CN211424563U - Energy-saving type variable dehumidification heat pump type rotating wheel dehumidification unit - Google Patents
Energy-saving type variable dehumidification heat pump type rotating wheel dehumidification unit Download PDFInfo
- Publication number
- CN211424563U CN211424563U CN202020048462.1U CN202020048462U CN211424563U CN 211424563 U CN211424563 U CN 211424563U CN 202020048462 U CN202020048462 U CN 202020048462U CN 211424563 U CN211424563 U CN 211424563U
- Authority
- CN
- China
- Prior art keywords
- dehumidification
- air
- rotating wheel
- condenser
- pipeline
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
Images
Landscapes
- Air Conditioning Control Device (AREA)
Abstract
The utility model relates to an energy-saving type variable dehumidification heat pump type rotating wheel dehumidification unit, which mainly comprises a precooling evaporator, a primary dehumidification rotating wheel, an intermediate cooling evaporator, a secondary dehumidification rotating wheel, a post cooling evaporator, an air supply fan, a first electric air valve and a second electric air valve; when the dehumidification capacity required by the system is large, the first electric air valve is opened, and the dehumidified air can continuously pass through the precooling evaporator, the primary dehumidifying rotating wheel, the intermediate cooling evaporator, the secondary dehumidifying rotating wheel and the post-cooling evaporator. When the dehumidification amount required by the system is small, the second electric air valve is opened, the dehumidified air can directly enter the intermediate cooling evaporator through the bypass pipeline and then sequentially pass through the secondary dehumidification rotating wheel and the after-cooling evaporator. The utility model discloses in, when low dehumidification volume, the operational mode of runner dehumidification unit can be single-stage runner operational mode, has the advantage that system's tuber pipe pipeline resistance is little and dehumidification air temperature rise is little to reach the purpose of the dehumidification energy consumption of reduction system.
Description
Technical Field
The utility model relates to a rotary dehumidifier field especially relates to an energy-saving becomes dehumidification heat pump formula rotary dehumidifier unit.
Background
The main material of the dehumidification rotating wheel is an adsorbing material with high specific surface area, and the dehumidification rotating wheel can adsorb water vapor in air so as to perform dehumidification. The adsorption material after adsorption saturation can be used for adsorption and dehumidification again after needing desorption regeneration, and the desorption regeneration needs to use high-temperature regeneration air (the temperature of the high-temperature regeneration air is 50-120 ℃ generally according to different dehumidification amounts). For continuous operation in actual use, the desiccant wheel is generally divided into two zones, a desiccant zone and a regeneration zone. The adsorption material can repeatedly pass through the dehumidification zone and the regeneration zone along with the rotation of the dehumidification rotating wheel.
The heat pump regeneration type rotary wheel dehumidification air-conditioning system heats the regeneration air of the dehumidification rotary wheel by recovering heat discharged by the heat pump condenser, and can reduce the regeneration energy consumption of the dehumidification rotary wheel. In this system, the heat pump is mainly used to reduce the air temperature (process the damp heat load), the condenser is used to reject heat to heat the regeneration air of the desiccant rotor, and the desiccant rotor is mainly used to reduce the air humidity (process the damp load). In a place with a low humidity requirement, the dew point temperature of the supplied air is extremely low, and a two-stage rotary wheel dehumidification air-conditioning system is generally required. The high-temperature regeneration air of the dehumidification rotating wheel has high air temperature, so the high-temperature regeneration air can heat the rotating wheel after passing through the dehumidification rotating wheel. As the temperature of the dehumidified air increases as it passes through the desiccant rotor, it is often necessary to reduce the temperature of the dehumidified air before it passes through the second stage desiccant rotor to increase the dehumidification effect. Therefore, in a two-stage runner dehumidification air conditioning system, an intermediate cooling device is generally provided between the primary runner and the secondary runner. Many recent studies have also pointed out that: the air conditioning system using the two-stage dehumidification rotating wheel and the intermediate cooling device in comfortable air conditioning places (such as houses, office buildings, shops and the like) can also effectively reduce the regeneration energy consumption of the dehumidification rotating wheel.
In the existing scheme, a two-stage rotating wheel dehumidification system which operates in combination with a heat pump precools air to be dehumidified by using a high-temperature refrigerant, and a dehumidification area of a one-stage rotating wheel dehumidifies the precooled air. The air is cooled by a first-stage heat pump evaporator and then enters a second-stage rotating wheel dehumidification area. And the dehumidified air enters a secondary heat pump evaporator for final cooling. The regenerated air passes through the first-stage heat pump condenser, the second-stage dehumidification rotating wheel regeneration area, the second-stage heat pump condenser, the first-stage dehumidification rotating wheel regeneration area and the third-stage heat pump condenser in sequence by utilizing indoor exhaust air or outdoor fresh air.
In other prior proposals, heat pumps include low temperature heat pumps and high temperature heat pumps. The low-temperature heat pump is provided with two evaporators for pre-cooling the dehumidified air in front of the primary rotating wheel and in front of the secondary rotating wheel in sequence. The high-temperature heat pump heats the regeneration air through the heat discharged by the condenser, and then the regeneration air sequentially passes through the primary electric heater, the secondary dehumidification rotating wheel, the secondary electric heater and the primary dehumidification rotating wheel.
In the prior art, the design of the rotary wheel dehumidification system is designed according to the maximum dehumidification amount. When the single-stage dehumidification rotating wheel system cannot meet the requirement of the maximum dehumidification amount, a two-stage dehumidification rotating wheel system is adopted. In the in-service use, the dehumidification volume is dynamic change, and many times, runner dehumidification system need not be with the maximum load operation to when single-stage dehumidification runner system operation can satisfy the dehumidification demand, but still operates with two-stage dehumidification runner system, and system's tuber pipe pipeline resistance is big, causes fan energy consumption and dehumidification runner drive energy consumption unnecessary extravagant. On the other hand, the second-stage dehumidification rotating wheel has small dehumidification amount, but the air outlet temperature is higher after the second-stage dehumidification rotating wheel exchanges heat with the high-temperature regeneration air, and more energy needs to be consumed to reduce the air supply temperature.
