Evaporative cooling device and method for heat-driven rotary dehumidification

Abstract

The invention relates to the technical field of refrigeration engineering, and discloses an evaporative cooling device and method for heat-driven rotary dehumidification. By utilizing low-grade heat energy to drive, the output of cold water and air with low moisture content below the dew point temperature of ambient air is achieved, thereby effectively improving the refrigeration capacity of the system, and the low-grade heat energy drive with lower temperature is achieved; by arranging multi-stage dehumidification, precooling, preheating and heat recovery and other links, the regeneration temperature and regeneration energy consumption are reduced, the energy utilization efficiency of the system is improved, and the energy efficiency of the system is increased; on the design principle of energy cascade utilization and recovery, the heat and mass transfer mechanism is utilized to organically combine the rotary dehumidification with the evaporative cooling system, thereby improving the thermal cycle process of the system, reducing the thermal loss of the system, and improving the thermal performance coefficient of the system; the thermal characteristics of the cold water and air output by the system are considered, and a better indoor air conditioning form is matched with them, thereby achieving better thermal comfort of the system.

Description

Technical Field

[0001] The invention relates to the technical field of refrigeration engineering, and in particular to an evaporative cooling device and method for heat energy driven rotary dehumidification. Background Art

[0002] The air conditioning system that combines rotary dehumidification with evaporative cooling can achieve independent control of temperature and humidity, so that the system can use low-grade thermal energy to drive dehumidification and high-temperature cold source to cool down. It can effectively solve the problems of energy waste, poor comfort, small dehumidification capacity and mold growth caused by condensed water precipitation caused by the combined treatment of heat and humidity in traditional cooling dehumidification methods; at the same time, because this type of system uses natural working fluid-water as refrigerant, it can also avoid the environmental problems of ozone layer depletion and greenhouse effect caused by the use of chlorofluorocarbons (CFC) in traditional air conditioning.

[0003] However, the existing air conditioning system combining rotary dehumidification with evaporative cooling has a high regeneration temperature (generally above 100°C) required for dehumidification of the system, because its dehumidification process is mostly a single-rotor single-stage dehumidification and a process of direct dehumidification of the treated air without pre-cooling, which makes it inconvenient to use many low-grade thermal energies (such as low-temperature heat sources such as solar energy and geothermal energy). Therefore, it is necessary to supplement with high-grade electric energy for heating to achieve a higher regeneration temperature; on the other hand, the high regeneration temperature makes the regeneration exhaust temperature also high, so the existing system has serious exhaust heat loss; furthermore, the existing system does not effectively recover the adsorption heat, which is also a reason for the high regeneration temperature of the system, and also causes high regeneration energy consumption; the existing system combining rotary dehumidification with evaporative cooling, its evaporative cooling subsystem is not a dew point evaporative cooling subsystem, but a conventional direct evaporative cooling device with heat recovery, so it is impossible to output cold water or cold air at a lower temperature, so the system sensible heat treatment capacity (cooling capacity) is insufficient. Finally, the existing system combining rotary dehumidification and evaporative cooling is only a simple, mechanical combination of the two, and is not designed from the perspective of the operating characteristics of the dehumidification wheel and evaporative cooling, energy cascade utilization and recovery. Therefore, the existing system has low energy efficiency and poor cooling capacity.

[0004] In summary, the existing system combining rotary dehumidification and evaporative cooling has the following shortcomings: (1) high regeneration temperature and high regeneration energy consumption; (2) serious system heat loss; (3) low system energy efficiency (low thermal performance coefficient) and obviously insufficient cooling capacity.

[0005] The prior art discloses a dehumidification wheel and heat pump coupled indirect evaporative cooling heat recovery fresh air air conditioner, belonging to the field of air conditioning equipment and energy-saving technology. The unit consists of a heat pump system, a dehumidification wheel, an indirect evaporative condenser, an exhaust fan and a fresh air fan. The condensation heat of the heat pump system is used to provide regeneration heat for the dehumidification wheel, while recovering the energy of the indoor exhaust air. After being organically combined with the indirect evaporative cooling technology, the efficiency of the heat pump system is improved while cooling and dehumidifying the fresh air, reducing the energy consumption of fresh air treatment and improving the indoor air quality. This prior art has the problems of direct dehumidification without pre-cooling of the treated air, high regeneration temperature required for dehumidification, and inconvenient use of low-grade thermal energy. Summary of the invention

[0006] The object of the present invention is to provide an evaporative cooling device and method for heat-driven rotary dehumidification, so as to achieve high energy efficiency, large cooling capacity, good thermal perfection and low-temperature driven refrigeration effect of the evaporative cooling device.

