Balanced heat distribution rotary dehumidification system and control method

Abstract

This invention relates to the field of air conditioning and discloses a balanced heat distribution rotary dehumidification system and control method. The system includes a fresh air duct, a cooling air duct, a regeneration air duct, a rotary dehumidification unit, a coupled heat pump unit, a deep dehumidification unit, an inlet pipe, and an outlet pipe. The coupled heat pump unit includes a first heat exchanger, a first control valve, a second control valve, a third control valve, a fourth control valve, a second throttling device, a third throttling device, a second evaporator, a second compressor, and a second condenser. When the system operates in summer mode, heat is transferred from the processing area of ​​the first dehumidification wheel to the regeneration area of ​​the first dehumidification wheel through the coupled heat pump unit. When the system operates in winter mode, heat is recovered from the regeneration area of ​​the first dehumidification wheel and transferred to the processing area and the air inlet side of the first dehumidification wheel in the regeneration area through the coupled heat pump unit. The system adopts multi-stage multi-heat exchanger coupled heat pump technology, achieving a balance of cooling and heating throughout the year, and efficiently realizing energy transfer and energy saving.

Description

Technical Field

[0001] This invention relates to the field of air conditioning, and more particularly to a balanced heat distribution rotary dehumidification system and control method. Background Technology

[0002] Traditional rotary dehumidifiers use a desiccant wheel core made of solid silica gel or molecular sieve material to absorb water molecules in the treatment zone. After being transferred to the regeneration zone, the desorption process requires a high temperature of about 130°C, which consumes a large amount of high-grade energy and has a high energy consumption. The regeneration heat source is generally electric heating, steam heating, thermal oil heating, heat pump heating, etc.

[0003] Traditional rotary dehumidifiers use conventional heating methods such as electric heating, steam heating, and thermal oil heating, which are energy-intensive and not energy-efficient.

[0004] Typical energy-saving heat pump rotary dehumidifiers utilize heat pump heating to extract low-grade heat from regeneration exhaust air or ambient air. This heat is then upgraded to a high-temperature heat source by the first compressor for regeneration heating, resulting in energy efficiency. During summer operation, the system operates with a heat-driven cooling system, achieving a balance and normal operation. However, during winter operation, the fresh air in the treatment zone requires preheating, and the air entering the dehumidifier in the regeneration zone also needs regeneration heating. This leads to an imbalance between the required heat and cooling capacity, causing the heat pump system to malfunction year-round. Summary of the Invention

[0005] The first objective of this invention is to provide a balanced heat distribution rotary dehumidification system, which aims to solve the technical problem of unbalanced heating and cooling demand in existing heat pump systems, which prevents the heat pump system from operating normally throughout the year.

[0006] To achieve the above objectives, the present invention provides a balanced heat distribution rotary dehumidification system, comprising a fresh air duct, a cooling air duct, a regeneration air duct, a rotary dehumidification unit, a coupled heat pump unit, a deep dehumidification unit, an inlet pipe, and an outlet pipe; the rotary dehumidification unit comprises a first dehumidification wheel, a second dehumidification wheel, a surface cooler, an air pressurization device, a first evaporator, a temperature-regulating heat exchanger, a temperature-regulating heating device, a first condenser, a first compressor, a first throttling device, a secondary regeneration heating device, a primary regeneration heating device, and a regeneration fan, wherein the first dehumidification wheel and the second dehumidification wheel are respectively simultaneously arranged on the fresh air duct and the regeneration air duct;

[0007] The coupled heat pump unit includes a first heat exchanger, a first control valve, a second control valve, a third control valve, a fourth control valve, a second throttling device, a third throttling device, a second evaporator, a second compressor, and a second condenser. The first heat exchanger, the second throttling device, the second evaporator, the second compressor, the second control valve, the second condenser, the first dehumidifying wheel, and the third throttling device are connected end to end in sequence. The first control valve is connected in parallel on both sides of the second throttling device. One end of the third control valve is located between the second control valve and the second compressor, and the other end is located between the second condenser and the first dehumidifying wheel. The fourth control valve is connected in parallel on both sides of the third throttling device.

[0008] The first heat exchanger, the surface cooler, the deep dehumidification unit, the first dehumidification wheel, the air booster, the first evaporator, the second dehumidification wheel, the temperature-regulating heat exchanger, and the temperature-regulating heating device are sequentially arranged on the fresh air duct. The outlet of the fresh air duct is used to connect to the clean drying room. The water inlets of the surface cooler and the temperature-regulating heat exchanger are respectively connected to the water inlet pipe, and the water outlets of the surface cooler and the temperature-regulating heat exchanger are respectively connected to the water outlet pipe. The first condenser, the first compressor, and the secondary regenerator are also included. The heating device, the second condenser, the first-stage regeneration heating device, the second evaporator, and the regeneration fan are sequentially arranged on the regeneration air duct along the regeneration direction. The first compressor, the first condenser, the first throttling device, and the first evaporator are connected end to end in sequence. One end of the cooling air duct is connected to the fresh air duct and is located between the air pressurization device and the first evaporator. The other end is connected to the regeneration air duct through the second dehumidification wheel. The deep dehumidification unit is used to cool the fresh air passing through the surface cooler to a preset temperature and preset humidity.

[0009] Preferably, the deep dehumidification unit includes a third condenser, a third compressor, a third evaporator, and a fourth throttling device. The third condenser, the third compressor, the third evaporator, and the fourth throttling device are connected end to end. The water inlet of the third condenser is connected to the water inlet pipe, and the water outlet of the third condenser is connected to the water outlet pipe. The third condenser is disposed on the fresh air duct and located between the surface cooler and the first dehumidification wheel.

[0010] Preferably, the coupled heat pump unit further includes a first gas-liquid separator, and the deep dehumidification unit further includes a second gas-liquid separator. The first gas-liquid separator is disposed between the second evaporator and the second compressor, and the second gas-liquid separator is disposed between the third compressor and the third evaporator.

[0011] Preferably, proportional regulating valves are respectively provided at the water inlet of the surface cooler, the water inlet of the temperature regulating heat exchanger, and the water inlet of the third condenser.