Therefore, in the existing technical scheme, the two-stage dehumidification rotary wheel system has the defects of large dehumidification capacity, limited system dynamic regulation capacity and low system energy efficiency during partial load operation, and the two-stage dehumidification rotary wheel system is usually in overload operation when the dehumidification demand is very small, so that unnecessary energy waste is caused.
SUMMERY OF THE UTILITY MODEL
The utility model aims at providing an energy-saving change dehumidification heat pump formula runner dehumidification unit to reach the purpose of the dehumidification energy consumption of reduction system.
In order to achieve the above object, the utility model provides a following scheme:
an energy-saving type variable dehumidification heat pump type rotary-wheel dehumidification unit comprises a heat pump type rotary-wheel dehumidification air-conditioning system and a control system; the heat pump type rotating wheel dehumidification air-conditioning system comprises a precooling evaporator, a primary dehumidification rotating wheel, an intermediate cooling evaporator, a secondary dehumidification rotating wheel, a post cooling evaporator, an air supply fan, a secondary rotating wheel heat recovery condenser, a secondary rotating wheel auxiliary heater, a secondary rotating wheel regeneration fan, a primary rotating wheel heat recovery condenser and a primary rotating wheel auxiliary heater; the control system comprises a controller, and a first electric air valve, a second electric air valve, an air humidity sensor, a first air temperature sensor, a second air temperature sensor and a third air temperature sensor which are electrically connected with the controller;
the first outdoor fresh air inflow pipeline is sequentially communicated with the precooling evaporator, the dehumidification area of the primary dehumidification rotating wheel, the intermediate cooling evaporator, the dehumidification area of the secondary dehumidification rotating wheel, the post-cooling evaporator and the air supply fan through a main pipeline; the first outdoor fresh air inflow pipeline is also directly communicated with the intermediate cooling evaporator through a bypass pipeline; the indoor exhaust pipeline is sequentially communicated with the secondary runner heat recovery condenser, the secondary runner auxiliary heater, the regeneration area of the secondary dehumidification runner and the secondary runner regeneration fan through branch pipelines; the second outdoor fresh air inflow pipeline is communicated with the primary rotary wheel regeneration fan, the primary rotary wheel heat recovery condenser, the primary rotary wheel auxiliary heater and the regeneration area of the primary dehumidification rotary wheel in sequence through branch pipelines; the indoor air return pipeline is communicated with the rear cooling evaporator;
the first electric air valve is arranged on a main pipeline between the first outdoor fresh air inflow pipeline and the precooling evaporator, and the second electric air valve is arranged on a bypass pipeline between the first outdoor fresh air inflow pipeline and the intercooling evaporator; the indoor air return pipeline is provided with the air humidity sensor and the first air temperature sensor; the second air temperature sensor is arranged on a branch pipeline between the secondary runner heat recovery condenser and the secondary runner auxiliary heater, and the third air temperature sensor is arranged on a branch pipeline between the secondary runner auxiliary heater and the secondary dehumidification runner.
Optionally, the heat pump type rotary wheel dehumidification air-conditioning system further includes a compressor and an outdoor condenser;
a first output end of the outdoor condenser is sequentially communicated with input ends of the pre-cooling evaporator, the compressor, the secondary runner heat recovery condenser and the outdoor condenser through refrigerant pipes to form a first loop;
the first output end of the outdoor condenser is communicated with the intermediate cooling evaporator, the compressor, the secondary runner heat recovery condenser and the input end of the outdoor condenser in sequence through refrigerant pipes to form a second loop;
the first output end of the outdoor condenser is communicated with the input ends of the after-cooling evaporator, the compressor, the secondary runner heat recovery condenser and the outdoor condenser in sequence through refrigerant pipes to form a third loop;
and the compressor is sequentially communicated with the first-stage runner heat recovery condenser and the input end of the outdoor condenser through refrigerant pipes to form a fourth loop.
Optionally, in the first loop the compressor, the second stage runner heat recovery condenser, the route between the outdoor condensers, in the second loop the compressor, the second stage runner heat recovery condenser, the route between the outdoor condensers and in the third loop the compressor, the second stage runner heat recovery condenser, the route between the outdoor condensers are the same route.
Optionally, an axial flow fan is arranged at a second output end of the outdoor condenser.
Optionally, the control system further includes a first electromagnetic expansion valve, a second electromagnetic expansion valve, a third electromagnetic expansion valve, a fourth electromagnetic expansion valve, and a fifth electromagnetic expansion valve, which are electrically connected to the controller, respectively;
the first electromagnetic expansion valve is arranged on a refrigerant pipe between the compressor and the secondary runner heat recovery condenser;
the second electromagnetic expansion valve is arranged on a refrigerant pipe between the compressor and the first-stage runner heat recovery condenser;
the third electromagnetic expansion valve is arranged on a refrigerant pipe between the outdoor condenser and the precooling evaporator;
the fourth electromagnetic expansion valve is arranged on a refrigerant pipe between the outdoor condenser and the intermediate cooling evaporator;
the fifth electromagnetic expansion valve is arranged on a refrigerant pipe between the outdoor condenser and the rear cooling evaporator.
Optionally, the heat pump type rotary wheel dehumidification air-conditioning system includes a first filter, a second filter and a third filter;
the first filter is arranged on a pipeline between the first outdoor fresh air inflow pipeline and the first electric air valve;
the second filter is arranged on a pipeline between the indoor exhaust pipeline and the secondary runner heat recovery condenser;
the third filter is arranged on a pipeline between the second outdoor fresh air inflow pipeline and the primary rotary wheel regeneration fan.