[0007] In order to achieve the above-mentioned purpose, the present invention provides an evaporative cooling device for heat energy driven rotary dehumidification, comprising a primary surface cooler, a primary dehumidification rotary dehumidification zone, a primary sensible heat exchanger, a secondary surface cooler, a secondary dehumidification rotary dehumidification zone, a secondary sensible heat exchanger, a second air heater, a secondary dehumidification rotary regeneration zone, a second regeneration exhaust fan, a first air heater, a primary dehumidification rotary regeneration zone, a first regeneration exhaust fan, a primary dehumidification rotary wheel, a secondary dehumidification rotary wheel, a third sensible heat exchanger, a third surface cooler, a filler, a countercurrent direct evaporative cooling tower, a nozzle, a treatment fan, a cooling water pump, a terminal heat exchange device, a hot water source, a hot water pump, an air heat source and a heating fan, wherein the nozzle is arranged on the inner upper wall of the countercurrent direct evaporative cooling tower, the filler is located below the nozzle, the air input end of the primary surface cooler is connected to the ambient air and the air output end is connected to the input end of the primary dehumidification rotary dehumidification zone, the water output end of the primary surface cooler is connected to the water input end of the secondary surface cooler, the primary dehumidification rotary wheel is connected to the water output end of the primary surface cooler, The output end of the rotary dehumidification zone is connected to the input end of the first-stage sensible heat exchanger, and the input end of the first-stage sensible heat exchanger is also connected to the ambient air. The output end of the first-stage sensible heat exchanger is respectively connected to the air input end of the second-stage surface cooler and the air input end of the first air heater. The air output end of the second-stage surface cooler is connected to the input end of the second-stage dehumidification rotary dehumidification zone and the water output end of the second-stage surface cooler is connected to the nozzle. The output end of the second-stage dehumidification rotary dehumidification zone is connected to the input end of the second-stage sensible heat exchanger, and the input end of the second-stage sensible heat exchanger is also connected to the ambient air. The output end of the second-stage sensible heat exchanger is respectively connected to the input end of the third-stage sensible heat exchanger and the air input end of the second air heater. The air output end of the second air heater is connected to the input end of the second-stage dehumidification rotary regeneration zone. When the heat source used is a hot water source or an air heat source, the output end of the second air heater is also connected to the input end of the first air heater.The output end of the secondary dehumidification wheel regeneration zone is connected to the external environment through the second regeneration exhaust fan, the air output end of the first air heater is connected to the input end of the primary dehumidification wheel regeneration zone, the output end of the primary dehumidification wheel regeneration zone is connected to the external environment through the first regeneration exhaust fan, the output end of the three-stage sensible heat exchanger is respectively connected to the external environment and the air input end of the three-stage surface cooler, the air output end of the three-stage surface cooler is connected to the air-conditioned room through the fresh air regulating valve and the fresh air fan, the air output end of the three-stage surface cooler is also connected to the air input end of the countercurrent direct evaporative cooling tower, and the water output end of the three-stage surface cooler is connected to a The water input end of the first-stage condenser is connected, the air output end of the counter-flow direct evaporative cooling tower is connected to the air input end of the third-stage sensible heat exchanger through a processing fan, and the water output end of the counter-flow direct evaporative cooling tower is connected to the water input end of the third-stage condenser through a cooling water pump, the input end of the terminal heat exchange device is connected to the water output end of the counter-flow direct evaporative cooling tower through a cooling water pump, and the output end of the terminal heat exchange device is connected to the water input end of the first-stage condenser, the hot water source is connected to the water input end of the second air heater through a hot water supply pump, and the air heat source is connected to the air input end of the second air heater through a heating fan. ;

[0008] Preferably, it further comprises a fresh air fan and a fresh air regulating valve, and the air output end of the three-stage surface cooler is also connected to the air-conditioned room through the fresh air regulating valve and the fresh air fan.

[0009] Preferably, it also includes a terminal water volume regulating valve and a pre-cooling water volume regulating valve. The cold water output from the water output end of the countercurrent direct evaporative cooling tower passes through the cooling water pump and then passes through the pre-cooling water volume regulating valve and the terminal water volume regulating valve and input into the terminal heat exchange equipment and the three-stage surface cooler.

[0010] The present invention also provides an evaporative cooling method for heat-driven rotary dehumidification, which is applied to the evaporative cooling device for heat-driven rotary dehumidification as described in the above-mentioned embodiment of the invention, and includes an air processing method, an air regeneration method, a cold water transportation method and a heating method, wherein the heating method includes a low-grade heat source heating method when the heating medium is hot water and a low-grade heat source heating method when the heating medium is high-temperature air, and the specific steps are as follows:

[0011] The air treatment method is as follows: the high-temperature and high-humidity ambient air is dry-cooled and cooled by the first-stage surface cooler, and then sent to the first-stage dehumidification wheel dehumidification zone. After drying and dehumidification, it is sent to the first-stage sensible heat exchanger to exchange sensible heat with the air from the ambient temperature with a lower temperature, and then sent to the second-stage surface cooler. After pre-cooling and cooling, it is sent to the second-stage dehumidification wheel dehumidification zone, and then sent to the second-stage sensible heat exchanger after heating, and then exchange sensible heat with the ambient air from the lower temperature with a lower temperature, and then sent to the third-stage sensible heat exchanger to exchange heat with the low-temperature exhaust air from the countercurrent direct evaporative cooling tower, and then sent to the third-stage surface cooler, and then exchange heat with the output cold water from the countercurrent direct evaporative cooling tower and then sent to the air-conditioned room and the countercurrent direct evaporative cooling tower, and finally sent to the third-stage sensible heat exchanger to be discharged after heating.

[0012] The regeneration air method is as follows: the ambient air with a relatively low temperature is first sent to the secondary sensible heat exchanger, and after sensible heat exchange with the treated air with a relatively high temperature, it is further heated by the second air heater to the regeneration temperature required for dehumidification, and then sent to the regeneration area of ​​the secondary dehumidification wheel, and then driven by the second regeneration exhaust fan to be discharged; the ambient air with a relatively low temperature is first heated by the primary sensible heat exchanger to increase its temperature, and then heated by the first air heater to the regeneration air that meets the dehumidification requirements, and then sent to the regeneration area of ​​the primary dehumidification wheel, and finally driven by the first regeneration exhaust fan to be discharged;

[0013] The cold water delivery method is as follows: the low-temperature cold water prepared in the countercurrent direct evaporative cooling tower is respectively delivered to the three-stage surface cooler and the terminal heat exchange equipment under the drive of the cold water supply pump, and is delivered to the terminal heat exchange equipment and mixed with the return water of the three-stage surface cooler after the temperature rises, and then delivered to the first-stage surface cooler to exchange heat with the higher temperature air from the environment, and then used as the supply water of the second-stage surface cooler to exchange heat with the higher temperature process air, further increase the temperature, and finally sprayed on the filler surface through the nozzle, and countercurrent heat and mass exchange is carried out with the low-temperature and low-humidity process air, and the temperature is reduced to the low-temperature supply water close to the dew point temperature;

[0014] When the heating medium is hot water, the low-grade heat source heating method is as follows: the hot water from the hot water source is driven by a hot water pump and sent to the second air heater, and then sent to the first air heater after heat exchange with the regeneration air at a lower temperature, and then sent to the first air heater after heat exchange with the regeneration air at a lower temperature, and then returned to the hot water source after being converted into return water at a lower temperature;

[0015] When the heating medium is high-temperature air, the low-grade heat source heating method is as follows: the high-temperature air coming out of the air heat source is driven by the heating fan and sent to the second air heater to exchange heat with the regeneration air with a lower temperature, and then sent to the first air heater to exchange heat with the regeneration air with a lower temperature and then discharged.

