A heat exchange system and a dehumidifier

Abstract

This utility model provides a heat exchange system and a dehumidifier, belonging to the field of dehumidifier technology. The heat exchange system includes a compressor, a throttling valve, an evaporator, and a condenser connected by refrigerant pipes. A first air duct is provided at the evaporator, with the air inlet located at the bottom of the evaporator and the air outlet located at the top of the evaporator. A second air duct is provided at the condenser, isolated from the first air duct. A baffle is provided on the condenser, dividing the second air duct into several temperature zones arranged along the height direction. This heat exchange system has high heat exchange efficiency and low energy consumption. When used in dehumidifiers, it can reduce the energy consumption of dehumidifiers, reduce heat loss, and improve the market competitiveness of dehumidifiers.

Description

Technical Field

[0001] This utility model relates to the field of dehumidifier technology, and in particular to a heat exchange system and a dehumidifier. Background Technology

[0002] Dehumidifiers, as devices used to reduce humidity in the air, are widely used in various scenarios such as homes, offices, and warehousing and logistics. Especially in high-temperature and high-humidity environments (such as subtropical climates), their performance directly affects environmental comfort and the safety of stored items.

[0003] Current dehumidifiers generally employ a top-in, bottom-out air duct design for their evaporators, meaning air enters from the top and exits from the bottom, with the refrigerant inlet typically located at the top. This structure easily leads to condensate accumulation at the bottom of the evaporator, covering the fin surface and compressing the effective heat exchange area, resulting in uneven heat transfer. Furthermore, in terms of condenser design, existing structures lack effective temperature field isolation measures. Different areas of the condenser exhibit significant temperature gradients due to differences in refrigerant conditions, but without zoning, the heat radiation from high-temperature and low-temperature zones interferes with each other, causing temperature field mixing. Heat from the high-temperature zone is transferred to the low-temperature zone, resulting in significant heat loss. This cross-regional heat conduction disrupts the temperature field independence required for condensation, reducing condensation efficiency and preventing the refrigerant from fully realizing its liquefaction and heat release process.

[0004] Therefore, it is necessary to improve the structure of existing dehumidifiers to overcome the shortcomings of existing technology. Utility Model Content

[0005] To overcome the problems existing in related technologies, one of the objectives of this utility model is to provide a heat exchange system with high heat exchange efficiency and low energy consumption. When used in dehumidifiers, this system can reduce the energy consumption and heat loss of dehumidifiers, thereby improving their market competitiveness.

[0006] A heat exchange system includes a compressor, a throttle valve, an evaporator, and a condenser connected by refrigerant pipes;

[0007] The evaporator is provided with a first air duct, the air inlet of the first air duct is located at the bottom of the evaporator, and the air outlet is located at the top of the evaporator;

[0008] A second air duct is provided at the condenser, which is isolated from the first air duct. A partition is provided on the condenser, which divides the second air duct into several temperature zones arranged along the height direction.

[0009] Specifically, the evaporator of this application adopts a parallel flow-dividing structure with copper tubes. The refrigerant inlet is located at the bottom of the evaporator, and the refrigerant is evenly distributed into each branch of the evaporator after being diverted by the copper tubes. The air inlet of the first air duct is located at the bottom of the evaporator, and a guide plate is provided at the air inlet. The air outlet is located at the top of the evaporator. Air is guided by the guide plate to enter the first air duct from the bottom, flows upward along the surface of the evaporator, and is discharged from the top air outlet. The condenser is divided into different temperature zones along the height direction by a partition. The second air duct is completely isolated from the first air duct and operates independently, which can avoid airflow interference between the evaporator and the condenser.

[0010] The evaporator in the first air duct adopts a bottom-in, top-out design, which, together with the bottom guide plate, forms a uniform upward airflow, avoiding local airflow turbulence, helping to reduce condensate accumulation and improve heat exchange efficiency. The baffles in the condenser effectively block cross-layer heat radiation, ensuring that each temperature field is independent, thus improving condensation efficiency.

[0011] In a preferred embodiment of this invention, the evaporator includes a heat exchange tube and multiple first fins, the multiple first fins being fixed on the heat exchange tube; the heat exchange tube is provided with a refrigerant inlet and a refrigerant outlet, the refrigerant inlet being located at the bottom of the evaporator and the refrigerant outlet being located at the top of the evaporator.

[0012] The refrigerant inlet at the bottom and the outlet at the top of the heat exchange tube, combined with the bottom-in, top-out first air duct, ensures that the refrigerant flow direction is consistent with the airflow direction, forming co-directional convection and improving the uniformity of heat exchange.

[0013] In a preferred embodiment of this utility model, along the height direction, the first fins are arranged in multiple layers on the heat exchange tube, and in each layer, two adjacent first fins are spaced apart.

[0014] Along the bottom to top direction of the evaporator, the spacing between adjacent first fins in the same layer gradually increases.