Optionally, the controller is further electrically connected to a switch controller of the secondary runner auxiliary heater.
According to the utility model provides a concrete embodiment, the utility model discloses a following technological effect:
the utility model provides an energy-saving becomes dehumidification heat pump formula runner dehumidification unit. When the system requires a large amount of dehumidification, the dehumidified air can continuously pass through the pre-cooling evaporator, the primary dehumidification rotating wheel, the intermediate cooling evaporator, the secondary dehumidification rotating wheel and the post-cooling evaporator. When the dehumidification amount required by the system is small, the dehumidified air can directly enter the intermediate cooling evaporator through the bypass pipeline and then sequentially passes through the secondary dehumidification rotating wheel and the after-cooling evaporator. Meanwhile, the primary runner regeneration fan and the primary runner auxiliary heater stop running. Under the single-stage runner operation mode of low dehumidification volume, the system tuber pipe pipeline resistance is little, and the dehumidification air temperature rise is little to reach the purpose that reduces system's dehumidification energy consumption.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings required to be used in the embodiments will be briefly described below, and it is obvious that the drawings in the following description are only some embodiments of the present invention, and for those skilled in the art, other drawings can be obtained according to these drawings without inventive labor.
Fig. 1 is a partial structure diagram of the energy-saving type variable dehumidification heat pump type rotary dehumidifier unit of the present invention.
Detailed Description
The technical solutions in the embodiments of the present invention will be described clearly and completely with reference to the accompanying drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only some embodiments of the present invention, not all embodiments. Based on the embodiments in the present invention, all other embodiments obtained by a person skilled in the art without creative work belong to the protection scope of the present invention.
The dehumidification rotary wheel dehumidification air-conditioning system is widely applied to places with dehumidification requirements, and has a certain application prospect in civil buildings in coastal regions represented by Yangtze river basin at present. In some places, the single-stage rotating wheel dehumidification system still cannot meet the maximum dehumidification requirement, and a two-stage rotating wheel dehumidification system is required. In practical use, the system dehumidification capacity is dynamically changed along with the change of the indoor wet source dehumidification capacity and the outdoor air moisture capacity in different seasons. When the dehumidification amount is reduced, the two-stage rotating wheel dehumidification system has large unit resistance due to more equipment, and the energy consumption of the fan is increased. Meanwhile, the cold and heat of the system are counteracted seriously when the two-stage rotary wheel dehumidification system operates, the heat pump refrigerating capacity required by unit dehumidification capacity is large when the system operates at partial load, and the energy consumption of the compressor is high.
To sum up, the utility model provides an energy-saving change dehumidification heat pump formula runner dehumidification unit to reach the purpose of reduction system dehumidification energy consumption.
In order to make the above objects, features and advantages of the present invention more comprehensible, the present invention is described in detail with reference to the accompanying drawings and the detailed description.
The utility model provides a pair of energy-saving becomes dehumidification heat pump formula runner dehumidification unit for solve the problem of the high energy consumption operation of system under the dynamic heat of in-service use, the wet load condition. The energy-saving variable dehumidification heat pump type rotating wheel dehumidification unit comprises a heat pump type rotating wheel dehumidification air-conditioning system and a control system. The control system adjusts the operation mode of the heat pump type rotating wheel dehumidification air-conditioning system by collecting monitoring point data.
As shown in fig. 1, the heat pump type rotary-wheel dehumidification air-conditioning system mainly includes a first filter 1, a pre-cooling evaporator 2, a primary dehumidification rotary wheel 3, an intermediate cooling evaporator 4, a secondary dehumidification rotary wheel 5, a post-cooling evaporator 6, an air supply fan 7, a second filter 8, a secondary rotary-wheel heat recovery condenser 9, a secondary rotary-wheel regeneration fan 10, a primary rotary-wheel regeneration fan 11, a primary rotary-wheel heat recovery condenser 12, a third filter 13, an outdoor condenser 14, a compressor 16, a primary rotary-wheel auxiliary heater 19, and a secondary rotary-wheel auxiliary heater 20. The outdoor condenser 14 is provided with an axial flow fan 15.
The control system comprises a controller, and a first electric air valve 18-1, a second electric air valve 18-2, an air humidity sensor, a first air temperature sensor, a second air temperature sensor, a third air temperature sensor, a first electromagnetic expansion valve 17-1, a second electromagnetic expansion valve 17-2, a third electromagnetic expansion valve 17-3, a fourth electromagnetic expansion valve 17-4 and a fifth electromagnetic expansion valve 17-5 which are electrically connected with the controller.
The heat pump refrigerant pipeline comprises a compressor 16, a first-stage runner heat recovery condenser 12, a second-stage runner heat recovery condenser 9, an outdoor condenser 14, a precooling evaporator 2, an intermediate cooling evaporator 4, a post-cooling evaporator 6, a first electromagnetic expansion valve 17-1, a second electromagnetic expansion valve 17-2, a third electromagnetic expansion valve 17-3, a fourth electromagnetic expansion valve 17-4 and a fifth electromagnetic expansion valve 17-5.
The automatic control monitoring point of the control system mainly comprises a temperature monitoring Tr and a humidity monitoring dr in the return air pipeline, and a front-rear air temperature difference delta T in the exhaust pipeline, and the monitoring equipment comprises an air humidity sensor, a first air temperature sensor, a second air temperature sensor and a third air temperature sensor; the actuators of the control system comprise a first electric air valve 18-1, a second electric air valve 18-2, a first electromagnetic expansion valve 17-1, a second electromagnetic expansion valve 17-2, a third electromagnetic expansion valve 17-3, a fourth electromagnetic expansion valve 17-4, a fifth electromagnetic expansion valve 17-5, a first-stage runner auxiliary heater 19, a second-stage runner auxiliary heater 20 and an on-off controller of a first-stage runner regeneration fan 11. The sensors and actuators of other control systems are similar to those of the existing systems, but are not the key or required protection content of the utility model.