[0016] Compared with the prior art, the present invention has the following beneficial effects:

[0017] By utilizing low-grade thermal energy at a lower temperature to drive, the output of cold water and air with low moisture content below the dew point temperature of the ambient air can be achieved, which effectively improves the cooling capacity of the system. The low-grade thermal energy at a lower temperature drives the full utilization of most common low-temperature thermal energy such as solar energy and geothermal energy. By setting up multi-stage dehumidification, precooling, preheating and heat recovery, the regeneration temperature and regeneration energy consumption are reduced, the energy utilization efficiency of the system is improved, and the energy efficiency of the system is increased. Based on the design principle of energy cascade utilization and recovery, the heat and mass transfer mechanism is used to organically combine the rotary dehumidification and evaporative cooling system, which improves the thermal cycle process of the system, reduces the thermal loss of the system, and improves the thermal performance coefficient of the system. Taking into account the thermal characteristics of the cold water and air output by the system, a better indoor air conditioning form is matched with it to achieve better thermal comfort of the system. BRIEF DESCRIPTION OF THE DRAWINGS

[0018] Figure 1 is a schematic structural diagram of an evaporative cooling device for heat energy driven rotary dehumidification according to an embodiment of the present invention;

[0019] Figure 2 Enthalpy-humidity diagram of processed air of the evaporative cooling device with heat-driven rotary dehumidification according to an embodiment of the present invention;

[0020] Figure 3 is a schematic diagram of a water supply method when the low-grade heat source is hot water according to an embodiment of the present invention;

[0021] Figure 4 It is a schematic diagram of the air supply method when the low-grade heat source is air in an embodiment of the present invention.

[0022] In the figure, 1, primary surface cooler; 2, primary dehumidification wheel dehumidification zone; 3, primary sensible heat exchanger; 4, secondary surface cooler; 5, secondary dehumidification wheel dehumidification zone; 6, secondary sensible heat exchanger; 7, second air heater; 8, secondary dehumidification wheel regeneration zone; 9, second regeneration exhaust fan; 10, first air heater; 11, primary dehumidification wheel regeneration zone; 12, first regeneration exhaust fan; 13, primary dehumidification wheel; 14, secondary dehumidification wheel; 15. Three-stage sensible heat exchanger; 16. Three-stage surface cooler; 17. Filler; 18. Countercurrent direct evaporative cooling tower; 19. Nozzle; 20. Processing fan; 21. Cooling water pump; 22. Terminal water volume regulating valve; 23. Terminal heat exchange equipment; 24. Air-conditioned room; 25. Fresh air fan; 26. Fresh air regulating valve; 27. Pre-cooling water volume regulating valve; 28. Hot water source; 29. ​​Hot water pump; 30. Air heat source; 31. Heating fan. DETAILED DESCRIPTION

[0023] The specific implementation of the present invention is further described in detail below in conjunction with the accompanying drawings and examples. The following examples are used to illustrate the present invention, but are not intended to limit the scope of the present invention.

[0024] In the description of the present invention, it should be noted that the terms "center", "longitudinal", "lateral", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside" and the like indicate positions or positional relationships based on the positions or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as limiting the present invention. In addition, the terms "first", "second", and "third" are used for descriptive purposes only and cannot be understood as indicating or implying relative importance.

[0025] In the description of the present invention, it should be noted that, unless otherwise clearly specified and limited, the terms "installed", "connected", and "connected" should be understood in a broad sense, for example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be a direct connection, or it can be indirectly connected through an intermediate medium, or it can be the internal communication of two components. For ordinary technicians in this field, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.

[0026] Furthermore, in the description of the present invention, unless otherwise specified, “plurality” means two or more.

