CN112378061A - Household independent temperature and humidity control system using double-cold-source heat pump host - Google Patents
Household independent temperature and humidity control system using double-cold-source heat pump host Download PDFInfo
- Publication number
- CN112378061A CN112378061A CN202011276025.6A CN202011276025A CN112378061A CN 112378061 A CN112378061 A CN 112378061A CN 202011276025 A CN202011276025 A CN 202011276025A CN 112378061 A CN112378061 A CN 112378061A
- Authority
- CN
- China
- Prior art keywords
- water
- pipe
- coil pipe
- fresh air
- air
- 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.)
- Granted
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F11/00—Control or safety arrangements
- F24F11/89—Arrangement or mounting of control or safety devices
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
- F24F1/0007—Indoor units, e.g. fan coil units
- F24F1/0035—Indoor units, e.g. fan coil units characterised by introduction of outside air to the room
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
- F24F1/0007—Indoor units, e.g. fan coil units
- F24F1/0059—Indoor units, e.g. fan coil units characterised by heat exchangers
- F24F1/0063—Indoor units, e.g. fan coil units characterised by heat exchangers by the mounting or arrangement of the heat exchangers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
- F24F1/0007—Indoor units, e.g. fan coil units
- F24F1/0071—Indoor units, e.g. fan coil units with means for purifying supplied air
- F24F1/0073—Indoor units, e.g. fan coil units with means for purifying supplied air characterised by the mounting or arrangement of filters
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B13/00—Compression machines, plants or systems, with reversible cycle
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B30/00—Heat pumps
- F25B30/06—Heat pumps characterised by the source of low potential heat
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B39/00—Evaporators; Condensers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
- F25B43/003—Filters
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Analytical Chemistry (AREA)
- Power Engineering (AREA)
- Air Conditioning Control Device (AREA)
- Central Air Conditioning (AREA)
Abstract
The invention provides a household independent temperature and humidity control system using a double-cold-source heat pump host, which is suitable for independent temperature and humidity control in small and medium-sized residential and office buildings, can effectively improve the energy efficiency of the system and reduce the cost of the system. The radiation end is arranged in indoor, the fresh air outlet end of the fresh air dehumidification unit is communicated to an indoor fresh air inlet through a pipeline, the integrated double-cold-source air source heat pump host comprises a water system part and a straight expansion part, the shell part of the integrated double-cold-source air source heat pump host is provided with a shell water pipe inlet corresponding to the water system part, a shell water pipe outlet is formed in the radiation end, the radiation end is communicated with the shell water pipe inlet through a water inlet pipe, two interfaces of a three-way regulating valve are integrated on the water inlet pipe, the radiation end is communicated with the shell water pipe outlet through a water return pipe, a water pump is integrated on the water return pipe, the radiation end is fed with water during the work of the water pump, and the other.
Description
Technical Field
The invention relates to the technical field of temperature and humidity control, in particular to a household independent temperature and humidity control system using a double-cold-source heat pump host.
Background
The independent temperature and humidity control system is used for performing temperature and humidity decoupling control on different characteristics of indoor sensible heat and latent heat load of a building. In large buildings, if waste heat is available, humidity control is often performed by using humidity control methods such as rotary dehumidification and saline solution dehumidification, and temperature control is performed by using end forms such as dry coils. The waste heat is utilized to regenerate the moisture absorption material, so that the energy utilization efficiency can be effectively improved. However, the salt solution dehumidification method can cause serious corrosion to the system, and the system is usually complex and is not completely suitable for small and medium-sized residences and office buildings.
Disclosure of Invention
Aiming at the problems, the invention provides a household independent temperature and humidity control system using a double-cold-source heat pump host, which is suitable for independent temperature and humidity control in small and medium-sized residences and office buildings, can effectively improve the energy efficiency of the system, reduce the system cost, and improve the comfort level by combining the zero blowing sense, low noise and zero blowing sense of a radiation air conditioner.