The specific connection relationship of each device is as follows:
a first outdoor fresh air inflow pipeline is sequentially communicated with the precooling evaporator 2, the dehumidification area of the primary dehumidification rotating wheel 3, the intermediate cooling evaporator 4, the dehumidification area of the secondary dehumidification rotating wheel 5, the post-cooling evaporator 6 and the air supply fan 7 through a main pipeline; the first outdoor fresh air inflow pipeline is also directly communicated with the intermediate cooling evaporator 4 through a bypass pipeline; the indoor exhaust pipeline is communicated with the secondary runner heat recovery condenser 9, the secondary runner auxiliary heater 20, the regeneration area of the secondary dehumidification runner 5 and the secondary runner regeneration fan 10 in sequence through branch pipelines; the second outdoor fresh air inflow pipeline is communicated with the primary runner regeneration fan 11, the primary runner heat recovery condenser 12, the primary runner auxiliary heater 19 and the regeneration area of the primary dehumidification runner 3 in sequence through branch pipelines; the indoor air return pipeline is communicated with the rear cooling evaporator 6; the first electric air valve 18-1 is arranged on a main pipeline between the first outdoor fresh air inflow pipeline and the pre-cooling evaporator 2, and the second electric air valve 18-2 is arranged on a bypass pipeline between the first outdoor fresh air inflow pipeline and the intermediate cooling evaporator 4; the indoor air return pipeline is provided with the air humidity sensor and the first air temperature sensor; the second air temperature sensor is arranged on a branch pipeline between the secondary runner heat recovery condenser 9 and the secondary runner auxiliary heater 20, and the third air temperature sensor is arranged on a branch pipeline between the secondary runner auxiliary heater 20 and the secondary dehumidification runner 5. The first filter 1 is arranged on a pipeline between the first outdoor fresh air inflow pipeline and the first electric air valve 18-1; the second filter 8 is arranged on a pipeline between the indoor exhaust pipeline and the secondary runner heat recovery condenser 9; the third filter 13 is arranged on a pipeline between the second outdoor fresh air inflow pipeline and the primary rotary wheel regeneration fan 11.
A first output end of the outdoor condenser 14 is sequentially communicated with the precooling evaporator 2, the compressor 16, the secondary runner heat recovery condenser 9 and an input end of the outdoor condenser 14 through refrigerant pipes to form a first loop; a first output end of the outdoor condenser 14 is sequentially communicated with the intermediate cooling evaporator 4, the compressor 16, the secondary runner heat recovery condenser 9 and an input end of the outdoor condenser 14 through refrigerant pipes to form a second loop; a first output end of the outdoor condenser 14 is sequentially communicated with input ends of the post-cooling evaporator 6, the compressor 16, the secondary runner heat recovery condenser 9 and the outdoor condenser 14 through refrigerant pipes to form a third loop; the compressor 16 is sequentially communicated with the input ends of the first-stage runner heat recovery condenser 12 and the outdoor condenser 14 through refrigerant pipes to form a fourth loop. Wherein the compressor 16, the secondary runner heat recovery condenser 9, the passage between the outdoor condensers 14 in the first circuit, the compressor 16, the secondary runner heat recovery condenser 9, the passage between the outdoor condensers 14 in the second circuit, and the passage between the compressor 16, the secondary runner heat recovery condenser 9, and the outdoor condensers 14 in the third circuit are the same passage. And a second output end of the outdoor condenser 14 is provided with an axial flow fan 15.
The first electromagnetic expansion valve 17-1 is arranged on a refrigerant pipe between the compressor 16 and the secondary runner heat recovery condenser 9; the second electromagnetic expansion valve 17-2 is arranged on a refrigerant pipe between the compressor 16 and the first-stage runner heat recovery condenser 12; the third electromagnetic expansion valve 17-3 is arranged on a refrigerant pipe between the outdoor condenser 14 and the pre-cooling evaporator 2; the fourth electromagnetic expansion valve 17-4 is arranged on a refrigerant pipe between the outdoor condenser 14 and the intermediate cooling evaporator 4; the fifth electromagnetic expansion valve 17-5 is disposed on the refrigerant pipe between the exterior condenser 14 and the rear cooling evaporator 6.
In practical application, the outdoor condenser 14 and the axial flow fan 15 need to be placed outdoors, the rest devices are placed in the air conditioning box, and the air circulation loop, namely the main through pipeline, the bypass pipeline and the branch pipeline, is connected by adopting an air pipe or directly utilizes the air conditioning box as a circulation channel. The refrigerant circuits are connected by refrigerant pipes. In the control system, the opening and closing and the opening control of a first electric air valve 18-1, a second electric air valve 18-2, a first electromagnetic expansion valve 17-1, a second electromagnetic expansion valve 17-2, a third electromagnetic expansion valve 17-3, a fourth electromagnetic expansion valve 17-4, a fifth electromagnetic expansion valve 17-5, a driving motor of a first-stage dehumidification rotating wheel 3, a driving motor of a second-stage dehumidification rotating wheel 5, an air supply fan 7, a second-stage rotating wheel regeneration fan 10, a first-stage rotating wheel regeneration fan 11, a compressor 16, a first-stage rotating wheel auxiliary heater 19 and a second-stage rotating wheel auxiliary heater 20 are all automatically controlled.
The heat sources of the primary runner auxiliary heater 19 and the secondary runner auxiliary heater 20 may utilize various devices, such as: electric heaters, boilers, high temperature heat pumps, solar energy or other industrial waste heat and waste heat, and the like.