[0012] Preferably, it further includes a fresh air valve, a fresh air exhaust valve, and a regeneration exhaust valve, wherein the fresh air valve is located at the inlet of the fresh air duct, the fresh air exhaust valve is located at the outlet of the fresh air duct, and the regeneration exhaust valve is located at the outlet of the regeneration duct.

[0013] Preferably, a pre-filter is provided between the fresh air valve and the first heat exchanger, and a medium-efficiency filter is provided between the temperature-regulating heat exchanger and the second dehumidifying wheel.

[0014] Preferably, it also includes a return air duct connected to the fresh air duct, the return air duct being located between the first dehumidifying wheel and the air pressurization device, the end of the return air duct away from the fresh air duct being used to connect to the clean drying room, and a return air valve being provided on the return air duct.

[0015] The second objective of this invention is to provide a control method for a balanced heat distribution rotary dehumidification system. This control method is used to implement the operational control of the balanced heat distribution rotary dehumidification system as described in any one of claims 1-7. The control method includes: real-time acquisition of the ambient fresh air dry-bulb temperature and ambient fresh air humidity; when the ambient fresh air dry-bulb temperature > 9°C or the ambient fresh air humidity > 6.8 g / kg, the balanced heat distribution rotary dehumidification system switches to summer operation mode, the coupled heat pump unit controls the switching to cooling mode, and the coupled heat pump unit controls the treatment of the fresh air before it enters the surface cooler to the required level. The system has a preset temperature and relative humidity value, and transfers the heat from the processing area of ​​the first dehumidifying wheel to the second condenser for release to the regeneration side for regeneration heating. When the ambient fresh air dry bulb temperature is ≤9℃ or the ambient fresh air moisture content is ≤6.8g / kg, the balanced heat distribution wheel dehumidification system switches to winter operation mode, and the coupled heat pump unit control switches to heating mode. The coupled heat pump unit processes the fresh air before it enters the surface cooler to a temperature greater than the second preset temperature, and recovers and transfers the heat from the regeneration area of ​​the first dehumidifying wheel to the processing area of ​​the first dehumidifying wheel and the air inlet of the first dehumidifying wheel in the regeneration area for preheating.

[0016] Preferably, when the coupled heat pump unit is switched to cooling mode, the first heat exchanger enters evaporative cooling mode, the second evaporator stops operating, the third control valve, the fourth control valve, and the second throttling device are closed, and the first control valve, the second control valve, the third throttling device, and the second compressor are opened. The third throttling device performs PID adjustment according to the control target of the first preset temperature and the preset relative humidity value. The second compressor transfers the heat from the processing area to the second condenser and releases it to the regeneration side for regeneration heating. The first-stage regeneration heating device is used for regeneration temperature compensation and performs PID adjustment according to the outlet air humidity after the first dehumidifier wheel. When the coupled heat pump unit is switched to heating mode, the coupled heat pump unit uses the outlet air of the first heat exchanger... When the temperature reaches the second preset temperature as the control target, the surface cooler stops operating, the first control valve, the second control valve, and the third throttling device are closed, and the third control valve, the fourth control valve, the second throttling device, and the second compressor are opened. The second throttling device performs PID adjustment according to the control target of the second preset temperature. When the control target is reached, the current of the second compressor is detected to determine whether the upper limit of the corresponding operating condition has been reached. If there is a margin, the second control valve is opened, and the remaining heat is used for regeneration heating of the first dehumidifying wheel regeneration zone. Heat is also collected from the second evaporator for heating the first heat exchanger and the second condenser. The first-stage regeneration heating device is used for regeneration temperature compensation and performs PID adjustment according to the humidity of the air outlet after the first dehumidifying wheel.

[0017] Preferably, the first preset temperature is 17°C, the preset relative humidity is 95%, and the second preset temperature is 5°C.

[0018] The balanced heat distribution rotary dehumidification system provided by this invention includes a fresh air duct, a cooling air duct, a regeneration air duct, a rotary dehumidification unit, a coupled heat pump unit, and a deep dehumidification unit. It adopts multi-stage multi-heat exchanger coupled heat pump technology, with heat exchangers installed at three locations: before the first dehumidification wheel on the fresh air side, at the regeneration air inlet of the second dehumidification wheel in the regeneration air duct, and at the regeneration exhaust of the first dehumidification wheel in the regeneration air duct. Multiple throttling devices and control valves are matched to balance the heat and cold of the rotary dehumidification system throughout the year, achieving efficient energy transfer and energy saving. Attached Figure Description

[0019] To more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on the structures shown in these drawings without creative effort.

[0020] Figure 1 This is a schematic diagram of the balanced heat distribution rotary dehumidification system provided in an embodiment of the present invention;

[0021] Figure 2 This is a schematic diagram of the structure of the coupled heat pump unit provided in an embodiment of the present invention;

[0022] Figure 3 This is a schematic diagram of the structure of the deep dehumidification unit provided in an embodiment of the present invention;

[0023] Figure 4 This is a flowchart of the control method for the balanced heat distribution rotary dehumidification system provided in the embodiments of the present invention.

[0024] Description of Figure Numbers:

[0025] 1. Fresh air valve; 2. Pre-filter; 3. First control valve; 4. Second throttling device; 5. First heat exchanger; 6. Surface cooler; 7. Water outlet pipe; 8. Water inlet pipe; 9. Proportional regulating valve; 12. First dehumidifying impeller; 13. First-stage rotary drive motor; 14. Return air valve; 15. Return air duct; 16. Air booster device; 17. Cooling air duct; 18. First evaporator; 19. Second dehumidifying impeller; 20. Second-stage rotary drive motor; 21. Medium-efficiency filter; 22. Temperature-regulating heat exchanger; 24. Temperature-regulating heating device; 25. Clean drying room; 26. First condenser; 27. First compressor; 28. Second-stage regenerative heating. Device; 29. ​​First throttling device; 30. Second condenser; 31. First-stage regenerative heating device; 32. Second compressor; 33. Third throttling device; 34. Fourth control valve; 35. Second evaporator; 36. Regenerative fan; 37. Regenerative exhaust valve; 38. Fresh air exhaust valve; 39. First gas-liquid separator; 42. Third condenser; 43. Third compressor; 44. Second gas-liquid separator; 45. Third evaporator; 46. Fourth throttling device; 52. Second control valve; 53. Third control valve; 100. Coupled heat pump unit; 200. Deep dehumidification unit; 300. Fresh air duct; 400. Regenerative air duct. Detailed Implementation

[0026] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those of ordinary skill in the art without creative effort are within the scope of protection of the present invention.