[0027] Embodiment 1

[0028] like Figure 1As shown, an evaporative cooling device for heat energy driven rotary dehumidification according to a preferred embodiment of the present invention comprises a primary surface cooler 1, a primary dehumidification rotary dehumidification zone 2, a primary sensible heat exchanger 3, a secondary surface cooler 4, a secondary dehumidification rotary dehumidification zone 5, a secondary sensible heat exchanger 6, a second air heater 7, a secondary dehumidification rotary regeneration zone 8, a second regeneration exhaust fan 9, a first air heater 10, a primary dehumidification rotary regeneration zone 11, a first regeneration exhaust fan 12, a primary dehumidification rotary wheel 13, a secondary dehumidification rotary wheel 14, a third sensible heat exchanger 15, a third surface cooler 16, a secondary dehumidification rotary dehumidification zone 17, a secondary dehumidification rotary wheel 18, a third surface cooler 19, a secondary dehumidification rotary wheel 20, a third surface cooler 21, a secondary dehumidification rotary wheel 22, a third surface cooler 23, a secondary dehumidification rotary wheel 24, a third surface cooler 25, a secondary dehumidification rotary wheel 26, a third surface cooler 27, a secondary dehumidification rotary wheel 28, a third surface cooler 29, a secondary dehumidification rotary wheel 30, a third surface cooler 31, a secondary dehumidification rotary wheel 32, a third surface cooler 33, a secondary dehumidification rotary wheel 34, a third surface cooler 35, a secondary dehumidification rotary wheel 36, a third surface cooler 37, a secondary dehumidification rotary wheel 38, a third surface cooler 39, a secondary dehumidification rotary wheel 40, a secondary dehumidification rotary wheel 41, a Cooler 16, filler 17, countercurrent direct evaporative cooling tower 18, nozzle 19, treatment fan 20, cold water pump 21, terminal heat exchange equipment 23, the nozzle 19 is arranged on the inner upper wall of the countercurrent direct evaporative cooling tower 18, the filler 17 is located below the nozzle 19, the air input end of the first-stage cooler 1 is connected with the ambient air and the air output end is connected with the input end of the first-stage dehumidification wheel dehumidification zone 2, the water output end of the first-stage cooler 1 is connected with the water input end of the second-stage cooler 4, the first-stage dehumidification wheel The output end of the dehumidification zone 2 is connected to the input end of the primary sensible heat exchanger 3, and the input end of the primary sensible heat exchanger 3 is also connected to the ambient air. The output end of the primary sensible heat exchanger 3 is respectively connected to the air input end of the secondary surface cooler 4 and the air input end of the first air heater 10. The air output end of the secondary surface cooler 4 is connected to the input end of the secondary dehumidification rotor dehumidification zone 5 and the water output end of the secondary surface cooler 4 is connected to the nozzle 19. The output end of the secondary dehumidification rotor dehumidification zone 5 is connected to the The input end of the secondary sensible heat exchanger 6 is connected, and the input end of the secondary sensible heat exchanger 6 is also connected to the ambient air. The output end of the secondary sensible heat exchanger 6 is respectively connected to the input end of the tertiary sensible heat exchanger 15 and the air input end of the second air heater 7. The air output end of the second air heater 7 is connected to the input end of the secondary dehumidification wheel regeneration zone 8. When the heat source used is the hot water source 28 or the air heat source 30, the output end of the second air heater 7 is also connected to the input end of the first air heater 10;The output end of the secondary dehumidification wheel regeneration zone 8 is communicated with the external environment through the second regeneration exhaust fan 9, the air output end of the first air heater 10 is communicated with the input end of the primary dehumidification wheel regeneration zone 11, the output end of the primary dehumidification wheel regeneration zone 11 is communicated with the external environment through the first regeneration exhaust fan 12, the output end of the three-stage sensible heat exchanger 15 is communicated with the external environment and the air input end of the three-stage surface cooler 16 respectively, the air output end of the three-stage surface cooler 16 is communicated with the air-conditioned room 24 through the fresh air regulating valve 26 and the fresh air fan 25, the air output end of the three-stage surface cooler 16 is also communicated with the air input end of the countercurrent direct evaporative cooling tower 18, and the water output end of the three-stage surface cooler 16 is communicated with the first surface cooler 16. The air output end of the counter-flow direct evaporative cooling tower 18 is connected to the air input end of the three-stage sensible heat exchanger 15 through the processing fan 20, and the water output end of the counter-flow direct evaporative cooling tower 18 is connected to the water input end of the three-stage surface cooler 16 through the cooling water pump 21. The input end of the terminal heat exchange device 23 is connected to the water output end of the counter-flow direct evaporative cooling tower 18 through the cooling water pump 21, and the output end of the terminal heat exchange device 23 is connected to the water input end of the first-stage surface cooler 1. The hot water source 28 is connected to the water input end of the second air heater 7 through the hot water pump 29, and the air heat source 30 is connected to the air input end of the second air heater 7 through the heating fan 31. ;

[0029] This embodiment further includes a hot water source 28 and a hot water supply pump 29 . The hot water source 28 is connected to the input end of the second air heater 7 through the hot water supply pump 29 .

[0030] This embodiment further includes a fresh air fan 25 and a fresh air regulating valve 26 , and the output end of the three-stage surface cooler 16 is also connected to the air-conditioned room 24 through the fresh air regulating valve 26 and the fresh air fan 25 .

[0031] This embodiment also includes a terminal water flow regulating valve 22 and a pre-cooling water flow regulating valve 27. The cold water output from the output end of the countercurrent direct evaporative cooling tower 18 passes through the cold water supply pump 21 and then passes through the pre-cooling water flow regulating valve 27 and the terminal water flow regulating valve 22 and input into the three-stage surface cooler 16 and the terminal heat exchange equipment 23.

[0032] This embodiment further includes an air heat source 30 and a heating fan 31 , and the air heat source 30 is connected to the input end of the second air heater 7 through the heating fan 31 .

[0033] By using low-grade thermal energy at a lower temperature to drive, the output of cold water and air with low humidity content below the dew point temperature of the ambient air can be achieved, which effectively improves the cooling capacity of the system. Low-grade thermal energy at a lower temperature drives the full utilization of most common low-temperature thermal energy such as solar energy and geothermal energy. By setting up multi-stage dehumidification, precooling, preheating and heat recovery, the regeneration temperature and regeneration energy consumption of the existing system are greatly reduced, the energy utilization efficiency of the system is improved, and the energy efficiency of the system is increased. Based on the design principle of energy cascade utilization and recovery, the heat and mass transfer mechanism is used to organically combine the rotary dehumidification and evaporative cooling system, improve the thermal cycle process of the system, reduce the thermal loss of the system, and improve the thermal performance coefficient (energy efficiency) of the system. Taking into account the thermal characteristics of the cold water and air output by the system, the better indoor air conditioning form is matched with it to achieve better thermal comfort of the system.

