Heat pump type rotating wheel dehumidification system

Abstract

The utility model relates to a heat pump type rotating wheel dehumidification system which is used for solving the technical problems that heat cannot be recycled, energy consumption is high, and steam water hammers are likely to be generated. The heat pump type rotating wheel dehumidification system comprises a first air duct and a second air duct, the first air duct comprises a first fresh air inlet, an evaporator, a middle surface air cooler, a dehumidification area, an air feeder, a rear surface air cooler, a first condenser and an air supply outlet, and the first fresh air inlet, the evaporator, the middle surface air cooler, the dehumidification area, the air feeder, the rear surface air cooler, the first condenser and the air supply outlet are sequentially arranged in the airflow direction. Comprising a second fresh air inlet, a second condenser, a regeneration auxiliary heater, a rotating wheel regeneration area, an exhaust fan, an exhaust outlet and a rotating wheel which are sequentially arranged in the airflow direction, one part of the end face of the rotating wheel is arranged in the dehumidification area, and the other part of the end face of the rotating wheel is arranged in the rotating wheel regeneration area. A water condensing device and a compressor are arranged below the evaporator, the middle surface air cooler and the rear surface air cooler respectively, the evaporator is in fluid communication with the compressor, and the first condenser and the second condenser are connected between an outlet of the compressor and an inlet of the evaporator in parallel.

Description

Technical Field

[0001] The present disclosure relates to the technical field of dehumidification equipment, and in particular to a heat pump type rotary dehumidification system. Background Art

[0002] In conventional rotary dehumidification systems, the surface cooling section typically uses chilled water for cooling, the post-heating section typically uses steam for heating, and the regeneration section typically uses steam for heating. This can lead to heat waste and very high energy consumption. During the non-heating season, to adjust the supply air temperature difference, the valve in the unit's steam post-heating section needs to be partially opened, which can easily cause steam water hammer. The pressure of water hammer is very high, which can cause severe deformation of pipelines and serious corrosion of terminal equipment. Utility Model Content

[0003] The purpose of the present disclosure is to provide a heat pump type rotary dehumidification system to solve the technical problems that the heat of the evaporator cannot be reused, the energy consumption is high and steam water hammer is easily generated.

[0004] In order to achieve the above-mentioned objectives, the present disclosure provides a heat pump type rotary dehumidification system, comprising: a first air duct, comprising a first fresh air inlet, an evaporator, an intermediate cooler, a dehumidification zone, a blower, a rear cooler, a first condenser and an air supply outlet, which are arranged in sequence along the flow direction of air; a second air duct, which is not connected to the first air duct, the second air duct comprising a second fresh air inlet, a second condenser, a regeneration auxiliary heater, a rotary regeneration zone, an exhaust fan and an exhaust outlet, which are arranged in sequence along the flow direction of air; a rotary wheel, a portion of an end surface of the rotary wheel is arranged in the dehumidification zone, and another portion of the end surface of the rotary wheel is arranged in the rotary regeneration zone, the rotary wheel is capable of rotating, a condensing device, the condensing device is respectively placed below the evaporator, the intermediate cooler and the rear cooler; and a compressor, the outlet of the evaporator is fluidically connected to the inlet of the compressor, the first condenser and the second condenser are connected in parallel between the outlet of the compressor and the inlet of the evaporator, and the outlet of the compressor is fluidically connected to the first condenser and the second condenser respectively.

[0005] Optionally, the first air duct also includes: a primary filter, which is arranged between the first fresh air inlet and the evaporator, and a medium-efficiency filter, which is respectively arranged between the intermediate cooler and the dehumidification zone and between the first condenser and the air supply outlet.

[0006] Optionally, a mixing box is further provided between the evaporator and the intermediate surface cooler, and the mixing box is provided with a return air inlet.

[0007] Optionally, a silencer static pressure box is provided at the air supply outlet.

[0008] Optionally, a first three-way valve is provided at the outlet of the compressor, and the outlet of the compressor, the inlet of the first condenser and the inlet of the second condenser are connected through the first three-way valve.