[0027] It should be noted that all directional indications (such as up, down, left, right, front, back, etc.) in the embodiments of the present invention are only used to explain the relative positional relationship and movement of each component in a certain specific posture (as shown in the figure). If the specific posture changes, the directional indication will also change accordingly.

[0028] It should also be noted that when a component is described as "fixed to" or "set on" another component, it can be directly on the other component or there may be an intervening component present. When a component is described as "connected to" another component, it can be directly connected to the other component or there may be an intervening component present.

[0029] Furthermore, the use of terms such as "first" and "second" in this invention is for descriptive purposes only and should not be construed as indicating or implying their relative importance or implicitly specifying the number of technical features indicated. Therefore, a feature defined with "first" or "second" may explicitly or implicitly include at least one of that feature. Additionally, the technical solutions of the various embodiments can be combined with each other, but only on the basis of being achievable by those skilled in the art. When the combination of technical solutions is contradictory or impossible to implement, such a combination of technical solutions should be considered non-existent and not within the scope of protection claimed by this invention.

[0030] like Figures 1 to 3 As shown, it is a balanced heat distribution rotary dehumidification system according to an embodiment of the present invention.

[0031] Please see Figure 1 and Figure 2 As shown, the balanced heat distribution rotary dehumidification system of this invention includes a fresh air duct 300, a cooling air duct 17, a regeneration air duct 400, a rotary dehumidification unit, a coupled heat pump unit 100, a deep dehumidification unit 200, an inlet pipe 8, and an outlet pipe 7.

[0032] The rotary dehumidification unit includes a first dehumidification wheel 12, a second dehumidification wheel 19, a surface cooler 6, an air pressurization device 16, a first evaporator 18, a temperature-regulating heat exchanger 22, a temperature-regulating heating device 24, a first condenser 26, a first compressor 27, a first throttling device 29, a secondary regeneration heating device 28, a primary regeneration heating device 31, and a regeneration fan 36. The first dehumidification wheel 12 and the second dehumidification wheel 19 are respectively installed on the fresh air duct 300 and the regeneration air duct 400.

[0033] The coupled heat pump unit 100 includes a first heat exchanger 5, a first control valve 3, a second control valve 52, a third control valve 53, a fourth control valve 34, a second throttling device 4, a third throttling device 33, a second evaporator 35, a second compressor 32, and a second condenser 30. The first heat exchanger 5, the second throttling device 4, the second evaporator 35, the second compressor 32, the second control valve 52, the second condenser 30, the first dehumidifying wheel 12, and the third throttling device 33 are connected end to end in sequence. The first control valve 3 is connected in parallel on both sides of the second throttling device 4. One end of the third control valve 53 is located between the second control valve 52 and the second compressor 32, and the other end is located between the second condenser 30 and the first dehumidifying wheel 12. The fourth control valve 34 is connected in parallel on both sides of the third throttling device 33.

[0034] The first heat exchanger 5, surface cooler 6, deep dehumidification unit 200, first dehumidification wheel 12, air booster 16, first evaporator 18, second dehumidification wheel 19, temperature-regulating heat exchanger 22, and temperature-regulating heating device 24 are sequentially arranged on the fresh air duct 300. The outlet of the fresh air duct 300 is used to connect to the clean drying room 25. The water inlet of the surface cooler 6 and the water inlet of the temperature-regulating heat exchanger 22 are respectively connected to the water inlet pipe 8, and the water outlet of the surface cooler 6 and the water outlet of the temperature-regulating heat exchanger 22 are respectively connected to the water outlet pipe 7. The first condenser 26, the first compressor 27, and the secondary regeneration heating device are also included. 28. The second condenser 30, the first-stage regeneration heating device 31, the second evaporator 35 and the regeneration fan 36 are arranged sequentially on the regeneration air duct 400 along the regeneration direction. The first compressor 27, the first condenser 26, the first throttling device 29 and the first evaporator 18 are connected end to end. One end of the cooling air duct 17 is connected to the fresh air duct 300 and is located between the air pressurization device 16 and the first evaporator 18. The other end is connected to the regeneration air duct 400 through the second dehumidification wheel 19. The deep dehumidification unit 200 is used to cool the fresh air passing through the surface cooler 6 to the preset temperature and preset humidity.

[0035] In this embodiment, the first heat exchanger 5 is an evaporator; in other embodiments, the first heat exchanger 5 may also be a condenser.

[0036] In this embodiment, the air booster device 16 is a booster fan used to boost air pressure and enhance air power.

[0037] In this embodiment, the first control valve 3, the second control valve 52, the third control valve 53, and the fourth control valve 34 are all proportional regulating ball valves.

[0038] In this embodiment, the first dehumidifying wheel 12 is connected to a primary rotary drive motor 13, and the second dehumidifying wheel 19 is connected to a secondary rotary drive motor 20. The primary rotary drive motor 13 drives the first dehumidifying wheel 12 to rotate, thereby adsorbing water vapor in the air. The secondary rotary drive motor 20 drives the second dehumidifying wheel 19 to rotate, thereby adsorbing water vapor in the air and further improving the dehumidification effect.

[0039] When the balanced heat distribution rotary dehumidification system switches to summer operation mode, the coupled heat pump unit 100 switches to cooling mode. The coupled heat pump unit 100 transfers heat from the processing area of ​​the first dehumidification wheel 12 to the regeneration area of ​​the first dehumidification wheel 12, thereby achieving local temperature control during summer operation. At the same time, it balances cooling and heating, and uses energy in both directions to maximize energy saving.

