valve is connected to a first end of the second heat exchanger via a refrigerant pipeline;

[0013] Among them, in the reheat dehumidification mode, the second expansion valve is at the maximum opening, the upper limit range of the gas flow of the first expansion valve is 15L / min to 35L / min, and the lower limit range of the gas flow of the first expansion valve is less than or equal to 6L / min.

[0014] In some embodiments, the upper limit of the gas flow rate of the first expansion valve ranges from 20 L / min to 30 L / min; the lower limit of the gas flow rate of the first expansion valve ranges from 2 L / min to 4 L / min.

[0015] In some embodiments, a ratio of a heat exchange area of ​​the second heat exchanger to a heat exchange area of ​​the third heat exchanger is 0.5 to 1.0.

[0016] In some embodiments, the ratio of the number of heat exchange tubes of the second heat exchanger to the number of heat exchange tubes of the third heat exchanger is 0.32 to 1.3.

[0017] In some embodiments, the ratio of the number of heat exchange tubes of the second heat exchanger to the number of heat exchange tubes of the third heat exchanger is 0.5 to 1.0.

[0018] In some embodiments, the second end fin of the second heat exchanger is provided with a special-shaped cut; and / or

[0019] The first end fin of the third heat exchanger is provided with a special-shaped cut.

[0020] In some embodiments, the outdoor side assembly further comprises:

[0021] A reversing valve, the first end of the reversing valve is connected to the second end of the compressor through a refrigerant pipeline, the second end of the reversing valve is connected to the first end of the first heat exchanger through a refrigerant pipeline, the third end of the reversing valve is connected to the first end of the compressor through a refrigerant pipeline, and the fourth end of the reversing valve is connected to the second end of the third heat exchanger through a refrigerant pipeline.

[0022] In some embodiments, further comprising:

[0023] a first stop valve, wherein a first end of the first stop valve is connected to a second end of the first expansion valve via a refrigerant pipeline, and a second end of the first stop valve is connected to a first end of the second heat exchanger via a refrigerant pipeline;

[0024] The second stop valve has a first end connected to the second end of the third heat exchanger through a refrigerant pipeline, and a second end connected to the first end of the compressor through a refrigerant pipeline.

[0025] In some embodiments, an air conditioner is provided, comprising a heat exchange system according to any of the above technical solutions and a controller for controlling the heat exchange system;

[0026] When the heat exchange system is in a reheat dehumidification mode, the controller is used to control the opening value of the second expansion valve to a maximum, and control the opening value of the first expansion valve to increase or decrease according to the exhaust temperature of the outdoor component;

[0027] When the heat exchange system is in cooling mode or heating mode, the controller is used to control the opening value of the first expansion valve to the maximum, and control the opening value of the second expansion valve to increase or decrease according to the exhaust temperature of the outdoor component.

[0028] In some embodiments, the reheat dehumidification air conditioner is a household cabinet-type top and bottom air-discharge air conditioner.

[0029] In some embodiments, a control method is provided for controlling the heat exchange system in any of the above technical solutions and / or the air conditioner in any of the above technical solutions, the control method comprising:

[0030] Receive control instructions;

[0031] When the control instruction is the reheat dehumidification mode, adjust the opening value of the second expansion valve to the maximum;

[0032] Get the exhaust temperature of the compressor;

[0033] Determine whether the exhaust temperature of the compressor is greater than the preset temperature value;

[0034] If so, the opening value of the first expansion valve is adjusted to increase;

[0035] If not, the opening value of the first expansion valve is adjusted to decrease.

[0036] In some embodiments, when the control instruction is a cooling mode or a heating mode, the opening value of the first expansion valve is adjusted to a maximum;

[0037] Get the exhaust temperature of the compressor;

[0038] Determine whether the exhaust temperature of the compressor is greater than the preset temperature value;

[0039] If yes, adjust the opening value of the second expansion valve to increase;

[0040] If not, the opening value of the second expansion valve is adjusted to decrease.

[0041] The technical solution provided by this utility model has the following beneficial effects compared with the prior art:

[0042] By setting a second heat exchanger, a first expansion valve and a third heat exchanger, and limiting the ratio range of the heat exchange area of ​​the second heat exchanger to the heat exchange area of ​​the third heat exchanger, the heat exchange system can take into account the performance when operating in cooling mode or heating mode and the performance of the heat exchange system when operating in reheat dehumidification mode, so that the heat exchange system can achieve the required comfort level in the indoor environment under various operating modes, and at the same time solve the problems of large energy efficiency attenuation in cooling mode or heating mode and poor performance in reheat dehumidification mode caused by an unreasonable heat exchange area ratio between the second heat exchanger and the third heat exchanger. BRIEF DESCRIPTION OF THE DRAWINGS

[0043] The accompanying drawings are part of the present invention and are used to provide a further understanding of the present invention. The illustrative embodiments of the present invention and their descriptions are used to explain the present invention but do not constitute an improper limitation of the present invention. Obviously, the drawings described below are only some embodiments. For those skilled in the art, other drawings can be obtained based on these drawings without inventive work. In the drawings:

[0044] Figure 1 This is a schematic diagram of the flow path circulation in the reheat dehumidification mode shown in an embodiment of the present invention;

[0045] Figure 2 This is a schematic diagram of a flow circuit in a cooling mode according to an embodiment of the present invention;

[0046] Figure 3 This is a schematic diagram of the flow circulation in the heating mode shown in an embodiment of the present invention;

[0047] Figure 4 This is a schematic diagram showing the variation trend of SMER with supply air temperature in the reheat dehumidification mode shown in an embodiment of the present invention;

[0048] Figure 5 1 is a schematic diagram showing a trend of change in refrigerant injection volume with outlet air temperature in a reheat dehumidification mode at different area ratios a according to an embodiment of the present invention;

[0049] Figure 6 1 is a schematic diagram showing a trend of a change in the rated cooling EER with the temperature drop between the second heat exchanger and the third heat exchanger at different area ratios a according to an embodiment of the present invention;

[0050] Figure 7 1 is a schematic diagram of a flow path circulation of an indoor side component according to an embodiment of the present invention, taking an area ratio a of 0.92 as an example;

[0051] Figure 8 1 is a schematic diagram of a flow path circulation of an indoor side component according to an embodiment of the present invention, taking an area ratio a of 0.56 as an example;

[0052] Figure 9 This is a schematic diagram of a flow path circulation of an indoor side component of the present invention, in which a second heat exchanger and a third heat exchanger are connected in series along the air flow direction, taking an area ratio a of 0.92 as an example;

[0053] Figure 10 This is one of the flow charts of the control method shown in the embodiment of the present utility model;

[0054] Figure 11 This is the second flow chart of the control method shown in the embodiment of the present utility model.