Aiming at the difference of dehumidification and refrigeration requirements in a control area, the control system has three operation modes which are respectively as follows: a single-stage no-auxiliary heating mode, a single-stage auxiliary heating mode, and a two-stage auxiliary heating mode. In the single-stage mode, instead of bypassing the primary desiccant wheel and the pre-cooling evaporator, the secondary desiccant wheel and the intercooling evaporator may also be bypassed, with the regeneration air side equipment and fan switch performing the same process accordingly.
In the single-stage non-auxiliary heating mode, the first electric air valve 18-1 is closed, the second electric air valve 18-2 is opened, the first electromagnetic expansion valve 17-1, the fourth electromagnetic expansion valve 17-4 and the fifth electromagnetic expansion valve 17-5 are opened, the second electromagnetic expansion valve 17-2 and the third electromagnetic expansion valve 17-3 are kept closed, and the first-stage runner regeneration fan 11, the first-stage runner auxiliary heater 19 and the second-stage runner auxiliary heater 20 are closed. Outdoor fresh air (OA) firstly passes through the first filter 1 and then enters the intermediate cooling evaporator 4 from the bypass pipeline for cooling and condensation dehumidification. And then the cooled, condensed and dehumidified air enters a dehumidification area of the secondary dehumidification rotary wheel 5 for further dehumidification. The dehumidified air is mixed with indoor Return Air (RA), and then enters the after-cooling evaporator 6 to be cooled and then is sent into the control area by the air supply fan 7. Meanwhile, the indoor Exhaust Air (EA) firstly passes through the second filter 8 and then enters the secondary drum heat recovery condenser 9 to exchange heat with the high-temperature refrigerant exhaust air of the compressor 16. The heated air enters the regeneration zone of the secondary dehumidification rotating wheel 5 to regenerate the dehumidification rotating wheel, and then is discharged to the outside by the secondary rotating wheel regeneration fan 10. In a refrigerant pipeline, an intermediate cooling evaporator 4 and a post cooling evaporator 6 are connected in parallel, and are compressed by a compressor 16 and then pass through a secondary runner heat recovery condenser 9 and an outdoor condenser 14 in sequence, so that redundant condensation heat is discharged.
In the single-stage assist heating mode, the secondary runner assist heater 20 is turned on for further heating the regeneration air of the secondary desiccant runner 5. The rest of the operation conditions are the same as the single-stage non-auxiliary heating mode.
In the two-stage auxiliary heating mode, the first electric air valve 18-1 is opened, the second electric air valve 18-2 is closed, the first electromagnetic expansion valve 17-1 is opened, the second electromagnetic expansion valve 17-2 is opened, the third electromagnetic expansion valve 17-3 is opened, the fourth electromagnetic expansion valve 17-4 is opened, the fifth electromagnetic expansion valve 17-5 is opened, the first-stage runner regeneration fan 11 is opened, the first-stage runner auxiliary heater 19 is opened, and the second-stage runner auxiliary heater 20 is opened. The primary-wheel auxiliary heater 19 and the secondary-wheel auxiliary heater 20 are respectively used to further heat the regeneration air of the primary desiccant rotor 3 and the secondary desiccant rotor 5. Fresh Outdoor Air (OA) is first passed through a first filter 1 and then to a pre-cooling evaporator 2 for pre-cooling and dehumidification. The precooled outdoor air enters a dehumidification area of the primary dehumidification rotary wheel 3 for further dehumidification. The dehumidified high-temperature air is cooled by the intermediate cooling evaporator 4 and then enters the dehumidification area of the secondary dehumidification rotary wheel 5 for final dehumidification. After being dehumidified, the outdoor fresh air and the indoor Return Air (RA) are mixed, cooled by the rear cooling evaporator 6 and then supplied by the air supply fan 7. Meanwhile, indoor Exhaust Air (EA) as regeneration air of the secondary desiccant rotor 5 first passes through the second filter 8, and then is heated by the secondary rotor heat recovery condenser 9 and the secondary rotor auxiliary heater 20 and then enters a regeneration zone of the secondary desiccant rotor 5 to regenerate the desiccant rotor. Outdoor Air (OA), which is the regeneration air of the primary desiccant rotor 3, first passes through the third filter 13 and the primary rotor regeneration fan 11, and then is heated by the primary rotor heat recovery condenser 12 and the primary rotor auxiliary heater 19, and then enters the regeneration zone of the primary desiccant rotor 3 to regenerate the desiccant rotor. In a refrigerant pipeline, a pre-cooling evaporator 2, an intermediate cooling evaporator 4 and a post-cooling evaporator 6 are connected in parallel, and are compressed by a compressor 16, then respectively pass through a first-stage runner heat recovery condenser 12 and a second-stage runner heat recovery condenser 9, and then are converged to enter an outdoor condenser 14, so that redundant condensation heat is discharged.
The control system needs to be debugged in advance before being actually used, and control parameter set values are determined, specifically, a set temperature threshold value Tset, a set humidity threshold value dset, a set temperature difference value delta Tset and a set maximum temperature difference value delta Tmax are determined.
In the actual use process of the control system, the return air temperature value Tr needs to be acquired by the first air temperature sensor in real time, the return air humidity value dr needs to be acquired by the air humidity sensor in real time, the front temperature value needs to be acquired by the second air temperature sensor in real time, the rear temperature value needs to be acquired by the third air temperature sensor in real time, and the difference between the front temperature value and the rear temperature value is determined as the front-rear air temperature difference Δ T of the secondary runner auxiliary heater 20.