[0040] In this embodiment, when the coupled heat pump unit 100 is switched to the cooling mode, the first heat exchanger 5 enters the evaporative cooling mode, the second evaporator 35 stops operating, the third control valve 53, the fourth control valve 34 and the second throttling device 4 are closed, the first control valve 3, the second control valve and the third throttling device 33 are opened, and then the second compressor 32 is turned on. The third throttling device 33 performs PID adjustment according to the control target of 17°C and 95% relative humidity. The second compressor 32 continuously transfers the heat from the processing area to the second condenser 30 and releases it to the regeneration side for regeneration heating. The first-stage regeneration heating device 31 is used for regeneration temperature compensation and performs PID adjustment according to the outlet air humidity after the first dehumidifying wheel 12.

[0041] Specifically, when the balanced heat distribution rotary dehumidification system switches to summer operation mode, the first heat exchanger 5 operates the evaporative cooling function to treat the fresh air to 17℃ / 95%; the surface cooler 6 treats the fresh air to 9℃ / 95%; the deep dehumidification unit 200 continues to treat the fresh air to 3℃ / 95%; then it enters the first dehumidification wheel 12 for adsorption dehumidification, mixes with the return air from the clean drying room 25, and is drawn in by the air pressurization device 16 to increase air pressure and improve airflow; a small portion of low-humidity, low-temperature air is separated into the cooling air duct 17, recovers heat in the subcooled zone of the second dehumidification wheel 19, and enters the regeneration air duct 400. Most of it flows along the processing zone channel, is temperature-controlled by the first evaporator 18, and then enters the processing zone of the second dehumidification wheel 19 for adsorption dehumidification again to reach the target dew point set in the system; then it is treated by the temperature-regulating heat exchanger 22 to reach the target dry-bulb temperature set in the system, finally reaching the system's set temperature, cleanliness, and ultra-low dew point, and is sent into the clean drying room 25. The regenerated air from the subcooled zone of the second dehumidifying wheel 19 passes through the first condenser 26. The heat absorbed by the first evaporator 18 is then transferred to the first condenser 26 by the first compressor 27, releasing heat to heat the regenerated air. This, combined with the secondary regeneration heating device 28, controls the regeneration temperature of the second dehumidifying wheel 19, ensuring accurate regeneration temperature and adjustable humidity based on the system settings. The regenerated air exiting the second dehumidifying wheel 19 still has a low humidity level and is used for primary regeneration. After passing through the second condenser 30, the heat absorbed in the first heat exchanger 5 is transferred to the second compressor 32 to heat the regenerated air exiting the second dehumidifying wheel 19. Similarly, this, combined with the primary regeneration heating device 31, controls the regeneration temperature of the first dehumidifying wheel 12, ensuring accurate regeneration temperature and adjustable humidity based on the dew point setting after the first dehumidifying wheel 12. The regenerated air exiting the first dehumidifying wheel 12 is then exhausted outdoors by the regeneration fan 36, completing the process of transferring moisture from the treatment area to the regeneration area for desorption and release. The second evaporator 35 is not used during summer operation.

[0042] When the balanced heat distribution dehumidification system switches to winter operation mode, the coupled heat pump unit 100 switches to heating mode. The coupled heat pump unit 100 recovers and transfers heat from the regeneration zone of the first dehumidification wheel 12 to the processing zone and the air inlet side of the first dehumidification wheel 12 in the regeneration zone. By recovering the waste heat from the regeneration exhaust, it ensures preheating heat in winter and partially uses it for regeneration heating, achieving high efficiency and energy saving through balanced heat distribution.

[0043] In this embodiment, when the coupled heat pump unit 100 switches to heating mode, the coupled heat pump unit 100 takes the outlet air temperature of the first heat exchanger 5 reaching 5°C as the control target. The surface cooler 6 stops operating, the first control valve 3, the second control valve 52 and the third throttling device 33 are closed, the third control valve 53, the fourth control valve 34 and the second throttling device 4 are opened, and then the second compressor 32 is started. The second throttling device 4 performs PID adjustment according to the 5°C control target. When the control target is reached, the current of the second compressor 32 is detected to determine whether the upper limit of the corresponding operating condition has been reached. If there is a margin, the second control valve 52 is gradually opened to use the remaining heat for regeneration heating of the regeneration zone of the first dehumidifying wheel 12. The maximum amount of heat is collected from the second evaporator 35 for heating the first heat exchanger 5 and the second condenser 30. The first-stage regeneration heating device 31 is used for regeneration temperature compensation and performs PID adjustment according to the outlet air humidity after the first dehumidifying wheel 12.

[0044] Specifically, when the balanced heat distribution rotary dehumidification system switches to winter operation mode, the first heat exchanger 5 operates in fresh air preheating mode, and the second compressor 32 controls the operation target to ensure that the air temperature before entering the surface cooler 6 is ≥5℃, performing preheating and antifreeze functions. The surface cooler 6 and the deep dehumidification unit 200 stop operating. Fresh air enters the first dehumidification wheel 12 for adsorption and dehumidification. After mixing with the return air from the clean drying room 25, it is drawn in by the air booster device 16 and pressurized to increase air power. A small portion of low-humidity and low-temperature air is separated and enters the cooling air duct 17. After recovering heat in the subcooled zone of the second dehumidification wheel 19, it enters the regeneration air duct 400. Most of the low-humidity and low-temperature air flows along the processing zone channel. After being temperature-controlled by the first evaporator 18, it enters the processing zone of the second dehumidification wheel 19 for adsorption and dehumidification again to reach the target dew point set in the system. Then, it is processed by the temperature-regulating heating device 24 to reach the target dry-bulb temperature set in the system, finally achieving the system's set temperature, cleanliness, and ultra-low dew point, and is then sent into the clean drying room 25. The regenerated air from the subcooled zone of the second dehumidifier wheel 19 passes through the first condenser 26. The heat absorbed by the first evaporator 18 is then transferred to the first condenser 26 by the first compressor 27, releasing heat to regenerate the air. This, combined with the secondary regeneration heating device 28, controls the regeneration temperature of the second dehumidifier wheel 19, ensuring precise temperature control and adjustable humidity based on system settings. The regenerated air exiting the second dehumidifier wheel 19 still has a low humidity level and is used for primary regeneration. The second condenser 30 assists in heating the regenerated air, and, combined with the primary regeneration heating device 31, controls the regeneration temperature of the first dehumidifier wheel 12, ensuring precise temperature control and adjustable humidity based on the dew point setting after the first dehumidifier wheel 12. The regenerated air exiting the first dehumidifier wheel 12 is then exhausted outdoors by the regeneration fan 36, completing the transfer of moisture absorbed in the treatment area to the regeneration area for desorption and release. In winter operation mode, heat extracted from the second evaporator 35 is preferentially used in the first heat exchanger 5, with any surplus heat applied to the second condenser 30.