[0009] Optionally, a throttling device is provided between the outlets of the first condenser and the second condenser and the inlet of the evaporator.

[0010] Optionally, the outlet of the first condenser, the outlet of the second condenser and the throttling device are connected via a second three-way valve.

[0011] Optionally, the condensation device includes: a condensation tank, the bottom wall of which is at least partially inclined so that the condensation water in the condensation tank gathers to the lowest point of the bottom wall; and a drainage pipe, which is arranged on the side wall of the condensation tank to discharge the condensation water gathered at the lowest point of the bottom wall, and the water inlet of the drainage pipe is provided with a filter.

[0012] Optionally, the drainage pipeline includes: a first drainage branch pipe, which is arranged at the lower part of the side wall, and a second drainage branch pipe, which is arranged at the upper part of the side wall.

[0013] Optionally, the condensation device further includes a honeycomb water baffle, which is arranged on the downstream side of the condensation tank along the flow direction of the air.

[0014] Through the above technical solution, in the heat pump type rotary dehumidification system disclosed in the present invention, the evaporator is arranged at the first fresh air inlet, and directly cools and dehumidifies the high-temperature and high-humidity outdoor air, replacing the front surface cooler of the conventional solution, and reducing the energy consumption of the equipment operation; the first condenser performs isohyperhumidity heating on the supply air after the rotary treatment, replacing the steam after-heater of the conventional solution, which not only reduces the operating energy consumption of the system, but also solves the steam water hammer problem caused by the opening of the after-heater; in addition, through the compressor, the heat absorbed by the evaporator from the first fresh air inlet can be used for the first condenser and the second condenser, the first condenser can heat the supply air, and the second condenser and the regeneration auxiliary heater can couple and heat the regenerated air entering the second air duct for dehumidification and regeneration of the rotary regeneration area. The heat absorbed by the evaporator can be effectively utilized to avoid heat waste, with significant energy-saving effects.

[0015] Other features and advantages of the present disclosure will be described in detail in the following detailed description. BRIEF DESCRIPTION OF THE DRAWINGS

[0016] The accompanying drawings are used to provide a further understanding of the present disclosure and constitute a part of the specification. Together with the following detailed description, they are used to explain the present disclosure but do not constitute a limitation of the present disclosure. In the accompanying drawings:

[0017] Figure 1 2 is a schematic structural diagram of a heat pump type rotary dehumidification system in a specific embodiment of the present disclosure;

[0018] Figure 2 is a schematic diagram of the connection principle of the heat pump module in a specific embodiment of the present disclosure;

[0019] Figure 3 It is a structural schematic diagram of the water condensation device in a specific embodiment of the present disclosure.

[0020] Description of Reference Numerals

[0021] 1-first air duct, 101-first fresh air inlet, 102-supply air outlet, 10-dehumidification area, 11-evaporator, 12-intermediate surface cooler, 13-supply fan, 14-rear surface cooler, 15-first condenser, 16-primary filter, 17-medium efficiency filter, 18-mixing box, 181-return air inlet, 19-silencer static pressure box,

[0022] 2-second air duct, 201-second fresh air inlet, 202-exhaust outlet, 20-rotor regeneration area, 21-second condenser, 22-regeneration auxiliary heater, 23-exhaust fan,

[0023] 3-wheel,

[0024] 4- condensate device, 41- condensate tank, 411- bottom wall, 412- side wall, 42- drainage pipe, 420- filter screen, 421- first drainage branch pipe, 422- second drainage branch pipe, 43- honeycomb water retaining plate,

[0025] 5-Compressor,

[0026] 61-first three-way valve, 62-second three-way valve,

[0027] 7-Throttling device,

[0028] 8-Refrigerant pipe,

[0029] 9-Current balancing maintenance section. DETAILED DESCRIPTION

[0030] The following describes the specific embodiments of the present disclosure in detail with reference to the accompanying drawings. It should be understood that the specific embodiments described herein are only used to illustrate and explain the present disclosure and are not intended to limit the present disclosure.