The utility model discloses in, need judge second grade runner auxiliary heater 20 heating volume according to definite control parameter, air temperature difference value delta T judges around concrete implementation mode accessible second grade runner auxiliary heater 20, can regard second grade runner auxiliary heater 20 to be in zero load running state when current back air temperature difference value delta T is less than the setting value. The other quantity to be determined by pre-debugging is the maximum heating quantity of the secondary runner auxiliary heater 20, the specific implementation mode can be judged by the front and rear air temperature difference delta T of the secondary runner auxiliary heater 20, and the secondary runner auxiliary heater 20 can be considered to be in a full-load operation state when the front and rear air temperature difference delta T reaches the set maximum value.
The control process of the present invention is described below by comparing operation logic in the prior art. When the machine is started, the machine is started in a two-stage auxiliary heating mode, the primary runner auxiliary heater 19 runs at full load, and the secondary runner auxiliary heater runs at zero load.
The temperature in the control area is controlled by the refrigerating capacity of the post-cooling evaporator 6, and the specific implementation mode is that the opening degree of the fifth electromagnetic expansion valve 17-5 is adjusted according to the size relation between the return air temperature value Tr and the set temperature threshold value Tset in the control area. When the return air temperature value Tr < the set temperature threshold Tset in the control area indicates that the cooling capacity of the rear cooling evaporator 6 is greater than the required cooling capacity, the opening degree of the fifth electromagnetic expansion valve 17-5 is reduced, and vice versa.
The system dehumidification in the control area is adjusted by adjusting the heating capacity of the secondary runner auxiliary heater 20. When the return air humidity value dr > is greater than the set humidity threshold dset in the control area, the system dehumidification amount is smaller than the required dehumidification amount, and the heating amount of the secondary runner auxiliary heater 20 is increased. When the return air humidity value dr is smaller than a set humidity threshold dset in the control area, it is indicated that the system dehumidification capacity is larger than the required dehumidification capacity, at this time, the heating capacity of the secondary runner auxiliary heater 20 needs to be judged, and the judgment basis can be according to the set temperature difference Δ Tset and the front and rear air temperature difference Δ T of the secondary runner auxiliary heater 20. When the difference between the measured air temperature Δ T before and after the measurement > the set temperature difference Δ Tset, the heating amount of the secondary runner auxiliary heater 20 needs to be reduced to reduce the dehumidification amount of the system, and conversely, when the difference between the measured air temperature Δ T before and after the measurement < the set temperature difference Δ Tset, it indicates that the heating amount of the primary runner auxiliary heater 19 is extremely small or is basically in a non-operation state, and at this time, the system may enter a single-stage auxiliary heating mode. When the system operates in the single-stage auxiliary heating mode, the dehumidification capacity of the system is adjusted by adjusting the heating capacity of the secondary runner auxiliary heater 20. In the single-stage auxiliary heating mode, when the return air humidity value dr is greater than the set humidity threshold dset in the control area and the difference value Δ T between the actually measured air temperatures before and after the set humidity threshold dset is equal to the set maximum temperature difference Δ Tmax, it is described that the system dehumidification amount is still insufficient when the secondary auxiliary heater 20 is in full load operation, at this time, the control system enters the two-stage auxiliary heating mode again, and when the return air humidity value dr is greater than the set humidity threshold dset in the control area and the difference value Δ T between the actually measured air temperatures before and after the set humidity threshold dset is not equal to the set maximum temperature difference Δ Tmax, the heating amount of the secondary. In the single-stage auxiliary heating mode, when the return air humidity value dr is less than the set humidity threshold dset in the control area, the heating amount of the secondary runner auxiliary heater 20 needs to be reduced to reduce the system dehumidification amount.
The return air humidity value can use return air moisture content, return air relative humidity or return air dew point temperature as a control parameter; the heating amount of the auxiliary heater can use the air temperature difference between the front and the back of the heater, the heater power (mainly aiming at an electric heater, a heat pump, a boiler and the like) or the heating medium flow (mainly aiming at a water-air heat exchanger or a steam-air heat exchanger and the like) as control parameters.
Compared with the prior art, the utility model has the advantages of it is following:
firstly, the dehumidification air can directly enter the intermediate cooling evaporator through the bypass pipeline by arranging the bypass pipeline, so that the operation mode of the system can be changed from a two-stage auxiliary heating mode to a single-stage auxiliary heating/single-stage non-auxiliary heating mode, and when the dehumidification amount required by the system is large, the dehumidification air can continuously pass through the precooling evaporator, the one-stage dehumidification rotating wheel, the intermediate cooling evaporator, the two-stage dehumidification rotating wheel and the after-cooling evaporator. When the dehumidification quantity required by the system is small, the dehumidification air can directly enter the intermediate cooling evaporator through the bypass pipeline and then sequentially passes through the secondary dehumidification rotating wheel and the post-cooling evaporator, so that the aims of small resistance of the air pipe pipeline of the system, small temperature rise of the dehumidification air and reduction of dehumidification energy consumption of the system in a single-stage rotating wheel operation mode with low dehumidification capacity are fulfilled.
Secondly, the system controls the operation mode according to the moisture content of return air and the heating quantity of an auxiliary heater: when the moisture content of the return air is lower than the moisture content of the indoor design, the system firstly adjusts the heating capacity of the secondary runner auxiliary heating device. When the moisture content of return air is still lower than the indoor design moisture content when the secondary runner auxiliary heating device is turned off, the system is switched to a single-stage auxiliary heating mode, and the heating quantity of the secondary runner auxiliary heating device is adjusted, namely the system is controlled only by taking the moisture content of the return air and the heating quantity of the runner auxiliary heater as control parameters for adjusting each operation mode of the system and the two auxiliary heating devices, and the control logic is simple.