[0015] The design of the first fin spacing gradually increasing from bottom to top is adapted to the condensation requirements of the high-humidity airflow at the bottom (closer spacing increases the heat exchange area in a small space) and the flow requirements of the low-humidity airflow at the top (sparser spacing reduces airflow resistance), effectively preventing condensate from accumulating between the bottom fins, while improving the utilization of the overall heat exchange area.

[0016] In a preferred embodiment of this invention, a guide plate is provided at the air inlet at the bottom of the evaporator, and the guide plate is set at an angle α with the vertical direction, wherein 3° < α < 6°.

[0017] The baffle plate within this angle range guides air in from the bottom air inlet, forming a stable and uniform upward airflow. This avoids localized turbulence (such as eddies and uneven airflow) caused by direct vertical impact of airflow on the bottom of the evaporator. It ensures that air flows evenly across every fin of the evaporator, especially in the densely spaced fin area at the bottom, improving the overall heat exchange area utilization of the evaporator. The uniform upward airflow makes full contact with the fins at the bottom of the evaporator (where the refrigerant temperature is lower). Combined with the denser fin spacing at the bottom and sparser at the top, this more efficiently condenses water vapor in the air into liquid water, reducing "ineffective heat exchange areas" caused by insufficient local airflow and indirectly contributing to improved evaporator heat exchange efficiency.

[0018] In a preferred embodiment of this invention, the first fin includes a fin body and a hydrophilic layer, wherein the hydrophilic layer covers the outer wall of the fin body and the thickness of the hydrophilic layer is 0.05mm-0.15mm.

[0019] The bottom of the evaporator is provided with a water guide groove, the cross-section of which is V-shaped and the depth of which is 2mm-3mm.

[0020] In this embodiment, the hydrophilic layer significantly reduces the surface tension of condensate on the fin surface, promoting rapid spread and sliding of condensate along the fin surface, preventing water droplets from accumulating and covering the effective heat exchange area of ​​the fins. This thickness range ensures the stability of the hydrophilic effect (too thin and it is prone to wear and failure, too thick and it may increase thermal resistance), and it can also adapt to the fin spacing design with denser spacing at the bottom and sparser spacing at the top. In the densely spaced area at the bottom, the hydrophilic layer can accelerate the flow of condensate between the dense fins, reduce the "insulation layer" formed by water droplet accumulation, and ensure that the heat exchange between the fins and the air is not hindered, thus effectively improving the heat exchange efficiency of the evaporator.

[0021] The V-shaped water guide channel quickly collects condensate that slides down the fins. The sloping sidewalls of the V-shaped channel guide the water flow to the bottom, preventing condensate from flowing freely at the bottom of the evaporator. The water guide channel directs the collected condensate to a collection pan, completely preventing condensate from stagnating at the bottom of the evaporator. This reduces the risk of frost formation at low temperatures due to water accumulation and also prevents water from corroding the bottom structure of the evaporator (such as refrigerant pipe connections), extending the equipment's lifespan.

[0022] In a preferred embodiment of this invention, at least two partitions are provided on the condenser along the height direction, and each partition divides the second air duct into several temperature zones along the height direction; and the temperature of the lower temperature zone is lower than the temperature of the upper temperature zone.

[0023] In a preferred embodiment of this invention, the condenser includes a heat exchange tube and a second fin, and different heat transfer coefficients of the second fin are provided in different temperature zones.

[0024] Furthermore, along the height direction of the condenser, the heat transfer coefficient of the lower second fin is less than that of the upper second fin.

[0025] At least two partitions along the vertical direction divide the second air duct into several temperature zones, with the lower temperature zone being lower than the upper one, forming an orderly temperature gradient from top to bottom. This effectively blocks cross-layer heat radiation and conduction between the high-temperature and low-temperature zones, preventing disordered heat transfer caused by temperature field mixing. This isolation design ensures that each temperature zone maintains an independent and stable temperature environment, making it difficult for heat from the high-temperature zone (upper layer) to diffuse to the low-temperature zone (lower layer), significantly reducing heat loss and providing stable temperature conditions for the condensation process.

[0026] Different temperature zones employ second fins with varying heat transfer coefficients. In the evaporator, the upper high-temperature zone is where the refrigerant is in a high-temperature, high-pressure gaseous state immediately after being discharged from the compressor. This zone requires the rapid release of a large amount of heat to promote liquefaction. The high heat transfer coefficient of the second fins allows for efficient heat transfer, enhancing the heat dissipation effect.

[0027] The lower low-temperature zone represents the medium-low temperature stage after the refrigerant has gradually liquefied, reducing heat dissipation requirements. The second fins with a low heat transfer coefficient can adapt to low-load condensation demands, avoiding energy waste caused by excessive heat dissipation. This synergistic design of materials and temperature zones ensures that the condensation efficiency of each region of the condenser reaches its optimal state. Combined with the stability of independent temperature fields, this improves the heat exchange efficiency of the condenser.

[0028] In a preferred embodiment of this utility model, two partitions are provided on the condenser along the height direction, and the two partitions divide the second air duct into a low temperature zone, a medium temperature zone and a high temperature zone along the height direction.