[0055] In the figure: 10-heat exchange system, 100-outdoor side component, 110-first heat exchanger, 120-compressor, 130-second expansion valve, 140-reversing valve, 200-indoor side component, 210-second heat exchanger, 220-third heat exchanger, 230-first expansion valve, 300-refrigerant pipeline, 400-first stop valve, 500-second stop valve, 600-diverter, 20-air conditioner.

[0056] It should be noted that these drawings and textual descriptions are not intended to limit the conceptual scope of the present invention in any way, but rather to illustrate the concept of the present invention for those skilled in the art by referring to specific embodiments. DETAILED DESCRIPTION

[0057] To meet dehumidification requirements, the air conditioner's evaporation temperature needs to be lower than the return air dew point; however, to meet comfort requirements, the return air temperature should not be too low. Therefore, on the one hand, when household inverter air conditioners are operating at low-load cooling, the evaporation temperature is typically high. To achieve both dehumidification and cooling, the indoor unit air volume needs to be reduced, thereby lowering the evaporation temperature. This reduces both the cooling energy efficiency ratio and the dehumidification per unit energy consumption. On the other hand, when household air conditioners are operating during the transition season for cooling and dehumidification, the indoor return air temperature and return air dew point gradually decrease. Once the indoor relative humidity reaches a certain level, it no longer decreases and may even increase. This results in a cold but not dry indoor environment, failing to meet the comfort requirements of dehumidification.

[0058] Based on this, the following embodiments are proposed:

[0059] Example 1

[0060] like Figure 1 、 Figure 2 and Figure 3 As shown, a heat exchange system 10 includes:

[0061] The outdoor component 100 includes a first heat exchanger 110;

[0062] An indoor side component 200 , wherein the indoor side component 200 includes a second heat exchanger 210 , a third heat exchanger 220 and a first expansion valve 230 ;

[0063] A refrigerant pipeline 300 connects the outdoor component 100 and the indoor component 200 so that the indoor component 200 and the outdoor component 100 form a closed refrigerant circuit;

[0064] The second heat exchanger 210, the first expansion valve 230, and the third heat exchanger 220 are sequentially connected to the refrigerant pipeline 300, and the second heat exchanger 210 receives refrigerant before the first expansion valve 230 and the third heat exchanger in the reheat dehumidification mode;

[0065] The ratio of the heat exchange area of ​​the second heat exchanger 210 to the heat exchange area of ​​the third heat exchanger 220 is 0.32 to 1.3;

[0066] In the reheat dehumidification mode, the first heat exchanger 110 is a condenser, the second heat exchanger 210 is a condenser, and the third heat exchanger 220 is an evaporator.

[0067] This embodiment proposes an optimal area ratio of the reheat section heat exchanger before the dehumidification valve of the indoor heat exchanger to the evaporation section heat exchanger after the dehumidification valve, which can take into account both cooling / heating energy efficiency and comprehensive reheat and dehumidification performance.

[0068] like Figure 1 、 Figure 2 and Figure 3As shown, in this embodiment, the heat exchange system 10 includes an outdoor component 100 and an indoor component 200. The outdoor component 100 is used to implement heat exchange functions in an outdoor environment, and the indoor component 200 is used to implement heat exchange functions in an indoor environment. The outdoor component 100 includes a first heat exchanger 110, and the indoor component 200 includes a second heat exchanger 210, a third heat exchanger 220, and a first expansion valve 230. The first expansion valve 230 is located between the second heat exchanger 210 and the third heat exchanger 220. The first expansion valve 230 can adjust the opening value, thereby changing the state of the refrigerant after flowing through the first expansion valve 230. The first end of the second heat exchanger 210 is connected to the outdoor component 100 through the refrigerant pipeline 300, the second end of the second heat exchanger 210 is connected to the first end of the first expansion valve 230 through the refrigerant pipeline 300, the second end of the first expansion valve 230 is connected to the first end of the third heat exchanger 220 through the refrigerant pipeline 300, and the second end of the third heat exchanger 220 is connected to the outdoor component 100 through the refrigerant pipeline 300. By connecting the outdoor component 100, the second heat exchanger 210, the first expansion valve 230 and the third heat exchanger 220 in series through the refrigerant pipeline 300 and the refrigerant pipeline 300, the overall structure of the heat exchange system 10 is simplified, and the function of regulating the indoor environment can be realized without affecting the external dimensions and original functions of the air conditioner 20.

[0069] like Figure 1As shown, when the heat exchange system 10 operates in the reheat dehumidification mode, the first heat exchanger 110 acts as a condenser to perform preliminary cooling on the refrigerant flowing through the first heat exchanger 110, so that after the refrigerant flows through the first heat exchanger 110, it is distributed by the refrigerant diverter 600 into each branch in the second heat exchanger 210. At this time, the second heat exchanger 210 acts as a condenser to cool the refrigerant again, so that the refrigerant can continue to condense and release heat more fully. At the same time, the surface temperature of the second heat exchanger 210 is higher than the indoor inlet air temperature, and the indoor return air can be heated to compensate for the sensible heat of the third heat exchanger 220 during the dehumidification process. After the refrigerant flows out of the second heat exchanger 210, it is merged through the diverter 600 and flows to the first expansion valve 230. When the refrigerant passes through the first expansion valve 230, the throttling and pressure-reducing action of the first expansion valve 230 causes the refrigerant to enter the various branches within the third heat exchanger 220 in a low-temperature, low-pressure two-phase state. The refrigerant is then distributed through the flow divider 600 and enters the various branches within the third heat exchanger 220. At this point, the low-pressure, low-temperature refrigerant absorbs heat and vaporizes in the third heat exchanger 220, rapidly decreasing the temperature of the third heat exchanger 220, which acts as an evaporator. After passing through the third heat exchanger 220, the refrigerant returns to the compressor 120 as a low-pressure, superheated, or saturated gas, thus completing the flow cycle of the heat exchange system 10 in the reheat dehumidification mode. Because the surface temperature of the third heat exchanger 220 is lower than the return air dew point at this point, heat exchange occurs between the third heat exchanger 220 and the indoor return air, causing water vapor to condense into water droplets that accumulate on the third heat exchanger 220 and are then smoothly discharged. The low-temperature and low-humidity airflow passing through the third heat exchanger 220 and the heated airflow passing through the second heat exchanger 210 will be mixed in the air duct before being sent into the room, forming a supply airflow with a lower moisture content and close to the inlet air temperature, thereby improving the dehumidification comfort in the transition season.