[0031] In this disclosure, unless otherwise indicated, directional terms such as "upper" and "lower" generally refer to the upper and lower positions of the condensate device in normal use. "Inside" and "outside" refer to the inside and outside relative to the outline of the corresponding component. "Upstream" and "downstream" refer to the upstream and downstream positions along the direction of air flow, i.e., air flows from upstream to downstream. Terms such as "first" and "second" used in this disclosure are intended to distinguish one element from another and do not convey sequentiality or importance. Furthermore, when the following description refers to the accompanying drawings, unless otherwise indicated, identical numbers in different drawings represent identical or similar elements.

[0032] According to a specific embodiment of the present disclosure, a heat pump type rotary dehumidification system is provided, referring to Figure 1 As shown, the heat pump type rotary dehumidification system may include a first air duct 1 , a second air duct 2 , a rotary wheel 3 and a condensing device 4 .

[0033] Among them, the first air duct 1 can include a first fresh air inlet 101, an evaporator 11, an intermediate surface cooler 12, a dehumidification area 10, a blower 13, a rear surface cooler 14, a first condenser 15 and an air outlet 102 arranged in sequence along the air flow direction. After the humid air that needs to be dehumidified enters the first air duct 1 from the first fresh air inlet 101, it is first cooled by the evaporator 11 and the intermediate cooler 12 in sequence. A part of the water vapor in the air will form condensed water on the surface of the evaporator 11 and the intermediate cooler 12, and then flows through the dehumidification area 10 to be dehumidified and dried by the rotor 3 described below, and then is blown to the rear cooler 14 and the first condenser 15 through the blower 13. When the supply air temperature is low, the rear cooler 14 does not work, and the first condenser 15 works to heat the supply air blown by the blower 13, so that the dehumidification system can deliver dry hot air to the room. When the supply air temperature is high, the first condenser 15 does not work, and the rear cooler 14 works to further cool the supply air blown by the blower 13, so that the dehumidification system can deliver dry cold air to the room.

[0034] The second air duct 2 is not connected to the first air duct 1 and may include a second fresh air inlet 201, a second condenser 21, a regeneration auxiliary heater 22, a rotor regeneration zone 20, an exhaust fan 23, and an exhaust outlet 202, which are sequentially arranged along the air flow direction. Regeneration air enters the second air duct 2 through the second fresh air inlet 201 and is heated by the second condenser 21 and the regeneration auxiliary heater 22 to become high-temperature hot air. The high-temperature hot air then flows through the rotor regeneration zone 20 to regenerate and reduce the desiccant in the rotor 3 described below, and is finally blown out of the exhaust outlet 202 through the exhaust fan 23.

[0035] The rotor 3 is a 125°C high-temperature dehumidification rotor. The rotor 3 is composed of a special glass fiber carrier containing a small amount of titanium and a composite of activated silica gel. Its honeycomb structure design can not only maximize the attachment of the desiccant, increase the surface area of ​​contact between the humid air and the desiccant, and improve the working efficiency of the dehumidification system, but also has high strength and can be well adapted to various complex working environments. A portion of the end face of the rotor 3 is arranged in the dehumidification zone 10, and another portion of the end face of the rotor 3 is arranged in the rotor regeneration zone 20. Specifically, the central angle of the sector surface of the rotor 3 located in the dehumidification zone 10 can be 270°, and the central angle of the sector surface of the rotor 3 located in the rotor regeneration zone 20 can be 90°. When the humid air to be dehumidified enters the first air duct 1 and flows through the dehumidification zone 10, the water vapor in the humid air is adsorbed by the activated silica gel in the rotor 3, thereby being dried. The dried air is then sent out through the blower 13. As the amount of absorbed moisture increases, the portion of the wheel 3 in the dehumidification zone 10 gradually approaches a saturated state. In order to maintain its stable dehumidification performance, the desiccant in the wheel 3 needs to be regenerated and restored. At this time, the wheel 3 can be rotated to rotate the portion of the wheel 3 that is saturated with moisture from the dehumidification zone 10 of the first air duct 1 to the wheel regeneration zone 20 of the second air duct 2. At the same time, the portion of the wheel 3 that has been regenerated and restored in the wheel regeneration zone 20 can be rotated to the dehumidification zone 10 of the first air duct 1 to continue dehumidifying the humid air.