[0034] Embodiment 2

[0035] like Figure 1 As shown, the present invention also provides an evaporative cooling system for thermal energy driven rotary dehumidification, which is composed of a rotary dehumidification subsystem, a dew point evaporative cooling subsystem, a user terminal subsystem and a low-grade heat source heating system;

[0036] The rotary dehumidification subsystem is mainly composed of a primary surface cooler 1, a primary dehumidification rotary wheel 13, a first air heater 10, a primary sensible heat exchanger 3, a secondary surface cooler 4, a secondary dehumidification rotary wheel 14, a second air heater 7, a secondary sensible heat exchanger 6, a first regeneration exhaust fan 12 and a second regeneration exhaust fan 9;

[0037] The primary dehumidification wheel 13 is divided into two functional areas, namely the primary dehumidification wheel dehumidification area 2 and the primary dehumidification wheel regeneration area 11;

[0038] The secondary dehumidification wheel 14 is also divided into two functional areas, namely the secondary dehumidification wheel dehumidification area 5 and the secondary dehumidification wheel regeneration area 8;

[0039] The dew point evaporative cooling subsystem is mainly composed of a three-stage sensible heat exchanger 15, a three-stage surface cooler 16, a counter-current direct evaporative cooling tower 18, a processing fan 20, a cooling water pump 21 and a pre-cooling water regulating valve 27;

[0040] The counter-current direct evaporative cooling tower 18 is mainly composed of fillers 17, nozzles 19 and other components;

[0041] The user terminal subsystem is mainly composed of terminal heat exchange equipment 23, terminal water flow regulating valve 22, fresh air regulating valve 26 and fresh air fan 25.

[0042] The terminal heat exchange device 23 may be a heat exchange device such as a radiation top plate, a capillary network or a fan coil unit.

[0043] The low-grade heat source heating subsystem can be divided into different forms according to the output medium. When hot water is used as the output medium, the low-grade heat source heating subsystem is mainly composed of hot water source, hot water pump, water pipe and other accessories. At this time, the first air heater and the second air heater should be air-water heat exchangers, preferably surface coolers; when high-temperature air is used as the output medium, the low-grade heat source heating subsystem is mainly composed of air heat source, heating fan, air duct and other accessories. At this time, the first air heater and the second air heater should be air-air heat exchangers, preferably cross-flow heat exchangers. The hot water source can be low-grade hot water such as solar water source, geothermal water source and industrial waste hot water. The air heat source can be industrial waste heat such as high-temperature exhaust gas from thermal power plants and industrial high-temperature flue gas.

[0044] The relationship between the subsystems that constitute the main system is as follows: (1) The rotary dehumidification subsystem provides the dew-point evaporative cooling subsystem with low-humidity treated air and high-temperature return water to increase the cooling efficiency (heat exchange efficiency) of the dew-point evaporative cooling subsystem and reduce the outlet water temperature and supply air temperature of the dew-point evaporative cooling subsystem; (2) The dew-point evaporative cooling subsystem provides low-temperature cold water and low-temperature and low-humidity fresh air to the user terminal subsystem, of which the low-temperature cold water bears most of the indoor sensible heat load, and the low-temperature and low-humidity fresh air bears all the indoor wet load and a small part of the sensible heat load, so as to realize independent control of the temperature and humidity of the air-conditioned room and achieve a comfortable and energy-saving air-conditioning effect; (3) The lower temperature return water of the user terminal subsystem is again provided to the rotary dehumidification subsystem for pre-cooling and cooling. , in order to eliminate the adverse effect of adsorption heat generated by the rotary dehumidification process on the dehumidification efficiency; (4) The low-grade heat source heating subsystem provides low-grade high-temperature heat energy to the rotary dehumidification subsystem to ensure that the rotary dehumidification subsystem meets the dehumidification drive requirements; (5) It is worth noting that in terms of water supply, the return water of the user terminal subsystem should be supplied to the first-level surface cooler of the rotary dehumidification subsystem first, and then the return water of the first-level surface cooler is used as the water supply of the second-level surface cooler, and finally the return water of the second-level surface cooler is used as the water supply of the dew point evaporative cooling subsystem; (6) The heat medium supply method of the low-grade heat source heating subsystem should also adopt a similar series supply method as mentioned above, that is, the second air heater of the rotary dehumidification subsystem is satisfied first, and then the first air heater is satisfied. The above two supply measures ensure that the system meets the principle of cascade utilization of energy, thereby improving the energy utilization efficiency of the system.

[0045] Embodiment 3

[0046] The present invention also provides an evaporative cooling method for heat-driven rotary dehumidification, the evaporative cooling method comprising an air processing method, an air regeneration method, a cold water delivery method and a heating method, wherein the heating method comprises a low-grade heat source heating method when the heating medium is hot water and a low-grade heat source heating method when the heating medium is high-temperature air, and the specific steps are as follows:

[0047] like Figure 1 , Figure 2 As shown, the air treatment method is as follows: the high-temperature and high-humidity ambient air a is firstly cooled to state point b by dry cooling in the primary surface cooler 1, and then sent to the primary dehumidification wheel dehumidification zone 2. After drying and dehumidification, it is dehumidified to a state point c with a higher temperature approximately at isenthalpy, and then sent to the primary sensible heat exchanger 3 to perform sensible heat exchange with the air p from the ambient temperature with a lower temperature, and the temperature is reduced to state point d. At this time, due to the limited primary dehumidification capacity and insufficient dehumidification capacity, the treated air d is further sent to the secondary surface cooler 4 to be pre-cooled to state point e, and then sent to the secondary dehumidification wheel dehumidification zone 5 again. After being dried by the adsorbent, it is heated to state point f approximately at isenthalpy, and then sent to the secondary sensible heat exchanger 6 to perform sensible heat exchange with the ambient air l from the lower temperature, and the temperature is reduced to state point g. At this time, the low-humidity air g is the output air of the rotary dehumidification subsystem. Subsequently, it is sent to the three-stage sensible heat exchanger 15 to exchange heat with the low-temperature exhaust air j from the countercurrent direct evaporative cooling tower 18, and is cooled to the state point h. Then, it is sent to the three-stage surface cooler 16 to exchange heat with the output cold water t from the countercurrent direct evaporative cooling tower 18, and is cooled to the state point i close to its dew point Li. It is then divided into two streams, one of which is sent to the air-conditioned room 24 as indoor dry cold fresh air i2, and the other (accounting for the majority) of low-temperature and low-humidity treated air i1 is sent to the countercurrent direct evaporative cooling tower 18 to exchange heat and mass with the return water x with a higher temperature from the rotary dehumidification subsystem in a countercurrent manner, and becomes the exhaust air state point j close to saturation. Finally, it is sent to the three-stage sensible heat exchanger 15 to exchange sensible heat with the supply air g with a higher temperature from the rotary dehumidification subsystem, and is discharged from the system as exhaust gas after the temperature rises to the state point k.