[0070] like Figure 2As shown, when the heat exchange system 10 operates in cooling mode, the refrigerant flowing out of the first heat exchanger 110 is converted from a high-temperature, high-pressure liquid to a low-temperature, low-pressure gas after passing through the throttling of the second expansion valve 130. Through the distribution of the flow divider 600, the refrigerant is evenly distributed in the low-temperature, low-pressure gas state to the various branches within the second heat exchanger 210. After entering the second heat exchanger 210, the refrigerant evaporates and absorbs heat, causing the surface temperature of the second heat exchanger 210 to begin to decrease, thereby enabling the second heat exchanger 210 to exchange heat with the indoor air. The refrigerant flowing out of the second heat exchanger 210 is reunited through the flow divider 600 and flows to the first expansion valve 230. At this time, the first expansion valve 230 is at its maximum opening value to reduce the saturation temperature drop of the refrigerant. The refrigerant flowing out of the first expansion valve 230 is distributed by the flow divider 600 and flows evenly into the various branches within the third heat exchanger 220. After entering the third heat exchanger 220, the refrigerant continues to evaporate and absorb heat, causing the surface temperature of the third heat exchanger 220 to begin to decrease, allowing the third heat exchanger 220 to once again exchange heat with the indoor air. Finally, the refrigerant exits the third heat exchanger 220 as a low-temperature, low-pressure gas and flows back to the compressor 120 through the refrigerant pipeline 300, completing the flow cycle of the heat exchange system 10 in cooling mode.

[0071] like Figure 3 As shown, when the heat exchange system 10 operates in the heating mode, the flow direction of the refrigerant in the flow path of the heat exchange system 10 is opposite to that in the cooling mode. At this time, the first expansion valve 230 is at the maximum opening value, and the second heat exchanger 210 and the third heat exchanger 220 both act as condensers. The refrigerant flows into the third heat exchanger 220 and the second heat exchanger 210 in a high temperature and high pressure state, so that the surface temperature of the third heat exchanger 220 and the second heat exchanger 210 increases, and the indoor return air is heated and heated, thereby achieving the purpose of increasing the indoor temperature.

[0072] Specifically, if Figure 1 、 Figure 2 and Figure 3 As shown, the first end of the second heat exchanger is marked A in the drawings.

[0073] Specifically, if Figure 1 、 Figure 2 and Figure 3 As shown, the second end of the second heat exchanger is marked as B in the drawings.

[0074] Specifically, if Figure 1 、 Figure 2 and Figure 3 As shown, the first end of the first expansion valve is marked as C in the drawing.

[0075] Specifically, if Figure 1 、 Figure 2 and Figure 3As shown, the second end of the first expansion valve is marked as D in the drawing.

[0076] Specifically, if Figure 1 、 Figure 2 and Figure 3 As shown, the first end of the third heat exchanger is marked as E in the drawings.

[0077] Specifically, if Figure 1 、 Figure 2 and Figure 3 As shown, the second end of the third heat exchanger is marked F in the drawings.

[0078] Preferably, the outer diameter of the refrigerant pipeline 300 is greater than 8 mm to reduce the impact of the pressure drop generated by the first expansion valve 230 on the performance of the heat exchange system 10 in the cooling mode or the heating mode.

[0079] Preferably, the outer diameter of the refrigerant pipeline 300 may be 9 mm, 9.52 mm, or 12 mm.

[0080] Preferably, the flow splitter 600 may be a brass flow splitter 600 or an impeller flow splitter 600 .

[0081] Preferably, the ratio of the heat exchange area of ​​the second heat exchanger 210 to the heat exchange area of ​​the third heat exchanger 220 is set in the range of 0.32 to 1.3, which can take into account the performance of the heat exchange system 10 when operating in cooling mode or heating mode and the performance of the heat exchange system 10 when operating in reheat dehumidification mode, so that the indoor environment can reach the required comfort level in various operating modes, and at the same time solve the problems of large energy efficiency attenuation in cooling mode or heating mode and poor performance in reheat dehumidification mode caused by an unreasonable heat exchange area ratio between the second heat exchanger 210 and the third heat exchanger 220.

[0082] The following is the reheating and dehumidification effect of the corresponding flow path under different ranges of the heat exchange area ratio of the second heat exchanger 210 and the third heat exchanger 220:

[0083] Table 1 shows an embodiment of a combination of different ratio ranges of the heat exchange area of ​​the second heat exchanger 210 to the heat exchange area of ​​the third heat exchanger 220. When the area ratio a of the heat exchange area of ​​the second heat exchanger 210 to the heat exchange area of ​​the third heat exchanger 220 is 0.25 to 0.32, 0.32 to 0.7, 0.7 to 1.3, and 1.3 to 2.6, respectively, the corresponding flow paths are flow path a, flow path b, flow path c, and flow path d, respectively.

[0084]

[0085]

[0086] Table 1

[0087] like Figure 4 As shown in the figure, under the typical reheat dehumidification operating conditions of 22°C / 80% RH (the ratio of water vapor partial pressure to saturated water vapor pressure in humid air, Relative Humidity), a given exhaust saturation temperature of 45°C, a saturation temperature difference of 1°C at the inlets of the first heat exchanger 110 and the second heat exchanger 210, and the same dehumidification capacity and indoor supply air volume, the reheat dehumidification SMER (Specific Moisture Extraction Rate) changes with the supply air temperature.