[0036] refer to Figure 1 As shown, in order to remove the condensed water on the mobile phone evaporator 11, the middle surface cooler 12 and the rear surface cooler 12, a condensing device 4 can be placed under the evaporator 11, the middle surface cooler 12 and the rear surface cooler 14 respectively. The condensing device 4 can collect the condensed water and discharge it from the dehumidification system.

[0037] In the specific embodiment of the present disclosure, a heat pump module may also be included. Figure 2As shown, the heat pump module may include an evaporator 11, a compressor 5, a first condenser 15 and a second condenser 21 which are fluidically connected in sequence through a refrigerant pipe 8 along the flow direction of the refrigerant, wherein the outlet of the evaporator 11 can be fluidically connected to the inlet of the compressor 5, the first condenser 15 and the second condenser 21 can be connected in parallel between the outlet of the compressor 5 and the inlet of the evaporator 11, and the outlet of the compressor 5 can be fluidically connected to the first condenser 15 and the second condenser 21 respectively. Through the compressor 5, the heat of the evaporator 11 can be used for the first condenser 15 and the second condenser 21, thereby heating the supply air in the first air duct 1 and heating the regenerated air in the second air duct 2. In addition, when the supply air temperature is low, the compressor 5 can be connected with the first condenser 15 and the second condenser 21 to increase the supply air temperature and heat the regenerated air at the same time. When the supply air temperature is high, the compressor 5 can cut off the connection with the first condenser 15 and only connect with the second condenser 21. At this time, the rear surface cooler 14 cools the supply air and the second condenser 21 heats the regenerated air.

[0038] Through the above technical solution, in the heat pump type rotary dehumidification system disclosed in the present invention, the evaporator 11 is arranged at the first fresh air inlet 101, and directly cools and dehumidifies the outdoor high-temperature and high-humidity air, replacing the front surface cooler of the conventional solution, thereby reducing the equipment operation energy consumption; the first condenser 15 performs isohumid heating on the supply air after being processed by the rotary wheel 3, replacing the steam after-heater of the conventional solution, which not only reduces the system operation energy consumption, but also solves the steam water hammer problem caused by the opening of the after-heater; in addition, through the compressor 5, the heat absorbed by the evaporator 11 from the first fresh air inlet 101 can be used for the first condenser 15 and the second condenser 21, the first condenser 15 can heat the supply air, and the second condenser 21 and the regeneration auxiliary heater 22 can couple and heat the regenerated air entering the second air duct 2 for dehumidification and regeneration of the rotary wheel regeneration zone 20, and the heat absorbed by the evaporator 11 can be effectively utilized to avoid heat waste, thereby having a significant energy-saving effect.

[0039] In order to make the dehumidification system deliver clean and dust-free air to the room, refer to Figure 1 As shown, the first air duct 1 may further include a primary filter 16 and a secondary filter 17. The primary filter 16 may be disposed between the first fresh air inlet 101 and the evaporator 11 to prevent the air entering the first fresh air inlet 101 from bringing external dust into the first air duct 1 and causing blockage. A secondary filter 17 may also be disposed between the intermediate cooler 12 and the dehumidification zone 10, and between the first condenser 15 and the air outlet 102. After three filtration steps, the dehumidification system can deliver clean, dust-free air to the room.

[0040] refer to Figure 1As shown, a mixing box 18 can be provided between the evaporator 11 and the intermediate cooler 12. The mixing box 18 can be provided with a return air inlet 181. After the outdoor high-temperature and high-humidity air contacts the evaporator 11, it can achieve the effect of preliminary cooling and dehumidification. The treated air can be mixed with the return air entering through the return air inlet 181 in the mixing box 18, and then flow through the intermediate cooler 12 for further cooling.