[0045] The balanced heat distribution rotary dehumidification system implemented in this invention includes a fresh air duct 300, a cooling air duct 17, a regeneration air duct 400, a rotary dehumidification unit, a coupled heat pump unit 100, and a deep dehumidification unit 200. It adopts multi-stage multi-heat exchanger coupled heat pump technology. Heat exchangers are respectively set at three locations: before the air inlet of the first dehumidification wheel 12 on the fresh air side, at the regeneration air inlet of the second dehumidification wheel 19 in the regeneration air duct 400, and at the regeneration exhaust of the first dehumidification wheel 12 in the regeneration air duct 400. Multiple throttling devices and control valves are matched to balance the heat and cold of the rotary dehumidification system throughout the year, realize efficient energy transfer, and achieve the purpose of energy saving.

[0046] Please see Figure 3As shown, exemplarily, in some embodiments, the deep dehumidification unit 200 includes a third condenser 42, a third compressor 43, a third evaporator 45, and a fourth throttling device 46. The third condenser 42, the third compressor 43, the third evaporator 45, and the fourth throttling device 46 are connected end to end. The water inlet of the third condenser 42 is connected to the water inlet pipe 8, and the water outlet of the third condenser 42 is connected to the water outlet pipe 7. The third condenser 42 is disposed on the fresh air duct 300 and located between the surface cooler 6 and the first dehumidification wheel 12. Through the organic combination of the third condenser 42, the third compressor 43, the third evaporator 45, and the fourth throttling device 46, the fresh air passing through the surface cooler 6 can be cooled to a preset temperature and preset humidity (for example, during summer operation, the deep dehumidification unit 200 processes the fresh air to 3°C and 95% relative humidity). At the same time, the energy in the heat pump cycle can be reused, improving the energy efficiency of the system and reducing energy consumption costs.

[0047] In this embodiment, the third condenser 42 is a water-cooled condenser.

[0048] Please see Figure 1 and 2 As shown, exemplarily, in some embodiments, the coupled heat pump unit 100 further includes a first gas-liquid separator 39, and the deep dehumidification unit 200 further includes a second gas-liquid separator 44. The first gas-liquid separator 39 is disposed between the second evaporator 35 and the second compressor 32, and the second gas-liquid separator 44 is disposed between the third compressor 43 and the third evaporator 45. By setting the first gas-liquid separator 39 and the second gas-liquid separator 44, liquid working fluid can be prevented from entering the second compressor 32, the third compressor 43 and other key components, reducing the risk of corrosion and damage and extending the service life of the equipment.

[0049] Please see Figure 1 and Figure 3 As shown, by way of example, in some embodiments, proportional regulating valves 9 are respectively provided at the inlet of the surface cooler 6, the inlet of the temperature regulating heat exchanger 22, and the inlet of the third condenser 42. By setting proportional regulating valves 9 at the inlet of the surface cooler 6, the inlet of the temperature regulating heat exchanger 22, and the inlet of the third condenser 42, precise control of the flow rate can be achieved, saving energy and improving the flexibility and stability of the system.

[0050] Please see Figure 1 As shown, by way of example, in some embodiments, the balanced heat distribution rotary dehumidification system further includes a fresh air valve 1, a fresh air exhaust valve 38, and a regeneration exhaust valve 37. The fresh air valve 1 is located at the inlet of the fresh air duct 300, the fresh air exhaust valve 38 is located at the outlet of the fresh air duct 300, and the regeneration exhaust valve 37 is located at the outlet of the regeneration duct 400.

[0051] The fresh air valve 1 can adjust the intake of fresh air as needed, thereby regulating the fresh air exchange volume in the room. Reasonable control of the fresh air volume can reduce energy consumption, improve energy utilization efficiency, and help save energy and reduce emissions.

[0052] The fresh air exhaust valve 38 can adjust the amount of fresh air discharged as needed, thereby regulating the amount of fresh air exchanged indoors. Reasonable control of the fresh air volume can reduce energy consumption, improve energy utilization efficiency, and help save energy and reduce emissions.

[0053] Similarly, the regeneration exhaust valve 37 can effectively control the exhaust volume of the regeneration duct 400, realize energy recovery and reuse, and reasonably control the exhaust volume of the regeneration duct 400 can also improve the energy efficiency of the system and reduce energy waste.

[0054] Furthermore, a primary filter 2 is installed between the fresh air valve 1 and the first heat exchanger 5. Fresh air enters the unit from the fresh air valve 1 and undergoes air purification treatment in the primary filter 2. The primary filter 2 can effectively filter large particles and dust in the air, preventing these impurities from entering the first heat exchanger 5 and protecting the first heat exchanger 5 from damage.

[0055] Furthermore, a medium-efficiency filter 21 is installed between the temperature-regulating heat exchanger 22 and the second dehumidifying wheel 19. The low-humidity, low-temperature air that enters the processing area of ​​the second dehumidifying wheel 19 and is dehumidified again passes through the medium-efficiency filter 21 for clean filtration, and then is processed by the temperature-regulating heat exchanger 22 to reach the target dry-bulb temperature set in the system. The medium-efficiency filter 21 can effectively filter out smaller particulate matter and pollutants in the air, preventing them from entering the temperature-regulating heat exchanger 22 and protecting the temperature-regulating heat exchanger 22 from damage.