[0048] like Figure 1 As shown, the regeneration air method is as follows: the ambient air l with a relatively low temperature is first sent to the secondary sensible heat exchanger 6, and performs sensible heat exchange with the processed air f with a relatively high temperature, and the temperature rises to the state point m, and then is further heated by the second air heater 7 to the regeneration temperature n required for dehumidification, and then is sent to the secondary dehumidification wheel regeneration zone 8, and the saturated desiccant is desorbed and regenerated to become the state point o, and is driven by the second regeneration exhaust fan 9 to be discharged from the system; similarly, the ambient air p with a relatively low temperature is first heat-exchanged by the primary sensible heat exchanger 3, and the temperature rises to the state point q, and then is heated by the first air heater 10 to the regeneration air r that meets the dehumidification requirements, and then is sent to the primary dehumidification wheel regeneration zone 11, and the saturated adsorbent is desorbed and dried to become the regeneration exhaust air s, and finally is driven by the first regeneration exhaust fan 12 to be discharged from the system;

[0049] The system's low-temperature cold water transportation method is as follows: the low-temperature cold water t prepared by the system in the countercurrent direct evaporative cooling tower 18 is divided into two streams under the drive of the cold water supply pump 21. One stream is used as the low-temperature cold water t2 for cooling the dew point evaporative cooling subsystem itself (the cold water t2 is sent to the three-stage surface cooler 16 to exchange heat with the high-temperature treated air h, and the temperature rises to the return water y), and the other stream is used as the water supply t1 of the user terminal subsystem (its flow rate is adjusted by the terminal water volume regulating valve 22 according to the load size of the air-conditioned room 24), and is heated by the terminal heat exchange equipment 23 to rise to the terminal return water u, and then mixed with the return water y of the three-stage surface cooler 16 to become return water v, and then sent to the first-stage surface cooler 1 of the rotary dehumidification subsystem, and heat-exchanged with the higher-temperature air a from the environment to become return water w, and then used as the water supply of the second-stage surface cooler 4 to exchange heat with the high-temperature treated air d, and further rise to the return water x. Finally, the return water x is used as the return water of the dew point evaporative cooling subsystem, and is sprayed on the surface of the filler 17 through the nozzle 19 of the countercurrent direct evaporative cooling tower 18, and performs countercurrent heat and mass exchange with the low-temperature and low-humidity treated air i1, and is cooled to a low-temperature supply water t close to the dew point temperature Li, and finally sent to the user terminal subsystem;

[0050] like Figure 3 As shown, when the heating medium is hot water, the low-grade heat source heating method is as follows: the hot water from the hot water source 28 is driven by the hot water pump 29, sent to the second air heater 7, and heat-exchanged with the regeneration air m with a lower temperature from the rotary dehumidification subsystem to become return water B, and then sent to the first air heater 10, and heat-exchanged with the regeneration air q with a lower temperature to become return water C with a lower temperature, and finally returned to the hot water source 28. At this time, the second air heater 7 and the first air heater 10 are air-water heat exchangers, and it is recommended to use a surface cooler; the hot water source 28 can use low-grade hot water such as solar hot water, geothermal hot water, and industrial waste hot water;

[0051] like Figure 4 As shown, when the heating medium is high-temperature air, the low-grade heat source heating method is as follows: the high-temperature air D from the air heat source 30 is driven by the heating fan 31 and sent to the second air heater 7, and heat-exchanged with the regeneration air m with a lower temperature from the rotary dehumidification subsystem to become the return air E, and then sent to the first air heater 10, and heat-exchanged with the regeneration air q with a lower temperature to become the return air F with a lower temperature, and finally discharged from the system. At this time, the second air heater 7 and the first air heater 10 are air-to-air heat exchangers, and it is recommended to use a cross-flow heat exchanger; the air heat source 30 can use industrial waste heat such as high-temperature exhaust gas from thermal power plants and industrial high-temperature smoke exhaust.

[0052] The dehumidification process of the dehumidification wheel is an approximately isenthalpic dehumidification process. Therefore, increasing precooling does not increase the cooling capacity of the system. On the contrary, due to the existence of precooling, the temperature of the processed air entering the dehumidification wheel is reduced, thereby reducing the desiccant temperature in the dehumidification zone and the water vapor partial pressure on the desiccant surface, thereby increasing the water vapor partial pressure difference between the processed air and the desiccant surface of the desiccant wheel (dehumidification driving force). The final result is an increase in the dehumidification efficiency.

[0053] The rotary dehumidification subsystem is equipped with a primary sensible heat exchanger and a secondary sensible heat exchanger, which have the following functions: on the one hand, precooling the process air to increase the dehumidification efficiency of the dehumidification wheel, and on the other hand, preheating the regeneration air to reduce the heating energy consumption of the regeneration air. The function of the third-stage sensible heat exchanger in the dew point evaporative cooling subsystem is to recover the exhaust cooling capacity of the counterflow evaporative cooling tower to reduce the cooling capacity of the process air.

[0054] In the dew-point evaporative cooling subsystem, the low-temperature cold water generated by itself is first used to cool the treated air, and then sent to the countercurrent direct evaporative cooling tower. This thermal treatment process can achieve low-temperature cold water t close to the dew point temperature of the treated air i. Since the ambient air is first dehumidified and then evaporated for heat exchange, the temperature of the low-temperature cold water t output by the system can be lower than the dew point temperature of the environment a.