[0041] In order to eliminate the noise of the dehumidification system sending air into the room, refer to Figure 1 As shown, a silencer static pressure box 19 may also be provided at the air outlet 102 .

[0042] In order to ensure uniform air supply, a flow equalization maintenance section 9 may be provided between the reference air blower 13 and the rear surface cooler 14 .

[0043] In order to realize the on-off communication between the compressor 5 and the first condenser 15 and the second condenser 21, refer to Figure 1 and Figure 2 As shown, a first three-way valve 61 may be provided at the outlet of the compressor 5, and the outlet of the compressor 5, the inlet of the first condenser 15, and the inlet of the second condenser 21 may be connected via the first three-way valve 61. The first three-way valve 61 can not only control the on-off connection between the compressor 5 and the first condenser 15 and the second condenser 21, but also control the flow rate of the refrigerant flowing to the first condenser 15 and the second condenser 21, thereby controlling the heating temperature of the first condenser 15 and the second condenser 21. When the supply air temperature is low, the compressor 5 is connected to the first condenser 15 and the second condenser 21 through the adjustment of the first three-way valve 61 to increase the supply air temperature and heat the regenerated air at the same time; when the supply air temperature is still not high enough, the flow rate of the refrigerant flowing to the first condenser 15 can be increased through the first three-way valve 61 to further increase the supply air temperature; when the supply air temperature is high, the flow rate of the refrigerant flowing to the first condenser 15 can be reduced through the adjustment of the first three-way valve 61 to lower the supply air temperature; when the supply air temperature is still not low enough, the connection between the compressor 5 and the first condenser 15 can be cut off through the first three-way valve 61, so that the compressor 5 is only connected to the second condenser 21. At this time, the rear surface cooler 14 cools the supply air to further lower the supply air temperature.

[0044] refer to Figure 1 and Figure 2 As shown, a throttling device 7 may be provided between the outlets of the first condenser 15 and the second condenser 21 and the inlet of the evaporator 11 . The outlet of the first condenser 15 , the outlet of the second condenser 21 and the throttling device 7 may also be connected via a second three-way valve 62 .

[0045] refer to Figure 1 and Figure 3As shown, the condensate device 4 may include a condensate tank 41 and a drainage pipe 42, wherein the bottom wall 411 of the condensate tank 41 may be at least partially tilted so that the condensate in the condensate tank 41 gathers to the lowest point of the bottom wall 411 to overcome the problem of poor drainage of the flat condensate tray. The drainage pipe 42 may be arranged on the side wall 412 of the condensate tank 41 to discharge the condensate gathered to the lowest point of the bottom wall 411. The water inlet of the drainage pipe 42 may be provided with a filter 420 to prevent impurities from clogging the drainage pipe 42.

[0046] In order to further prevent the condensate from being discharged in time due to blockage of the drainage pipe 42, refer to Figure 3 As shown, the drainage pipe 42 can also include a first drainage branch pipe 421 and a second drainage branch pipe 422. The first drainage branch pipe 421 can be set at the lower part of the side wall 412 and corresponding to the lowest point of the bottom wall 411, so that the condensed water can be discharged smoothly through the drainage branch pipe 421. The second drainage branch pipe 422 can be set at the upper part of the side wall 412. Once the first drainage branch pipe 421 is blocked, the water level in the condensate tank 41 rises. When the condensed water level reaches the second drainage branch pipe 422, the condensed water can also be discharged in time through the second drainage branch pipe 422.

[0047] In addition, in order to prevent the airflow in the first air duct 1 from sucking the condensed water in the condensation tank 41, Figure 1 and Figure 3 As shown, the condensation device 4 can also include a honeycomb water baffle 43. The honeycomb water baffle 43 can be arranged on the downstream side of the condensation tank 41 along the flow direction of the air. Circular holes can be evenly distributed on the honeycomb water baffle 43. The height of the honeycomb water baffle 43 can be 0.5m, and the diameter of the circular holes can be 0.02m. The circular holes can allow airflow to pass through and can effectively prevent condensed water from drifting away with the airflow.