[0088] from Figure 4 It can be seen that with the increase of the area ratio а, the maximum indoor supply air temperature that the heat exchange system 10 can reach in the reheat dehumidification mode also increases accordingly. The maximum indoor supply air temperature that can be reached by flow paths b and flow paths c is higher than that of a. As the area ratio а increases to a certain value, although flow path d has a higher maximum indoor supply air temperature, its reheat dehumidification energy efficiency SMER is significantly reduced. This proves that compared with flow paths a and flow paths d, flow paths b and flow paths c can be adjusted to a higher indoor supply air temperature in the reheat dehumidification mode while having a higher reheat dehumidification energy efficiency.

[0089] like Figure 5 As shown in Figure 2, the changing trend of refrigerant injection volume with outlet air temperature in the reheat dehumidification mode under different area ratios a.

[0090] from Figure 5 It can be seen that as the area ratio а increases, the refrigerant filling amount in the heat exchange system 10 in the reheat dehumidification mode also increases. At the same time, the closer it is to the filling amount in the cooling mode, the more matched the filling amounts in the cooling and reheat dehumidification modes are. When the above four flow paths are maintained in operation with the same refrigerant filling volume, the indoor supply air temperature reached by flow path a is the lowest. Too low a supply air temperature will cause the indoor temperature to drop rapidly to a lower temperature, making the user feel uncomfortable and unable to work or rest for a long time indoors; the indoor supply air temperature reached by flow path d is the highest, which will cause the indoor temperature to rise rapidly. Too high an indoor temperature will also make the user feel uncomfortable and unable to work or rest for a long time indoors; the indoor supply air temperature reached by flow paths b and flow paths c can make the user feel comfortable, so that the heat exchange system 10 can effectively reduce the moisture content in the indoor air and keep the indoor temperature within a range that makes the user feel comfortable in the reheat dehumidification mode. Therefore, the effects of flow paths b and flow paths c in the reheat dehumidification mode are better than those of flow paths a and flow paths d.

[0091] like Figure 61 and 2 show the changing trends of the rated cooling EER (Energy Efficiency Ratio) with the temperature drop between the second heat exchanger 210 and the third heat exchanger 220 under different area ratios a.

[0092] from Figure 6 It can be seen that the rated cooling EER in each flow path shows a decreasing trend as the saturation temperature drop between the second heat exchanger 210 and the third heat exchanger 220 increases. That is, the greater the saturation temperature drop between the second heat exchanger 210 and the third heat exchanger 220, the lower the rated cooling EER in the flow path. At the same saturation temperature drop, the rated cooling EER will also decrease with an increase in the area ratio a. When the four flow paths are at the same saturation temperature drop, flow path a has the highest rated cooling EER. At this time, flow path a achieves the lowest indoor supply air temperature. A too low supply air temperature will cause the indoor temperature to drop rapidly to a low temperature, making the user uncomfortable and unable to work or rest for long periods of time indoors. Flow path d has the lowest rated cooling EER. At this time, flow path d achieves the highest indoor supply air temperature, causing the indoor temperature to rise rapidly. Excessively high indoor temperatures will also make the user uncomfortable and unable to work or rest for long periods of time indoors. The rated cooling EERs of flow paths b and flow path c are between those of flow paths a and flow path d, respectively. Therefore, the indoor supply air temperatures achieved by flow paths b and flow path c are neither too high nor too low, ensuring user comfort. This allows the heat exchange system 10 to effectively reduce the moisture content in the indoor air while maintaining the indoor temperature within a range that provides user comfort in the reheat dehumidification mode. Therefore, flow paths b and flow path c perform better than flow paths a and flow path d in the reheat dehumidification mode.

[0093] In summary, when the heat exchange system 10 operates in cooling mode or heating mode, since the heat exchange functions realized by the second heat exchanger 210 and the third heat exchanger 220 are the same, the value of the area ratio a does not affect the operating effect of the heat exchange system 10. When the heat exchange system 10 operates in reheat dehumidification mode, flow path b and flow path c can enable the heat exchange system 10 to effectively reduce the moisture content in the indoor air and maintain the indoor temperature within a range that makes the user feel comfortable in the reheat dehumidification mode. Therefore, the effects of flow path b and flow path c in the reheat dehumidification mode are better than those of flow path a and flow path d.

[0094] Optionally, in an implementation of this embodiment, as Figure 1 、 Figure 2 and Figure 3 As shown, the outdoor side assembly 100 further includes:

[0095] A compressor 120, wherein a first end of the compressor 120 is connected to a second end of the third heat exchanger 220 via a refrigerant pipe 300, and a second end of the compressor 120 is connected to a first end of the first heat exchanger 110 via a refrigerant pipe 300;

[0096] A second expansion valve 130, wherein a first end of the second expansion valve 130 is connected to a second end of the first heat exchanger 110 via a refrigerant pipe 300; a second end of the second expansion valve 130 is connected to a first end of the second heat exchanger 210 via a refrigerant pipe 300;

[0097] Among them, in the reheat dehumidification mode, the second expansion valve 130 is at the maximum opening, the upper limit range of the gas flow of the first expansion valve 230 is 15L / min to 35L / min, and the lower limit range of the gas flow of the first expansion valve 230 is less than or equal to 6L / min.