The utility model provides an use family formula humiture independent control system of double cold source heat pump host computer which characterized in that: the integrated double-cold-source air source heat pump comprises an integrated double-cold-source air source heat pump host, a fresh air dehumidifying unit, a three-way regulating valve, a water pump and a radiation tail end, wherein the radiation tail end is arranged indoors, a fresh air outlet end of the fresh air dehumidifying unit is communicated to a fresh air inlet in the room through a pipeline, the integrated double-cold-source air source heat pump host comprises a water system part and a straight expansion part, a shell water pipe inlet and a shell water pipe outlet are arranged on a shell part of the integrated double-cold-source air source heat pump host corresponding to the water system part, the radiation tail end is communicated with the shell water pipe inlet through a water inlet pipe, two interfaces of the three-way regulating valve are integrated on the water inlet pipe, the radiation tail end is communicated with the shell water pipe outlet through a water return pipe, the water pump is integrated on the water return pipe, the water pump is fed into the radiation tail end when the, the pipeline part of the water inlet pipe, which is close to the inlet of the shell water pipe, is connected to the coil pipe No. 1 of the fresh air dehumidifying unit through a first branch, the pipeline part of the water return pipe, which is close to the outlet of the shell water pipe, is connected to the coil pipe No. 1 through a second branch, the shell part is provided with two shell refrigerant pipeline interfaces corresponding to the straight expansion part, namely a first shell refrigerant pipeline interface and a second shell refrigerant pipeline interface, the inner end of the first shell refrigerant pipeline interface is connected with the output end of the refrigerating part, the outer end of the first shell refrigerant pipeline interface is communicated to the coil pipe No. 3 through a pipeline, the outer end of the second shell refrigerant pipeline interface is connected to the coil pipe No. 2 through a pipeline, the coil pipe No. 2 and the coil pipe No. 3 are connected through an electronic expansion valve No. 3, and a fresh air inlet, an air filter, no. 1 coil pipe, No. 2 coil pipe, No. 3 coil pipe, breakwater, humidifier, new trend forced draught blower arrange in order.
It is further characterized in that:
the water system part comprises a water system compressor, a first four-way reversing valve, a first air-cooled heat exchanger provided with a first fan, a first receiver, a first drying filter, a first liquid viewing mirror and a plate heat exchanger, the exhaust pipe of the water system compressor is connected with the D port of the first four-way reversing valve, the C port of the first four-way reversing valve is connected with the first air-cooled heat exchanger, the first air-cooled heat exchanger is connected with a first receiver, a first drying filter, a first liquid viewing mirror and a No. 1 electronic expansion valve in sequence through a refrigerator pipeline and then is connected with a refrigerant pipe of the plate heat exchanger, the refrigerant outlet interface of the plate heat exchanger is connected with the interface E of the first four-way reversing valve, an S port of the first four-way reversing valve is communicated to an air suction pipe of the water system compressor to form a complete water-cooling refrigerating system;
the water inlet pipe is connected to a water inlet of the plate heat exchanger through a shell water pipe inlet, and the water inlet pipe is used as a water supply and return pipe interface of high-temperature chilled water or hot water; the water return pipe is connected to a water outlet of the plate heat exchanger through a shell water pipe outlet, and in a main water system part, the water system is divided into two paths for supplying and returning water, wherein firstly, one path is sent to a No. 1 coil pipe of a multifunctional fresh air dehumidifying unit, namely a water coil pipe, and the fresh air is pretreated; the other water supply pipe is connected with the indoor radiation tail end, so that the air temperature in the regulation and control space can be controlled by using high-temperature chilled water or hot water;
the direct expansion part specifically comprises a direct expansion compressor, a second four-way reversing valve, a second heat exchanger provided with a second fan, a second receiver, a second drying filter, a second liquid viewing mirror and a No. 2 electronic expansion valve, an exhaust pipe of the direct expansion compressor is connected with a D port of the second four-way reversing valve, a C port of the second four-way reversing valve is connected with the second air-cooling heat exchanger, the second air-cooling heat exchanger is sequentially connected with the second receiver, the second drying filter, the second liquid viewing mirror and the No. 2 electronic expansion valve through refrigerator pipelines and then is connected with a No. 3 coil pipe through a pipeline, an outlet of the No. 2 coil pipe is connected with an E port of the second four-way reversing valve through a pipeline, and an S port of the second four-way reversing valve is connected with an air suction pipe of the direct expansion compressor to form a complete direct expansion refrigeration system;
the direct expansion refrigeration system is provided with a No. 2 electronic expansion valve and a No. 3 electronic expansion valve which respectively correspond to the No. 2 coil pipe and the No. 3 coil pipe, when the No. 2 electronic expansion valve is fully opened, the throttling function is not achieved, the No. 3 coil pipe connected with the direct expansion refrigeration system serves as a subcooler, the supercooling degree of a refrigerant at the outlet of the No. 3 coil pipe is improved, the system energy efficiency can be effectively improved, the No. 3 coil pipe plays a role in reheating air supply of a fresh air dehumidifying unit, the No. 3 electronic expansion valve connected between the No. 2 coil pipe and the No. 3 coil pipe serves as a throttling device, and the superheat degree of the system is controlled through the; when the No. 2 electronic expansion valve is used for opening degree adjustment to control the moisture content of the outlet air of the No. 3 coil pipe, the No. 2 electronic expansion valve is used as a primary throttling device, the No. 3 electronic expansion valve connected between the No. 2 coil pipe and the No. 3 coil pipe is used as a secondary throttling device, and the opening degree is used for adjusting and adjusting the superheat degree of a control system;
the temperature and humidity control system can be flexibly applied to small and medium-sized residences and office buildings, and independent temperature and humidity control is realized in annual operation by adopting a system form of combining a fresh air dehumidifier unit and a radiation tail end. Specifically, the main modes of operation of the host include, but are not limited to: transition season working conditions, summer high temperature and high humidity working conditions and winter working conditions.