[0029] The condenser includes heat exchange tubes and second fins, and different heat transfer coefficients are provided in different temperature zones;

[0030] The thermal conductivity of the second fin in the high-temperature zone is ≥350W / (m·K); the thermal conductivity of the second fin in the medium-temperature zone is ≤220W / (m·K); and the second fin in the low-temperature zone is made of copper-aluminum composite material.

[0031] In a preferred embodiment of this invention, the surface of the partition is coated with a heat-insulating coating, the thickness of which is ≤50μm and the thermal conductivity is ≤0.05W / (m·K).

[0032] In a more specific implementation, the two partitions, together with the interlayer thermal coating, clearly divide the condenser into high-temperature, medium-temperature, and low-temperature zones from top to bottom, forming an orderly temperature gradient (high-temperature zone > medium-temperature zone > low-temperature zone). This physical isolation structure effectively blocks heat radiation and conduction from the high-temperature zone to the medium-temperature and low-temperature zones, avoiding the disordered heat transfer caused by temperature field mixing in traditional condensers, ensuring that each temperature zone maintains an independent and stable temperature environment, and significantly reducing heat loss.

[0033] In a preferred embodiment of this invention, a first fan is provided in the first air duct, and the first fan is positioned toward the evaporator.

[0034] A second fan is installed in the second air duct, and the second fan is positioned toward the condenser.

[0035] The first fan is positioned facing the evaporator, which can drive the air to flow precisely along the "bottom in, top out" path of the first air duct, that is, the air enters from the bottom air inlet of the evaporator and exits from the top air outlet. Combined with the bottom guide plate and the gradient design of the fin spacing of the evaporator, it ensures that the airflow flows evenly through all areas of the evaporator, avoiding airflow stagnation or uneven distribution caused by insufficient natural convection power. It can give full play to the structural advantages of the evaporator: "high-efficiency condensation with dense fins at the bottom and reduced resistance with sparse fins at the top".

[0036] The second fan is positioned towards the condenser, enabling targeted airflow within the second air duct. It is compatible with the condenser's layered isolation structure of "high temperature zone, medium temperature zone, and low temperature zone," ensuring sufficient air circulation within the independent air ducts of each temperature zone.

[0037] The second objective of this utility model is to provide a dehumidifier, including the heat exchange system described above;

[0038] The dehumidifier also includes a control system, which includes a controller and a temperature sensor. The temperature sensor is located at the evaporator and the condenser, and the controller is electrically connected to the temperature sensor. A water tank is located below the evaporator.

[0039] In the control system, temperature sensors are installed at both the evaporator and condenser to monitor the heat exchange temperature of the evaporator (such as fin surface temperature and refrigerant inlet and outlet temperatures) and the actual temperature of each temperature zone in the condenser (such as the real-time temperatures of the high-temperature zone, medium-temperature zone, and low-temperature zone), feeding the data back to the controller. The controller dynamically adjusts the equipment's operating parameters based on the temperature data. This precise control based on real-time temperature feedback leverages the structural advantages of the heat exchange system, avoiding efficiency losses caused by over-adjustment or under-adjustment, and further improving the overall stability and energy efficiency ratio of the system.

[0040] The water tank below the evaporator serves as the final collection component for condensate, forming a complete drainage path together with the V-shaped water guide groove and water collection tray at the bottom of the evaporator, thus avoiding the problem of environmental water accumulation caused by direct discharge of condensate.

[0041] The beneficial effects of this utility model are as follows:

[0042] This invention provides a heat exchange system comprising a compressor, a throttling valve, an evaporator, and a condenser connected via refrigerant pipes. A first air duct is provided at the evaporator, with its inlet at the bottom and its outlet at the top. A second air duct is provided at the condenser, isolated from the first air duct. A baffle plate is installed on the condenser, dividing the second air duct into several temperature zones along its height. During operation, in the first air duct, air is guided by a baffle plate from the bottom, flows upward along the evaporator surface, and exits from the top outlet, forming a uniform upward airflow. This avoids localized airflow turbulence at the evaporator, helps reduce condensate accumulation, and thus improves heat exchange efficiency. In the condenser, the baffle plate divides the second air duct into different temperature zones, effectively blocking cross-layer heat radiation, ensuring independent temperature fields, avoiding the coupling loss of "high temperature dragging low temperature" in traditional integral condensers, and improving the heat exchanger's capacity. Overall, this heat exchange system has high heat exchange efficiency and low energy consumption. When used in dehumidifiers, it can reduce the energy consumption of dehumidifiers, reduce heat loss, and improve the market competitiveness of dehumidifiers.