[0098] In this embodiment, if Figure 1 、 Figure 2 and Figure 3As shown, the outdoor component 100 also includes a compressor 120 and a second expansion valve 130. The first end of the compressor 120 is connected to the second end of the third heat exchanger 220 through the refrigerant pipeline 300, so that the refrigerant can flow between the compressor 120 and the third heat exchanger 220 through the refrigerant pipeline 300. The second end of the compressor 120 is connected to the first end of the first heat exchanger 110 through the refrigerant pipeline 300, so that the refrigerant can flow between the compressor 120 and the first heat exchanger 110 through the refrigerant pipeline 300. The first end of the second expansion valve 130 is connected to the second end of the first heat exchanger 110 via a refrigerant line 300, and the second end of the second expansion valve 130 is connected to the first end of the second heat exchanger 210 via a refrigerant line 300. When the refrigerant flows between the first heat exchanger 110 and the second heat exchanger 210, it flows through the second expansion valve 130. By controlling the opening of the second expansion valve 130, the pressure of the refrigerant flowing through the second expansion valve 130 can be changed, thereby changing the refrigerant from a liquid to a gaseous state. The ratio of the change in air flow rate to the change in opening of the first expansion valve 230 must be sufficiently small to meet the regulation requirements under the variable operating conditions of the reheat dehumidification mode. When the heat exchange system 10 is operating in cooling mode or heating mode, the first expansion valve 230 needs to be adjusted to its maximum opening to reduce the pressure drop caused by the refrigerant flowing from the second heat exchanger 210 to the third heat exchanger 220 through a sufficiently large flow cross-sectional area. When the heat exchange system 10 operates in the reheat dehumidification mode, the refrigerant flows from the first heat exchanger 110 to the second heat exchanger 210. At this time, the refrigerant is in a superheated gas or two-phase state. The second expansion valve 130 needs to be adjusted to the maximum opening so that a sufficiently large flow cross-sectional area can be used to reduce the pressure drop generated when the refrigerant flows from the first heat exchanger 110 to the second heat exchanger 210. After the refrigerant flows into the second heat exchanger 210, it is still in a superheated gas or two-phase state and the pressure is maintained, so that the first heat exchanger 110 and the second heat exchanger 210 can both perform the function of a condenser in the reheat dehumidification mode. When the refrigerant flows from the second heat exchanger 210 to the third heat exchanger 220, it must pass through the first expansion valve 230. After passing through the first expansion valve 230, the refrigerant changes from a supercooled liquid or two-phase state to a low-pressure two-phase state. At this point, the refrigerant flowing into the third heat exchanger 220 absorbs a large amount of heat, causing the third heat exchanger 220 to function as an evaporator. By exchanging heat with the moisture-rich air, the moisture condenses into water droplets, effectively reducing the moisture content in the indoor air. This heat exchange system 10 can be used for both top and bottom air conditioners. By adjusting the air flow range of the first expansion valve 230, the air conditioner 20 can achieve temperature control and dehumidification functions during transitional seasons without affecting its dimensions or original functionality.

[0099] Specifically, when the heat exchange system 10 operates in the reheat dehumidification mode, the valve inlet gauge pressure is 0.1 MPa and the outlet is atmospheric pressure, by adjusting the opening range of the first expansion valve 230, the upper limit range of the air flow through the first expansion valve 230 is 15 L / min to 35 L / min, and the lower limit range is less than or equal to 6 L / min.

[0100] Specifically, when the heat exchange system 10 operates in cooling mode or heating mode, the valve inlet gauge pressure is 0.1 MPa and the outlet is atmospheric pressure, by adjusting the opening range of the first expansion valve 230, the air flow rate of the first expansion valve 230 in the maximum opening range is between 300 L / min and 600 L / min.

[0101] Furthermore, when the heat exchange system 10 operates in cooling mode or heating mode, the valve inlet gauge pressure is 0.1 MPa and the outlet is atmospheric pressure, by adjusting the opening range of the first expansion valve 230, the air flow rate of the first expansion valve 230 in the maximum opening range is between 400 L / min and 500 L / min.

[0102] Specifically, if Figure 1 、 Figure 2 and Figure 3 As shown, the first end of the compressor is G.

[0103] Specifically, if Figure 1 、 Figure 2 and Figure 3 As shown, the second end of the compressor is H.

[0104] Specifically, if Figure 1 、 Figure 2 and Figure 3 As shown, the first end of the second expansion valve is J.

[0105] Specifically, if Figure 1 、 Figure 2 and Figure 3 As shown, the second end of the second expansion valve is K.

[0106] Specifically, if Figure 1 、 Figure 2 and Figure 3 As shown, the first end of the first heat exchanger is W.

[0107] Specifically, if Figure 1 、 Figure 2 and Figure 3 As shown, the second end of the first heat exchanger is X.

[0108] Optionally, in an implementation of this embodiment, the upper limit range of the gas flow of the first expansion valve 230 is 20L / min to 30L / min; the lower limit range of the gas flow of the first expansion valve 230 is 2L / min to 4L / min.

[0109] In this embodiment, when the heat exchange system 10 operates in the reheat dehumidification mode, by adjusting the opening range of the first expansion valve 230, the upper limit range of the air flow through the first expansion valve 230 is 20L / min to 30L / min, and the lower limit range is 2L / min to 4L / min. The first expansion valve 230 can further enhance the evaporation heat absorption effect of the refrigerant in this opening range, and through the heat exchange between the third heat exchanger 220 and the air with a higher moisture content, more moisture is condensed into water droplets, thereby further reducing the moisture content in the indoor air.

[0110] Optionally, in an implementation of this embodiment, the ratio of the heat exchange area of ​​the second heat exchanger 210 to the heat exchange area of ​​the third heat exchanger 220 is 0.5 to 1.0 to achieve the effect of taking into account both cooling / heating energy efficiency and reheat dehumidification comprehensive performance.

[0111] In this embodiment, the ratio of the heat exchange area of ​​the second heat exchanger 210 to the heat exchange area of ​​the third heat exchanger 220 is set to 0.5 to 1.0. By further limiting the numerical range of the area ratio a, the performance of the heat exchange system 10 when operating in cooling mode or heating mode can be further improved, and the performance of the heat exchange system 10 when operating in reheat dehumidification mode can be further improved, so that the heat exchange system 10 can achieve the required comfort level in the indoor environment under various operating modes.

[0112] Preferably, if Figure 7 As shown, the area ratio α in this embodiment is 0.92.

[0113] Preferably, if Figure 8 As shown, the area ratio a in this embodiment is set to 0.56. This flow path form can further reduce the impact of the series flow paths in the heat exchange system 10 on the performance of the heat exchange system 10 in the cooling mode or the heating mode.

[0114] Preferably, if Figure 9As shown, the second heat exchanger 210 and the third heat exchanger 220 are arranged in series along the air flow direction, and the area ratio а in this embodiment is set to 0.92. The second heat exchanger 210 is arranged at the air outlet of the indoor side component 200, and the third heat exchanger 220 is arranged at the air inlet of the indoor side component 200. The third heat exchanger 220 can first cool down and dehumidify the indoor air with high moisture content, and then the second heat exchanger 210 heats up the low-temperature air that has been dehumidified, so that the heat exchange system 10 can effectively reduce the moisture content in the indoor air and keep the indoor temperature within a range that makes the user feel comfortable in the reheat dehumidification mode.