[0055] Increasing the return water temperature of the evaporative cooling tower can increase the heat transfer and mass transfer driving force between hot water and air, thereby improving the heat exchange efficiency of the evaporative cooling tower. Accordingly, the return water v from the user end first precools the treated air of the rotary dehumidification subsystem, and finally the return water x after temperature rise is sent to the countercurrent direct evaporative cooling tower. This measure increases the heat exchange efficiency of the cooling tower on the one hand, and on the other hand, the existence of precooling also improves the dehumidification efficiency of the rotary dehumidification subsystem.

[0056] Since the entire system outputs low-temperature cold water and low-temperature, low-humidity air, and the low-temperature cold water temperature is usually set above the indoor ambient dew point temperature, the cold water only needs to bear most of the indoor sensible heat load, while a small part of the sensible heat load and all the wet load are borne by the low-temperature, low-humidity fresh air. This indoor air conditioning method has no condensation, the temperature and humidity are evenly distributed, and the indoor thermal comfort is good.

[0057] During the pre-cooling, preheating and heat recovery process, the principle of cascade utilization and recovery of energy is followed, and the simple and mechanical combination of the existing rotary dehumidification and evaporative cooling system is abandoned. The system is designed from the heat and mass transfer mechanism of dehumidification and evaporation, realizing the organic combination of rotary dehumidification and evaporative cooling system, solving the defects of low energy efficiency and insufficient cooling capacity of the current systems.

[0058] In summary, the embodiments of the present invention provide an evaporative cooling device and method for heat-driven rotary dehumidification, which achieves the output of cold water and air with low moisture content below the dew point temperature of ambient air by utilizing low-grade heat energy at a lower temperature, thereby effectively improving the refrigeration capacity of the system. The low-grade heat energy at a lower temperature makes it possible to fully utilize most common low-temperature thermal energy such as solar energy and geothermal energy. By setting up multi-stage dehumidification, precooling, preheating and heat recovery links, the regeneration temperature and regeneration energy consumption are reduced, the energy utilization efficiency of the system is improved, and the energy efficiency of the system is increased. Based on the design principle of energy cascade utilization and recovery, the heat and mass transfer mechanism is utilized to organically combine the rotary dehumidification with the evaporative cooling system, thereby improving the thermal cycle process of the system, reducing the thermal loss of the system, and improving the thermal performance coefficient of the system. The thermal characteristics of the cold water and air output by the system are taken into consideration, and a better indoor air conditioning form is matched with it to achieve better thermal comfort of the system.

[0059] The above is only a preferred embodiment of the present invention. It should be pointed out that for ordinary technicians in this technical field, several improvements and substitutions can be made without departing from the technical principles of the present invention. These improvements and substitutions should also be regarded as the scope of protection of the present invention.

Claims

1. An evaporative cooling device for heat-driven rotary dehumidification, characterized in that: The invention comprises a first-stage surface cooler (1), a first-stage dehumidification wheel dehumidification zone (2), a first-stage sensible heat exchanger (3), a second-stage surface cooler (4), a second-stage dehumidification wheel dehumidification zone (5), a second-stage sensible heat exchanger (6), a second air heater (7), a second-stage dehumidification wheel regeneration zone (8), a second regeneration exhaust fan (9), a first air heater (10), a first-stage dehumidification wheel regeneration zone (11), a first regeneration exhaust fan (12), a first-stage dehumidification wheel (13), a second-stage dehumidification wheel (14), a third-stage sensible heat exchanger (15), a third-stage surface cooler (16), a filler (17), a countercurrent direct evaporative cooling tower (18), and a heat exchanger. ), a nozzle (19), a treatment fan (20), a cooling water pump (21), a terminal heat exchange device (23), a hot water source (28), a hot water pump (29), an air heat source (30) and a heating fan (31), wherein the nozzle (19) is arranged on the inner upper wall of the countercurrent direct evaporative cooling tower (18), the filler (17) is located below the nozzle (19), the air input end of the first-stage surface cooler (1) is connected to the ambient air and the air output end is connected to the input end of the first-stage dehumidification wheel dehumidification zone (2), the water output end of the first-stage surface cooler (1) is connected to the water input end of the second-stage surface cooler (4) The output end of the first dehumidification wheel dehumidification zone (2) is connected to the input end of the first sensible heat exchanger (3), and the input end of the first sensible heat exchanger (3) is also connected to the ambient air. The output end of the first sensible heat exchanger (3) is respectively connected to the air input end of the second surface cooler (4) and the air input end of the first air heater (10). The air output end of the second surface cooler (4) is connected to the input end of the second dehumidification wheel dehumidification zone (5), and the water output end of the second surface cooler (4) is connected to the nozzle (19). The output end of the second dehumidification wheel dehumidification zone (5) is connected to the input end of the second dehumidification wheel dehumidification zone (5). The output end is connected to the input end of the secondary sensible heat exchanger (6), and the input end of the secondary sensible heat exchanger (6) is also connected to the ambient air. The output end of the secondary sensible heat exchanger (6) is respectively connected to the input end of the tertiary sensible heat exchanger (15) and the air input end of the second air heater (7). The air output end of the second air heater (7) is connected to the input end of the secondary dehumidification wheel regeneration zone (8). When the heat source used is a hot water source (28) or an air heat source (30), the output end of the second air heater (7) is also connected to the input end of the first air heater (10);The output end of the secondary dehumidification wheel regeneration zone (8) is in communication with the external environment via the second regeneration exhaust fan (9); the air output end of the first air heater (10) is in communication with the input end of the primary dehumidification wheel regeneration zone (11); the output end of the primary dehumidification wheel regeneration zone (11) is in communication with the external environment via the first regeneration exhaust fan (12); the output end of the third-stage sensible heat exchanger (15) is in communication with the external environment and the air input end of the third-stage surface cooler (16), respectively; the air output end of the third-stage surface cooler (16) is in communication with the air-conditioned room (24) via the fresh air regulating valve (26) and the fresh air fan (25); the air output end of the third-stage surface cooler (16) is also in communication with the air input end of the countercurrent direct evaporative cooling tower (18); the water output end of the third-stage surface cooler (16) is in communication with the first-stage surface cooler ( 1), the air output end of the counter-flow direct evaporative cooling tower (18) is connected to the air input end of the three-stage sensible heat exchanger (15) through the processing fan (20), and the water output end of the counter-flow direct evaporative cooling tower (18) is connected to the water input end of the three-stage surface cooler (16) through the cooling water pump (21), the input end of the terminal heat exchange device (23) is connected to the water output end of the counter-flow direct evaporative cooling tower (18) through the cooling water pump (21), and the output end of the terminal heat exchange device (23) is connected to the water input end of the first-stage surface cooler (1), the hot water source (28) is connected to the water input end of the second air heater (7) through the hot water pump (29), and the air heat source (30) is connected to the air input end of the second air heater (7) through the heating fan (31). ; 2. The evaporative cooling device for heat-driven rotary dehumidification according to claim 1, characterized in that: It also includes a fresh air fan (25) and a fresh air regulating valve (26), and the air output end of the three-stage surface cooler (16) is also connected to the air-conditioned room (24) through the fresh air regulating valve (26) and the fresh air fan (25) in sequence.