[0056] Please see Figure 1 As shown, exemplarily, in some embodiments, the balanced heat distribution rotary dehumidification system further includes a return air duct 15 connected to the fresh air duct 300. The return air duct 15 is located between the first dehumidification wheel 12 and the air pressurization device 16. The end of the return air duct 15 away from the fresh air duct 300 is used to connect to the clean drying room 25. By connecting the return air duct 15 to the fresh air duct 300, partial recycling of indoor air can be achieved, reducing energy consumption and improving energy efficiency.

[0057] Furthermore, a return air valve 14 is installed on the return air duct 15. By reasonably adjusting the opening degree of the return air valve 14, the energy consumption of the system can be effectively controlled, thereby achieving the purpose of energy saving.

[0058] Please see Figures 1-4 As shown, this embodiment of the invention also provides a control method for a balanced heat distribution rotary dehumidifier system, used to achieve the operation control of the balanced heat distribution rotary dehumidifier system as described above. The control method includes:

[0059] S101. Real-time acquisition of ambient fresh air dry bulb temperature and ambient fresh air humidity content;

[0060] S102. When the ambient fresh air dry bulb temperature is >9℃ or the ambient fresh air moisture content is >6.8g / kg, the balanced heat distribution wheel dehumidification system switches to summer operation mode, the coupled heat pump unit 100 switches to cooling mode, the coupled heat pump unit 100 controls the fresh air before entering the surface cooler 6 to be treated to the first preset temperature and preset relative humidity value, and the heat of the treatment area of ​​the first dehumidification wheel 12 is transferred to the second condenser 30 and released to the regeneration side for regeneration heating.

[0061] S103. When the ambient fresh air dry bulb temperature is ≦9℃ or the ambient fresh air moisture content is ≦6.8g / kg, the balanced heat distribution wheel dehumidification system switches to winter operation mode, and the coupled heat pump unit 100 switches to heating mode. The coupled heat pump unit 100 processes the fresh air before entering the surface cooler 6 to a temperature greater than the second preset temperature, and recovers and transfers heat from the regeneration zone of the first dehumidification wheel 12 to the processing zone of the first dehumidification wheel 12 and the air intake of the first dehumidification wheel 12 in the regeneration zone for preheating.

[0062] In this embodiment, the first preset temperature is 17°C and the preset relative humidity is 95%.

[0063] In this embodiment, the second preset temperature is 5°C.

[0064] In this embodiment, when the coupled heat pump unit 100 switches to cooling mode, the first heat exchanger 5 enters evaporative cooling mode, the second evaporator 35 stops operating, the third control valve 53, the fourth control valve 34, and the second throttling device 4 are closed, and the first control valve 3, the second control valve 34, the third throttling device 33, and the second compressor 32 are opened. The third throttling device 33 performs PID adjustment according to the control target of the first preset temperature and preset relative humidity value. The second compressor 32 transfers the heat from the processing area to the second condenser 30 and releases it to the regeneration side for regeneration heating. The first-stage regeneration heating device 3... 1 is used for regeneration temperature compensation and performs PID adjustment based on the outlet air humidity after the first dehumidifying wheel 12; when the coupled heat pump unit 100 switches to heating mode, the surface cooler 6 stops running, the first control valve 3, the second control valve 52 and the third throttling device 33 are closed, and the third control valve 53, the fourth control valve 34, the second throttling device 4 and the second compressor 32 are opened. The second throttling device 4 performs PID adjustment based on the control target of the second preset temperature. The first-stage regeneration heating device 31 is used for regeneration temperature compensation and performs PID adjustment based on the outlet air humidity after the first dehumidifying wheel 12.

[0065] Specifically, when the balanced heat distribution rotary dehumidification system switches to summer operation mode, fresh air enters the unit through fresh air valve 1 and undergoes air purification treatment in the primary filter 2. The first heat exchanger 5 operates the evaporative cooling function to treat the fresh air to 17℃ / 95%. The proportional regulating valve 9 at the inlet of the surface cooler 6 opens to treat the fresh air to 9℃ / 95%. The deep dehumidification unit 200 continues to treat the fresh air to 3℃ / 95%. Then, it enters the first dehumidification wheel 12 for adsorption dehumidification. After mixing with the return air from the clean drying room 25, it is drawn in by the air pressurization device 16 and pressurized. Aerodynamics: A small portion of the low-humidity, low-temperature air is separated and enters the cooling air duct 17. After recovering heat in the subcooled zone of the second dehumidification wheel 19, it enters the regeneration air duct 400. Most of the low-humidity, low-temperature air flows along the processing zone channel. After being temperature-controlled by the first evaporator 18, it enters the processing zone of the second dehumidification wheel 19 for further adsorption and dehumidification to reach the target dew point set in the system. Then, it is cleaned by the medium-efficiency filter 21 and processed by the temperature-regulating heat exchanger 22 to reach the target dry-bulb temperature set in the system. Finally, it reaches the temperature, cleanliness and ultra-low dew point set by the system and is sent into the clean drying room 25. The regenerated air from the subcooled zone of the second dehumidifying wheel 19 passes through the first condenser 26. The heat absorbed by the first evaporator 18 is then transferred to the first condenser 26 by the first compressor 27, releasing heat to heat the regenerated air. This, combined with the secondary regeneration heating device 28, controls the regeneration temperature of the second dehumidifying wheel 19, ensuring accurate regeneration temperature and adjustable humidity based on system settings. The regenerated air exiting the second dehumidifying wheel 19 still has a low humidity level and is used for primary regeneration. After passing through the second condenser 30, the heat absorbed in the first heat exchanger 5 is transferred to the regenerated air exiting the second dehumidifying wheel 19 via the second compressor 32. Similarly, this, combined with the primary regeneration heating device 31, controls the regeneration temperature of the first dehumidifying wheel 12, ensuring accurate regeneration temperature and adjustable humidity based on the dew point setting after the first dehumidifying wheel 12. The regenerated air exiting the first dehumidifying wheel 12 is then discharged outdoors by the regeneration fan 36 and regeneration exhaust valve 37, completing the transfer of moisture absorbed in the treatment area to the regeneration area for desorption and release. The second evaporator 35 is not used during summer operation.