[0115] Optionally, in an implementation of this embodiment, the ratio of the number of heat exchange tubes in the second heat exchanger 210 to the number of heat exchange tubes in the third heat exchanger 220 is 0.32 to 1.3.

[0116] In this embodiment, the heat exchange area of ​​the heat exchanger is proportional to the number of heat exchange tubes of the heat exchanger to achieve a good heat exchange effect. Therefore, the ratio of the number of heat exchange tubes of the second heat exchanger 210 to the number of heat exchange tubes of the third heat exchanger 220 is set to 0.32 to 1.3, which can more accurately achieve the ratio of the heat exchange area of ​​the second heat exchanger 210 to the heat exchange area of ​​the third heat exchanger 220 in the range of 0.32 to 1.3, thereby taking into account the performance of the heat exchange system 10 when operating in cooling mode or heating mode and the performance of the heat exchange system 10 when operating in reheat dehumidification mode, and thus in various operating modes, the indoor environment can achieve the required comfort.

[0117] Specifically, for air conditioners 20 with different numbers of heat exchange tubes and lengths of heat exchangers, the flow path form can also be appropriately adjusted according to the area ratio a in this embodiment.

[0118] Optionally, in an implementation of this embodiment, the ratio of the number of heat exchange tubes in the second heat exchanger 210 to the number of heat exchange tubes in the third heat exchanger 220 is 0.5 to 1.0.

[0119] In this embodiment, the heat exchange area of ​​the heat exchanger is proportional to the number of heat exchange tubes of the heat exchanger to achieve a good heat exchange effect. Therefore, the ratio of the number of heat exchange tubes of the second heat exchanger 210 to the number of heat exchange tubes of the third heat exchanger 220 is set to 0.5 to 1.0, which can make the area ratio a more accurately within the range of 0.5 to 1.0, thereby further improving the performance of the heat exchange system 10 when operating in cooling mode or heating mode and the performance of the heat exchange system 10 when operating in reheat dehumidification mode, so that the heat exchange system 10 can achieve the required comfort level in the indoor environment under various operating modes.

[0120] Optionally, in an implementation of this embodiment, the second end fin of the second heat exchanger 210 is provided with a special-shaped cut; and / or the first end fin of the third heat exchanger 220 is provided with a special-shaped cut.

[0121] In this embodiment, in the heat exchange system 10, a special-shaped cut can be provided only at the second end fin of the second heat exchanger 210, or a special-shaped cut can be provided only at the first end fin of the third heat exchanger 220, or a special-shaped cut can be provided at both the second end fin of the second heat exchanger 210 and the first end fin of the third heat exchanger 220. Since the second end fin of the second heat exchanger 210 is adjacent to the first end fin of the third heat exchanger 220, providing a special-shaped cut at the adjacent fins between the second heat exchanger 210 and the third heat exchanger 220 can avoid the heat conduction effect caused by the close distance between the second heat exchanger 210 and the third heat exchanger 220, thereby improving the heat exchange effect between the third heat exchanger 220 and the air with a higher moisture content, so that the heat exchange system 10 can effectively reduce the moisture content in the indoor air and keep the indoor temperature within a range that makes the user feel comfortable in the reheat dehumidification mode.

[0122] Optionally, in an implementation of this embodiment, as Figure 1 、 Figure 2 and Figure 3 As shown, the outdoor side assembly 100 further includes:

[0123] The reversing valve 140, the first end of the reversing valve 140 is connected to the second end of the compressor 120 through the refrigerant pipeline 300, the second end of the reversing valve 140 is connected to the first end of the first heat exchanger 110 through the refrigerant pipeline 300, the third end of the reversing valve 140 is connected to the first end of the compressor 120 through the refrigerant pipeline 300, and the fourth end of the reversing valve 140 is connected to the second end of the third heat exchanger 220 through the refrigerant pipeline 300.

[0124] In this embodiment, if Figure 1 、 Figure 2 and Figure 3 As shown, the outdoor assembly 100 further includes a reversing valve 140. A first end of the reversing valve 140 is connected to the second end of the compressor 120 via a refrigerant pipeline 300. A second end of the reversing valve 140 is connected to the first end of the first heat exchanger 110 via a refrigerant pipeline 300. A third end of the reversing valve 140 is connected to the first end of the compressor 120 via a refrigerant pipeline 300. A fourth end of the reversing valve 140 is connected to the second end of the third heat exchanger 220 via a refrigerant pipeline 300. By providing the reversing valve 140, the flow direction of the refrigerant in the heat exchange system 10 can be changed, thereby ensuring that the heat exchange system 10 operates satisfactorily in the cooling mode, the heating mode, and the reheat dehumidification mode.

[0125] Specifically, if Figure 1 、 Figure 2 and Figure 3 As shown, when the refrigerant in the heat exchange system 10 needs to flow from the second end of the compressor 120 to the first heat exchanger 110, the refrigerant flows in from the first end of the reversing valve 140, flows out from the second end of the reversing valve 140 and flows to the first heat exchanger 110. After passing through the second heat exchanger 210 and the third heat exchanger 220, the refrigerant flows in from the fourth end of the reversing valve 140, flows out from the third end of the reversing valve 140 and flows into the first end of the compressor 120. When the refrigerant in the thermal system 10 needs to flow from the second end of the compressor 120 to the third heat exchanger 220, the refrigerant flows in from the first end of the reversing valve 140, flows out from the third end of the reversing valve 140 and flows to the third heat exchanger 220. After passing through the third heat exchanger 220, the second heat exchanger 210 and the first heat exchanger 110, the refrigerant flows in from the second end of the reversing valve 140, flows out from the fourth end of the reversing valve 140 and flows into the first end of the compressor 120.

[0126] Specifically, the reversing valve 140 is a four-way reversing valve.

[0127] Specifically, if Figure 1 、 Figure 2 and Figure 3 As shown, the first end of the reversing valve is N.

[0128] Specifically, if Figure 1 、 Figure 2 and Figure 3 As shown, the second end of the reversing valve is P.

[0129] Specifically, if Figure 1 、 Figure 2 and Figure 3 As shown, the third end of the reversing valve is Q.

[0130] Specifically, if Figure 1 、 Figure 2 and Figure 3 As shown, the fourth end of the reversing valve is R.