1) Transition season working conditions: the water system part of the integrated unit operates according to a refrigeration mode, the plate heat exchanger is used as an evaporator to prepare high-temperature chilled water at the temperature of 17 ℃, one branch of the water is sent to a coil pipe 1 of the fresh air dehumidifying unit to be used as a fresh air precooling treatment cold source, and the other branch of the water is sent to the indoor radiation tail end through a water supply pump to control the indoor temperature; meanwhile, the direct-expansion system part of the integrated unit operates according to a refrigeration mode, the No. 2 electronic expansion valve is fully opened at the moment, and the No. 3 coil of the fresh air unit carries out reheating treatment on fresh air subjected to cooling and dehumidifying treatment.
2) Summer high-temperature high-humidity working condition: the running mode of the water system part of the integrated unit is consistent with that of the integrated unit 1), and in the direct expansion part of the integrated unit, the electronic expansion valve No. 2 performs primary throttling, the coil pipe No. 3 operates as a direct expansion evaporator, fresh air is further cooled and dehumidified, the electronic expansion valve No. 3 performs secondary throttling, the surface temperature of the coil pipe of the direct expansion refrigerant No. 2 is further reduced, the fresh air is deeply dehumidified, the moisture content of the fresh air is low enough, and therefore indoor high humidity load is borne. The No. 2 electronic expansion valve is used for opening degree adjustment to control the moisture content of fresh air supply, and the No. 3 electronic expansion valve is used for opening degree adjustment to control the superheat degree of the system.
3) Working conditions in winter: the water system part of integral type unit is according to the mode operation that heats, through the switching-over of four-way reversing valve, and plate heat exchanger moves as the condenser, prepares hot water, and fresh air unit preheats as winter new trend is sent into in a branch road, and another branch road sends into indoor radiation end through mixing water governing valve and working shaft, carries out indoor temperature control. Meanwhile, the direct expansion type part of the integrated unit operates according to a heating mode and is reversed through a four-way reversing valve, the coil pipe No. 2 operates as a condenser to heat fresh air, the electronic expansion valve No. 3 is fully opened and does not play a throttling role, the coil pipe No. 3 also operates as a condenser to further heat the fresh air, the electronic expansion valve No. 2 plays a throttling role, and the superheat degree of the opening degree adjusting system is passed through.
It cools down the dehumidification to the new trend through new trend dehumidifier group, handles the new trend to lower moisture content to undertake indoor moisture load, carry out humidity control to the room air, along new trend air inlet direction in proper order be air cleaner, No. 1 coil pipe, No. 2 coil pipes, No. 3 coil pipes, breakwater, humidifier and forced draught blower, corresponding with the host computer operational mode, the new trend unit has different functions under different operational mode. In the working condition of a transition season, fresh air is filtered, is pretreated by high-temperature chilled water through a No. 1 coil pipe, is cooled and dehumidified through a No. 2 coil pipe, is reheated by a No. 3 coil pipe and is sent into a room; in the working condition of high temperature and high humidity in summer, fresh air is deeply dehumidified by the coil pipe No. 2 after being filtered and precooled by the coil pipe No. 1, and is further cooled and dehumidified at the coil pipe No. 3, so that the dehumidification effect of the fresh air is ensured; in winter working conditions, fresh air is filtered and preheated by the coil pipe No. 1, is respectively heated by the coil pipes No. 2 and No. 3, and is sent into a room after being humidified.