[0043] This application also provides a dehumidifier including the above-mentioned heat exchange system. The dehumidifier has high heat exchange efficiency and can solve the problems of uneven heat exchange, large heat loss and low energy efficiency of traditional dehumidifiers. It is especially suitable for high temperature and high humidity environments, significantly improves the performance indicators of dehumidifiers, and has stronger market competitiveness. Attached Figure Description

[0044] Figure 1 This is a first schematic diagram of the heat exchange system provided in an embodiment of the present invention;

[0045] Figure 2 This is a second schematic diagram of the heat exchange system provided in an embodiment of the present invention;

[0046] Figure 3 This is a first schematic diagram of an evaporator provided in an embodiment of this utility model;

[0047] Figure 4 This is a second schematic diagram of the evaporator provided in an embodiment of this utility model;

[0048] Figure 5 This is a schematic diagram of the first fin provided in an embodiment of the present invention being disposed on an evaporator;

[0049] Figure 6 This is a schematic diagram of the first fin provided in an embodiment of this utility model;

[0050] Figure 7 This is a schematic diagram of the baffle arrangement on the condenser provided in an embodiment of this utility model;

[0051] Figure 8 This is a schematic diagram of the dehumidifier provided in an embodiment of this utility model.

[0052] Figure label:

[0053] 1. Compressor; 2. Throttling valve; 3. Evaporator; 31. First air duct; 32. Air inlet; 33. Air outlet; 34. Baffle plate; 35. Heat exchange tube; 36. First fin; 361. Fin body; 362. Hydrophilic layer; 4. Condenser; 41. Baffle plate; 5. Refrigerant pipe; 6. Water collection tray; 7. Water guide groove; 8. Water tank. Detailed Implementation

[0054] Preferred embodiments of the present invention will now be described in more detail with reference to the accompanying drawings. While preferred embodiments of the present invention are shown in the drawings, it should be understood that the present invention may be implemented in various forms and should not be limited to the embodiments set forth herein. Rather, these embodiments are provided so that the present invention will be thorough and complete, and will fully convey the scope of the present invention to those skilled in the art.

[0055] Current dehumidifiers generally employ a top-in, bottom-out air duct design for their evaporators, meaning air enters from the top and exits from the bottom, with the refrigerant inlet typically located at the top. This structure easily leads to condensate accumulation at the bottom of the evaporator, covering the surface of the first fins and compressing the effective heat exchange area, resulting in uneven heat transfer. Furthermore, in terms of condenser design, existing structures lack effective temperature field isolation measures. Different areas of the condenser exhibit significant temperature gradients due to differences in refrigerant conditions, but without zoning, the heat radiation from the high-temperature and low-temperature zones interferes with each other, causing temperature field mixing. Heat from the high-temperature zone is transferred to the low-temperature zone, resulting in significant heat loss. This cross-regional heat conduction disrupts the temperature field independence required for condensation, reducing condensation efficiency and preventing the refrigerant from fully realizing its liquefaction and heat release process.

[0056] Based on this, this application provides a heat exchange system.

[0057] Example 1

[0058] like Figure 1 As shown, this embodiment provides a heat exchange system including a compressor 1, a throttle valve 2, an evaporator 3, and a condenser 4 connected by a refrigerant pipe 55;

[0059] The evaporator 3 is provided with a first air duct 31, the air inlet 32 ​​of the first air duct 31 is located at the bottom of the evaporator 3, and the air outlet 33 is located at the top of the evaporator 3.

[0060] A second air duct is provided at the condenser 4, which is isolated from the first air duct 31. A partition 41 is provided on the condenser 4, which divides the second air duct into several temperature zones arranged along the height direction.

[0061] Specifically, the evaporator 3 of this application adopts a parallel flow distribution structure with copper tubes. The refrigerant inlet is located at the bottom of the evaporator 3, and the refrigerant is evenly distributed into each branch of the evaporator 3 after being distributed through the copper tubes. The air inlet 32 ​​of the first air duct 31 is located at the bottom of the evaporator 3, and a guide plate 34 is provided at the air inlet 32. The air outlet 33 is located at the top of the evaporator 3. Air is guided by the guide plate 34 to enter the first air duct 31 from the bottom, flows upward along the surface of the evaporator 3, and is discharged from the top air outlet 33. The condenser is divided into different temperature zones along the height direction by a baffle 41. The second air duct is completely isolated from the first air duct 31 and operates independently, which can avoid airflow interference between the evaporator 3 and the condenser 4.

[0062] The evaporator 3 in the first air duct 31 adopts a bottom-in, top-out design, which, together with the bottom guide plate 34, forms a uniform upward airflow, avoiding local airflow turbulence, helping to reduce condensate accumulation and improve heat exchange efficiency. The baffle 41 in the condenser 4 effectively blocks cross-layer heat radiation, ensuring that each temperature field is independent, which can improve condensation efficiency.

[0063] Example 2

[0064] This embodiment is an improvement on embodiment 1.

[0065] like Figure 1 As shown, in this embodiment, the evaporator 3 includes a heat exchange tube 35 and multiple first fins 36, with the multiple first fins 36 fixed on the heat exchange tube 35; the heat exchange tube 35 is provided with a refrigerant inlet and a refrigerant outlet, with the refrigerant inlet located at the bottom of the evaporator 3 and the refrigerant outlet located at the top of the evaporator 3.

[0066] The refrigerant inlet at the bottom and the outlet at the top of the heat exchange tube 35, combined with the bottom-in, top-out first air duct 31, ensures that the refrigerant flow direction is consistent with the airflow direction, forming co-directional convection and improving the uniformity of heat exchange.