[0048] In the specific embodiment of the present disclosure, the design and selection of the wheel 3, the middle surface cooler 12, and the rear surface cooler 14 are not described in detail. Only the calculation results are given, and the selection of key components of the heat pump type rotary dehumidification system is introduced in detail. The economic efficiency of the conventional dehumidifier and the heat pump type rotary dehumidification system provided by the present disclosure is compared and analyzed.

[0049] (1) Design and selection of the heat pump type rotary dehumidification system provided in this disclosure

[0050] Taking the heat pump type single-stage refrigeration two-stage condensation heating rotary dehumidification system as an example, its air supply volume is 15000m 3 / h, fresh air volume is 3500m 3 / h, regeneration air supply volume is 3500m 3 / h.

[0051] In Shenzhen, the outdoor dry-bulb temperature of air conditioners in summer is 33.7°C, the relative humidity is 70%, and the enthalpy is 95.3 kJ / kg. The dry-bulb temperature of fresh air after evaporation is 12°C, the relative humidity is 90%, and the enthalpy is 32.4 kJ / kg. The fresh air volume is 5000 m 3 / h, the rated cooling capacity Q1 of the evaporator is:

[0052] Q1(kW)=1.2kg / m 3 ×3500m 3 / h×(95.3kj / kg-32.4kj / kg) / 3600

[0053] Q1(kW)≈72kW

[0054] In summer, the first condenser 15 is used to increase the temperature of the post-heating section. The temperature rise is generally adjusted to 3°C to 5°C. In the embodiment of the present disclosure, 5°C is used. The heating amount Q of the first condenser 15 is 21 for:

[0055] Q 21 (kW)=1.2kg / m 3 ×15000m 3 / h×1.01×5 / 3600×1.2

[0056] Q 21 (kW)≈31kW

[0057] In summer, the second condenser 21 is set in the second air duct 2, and the regeneration air volume is 3500m 3 / h, the fresh air inlet dry bulb temperature is 36℃, the rated air outlet temperature of the second condenser 21 is 80℃, then the heating capacity of the second condenser 21 is Q 22 for:

[0058] Q 22 (kW)=1.2kg / m 3 ×3500m 3 / h×1.01×(80-36) / 3600×1.2

[0059] Q 22 (kW)≈65kW

[0060] According to the rated cooling capacity of the evaporator, the rated heating capacity of the first condenser 15 and the second condenser 21, the rated power N of the compressor 5 can be selected as: N = 24KW

[0061] The air heated by the second condenser 21 enters the regeneration auxiliary heater 22 for secondary heating, raising the temperature of the regeneration air from 80°C to 120°C. The heating capacity Q3 of the regeneration auxiliary heater 22 is:

[0062] Q3=1.2kg / m3×3500m3 / h×1.01×(120℃-80℃) / 3600≈47kw

[0063] According to the data, the latent heat value of 0.6Mpa saturated steam is 2066kj / kg, so the steam quantity M required for the regenerative auxiliary heater 22 is: M=47×3600 / 2066≈82kg / h.

[0064] (2) Energy-saving effect analysis

[0065] In actual lithium-ion battery production, the dehumidifier operates 24 hours a day, electricity costs are calculated at 0.7 yuan / kWh, steam costs are calculated at 300 yuan / ton, the COP of the air conditioning water system is calculated at 4.5, and the energy-saving effect analysis period is 360 days. The energy consumption calculation results for a traditional dehumidifier and the heat pump rotary dehumidification system provided in this disclosure are detailed in Table 1 below.

[0066] Table 1

[0067]

[0068] From Table 1 above, we can see that: taking Shenzhen as an example, the rated air supply volume of the dehumidification system is 15000m 3 / h, fresh air volume is 3500m 3 / h, regeneration air supply volume is 3500m 3 / h, compared with the conventional rotary dehumidification system, the heat pump rotary dehumidification system disclosed in the present invention saves 281,000 yuan in operating costs per year, with an energy saving rate of 28.5%.