[0066] Specifically, when the deep dehumidification unit 200 continues to process fresh air to 3℃ / 95%, the deep dehumidification unit 200 starts. When it detects water in the inlet pipe 8 and outlet pipe 7 and that the air pressurization device 16 is open, the third condenser 42 and the fourth throttling device 46 are opened, and the third compressor 43 is started. The fourth throttling device 46 aims to control the temperature of the outlet side of the third evaporator 45, and controls the condensing temperature of the third condenser 42 to ensure the minimum operating pressure difference between the evaporation side and the condensation side.

[0067] In this embodiment, the coupled heat pump unit 100 is switched to heating mode, the surface cooler 6 stops operating, the first control valve 3, the second control valve 52, and the third throttling device 33 are closed, and the third control valve 53, the fourth control valve 34, the second throttling device 4, and the second compressor 32 are opened. The second throttling device 4 is opened from the closed state to a preset 10%. The second throttling device 4 performs PID adjustment according to the control target of the second preset temperature. When the control target is reached, the current of the second compressor 32 is detected to determine whether the upper limit of the corresponding operating condition has been reached. If there is a margin, the second control valve 52 is opened, and the remaining heat is used for regeneration heating of the regeneration zone of the first dehumidifying wheel 12. Heat is also collected from the second evaporator 35 for heating the first heat exchanger 5 and the second condenser 30. The first-stage regeneration heating device 31 is used for regeneration temperature compensation and performs PID adjustment according to the humidity of the air outlet after the first dehumidifying wheel 12.

[0068] Specifically, when the balanced heat distribution rotary dehumidification system switches to winter operation mode, fresh air enters the unit through fresh air valve 1 and undergoes air purification treatment in the primary filter 2. The first heat exchanger 5 operates in fresh air preheating mode, and the second compressor 32 controls the operation target to ensure that the air temperature before entering the surface cooler 6 is ≥5℃, performing preheating and antifreeze functions. The surface cooler 6 stops operating, and the proportional regulating valve 9 at the inlet of the surface cooler 6 is closed. The deep dehumidification unit 200 stops operating. Fresh air enters the first dehumidification wheel 12 for adsorption and dehumidification, and after mixing with the return air from the clean drying room 25, it is pressurized by the air. After being drawn in, the device 16 pressurizes and enhances the airflow. A small portion of the low-humidity, low-temperature air is separated and enters the cooling duct 17. After recovering heat in the subcooled zone of the second dehumidifying wheel 19, it enters the regeneration duct 400. Most of the low-humidity, low-temperature air flows along the processing zone channel. After being temperature-controlled by the first evaporator 18, it enters the processing zone of the second dehumidifying wheel 19 for re-adsorption and dehumidification to reach the target dew point set in the system. Then, it is processed by the temperature-regulating heating device 24 to reach the target dry-bulb temperature set in the system. Finally, it reaches the temperature, cleanliness, and ultra-low dew point set by the system and is sent into the clean drying room 25. The regenerated air from the subcooled zone of the second dehumidifying wheel 19 passes through the first condenser 26. The heat absorbed by the first evaporator 18 is then transferred to the first condenser 26 by the first compressor 27, releasing heat to heat the regenerated air. This, combined with the secondary regeneration heating device 28, controls the regeneration temperature of the second dehumidifying wheel 19, ensuring accurate regeneration temperature and adjustable humidity according to the system settings. The regenerated air exiting the second dehumidifying wheel 19 still has a low humidity level and is used for primary regeneration. The second condenser 30 assists in heating the regenerated air, and together with the primary regeneration heating device 31, controls the regeneration temperature of the first dehumidifying wheel 12, ensuring accurate regeneration temperature and adjustable humidity according to the dew point setting after the first dehumidifying wheel 12. The regenerated air exiting the first dehumidifying wheel 12 is then discharged outdoors by the regeneration fan 36 and the regeneration exhaust valve 37, completing the transfer of moisture absorbed in the treatment area to the regeneration area for desorption and release. In winter operation mode, heat extracted from the second evaporator 35 is preferentially used for the first heat exchanger 5, and any surplus heat is applied to the second condenser 30.

[0069] The above description is merely a preferred embodiment of the present invention and does not limit the patent scope of the present invention. Any equivalent structural transformations made using the contents of the present invention's specification and drawings under the inventive concept of the present invention, or direct / indirect applications in other related technical fields, are included within the patent protection scope of the present invention.

Claims

1. A balanced heat distribution rotary dehumidification system, characterized in that, It includes a fresh air duct, a cooling air duct, a regeneration air duct, a rotary dehumidifier unit, a coupled heat pump unit, a deep dehumidifier unit, an inlet water pipe, and an outlet water pipe; The rotary dehumidification unit includes a first dehumidification wheel, a second dehumidification wheel, a surface cooler, an air booster, a first evaporator, a temperature-regulating heat exchanger, a temperature-regulating heating device, a first condenser, a first compressor, a first throttling device, a secondary regeneration heating device, a primary regeneration heating device, and a regeneration fan. The first dehumidification wheel and the second dehumidification wheel are respectively installed on the fresh air duct and the regeneration duct. The coupled heat pump unit includes a first heat exchanger, a first control valve, a second control valve, a third control valve, a fourth control valve, a second throttling device, a third throttling device, a second evaporator, a second compressor, and a second condenser. The first heat exchanger, the second throttling device, the second evaporator, the second compressor, the second control valve, the second condenser, the first dehumidifying wheel, and the third throttling device are connected end to end in sequence. The first control valve is connected in parallel on both sides of the second throttling device. One end of the third control valve is located between the second control valve and the second compressor, and the other end is located between the second condenser and the first dehumidifying wheel. The fourth control valve is connected in parallel on both sides of the third throttling device. The first heat exchanger, the surface cooler, the deep dehumidification unit, the first dehumidification wheel, the air booster, the first evaporator, the second dehumidification wheel, the temperature-regulating heat exchanger, and the temperature-regulating heating device are sequentially arranged on the fresh air duct. The outlet of the fresh air duct is used to connect to the clean drying room. The water inlets of the surface cooler and the temperature-regulating heat exchanger are respectively connected to the water inlet pipe, and the water outlets of the surface cooler and the temperature-regulating heat exchanger are respectively connected to the water outlet pipe. The first condenser, the first compressor, and the secondary regenerator are also included. The heating device, the second condenser, the first-stage regeneration heating device, the second evaporator, and the regeneration fan are sequentially arranged on the regeneration air duct along the regeneration direction. The first compressor, the first condenser, the first throttling device, and the first evaporator are connected end to end in sequence. One end of the cooling air duct is connected to the fresh air duct and is located between the air pressurization device and the first evaporator. The other end is connected to the regeneration air duct through the second dehumidification wheel. The deep dehumidification unit is used to cool the fresh air passing through the surface cooler to a preset temperature and preset humidity.