3. The evaporative cooling device for heat-driven rotary dehumidification according to claim 1, characterized in that: It also includes a terminal water volume regulating valve (22) and a pre-cooling water volume regulating valve (27). The cold water output from the water output end of the counter-current direct evaporative cooling tower (18) passes through a cold water supply pump (21) and then passes through the pre-cooling water volume regulating valve (27) to be input into the three-stage surface cooler (16) and passes through the terminal water volume regulating valve (22) to be input into the terminal heat exchange device (23).

4. An evaporative cooling method for heat-driven rotary dehumidification, characterized in that: The evaporative cooling method is applied to the evaporative cooling device of the heat energy driven rotary dehumidification as claimed in any one of claims 1 to 3, including an air processing method, an air regeneration method, a cold water delivery method and a heating method, wherein the heating method includes a low-grade heat source heating method when the heating medium is hot water and a low-grade heat source heating method when the heating medium is high-temperature air, and the specific steps are as follows: The air treatment method is as follows: the high-temperature and high-humidity ambient air is dry-cooled and cooled by the first-stage surface cooler (1) and then sent to the first-stage dehumidification wheel dehumidification zone (2). After being dried and dehumidified, the air is sent to the first-stage sensible heat exchanger (3) to exchange sensible heat with the air from the ambient temperature with a lower temperature and then sent to the second-stage surface cooler (4). After pre-cooling and cooling, the air is sent to the second-stage dehumidification wheel dehumidification zone (5). After being heated, the air is sent to the second-stage sensible heat exchanger (6) to exchange sensible heat with the air from the ambient temperature with a lower temperature. The air is cooled by sensible heat exchange and sent to the three-stage sensible heat exchanger (15), and is cooled by heat exchange with the low-temperature exhaust air from the countercurrent direct evaporative cooling tower (18), and is then sent to the three-stage surface cooler (16), and is cooled by heat exchange with the output cold water from the countercurrent direct evaporative cooling tower (18), and is then sent to the air-conditioned room (24) and the countercurrent direct evaporative cooling tower (18), and finally sent to the three-stage sensible heat exchanger (15), and is discharged after being heated; The regeneration air method is as follows: the ambient air with a relatively low temperature is first sent to the secondary sensible heat exchanger (6), and after sensible heat exchange with the treated air with a relatively high temperature, is further heated by the second air heater (7) to the regeneration temperature required for dehumidification, and is sent to the secondary dehumidification wheel regeneration zone (8), and is driven by the second regeneration exhaust fan (9) to be discharged; the ambient air with a relatively low temperature is first heated by the primary sensible heat exchanger (3), and is then heated by the first air heater (10) to the regeneration air that meets the dehumidification requirements, and is then sent to the primary dehumidification wheel regeneration zone (11), and is finally driven by the first regeneration exhaust fan (12) to be discharged; The cold water delivery method is as follows: the low-temperature cold water prepared in the countercurrent direct evaporative cooling tower (18) is driven by a cold water supply pump (21) to be respectively delivered to the third-stage surface cooler (16) and the terminal heat exchange device (23), delivered to the terminal heat exchange device (23) to be mixed with the return water of the third-stage surface cooler (16) after the temperature rises, and then delivered to the first-stage surface cooler (1) to exchange heat with the relatively high-temperature air from the environment, and then used as the supply water of the second-stage surface cooler (4) to exchange heat with the relatively high-temperature process air, further increase the temperature, and finally sprayed on the surface of the filler (17) through the nozzle (19), to perform countercurrent heat and mass exchange with the low-temperature and low-humidity process air, and to cool down to a low-temperature supply water close to the dew point temperature; When the heating medium is hot water, the low-grade heat source heating method is as follows: the hot water from the hot water source (28) is driven by a hot water pump (29) and sent to the second air heater (7), and then sent to the first air heater (10) after exchanging heat with the regeneration air at a lower temperature, and then sent to the first air heater (10) after exchanging heat with the regeneration air at a lower temperature, and then returned to the hot water source (28) after being converted into return water at a lower temperature; When the heating medium is high-temperature air, the low-grade heat source heating method is as follows: the high-temperature air coming out of the air heat source (30) is driven by a heating fan (31) and sent to the second air heater (7), where it exchanges heat with the regeneration air at a lower temperature, and then is sent to the first air heater (10), where it exchanges heat with the regeneration air at a lower temperature and is then discharged.

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