[0069] The preferred embodiments of the present disclosure are described in detail above in conjunction with the accompanying drawings. However, the present disclosure is not limited to the specific details of the above embodiments. Within the technical concept of the present disclosure, various simple modifications can be made to the technical solutions of the present disclosure, and these simple modifications all fall within the scope of protection of the present disclosure.

[0070] It should also be noted that the various specific technical features described in the above specific embodiments can be combined in any appropriate manner without contradiction. In order to avoid unnecessary repetition, the present disclosure will not further describe various possible combinations.

[0071] In addition, the various embodiments of the present disclosure may be arbitrarily combined, and as long as they do not violate the concept of the present disclosure, they should also be regarded as the contents disclosed by the present disclosure.

Claims

1. A heat pump type rotary dehumidification system, characterized in that: include: The first air duct includes a first fresh air inlet, an evaporator, a middle cooler, a dehumidification area, a blower, a rear cooler, a first condenser and an air outlet, which are sequentially arranged along the air flow direction. The second air duct is not connected to the first air duct, and the second air duct includes a second fresh air inlet, a second condenser, a regeneration auxiliary heater, a rotor regeneration area, an exhaust fan and an exhaust outlet, which are arranged in sequence along the flow direction of the air. A rotor, a portion of an end surface of the rotor is arranged in the dehumidification zone, another portion of the end surface of the rotor is arranged in the rotor regeneration zone, and the rotor is capable of rotating, A condensing device is placed under the evaporator, the middle cooler and the rear cooler, and The outlet of the evaporator is fluidically connected to the inlet of the compressor, the first condenser and the second condenser are connected in parallel between the outlet of the compressor and the inlet of the evaporator, and the outlet of the compressor is fluidically connected to the first condenser and the second condenser respectively.

2. The heat pump type rotary dehumidification system according to claim 1, characterized in that: The first air duct also includes: a primary filter, arranged between the first fresh air inlet and the evaporator, and Medium efficiency filters are respectively arranged between the intermediate cooler and the dehumidification zone and between the first condenser and the air supply outlet.

3. The heat pump type rotary dehumidification system according to claim 1, characterized in that: A mixing box is also provided between the evaporator and the intermediate surface cooler, and the mixing box is provided with a return air inlet.

4. The heat pump type rotary dehumidification system according to claim 1, characterized in that: A silencer static pressure box is arranged at the air supply outlet.

5. The heat pump type rotary dehumidification system according to claim 1, characterized in that: A first three-way valve is provided at the outlet of the compressor, and the outlet of the compressor, the inlet of the first condenser and the inlet of the second condenser are connected through the first three-way valve.

6. The heat pump type rotary dehumidification system according to claim 1, characterized in that: A throttling device is provided between the outlets of the first condenser and the second condenser and the inlet of the evaporator.

7. The heat pump type rotary dehumidification system according to claim 6, characterized in that: The outlet of the first condenser, the outlet of the second condenser and the throttling device are connected via a second three-way valve.

8. The heat pump type rotary dehumidification system according to claim 1, characterized in that: The water condensation device comprises: a condensation water tank, the bottom wall of which is at least partially inclined so that condensed water in the condensation water tank is collected at the lowest point of the bottom wall, and A drainage pipeline is arranged on the side wall of the condensate tank to discharge the condensate collected at the lowest point of the bottom wall, and a filter is arranged at the water inlet of the drainage pipeline.

9. The heat pump type rotary dehumidification system according to claim 8, characterized in that: The drainage pipeline comprises: a first drainage branch pipe, arranged at the lower part of the side wall, and The second drainage branch pipe is arranged on the upper part of the side wall.

10. The heat pump type rotary dehumidification system according to claim 8, characterized in that: The condensation device further comprises a honeycomb water baffle plate, which is arranged on the downstream side of the condensation tank along the flow direction of air.

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