[0067] In this embodiment, along the height direction, the first fin 36 is provided in multiple layers on the heat exchange tube 35, and in each layer, two adjacent first fins 36 are spaced apart.

[0068] Along the bottom to top direction of the evaporator 3, the spacing between adjacent first fins 36 in the same layer gradually increases.

[0069] The design of the first fin's 36-inch spacing gradually increasing from bottom to top adapts to the condensation requirements of the high-humidity airflow at the bottom (closer spacing increases the heat exchange area in a small space) and the flow requirements of the low-humidity airflow at the top (sparser spacing reduces airflow resistance), effectively preventing condensate from accumulating between the bottom fins while improving the utilization of the overall heat exchange area.

[0070] In this embodiment, a guide plate 34 is provided at the air inlet 32 ​​at the bottom of the evaporator 3. The guide plate 34 is set at an angle α with the vertical direction, where 3° < α < 6°.

[0071] The guide vane 34, within this angle range, guides air in through the bottom air inlet 32, forming a stable and uniform upward airflow. This avoids localized turbulence (such as eddies or uneven airflow) caused by the airflow directly impacting the bottom of the evaporator 3 vertically. It ensures that air flows evenly across every fin of the evaporator 3, especially the densely spaced fins at the bottom, improving the overall heat exchange area utilization of the evaporator 3. The uniform upward airflow makes full contact with the fins at the bottom of the evaporator 3 (where the refrigerant temperature is lower). Combined with the denser fin spacing at the bottom and sparser at the top, this more efficiently condenses water vapor in the air into liquid water, reducing "ineffective heat exchange areas" caused by insufficient local airflow and indirectly contributing to improved heat exchange efficiency of the evaporator 3.

[0072] In one specific embodiment, along the height direction of the evaporator 3, the multiple first fins 36 are arranged in layers on the heat exchange tube 35, with adjacent first fins 36 in each layer spaced apart to form airflow gaps; and along the direction from the bottom to the top of the evaporator 3, the spacing between adjacent first fins 36 gradually increases in a gradient: the adjacent spacing of the bottom first layer of fins is 1.8 mm, the adjacent spacing of the middle second layer of fins is 2.5 mm, and the adjacent spacing of the top third layer of fins is 3.2 mm, adapting to the difference in moisture content of the airflow at different heights through the gradient of spacing. A guide plate 34 is provided at the air inlet 32 ​​of the first air duct 31 at the bottom of the evaporator 3, and the angle α between the guide plate 34 and the vertical direction is 5°.

[0073] When the dehumidifier is running, the refrigerant enters from the refrigerant inlet at the bottom of the heat exchange tube 35 and flows from bottom to top along the copper tube; at the same time, under the guidance of the first air duct 31, the outside air enters through the bottom air inlet 32 ​​and forms a uniform upward airflow under the action of the guide plate 34, flowing sequentially through the first fin 36 area at the bottom (fin spacing 1.8mm), middle (2.5mm), and top (3.2mm) of the evaporator 3.

[0074] Because the refrigerant flows from bottom to top within the heat exchange tube 35 (the refrigerant temperature is lower at the bottom), and the bottom fins are more closely spaced (1.8mm), combined with the uniformly rising high-humidity airflow, it can efficiently condense water vapor in the air into liquid water. As the airflow rises, the moisture content in the air decreases, and the wider spacing of the upper fins (3.2mm) reduces airflow resistance, ensuring smooth airflow discharge. The uniform airflow guided by the baffle 34 can fully flow through each fin, avoiding heat exchange dead zones caused by insufficient local airflow, thus significantly improving the heat exchange efficiency of the evaporator 3.

[0075] Example 3

[0076] This embodiment is an improvement on embodiment 2.

[0077] like Figure 1 As shown, in this embodiment, the first fin 36 includes a fin body 361 and a hydrophilic layer 362. The hydrophilic layer 362 covers the outer wall of the fin body 361, and the thickness of the hydrophilic layer 362 is 0.05mm-0.15mm. Specifically, the hydrophilic layer 362 is a hydrophilic aluminum foil.

[0078] The bottom of the evaporator 3 is provided with a water guide groove 7, the cross-section of the water guide groove 7 is V-shaped, and the depth of the water guide groove 7 is 2mm-3mm.

[0079] In this embodiment, the hydrophilic layer 362 significantly reduces the surface tension of condensate on the fin surface, promoting rapid spread and sliding of condensate along the fin surface, thus preventing water droplets from accumulating and covering the effective heat exchange area of ​​the fins. This thickness range ensures the stability of the hydrophilic effect (too thin and it is prone to wear and failure, too thick and it may increase thermal resistance), and it can also adapt to the fin spacing design with denser spacing at the bottom and sparser spacing at the top. In the densely spaced area at the bottom, the hydrophilic layer 362 can accelerate the flow of condensate between the dense fins, reduce the "insulation layer" formed by water droplet accumulation, and ensure that the heat exchange between the fins and the air is not hindered, thereby effectively improving the heat exchange efficiency of the evaporator 3.