Third, when the required dehumidification is reduced, the system first reduces the heating capacity of the secondary runner auxiliary heating device for adjustment. When the required dehumidification amount is further reduced to be within the dehumidification amount range of the single-stage dehumidification system, the system reduces the operation energy consumption of the system by bypassing the dehumidification air and closing the primary runner regeneration fan. When the required dehumidification amount is reduced again, the system is adjusted by reducing the heating amount of the secondary runner auxiliary heating device. Within each dehumidification amount range, the system can be operated with the lowest energy consumption.
Fourth, the utility model discloses a low wet indoor regeneration air as the dehumidification runner of airing exhaust of make full use of can improve dehumidification runner dehumidification efficiency, reduces the regeneration energy consumption of dehumidification runner.
Fifth, the utility model discloses refrigerating system's evaporating temperature is high, and compressor operating efficiency is high, but the fully reduced refrigerating system operation energy consumption.
The embodiments in the present description are described in a progressive manner, each embodiment focuses on differences from other embodiments, and the same and similar parts among the embodiments are referred to each other.
The principle and the implementation of the present invention are explained herein by using specific examples, and the above description of the embodiments is only used to help understand the method and the core idea of the present invention; meanwhile, for the general technical personnel in the field, according to the idea of the present invention, there are changes in the concrete implementation and the application scope. In summary, the content of the present specification should not be construed as a limitation of the present invention.
Claims (7)
1. An energy-saving variable dehumidification heat pump type rotary wheel dehumidification unit is characterized by comprising a heat pump type rotary wheel dehumidification air-conditioning system and a control system; the heat pump type rotating wheel dehumidification air-conditioning system comprises a precooling evaporator, a primary dehumidification rotating wheel, an intermediate cooling evaporator, a secondary dehumidification rotating wheel, a post cooling evaporator, an air supply fan, a secondary rotating wheel heat recovery condenser, a secondary rotating wheel auxiliary heater, a secondary rotating wheel regeneration fan, a primary rotating wheel heat recovery condenser and a primary rotating wheel auxiliary heater; the control system comprises a controller, and a first electric air valve, a second electric air valve, an air humidity sensor, a first air temperature sensor, a second air temperature sensor and a third air temperature sensor which are electrically connected with the controller;
the first outdoor fresh air inflow pipeline is sequentially communicated with the precooling evaporator, the dehumidification area of the primary dehumidification rotating wheel, the intermediate cooling evaporator, the dehumidification area of the secondary dehumidification rotating wheel, the post-cooling evaporator and the air supply fan through a main pipeline; the first outdoor fresh air inflow pipeline is also directly communicated with the intermediate cooling evaporator through a bypass pipeline; the indoor exhaust pipeline is sequentially communicated with the secondary runner heat recovery condenser, the secondary runner auxiliary heater, the regeneration area of the secondary dehumidification runner and the secondary runner regeneration fan through branch pipelines; the second outdoor fresh air inflow pipeline is communicated with the primary rotary wheel regeneration fan, the primary rotary wheel heat recovery condenser, the primary rotary wheel auxiliary heater and the regeneration area of the primary dehumidification rotary wheel in sequence through branch pipelines; the indoor air return pipeline is communicated with the rear cooling evaporator;
the first electric air valve is arranged on a main pipeline between the first outdoor fresh air inflow pipeline and the precooling evaporator, and the second electric air valve is arranged on a bypass pipeline between the first outdoor fresh air inflow pipeline and the intercooling evaporator; the indoor air return pipeline is provided with the air humidity sensor and the first air temperature sensor; the second air temperature sensor is arranged on a branch pipeline between the secondary runner heat recovery condenser and the secondary runner auxiliary heater, and the third air temperature sensor is arranged on a branch pipeline between the secondary runner auxiliary heater and the secondary dehumidification runner.
2. The energy-saving variable dehumidification heat pump type rotary wheel dehumidification unit according to claim 1, wherein the heat pump type rotary wheel dehumidification air-conditioning system further comprises a compressor and an outdoor condenser;
a first output end of the outdoor condenser is sequentially communicated with input ends of the pre-cooling evaporator, the compressor, the secondary runner heat recovery condenser and the outdoor condenser through refrigerant pipes to form a first loop;
the first output end of the outdoor condenser is communicated with the intermediate cooling evaporator, the compressor, the secondary runner heat recovery condenser and the input end of the outdoor condenser in sequence through refrigerant pipes to form a second loop;
the first output end of the outdoor condenser is communicated with the input ends of the after-cooling evaporator, the compressor, the secondary runner heat recovery condenser and the outdoor condenser in sequence through refrigerant pipes to form a third loop;
and the compressor is sequentially communicated with the first-stage runner heat recovery condenser and the input end of the outdoor condenser through refrigerant pipes to form a fourth loop.
3. The energy-saving variable dehumidification heat pump type rotary wheel dehumidification unit as set forth in claim 2, wherein said compressor, said secondary rotary wheel heat recovery condenser, a passage between said outdoor condensers in said first circuit, said compressor, said secondary rotary wheel heat recovery condenser, a passage between said outdoor condensers in said second circuit, and a passage between said compressor, said secondary rotary wheel heat recovery condenser, and said outdoor condensers in said third circuit are the same passage.
4. The energy-saving variable dehumidification heat pump type rotating wheel dehumidification unit as claimed in claim 2, wherein an axial flow fan is arranged at the second output end of the outdoor condenser.
5. The energy-saving variable dehumidification heat pump type rotating wheel dehumidification unit as claimed in claim 2, wherein the control system further comprises a first electromagnetic expansion valve, a second electromagnetic expansion valve, a third electromagnetic expansion valve, a fourth electromagnetic expansion valve and a fifth electromagnetic expansion valve, which are electrically connected with the controller respectively;
the first electromagnetic expansion valve is arranged on a refrigerant pipe between the compressor and the secondary runner heat recovery condenser;
the second electromagnetic expansion valve is arranged on a refrigerant pipe between the compressor and the first-stage runner heat recovery condenser;
the third electromagnetic expansion valve is arranged on a refrigerant pipe between the outdoor condenser and the precooling evaporator;
the fourth electromagnetic expansion valve is arranged on a refrigerant pipe between the outdoor condenser and the intermediate cooling evaporator;
the fifth electromagnetic expansion valve is arranged on a refrigerant pipe between the outdoor condenser and the rear cooling evaporator.