[0131] Optionally, in an implementation of this embodiment, as Figure 1 、 Figure 2 and Figure 3 As shown, the heat exchange system 10 also includes:

[0132] a first stop valve 400 , wherein a first end of the first stop valve 400 is connected to a second end of the first expansion valve 230 via a refrigerant pipe 300 , and a second end of the first stop valve 400 is connected to a first end of the second heat exchanger 210 via a refrigerant pipe 300 ;

[0133] The second stop valve 500 has a first end connected to the second end of the third heat exchanger 220 through the refrigerant pipeline 300 , and a second end connected to the first end of the compressor 120 through the refrigerant pipeline 300 .

[0134] In this embodiment, if Figure 1 、 Figure 2 and Figure 3 As shown, the heat exchange system 10 further includes a first stop valve 400 and a second stop valve 500. The first end of the first stop valve 400 is connected to the second end of the first expansion valve 230 via the refrigerant pipeline 300, and the second end of the first stop valve 400 is connected to the first end of the second heat exchanger 210 via the refrigerant pipeline 300. The first end of the second stop valve 500 is connected to the second end of the third heat exchanger 220 via the refrigerant pipeline 300, and the second end of the second stop valve 500 is connected to the first end of the compressor 120 via the refrigerant pipeline 300. The stop valves can control the flow of refrigerant in the flow path. The first stop valve 400 and the second stop valve 500 are respectively disposed at the connection between the outdoor assembly 100 and the indoor assembly 200 to control the flow of refrigerant between the outdoor assembly 100 and the indoor assembly 200, thereby facilitating operations such as repair and maintenance of the heat exchange system 10.

[0135] Specifically, if Figure 1 、 Figure 2 and Figure 3 As shown, the first end of the first stop valve is S.

[0136] Specifically, if Figure 1 、 Figure 2 and Figure 3 As shown, the second end of the first stop valve is T.

[0137] Specifically, if Figure 1 、 Figure 2 and Figure 3 As shown, the first end of the second stop valve is L.

[0138] Specifically, if Figure 1 、 Figure 2 and Figure 3 As shown, the second end of the second stop valve is M.

[0139] Example 2

[0140] In this embodiment, an air conditioner 20 is provided. Figure 1 As shown, it includes the heat exchange system 10 in embodiment 1 and a controller for controlling the heat exchange system 10;

[0141] When the heat exchange system 10 is in the reheat dehumidification mode, the controller is used to control the opening value of the second expansion valve 130 to the maximum, and control the opening value of the first expansion valve 230 to increase or decrease according to the exhaust temperature of the outdoor component 100;

[0142] When the heat exchange system 10 is in cooling mode or heating mode, the controller is used to control the opening value of the first expansion valve 230 to the maximum, and control the opening value of the second expansion valve 130 to increase or decrease according to the exhaust temperature of the outdoor component 100.

[0143] In this embodiment, the air conditioner 20 has all the beneficial effects of the heat exchange system 10 in the first embodiment, which will not be described in detail here.

[0144] Preferably, the reheat dehumidification air conditioner is a household cabinet-type top and bottom air-discharge air conditioner.

[0145] Example 3

[0146] This embodiment provides a control method, such as Figure 10 As shown, for controlling the heat exchange system in the first embodiment and / or the air conditioner in the second embodiment, the control method includes:

[0147] Receive control instructions;

[0148] Identify the control command as reheat dehumidification mode;

[0149] Adjust the opening value of the second expansion valve to the maximum;

[0150] Get the exhaust temperature of the compressor;

[0151] Determine whether the exhaust temperature of the compressor is greater than the preset temperature value;

[0152] If so, the opening value of the first expansion valve is adjusted to increase;

[0153] If not, the opening value of the first expansion valve is adjusted to decrease.

[0154] In this embodiment, if Figure 10As shown, this control method can be used to control both the heat exchange system of the first embodiment and the air conditioner of the second embodiment. This control method simplifies the control of the heat exchange system by implementing decoupling control of the expansion valves connected in series in different operating modes. This control method first identifies a received control instruction. When the control instruction is for the reheat dehumidification mode, the opening value of the second expansion valve is first adjusted to the maximum. Then, the compressor exhaust temperature is continuously obtained and it is continuously determined whether the compressor exhaust temperature is greater than a preset temperature value. When the compressor exhaust temperature is greater than the preset temperature value, the opening value of the first expansion valve is adjusted to increase. When the compressor exhaust temperature is less than the preset temperature value, the opening value of the first expansion valve is adjusted to decrease. The adjustment of the opening value of the first expansion valve by determining whether the compressor exhaust temperature is greater than the preset temperature value can be coordinated with the variable frequency operation of the compressor, so that the compressor can achieve the effect of effectively reducing the moisture content in the indoor air while maintaining the indoor temperature within a range that is comfortable for the user, regardless of whether it is operating in low-frequency or medium-high-frequency modes.

[0155] like Figure 10 Specifically, the control method includes:

[0156] Step 202: receiving a control instruction;

[0157] Step 204: Identify that the control instruction is a reheat dehumidification mode;

[0158] Step 206: Adjust the opening value of the second expansion valve to the maximum;

[0159] Step 208: Obtain the exhaust temperature of the compressor;

[0160] Step 210: Determine whether the exhaust temperature of the compressor is greater than a preset temperature value;

[0161] Step 214: If yes, adjust the opening value of the first expansion valve to increase;

[0162] Step 212: If not, adjust the opening value of the first expansion valve to decrease.

[0163] Optionally, in an implementation of this embodiment, as Figure 11 As shown,

[0164] Identify the control command as cooling mode or heating mode;

[0165] Adjust the opening value of the first expansion valve to the maximum;

[0166] Get the exhaust temperature of the compressor;

[0167] Determine whether the exhaust temperature of the compressor is greater than the preset temperature value;

[0168] If yes, adjust the opening value of the second expansion valve to increase;

[0169] If not, the opening value of the second expansion valve is adjusted to decrease.