[0080] The V-shaped water guide trough 7 can quickly collect condensate that slides off the fins: the inclined sidewalls of the V-shaped trough guide the water flow to the bottom of the trough, preventing condensate from flowing randomly at the bottom of the evaporator 3. The water guide trough 7 directs the collected condensate to the water collection tray 6, completely preventing condensate from stagnating at the bottom of the evaporator 3, reducing the risk of frost formation under low-temperature conditions due to water accumulation, and preventing water accumulation from corroding the bottom structure of the evaporator 3 (such as the refrigerant pipe 55 interface), thus extending the service life of the equipment.

[0081] Example 4

[0082] This embodiment is an improvement on embodiment 1.

[0083] In this embodiment, at least two partitions 41 are provided on the condenser 4 along the height direction, and each partition 41 divides the second air duct into a number of temperature zones arranged along the height direction; and the temperature of the lower temperature zone is lower than the temperature of the upper temperature zone.

[0084] In this embodiment, the condenser 4 includes a heat exchange tube 35 and a second fin, and the second fins with different heat transfer coefficients are provided in different temperature zones;

[0085] Furthermore, along the height direction of the condenser 4, the heat transfer coefficient of the lower second fin is less than that of the upper second fin.

[0086] At least two partitions 41 arranged along the height divide the second air duct into several temperature zones, with the temperature of the lower temperature zone being lower than that of the upper zone, forming an orderly temperature gradient from top to bottom. This effectively blocks cross-layer heat radiation and heat conduction between the high-temperature zone and the low-temperature zone, avoiding disordered heat transfer caused by temperature field mixing. This isolation design ensures that each temperature zone maintains an independent and stable temperature environment, making it difficult for heat from the high-temperature zone (upper layer) to diffuse to the low-temperature zone (lower layer), significantly reducing heat loss and providing stable temperature conditions for the condensation process.

[0087] Different temperature zones employ second fins with varying heat transfer coefficients. In the evaporator 3, the upper high-temperature zone is where the refrigerant is in a high-temperature, high-pressure gaseous state immediately after being discharged from the compressor 1. This zone requires the rapid release of a large amount of heat to promote liquefaction. The second fins with high heat transfer coefficients can efficiently transfer heat, enhancing the heat dissipation effect.

[0088] The lower low-temperature zone represents the medium-low temperature stage after the refrigerant gradually liquefies, reducing heat dissipation requirements. The second fins with a low heat transfer coefficient can adapt to low-load condensation demands, avoiding energy waste caused by excessive heat dissipation. This synergistic design of materials and temperature zones ensures that the condensation efficiency of each region of condenser 4 reaches its optimal state. Combined with the stability of independent temperature fields, this improves the heat exchange efficiency of condenser 4.

[0089] Example 5

[0090] This embodiment is an improvement on embodiment 1.

[0091] like Figure 1 As shown, in this embodiment, along the height direction, the condenser 4 is provided with two partitions 41, which divide the second air duct into a low temperature zone, a medium temperature zone and a high temperature zone along the height direction.

[0092] The condenser 4 includes a heat exchange tube 35 and a second fin, and the second fins with different heat transfer coefficients are provided in different temperature zones;

[0093] The thermal conductivity of the second fin in the high-temperature zone is ≥350W / (m·K); the thermal conductivity of the second fin in the medium-temperature zone is ≤220W / (m·K); and the second fin in the low-temperature zone is made of copper-aluminum composite material.

[0094] In this embodiment, the surface of the partition 41 is coated with a heat-insulating coating, the thickness of which is ≤50μm and the thermal conductivity is ≤0.05W / (m·K).

[0095] In a more specific embodiment, the two partitions 41, together with the interlayer thermal coating, can clearly divide the condenser 4 into a high-temperature zone, a medium-temperature zone, and a low-temperature zone from top to bottom, forming an orderly temperature gradient (high-temperature zone > medium-temperature zone > low-temperature zone). This physical isolation structure can effectively block heat radiation and heat conduction from the high-temperature zone to the medium-temperature zone and the low-temperature zone, avoid the disordered heat transfer caused by temperature field mixing in traditional condensers 4, ensure that each temperature zone maintains an independent and stable temperature environment, and significantly reduce heat loss.

[0096] More specifically, the partition 41 is made of 0.5mm thick aluminum alloy and extends along the width of the condenser 4, completely separating the airflow between adjacent temperature zones. Both partitions 41 are coated with a heat-insulating coating, which is a nano-ceramic material with a thickness of 40μm and a thermal conductivity of 0.05W / (m·K), used to block heat radiation and heat conduction between the high-temperature zone and the medium-temperature zone, and between the medium-temperature zone and the low-temperature zone. When the dehumidifier is running, the high-temperature, high-pressure gaseous refrigerant discharged from the compressor 1 enters the condenser 4 through a pipe, first flowing through the upper high-temperature zone: under the action of the high thermal conductivity second fin (380W / (m·K)), it rapidly releases a large amount of heat, and the gaseous refrigerant begins to liquefy; subsequently, the refrigerant enters the middle medium-temperature zone, where it continues to dissipate heat and further liquefies under the action of the low thermal conductivity fin (200W / (m·K)); finally, the refrigerant enters the lower low-temperature zone, where it completes liquefaction under the action of the copper-aluminum composite fin, becoming a high-pressure liquid refrigerant before flowing into the throttling valve 2.