2. The balanced heat distribution rotary dehumidification system as described in claim 1, characterized in that, The deep dehumidification unit includes a third condenser, a third compressor, a third evaporator, and a fourth throttling device. The third condenser, the third compressor, the third evaporator, and the fourth throttling device are connected end to end. The water inlet of the third condenser is connected to the water inlet pipe, and the water outlet of the third condenser is connected to the water outlet pipe. The third condenser is installed on the fresh air duct and located between the surface cooler and the first dehumidification wheel.

3. The balanced heat distribution rotary dehumidification system as described in claim 2, characterized in that, The coupled heat pump unit further includes a first gas-liquid separator, and the deep dehumidification unit further includes a second gas-liquid separator. The first gas-liquid separator is disposed between the second evaporator and the second compressor, and the second gas-liquid separator is disposed between the third compressor and the third evaporator.

4. The balanced heat distribution rotary dehumidification system as described in claim 2, characterized in that, A proportional regulating valve is installed at the water inlet of the surface cooler, the water inlet of the temperature regulating heat exchanger, and the water inlet of the third condenser.

5. The balanced heat distribution rotary dehumidification system as described in claim 1, characterized in that, It also includes a fresh air valve, a fresh air exhaust valve, and a regeneration exhaust valve. The fresh air valve is located at the inlet of the fresh air duct, the fresh air exhaust valve is located at the outlet of the fresh air duct, and the regeneration exhaust valve is located at the outlet of the regeneration duct.

6. The balanced heat distribution rotary dehumidification system as described in claim 5, characterized in that, A primary filter is provided between the fresh air valve and the first heat exchanger, and a medium-efficiency filter is provided between the temperature-regulating heat exchanger and the second dehumidifying wheel.

7. The balanced heat distribution rotary dehumidification system as described in claim 5, characterized in that, It also includes a return air duct connected to the fresh air duct, the return air duct being located between the first dehumidifying wheel and the air pressurization device, the end of the return air duct away from the fresh air duct being used to connect to the clean drying room, and a return air valve being provided on the return air duct.

8. A control method for a balanced heat distribution rotary dehumidification system, characterized in that, The control method is used to implement the operation control of the balanced heat distribution rotary dehumidification system as described in any one of claims 1-7, and the control method includes: Real-time acquisition of ambient fresh air dry-bulb temperature and ambient fresh air humidity; When the ambient fresh air dry bulb temperature is >9℃ or the ambient fresh air moisture content is >6.8g / kg, the balanced heat distribution wheel dehumidification system switches to summer operation mode, the coupled heat pump unit control switches to cooling mode, the coupled heat pump unit control processes the fresh air before entering the surface cooler to the first preset temperature and preset relative humidity value, and transfers the heat of the processing area of ​​the first dehumidification wheel to the second condenser to be released to the regeneration side for regeneration heating; When the ambient fresh air dry bulb temperature is ≤9℃ or the ambient fresh air moisture content is ≤6.8g / kg, the balanced heat distribution rotary dehumidification system switches to winter operation mode, and the coupled heat pump unit control switches to heating mode. The coupled heat pump unit processes the fresh air before it enters the surface cooler to a temperature greater than the second preset temperature, and recovers and transfers heat from the regeneration zone of the first dehumidification wheel to the processing zone of the first dehumidification wheel and the air inlet of the first dehumidification wheel in the regeneration zone for preheating.

9. The control method as described in claim 8, characterized in that, When the coupled heat pump unit is switched to cooling mode, the first heat exchanger enters evaporative cooling mode, the second evaporator stops running, the third control valve, the fourth control valve, and the second throttling device are closed, and the first control valve, the second control valve, the third throttling device, and the second compressor are opened. The third throttling device performs PID adjustment according to the control target of the first preset temperature and the preset relative humidity value. The second compressor transfers the heat from the processing area to the second condenser and releases it to the regeneration side for regeneration heating. The first-stage regeneration heating device is used for regeneration temperature compensation and performs PID adjustment according to the outlet air humidity after the first dehumidifier wheel. When the coupled heat pump unit is switched to heating mode, the surface cooler stops running, the first control valve, the second control valve, and the third throttling device are closed, and the third control valve, the fourth control valve, the second throttling device, and the second compressor are opened. The second throttling device performs PID adjustment according to the control target of the second preset temperature. Once the control target is reached, the current of the second compressor is checked to determine whether the upper limit of the corresponding operating condition has been reached. If there is a margin, the second control valve is opened to use the remaining heat for regeneration heating of the first dehumidifying wheel regeneration zone, and heat is collected from the second evaporator for heating the first heat exchanger and the second condenser. The first-stage regeneration heating device is used for regeneration temperature compensation and PID adjustment is performed according to the humidity of the air outlet after the first dehumidifying wheel.

10. The control method as described in claim 9, characterized in that, The first preset temperature is 17°C, the preset relative humidity is 95%, and the second preset temperature is 5°C.

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