[0170] In this embodiment, if Figure 11 As shown, the control method first identifies the received control instruction. When the control instruction is a cooling mode or a heating mode, the opening value of the first expansion valve is first adjusted to the maximum, and then the exhaust temperature of the compressor is continuously obtained, and whether the exhaust temperature of the compressor is greater than the preset temperature value is continuously judged. When the exhaust temperature of the compressor is greater than the preset temperature value, the opening value of the second expansion valve is adjusted to increase. When the exhaust temperature of the compressor is less than the preset temperature value, the opening value of the second expansion valve is adjusted to decrease. By judging whether the exhaust temperature of the compressor is greater than the preset temperature value to adjust the opening value of the second expansion valve, it can be coordinated with the variable frequency working condition of the compressor to enable the heat exchange system to continuously maintain good heat exchange energy efficiency.

[0171] like Figure 11 Specifically, the control method includes:

[0172] Step 302: receiving a control instruction;

[0173] Step 304: Identify whether the control instruction is a cooling mode or a heating mode;

[0174] Step 306: Adjust the opening value of the first expansion valve to the maximum;

[0175] Step 308: Obtain the exhaust temperature of the compressor;

[0176] Step 310: Determine whether the exhaust temperature of the compressor is greater than a preset temperature value;

[0177] Step 314: If yes, adjust the opening value of the second expansion valve to increase;

[0178] Step 312: If not, adjust the opening value of the second expansion valve to decrease.

Claims

1. A heat exchange system, characterized in that: include: An outdoor side component (100), the outdoor side component (100) comprising a first heat exchanger (110); An indoor side component (200), the indoor side component (200) comprising a second heat exchanger (210), a third heat exchanger (220) and a first expansion valve (230); A refrigerant pipeline (300) connects the outdoor component (100) and the indoor component (200) so that the indoor component (200) and the outdoor component (100) form a closed refrigerant circuit; The second heat exchanger (210), the first expansion valve (230), and the third heat exchanger (220) are sequentially connected to the refrigerant pipeline (300), and the second heat exchanger (210) flows refrigerant before the first expansion valve (230) and the third heat exchanger in a reheat dehumidification mode; The ratio of the heat exchange area of ​​the second heat exchanger (210) to the heat exchange area of ​​the third heat exchanger (220) is 0.32 to 1.3; Wherein, in the reheat dehumidification mode, the first heat exchanger (110) is a condenser, the second heat exchanger (210) is a condenser, and the third heat exchanger (220) is an evaporator.

2. The heat exchange system according to claim 1, characterized in that: The outdoor side assembly (100) further includes: a compressor (120), wherein a first end of the compressor (120) is connected to a second end of the third heat exchanger (220) via the refrigerant pipeline (300), and a second end of the compressor (120) is connected to a first end of the first heat exchanger (110) via the refrigerant pipeline (300); a second expansion valve (130), wherein a first end of the second expansion valve (130) is connected to a second end of the first heat exchanger (110) via the refrigerant pipeline (300); and a second end of the second expansion valve (130) is connected to a first end of the second heat exchanger (210) via the refrigerant pipeline (300); In the reheat dehumidification mode, the second expansion valve (130) is at its maximum opening, the upper limit range of the gas flow of the first expansion valve (230) is 15 L / min to 35 L / min, and the lower limit range of the gas flow of the first expansion valve (230) is less than or equal to 6 L / min.

3. The heat exchange system according to claim 2, characterized in that: The upper limit range of the gas flow rate of the first expansion valve (230) is 20L / min to 30L / min; The lower limit range of the gas flow rate of the first expansion valve (230) is 2 L / min to 4 L / min.

4. The heat exchange system according to claim 1, characterized in that: The ratio of the heat exchange area of ​​the second heat exchanger (210) to the heat exchange area of ​​the third heat exchanger (220) is 0.5 to 1.

0.

5. The heat exchange system according to claim 1, characterized in that: The ratio of the number of heat exchange tubes of the second heat exchanger (210) to the number of heat exchange tubes of the third heat exchanger (220) is 0.32 to 1.

3.

6. The heat exchange system according to claim 5, characterized in that: The ratio of the number of heat exchange tubes of the second heat exchanger (210) to the number of heat exchange tubes of the third heat exchanger (220) is 0.5 to 1.

0.

7. The heat exchange system according to any one of claims 1 to 6, characterized in that: The second end fin of the second heat exchanger (210) is provided with a special-shaped cut; and / or The first end fin of the third heat exchanger (220) is provided with a special-shaped cut.

8. The heat exchange system according to claim 2, characterized in that: The outdoor side assembly (100) further includes: A reversing valve (140), wherein the first end of the reversing valve (140) is connected to the second end of the compressor (120) through the refrigerant pipeline (300), the second end of the reversing valve (140) is connected to the first end of the first heat exchanger (110) through the refrigerant pipeline (300), the third end of the reversing valve (140) is connected to the first end of the compressor (120) through the refrigerant pipeline (300), and the fourth end of the reversing valve (140) is connected to the second end of the third heat exchanger (220) through the refrigerant pipeline (300).

9. The heat exchange system according to claim 8, characterized in that: Also includes: a first stop valve (400), wherein a first end of the first stop valve (400) is connected to a second end of the first expansion valve (230) through the refrigerant pipeline (300), and a second end of the first stop valve (400) is connected to a first end of the second heat exchanger (210) through the refrigerant pipeline (300); A second stop valve (500), wherein a first end of the second stop valve (500) is connected to a second end of the third heat exchanger (220) through the refrigerant pipeline (300), and a second end of the second stop valve (500) is connected to a first end of the compressor (120) through the refrigerant pipeline (300).

10. A reheat dehumidification air conditioner, characterized in that: include: The heat exchange system (10) according to any one of claims 1 to 9, and a controller for controlling the heat exchange system (10); The controller is designed such that: when the heat exchange system (10) is in a reheat dehumidification mode, the controller controls the opening value of the second expansion valve (130) to a maximum, and controls the opening value of the first expansion valve (230) to increase or decrease according to the exhaust temperature of the outdoor component (100); When the heat exchange system (10) is in cooling mode or heating mode, the controller controls the opening value of the first expansion valve (230) to be maximum, and controls the opening value of the second expansion valve (130) to increase or decrease according to the exhaust temperature of the outdoor component (100).

11. The reheat dehumidification air conditioner according to claim 10, characterized in that: The reheat dehumidification air conditioner is a household cabinet-type air conditioner with top and bottom air outlets.

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