[0097] During this process, the two aluminum alloy partitions 41, together with the nano-ceramic heat insulation coating (40μm thick, 0.04W / (m·K)) on their surfaces, effectively block cross-layer heat conduction from the high-temperature zone to the medium-temperature zone and from the medium-temperature zone to the low-temperature zone, keeping the high-temperature zone at a higher temperature (which is beneficial for heat dissipation of gaseous refrigerant) and the low-temperature zone at a lower temperature (which is beneficial for the stability of liquid refrigerant), forming an orderly temperature gradient of "high-temperature zone > medium-temperature zone > low-temperature zone".

[0098] Example 6

[0099] This embodiment is an improvement on embodiment 1.

[0100] like Figure 1As shown, in this embodiment, a first fan is provided in the first air duct 31, and the first fan is positioned towards the evaporator 3;

[0101] A second fan is installed in the second air duct, and the second fan is positioned toward the condenser 4.

[0102] The first fan is positioned facing the evaporator 3, which can drive the air to flow precisely along the "bottom in, top out" path of the first air duct 31. That is, the air enters from the bottom air inlet 32 ​​of the evaporator 3 and exits from the top air outlet 33. With the bottom guide plate 34 of the evaporator 3 and the gradient design of the fin spacing, the airflow is ensured to flow evenly through all areas of the evaporator 3, avoiding airflow stagnation or uneven distribution caused by insufficient natural convection power. This fully utilizes the structural advantages of the evaporator 3, which features "high-efficiency condensation with dense fins at the bottom and reduced resistance with sparse fins at the top".

[0103] The second fan is positioned towards the condenser 4, and can drive air to flow in the second air duct in a targeted manner. It is compatible with the layered isolation structure of the condenser 4, which has "high temperature zone, medium temperature zone, and low temperature zone", to ensure sufficient air circulation in the independent air duct of each temperature zone.

[0104] Example 7

[0105] like Figures 1-2 As shown, this embodiment provides a dehumidifier, including the heat exchange system described above;

[0106] The dehumidifier also includes a control system, which includes a controller and a temperature sensor. The temperature sensor is located at the evaporator 3 and the condenser 4. The controller is electrically connected to the temperature sensor. A water tank 8 is located below the evaporator 3.

[0107] In the control system, temperature sensors are installed at the evaporator 3 and condenser 4, respectively, to monitor the heat exchange temperature of the evaporator 3 (such as fin surface temperature and refrigerant inlet and outlet temperatures) and the actual temperature of each temperature zone in the condenser 4 (such as the real-time temperatures of the high-temperature zone, medium-temperature zone, and low-temperature zone), and feed the data back to the controller. The controller dynamically adjusts the equipment operating parameters based on the temperature data. This precise control based on real-time temperature feedback leverages the structural advantages of the heat exchange system, avoids efficiency losses caused by "over-adjustment" or "under-adjustment," and further improves the stability and energy efficiency ratio of the entire unit.

[0108] The water tank 8 below the evaporator 3 serves as the final collection component for condensate, forming a complete drainage path together with the V-shaped water guide trough 7 and the water collection tray 6 at the bottom of the evaporator 3. This avoids the problem of environmental water accumulation caused by direct discharge of condensate.

[0109] When the dehumidifier is running, the heat exchange system achieves efficient heat exchange through the bottom inlet and top outlet air duct of the evaporator 3 and the layered isolation structure of the condenser 4: water vapor in the air is condensed into liquid water by the evaporator 3, and flows into the water tank 8 below through the V-shaped water guide trough 7 and the water collection tray 6 in sequence; at the same time, the temperature sensor of the control system monitors the temperature of each layer of the evaporator 3 (fins, refrigerant inlet and outlet) and the condenser 4 in real time. After the data is transmitted to the controller, the controller dynamically adjusts the speed of the first fan and the second fan and the power of the compressor 1 to ensure that the heat exchange of the evaporator 3 is uniform (avoiding frost) and that each temperature field of the condenser 4 is independent.

[0110] Unless otherwise specifically stated, the relative arrangement, numerical expressions, and values ​​of the components and steps described in these embodiments do not limit the scope of this application. It should also be understood that, for ease of description, the dimensions of the various parts shown in the drawings are not drawn to actual scale. Techniques, methods, and devices known to those skilled in the art may not be discussed in detail, but where appropriate, such techniques, methods, and devices should be considered part of the specification. In all examples shown and discussed herein, any specific values ​​should be interpreted as merely exemplary and not as limitations. Therefore, other examples of exemplary embodiments may have different values. It should be noted that similar reference numerals and letters in the following drawings denote similar items; therefore, once an item is defined in one drawing, it need not be further discussed in subsequent drawings. In the description of this application, it should be understood that the orientation or positional relationship indicated by directional terms such as "front, back, up, down, left, right", "horizontal, vertical, horizontal" and "top, bottom" is usually based on the orientation or positional relationship shown in the accompanying drawings, and is only for the convenience of describing this application and simplifying the description. Unless otherwise stated, these directional terms do not indicate or imply that the device or element referred to must have a specific orientation or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation on the scope of protection of this application; the directional terms "inner" and "outer" refer to the inner and outer contours relative to the outline of each component itself.