6. The energy-saving variable dehumidification heat pump rotary wheel dehumidification unit according to claim 1, wherein the heat pump rotary wheel dehumidification air-conditioning system comprises a first filter, a second filter and a third filter;
the first filter is arranged on a pipeline between the first outdoor fresh air inflow pipeline and the first electric air valve;
the second filter is arranged on a pipeline between the indoor exhaust pipeline and the secondary runner heat recovery condenser;
the third filter is arranged on a pipeline between the second outdoor fresh air inflow pipeline and the primary rotary wheel regeneration fan.
7. The energy-saving variable dehumidification heat pump type rotating wheel dehumidification unit as claimed in claim 1, wherein said controller is further electrically connected to a switch controller of said secondary rotating wheel auxiliary heater.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202020048462.1U CN211424563U (en) | 2020-01-10 | 2020-01-10 | Energy-saving type variable dehumidification heat pump type rotating wheel dehumidification unit |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202020048462.1U CN211424563U (en) | 2020-01-10 | 2020-01-10 | Energy-saving type variable dehumidification heat pump type rotating wheel dehumidification unit |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN211424563U true CN211424563U (en) | 2020-09-04 |
Family
ID=72275079
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202020048462.1U Active CN211424563U (en) | 2020-01-10 | 2020-01-10 | Energy-saving type variable dehumidification heat pump type rotating wheel dehumidification unit |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN211424563U (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111102661A (en) * | 2020-01-10 | 2020-05-05 | 同济大学 | Energy-saving type variable dehumidification heat pump type rotary wheel dehumidification unit and control method thereof |
| CN113713576A (en) * | 2021-09-26 | 2021-11-30 | 南京东达智慧环境能源研究院有限公司 | Suspension bridge main cable composite dehumidification system for recycling condensation heat by using separated heat pipes |
| CN113865208A (en) * | 2021-09-16 | 2021-12-31 | 同济大学 | Heat pump rotating wheel coupling device for frostless refrigeration house and operation method |
-
2020
- 2020-01-10 CN CN202020048462.1U patent/CN211424563U/en active Active
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111102661A (en) * | 2020-01-10 | 2020-05-05 | 同济大学 | Energy-saving type variable dehumidification heat pump type rotary wheel dehumidification unit and control method thereof |
| CN111102661B (en) * | 2020-01-10 | 2023-11-24 | 同济大学 | Energy-saving variable-dehumidification-capacity heat pump type rotary dehumidifier unit and control method thereof |
| CN113865208A (en) * | 2021-09-16 | 2021-12-31 | 同济大学 | Heat pump rotating wheel coupling device for frostless refrigeration house and operation method |
| CN113713576A (en) * | 2021-09-26 | 2021-11-30 | 南京东达智慧环境能源研究院有限公司 | Suspension bridge main cable composite dehumidification system for recycling condensation heat by using separated heat pipes |
| CN113713576B (en) * | 2021-09-26 | 2024-04-23 | 南京东达智慧环境能源研究院有限公司 | Suspension bridge main cable composite dehumidification system for recovering condensation heat by using separated heat pipes |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN111102661B (en) | Energy-saving variable-dehumidification-capacity heat pump type rotary dehumidifier unit and control method thereof | |
| KR100943285B1 (en) | Hybrid desiccant dehumidification apparatus and threrof control method | |
| CN211424563U (en) | Energy-saving type variable dehumidification heat pump type rotating wheel dehumidification unit | |
| EP1734317B1 (en) | Cogeneration system | |
| US7428821B2 (en) | Dehumidifying system | |
| CN101790667B (en) | Air conditioning/ventilating system | |
| CN106196346B (en) | Energy-saving low-dew-point rotary dehumidifier | |
| CN201302243Y (en) | Energy-saving full fresh air dehumidifier machine | |
| CN103322656A (en) | Heat recycling air conditioner set | |
| CN102538112A (en) | Household heat and humidity separate control radiation air conditioning system and control method thereof | |
| WO1998029694A1 (en) | Air conditioning system | |
| CN103017332B (en) | Heat-accumulating and dehumidifying coupled frostless air source heat pump water heater | |
| TW201631284A (en) | Adsorption dehumidifier | |
| CN104760601B (en) | Rail traffic vehicles frequency conversion heat pump air-conditioning | |
| CN110173776B (en) | Pre-cooling type runner humidifying fresh air treatment device | |
| JPH11316061A (en) | Air conditioning system and its operation method | |
| CN105042748A (en) | Machine room air conditioner | |
| CN105387584A (en) | Multifunctional household fresh air purification treatment machine with air exhausting and heat recycling functions | |
| CN111536608A (en) | Circulating type rotating wheel dehumidification device and dehumidification method | |
| KR100816450B1 (en) | Air conditioning method and system using brine heat exchanger | |
| KR102257544B1 (en) | Energy enhanced air-conditioning system and control method thereof | |
| CN112880067B (en) | Adsorption type refrigeration and dehumidification combined system and method thereof | |
| CN112742060B (en) | Suspension bridge integrated condensation and rotating wheel cooperative dehumidification system and control method | |
| CN212204822U (en) | Circulating runner dehydrating unit | |
| CN114198808A (en) | Reheating type passive environmental control integrated machine set |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| GR01 | Patent grant | ||
| GR01 | Patent grant |