[0111] For ease of description, spatial relative terms such as "above," "on top of," "on the upper surface of," "above," etc., are used herein to describe the spatial positional relationship of a device or feature as shown in the figures to other devices or features. It should be understood that spatial relative terms are intended to encompass different orientations in use or operation beyond the orientation of the device as described in the figures. For example, if the device in the figures were inverted, a device described as "above" or "on top of" other devices or structures would subsequently be positioned as "below" or "under" other devices or structures. Thus, the exemplary term "above" can include both "above" and "below." The device may also be positioned in other different ways (rotated 90 degrees or in other orientations), and the spatial relative descriptions used herein will be interpreted accordingly.

[0112] Furthermore, it should be noted that the use of terms such as "first" and "second" to define components is merely for the purpose of distinguishing the corresponding components. Unless otherwise stated, the above terms have no special meaning and therefore cannot be construed as limiting the scope of protection of this application.

[0113] The above description is merely a preferred embodiment of this utility model and is not intended to limit the utility model. Various modifications and variations can be made to this utility model by those skilled in the art. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of this utility model should be included within the protection scope of this utility model.

Claims

1. A heat exchange system comprising a compressor, a throttling valve, an evaporator, and a condenser connected via refrigerant pipes, characterized in that: The evaporator is provided with a first air duct, the air inlet of the first air duct is located at the bottom of the evaporator, and the air outlet is located at the top of the evaporator; A second air duct is provided at the condenser, which is isolated from the first air duct. A partition is provided on the condenser, which divides the second air duct into several temperature zones arranged along the height direction.

2. The heat exchange system according to claim 1, characterized in that: The evaporator includes a heat exchange tube and multiple first fins, the multiple first fins being fixed on the heat exchange tube; the heat exchange tube is provided with a refrigerant inlet and a refrigerant outlet, the refrigerant inlet being located at the bottom of the evaporator and the refrigerant outlet being located at the top of the evaporator.

3. The heat exchange system according to claim 2, characterized in that: Along the height direction, the first fins are arranged in multiple layers on the heat exchange tube, and in each layer, two adjacent first fins are spaced apart. Along the bottom to top direction of the evaporator, the spacing between adjacent first fins in the same layer gradually increases.

4. The heat exchange system according to claim 2, characterized in that: A guide plate is provided at the air inlet at the bottom of the evaporator, and the guide plate is set at an angle α with the vertical direction, wherein 3° < α < 6°.

5. The heat exchange system according to claim 2, characterized in that: The first fin includes a fin body and a hydrophilic layer, the hydrophilic layer covering the outer wall of the fin body, and the thickness of the hydrophilic layer is 0.05mm-0.15mm; The bottom of the evaporator is provided with a water guide groove, the cross-section of which is V-shaped and the depth of which is 2mm-3mm.

6. The heat exchange system according to any one of claims 1-5, characterized in that: Along the height direction, the condenser is provided with at least two partitions, each partition dividing the second air duct into several temperature zones along the height direction; and the temperature of the lower temperature zone is lower than the temperature of the upper temperature zone.

7. The heat exchange system according to claim 6, characterized in that: The condenser includes heat exchange tubes and second fins, and different heat transfer coefficients are provided in different temperature zones; Furthermore, along the height direction of the condenser, the heat transfer coefficient of the lower second fin is less than that of the upper second fin.

8. The heat exchange system according to claim 7, characterized in that: Along the height direction, the condenser is provided with two partitions, which divide the second air duct into a low temperature zone, a medium temperature zone, and a high temperature zone along the height direction; The thermal conductivity of the second fin in the high-temperature zone is ≥350W / (m·K); the thermal conductivity of the second fin in the medium-temperature zone is ≤220W / (m·K); and the second fin in the low-temperature zone is made of copper-aluminum composite material.

9. The heat exchange system according to any one of claims 1-5 and 7-8, characterized in that: The surface of the partition is coated with a heat-insulating coating, the thickness of which is ≤50μm and the thermal conductivity is ≤0.05W / (m·K).

10. The heat exchange system according to any one of claims 1-5 and 7-8, characterized in that: A first fan is installed in the first air duct, and the first fan is positioned towards the evaporator; A second fan is installed in the second air duct, and the second fan is positioned toward the condenser.

11. A dehumidifier, characterized in that: Includes the heat exchange system as described in any one of claims 1-10; The dehumidifier also includes a control system, which includes a controller and a temperature sensor. The temperature sensor is located at the evaporator and the condenser, and the controller is electrically connected to the temperature sensor. A water tank is located below the evaporator.

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