After adopting this system, it has following beneficial effect:
1. according to the air conditioning system, independent control of indoor temperature and humidity of a building is achieved by combining fresh air dehumidification with radiation tail end, the problems of indoor blowing feeling and uneven temperature distribution caused by a traditional air conditioning mode can be effectively solved, the thermal comfort of indoor users is effectively improved, and the filtered and dehumidified (humidified) fresh air can effectively regulate and control indoor humidity, so that the indoor air quality is guaranteed;
2. two cold source air source heat pump host computers of system cold source host computer formula as an organic whole in this application, its water system part provides high temperature refrigerated water or hot water for radiation end and new trend preliminary treatment, therefore refrigerating system's evaporating temperature can improve greatly to effectively improve refrigeration cycle's efficiency, and the formula system part of directly expanding of host computer utilizes the direct and air heat transfer of refrigerant coil pipe, has reduced the loss that many times of heat transfer caused, and heat exchange efficiency improves, can reduce unit installed capacity, effective reduce cost.
3. The direct-expansion system part of the integrated double-cold-source air source heat pump host machine can realize the function of recovering partial condensation heat and reduce the energy consumption of the unit through the matching of different operation conditions of the two electronic expansion valves.
Drawings
FIG. 1 is a block diagram schematically illustrating a system according to the present invention;
the names corresponding to the sequence numbers in the figure are as follows:
integrated double-cold-source air source heat pump host 1, water system part 100 and straight expansion part 200
Fresh air dehumidifying unit 2, air filter 21, coil pipe No. 1, coil pipe No. 2, coil pipe No. 3, coil pipe No. 24, water baffle 25, humidifier 26, fresh air blower 27
Three-way regulating valve 3, water pump 4, radiation tail end 5, water inlet pipe 6, water return pipe 7, first branch 8 and second branch 9
The system comprises a water system compressor 11, a first four-way reversing valve 12, a first fan 13, a first air-cooled heat exchanger 14, a first receiver 15, a first drying filter 16, a first liquid observation mirror 17, an electronic expansion valve 18 No. 1, a plate heat exchanger 19, a shell water pipe inlet 110, a shell water pipe outlet 111, a straight expansion compressor 112, a second four-way reversing valve 113, a second fan 114, a second heat exchanger 115, a second receiver 116, a second drying filter 117, a second liquid observation mirror 118, an electronic expansion valve 119 No. 2, a first shell refrigerant pipeline interface 120, a second shell refrigerant pipeline interface 121 and an electronic expansion valve 122 No. 3.
Detailed Description
A household independent temperature and humidity control system using a double cold source heat pump host machine is shown in figure 1: the integrated double-cold-source air source heat pump comprises an integrated double-cold-source air source heat pump host 1, a fresh air dehumidifying unit 2, a three-way regulating valve 3, a water pump 4 and a radiation tail end 5, wherein the radiation tail end 5 is arranged indoors, a fresh air outlet end of the fresh air dehumidifying unit 2 is communicated to an indoor fresh air inlet through a pipeline, the integrated double-cold-source air source heat pump host 1 comprises a water system part 100 and a straight expansion part 200, a shell water pipe inlet 110 and a shell water pipe outlet 111 are arranged on a shell part of the integrated double-cold-source air source heat pump host 1 corresponding to the water system part 100, the radiation tail end 5 is communicated with the shell water pipe inlet 110 through a water inlet pipe 6, two interfaces of the three-way regulating valve 3 are integrated on the water inlet pipe 6, the radiation tail end 5 is communicated with the shell water pipe outlet 111 through a water return pipe 7, the water pump 4 is integrated on the water return pipe 7, the, the pipeline part of the water inlet pipe 6, which is positioned close to the shell water pipe inlet 110, is connected to the coil pipe 22 No. 1 of the fresh air dehumidifying unit 2 through the first branch 8, the pipeline part of the water return pipe 7, which is positioned close to the shell water pipe outlet 111, is connected to the coil pipe 22 No. 1 through the second branch 9, in order to prevent dew condensation on the radiation tip surface, which is caused by the radiation tip surface temperature being lower than the dew point temperature of the indoor air, precise and sensitive control of the chilled water supply water temperature of the radiation tip 5 is required, after the second branch 9 of the water return pipe 7, a three-way regulating valve 3 is arranged for mixed water temperature control, the water supply temperature of the radiation tail end 5 is accurately controlled to be higher than the dew point temperature of indoor air, because of the three-way regulating valve 3, the system resistance is increased, and in order to ensure that high-temperature chilled water or hot water can be smoothly fed into the water collecting and distributing device and the radiation tail end, the water outlet of the three-way regulating valve 3 is connected with the water pump 4;
the shell part is provided with two shell refrigerant pipeline interfaces corresponding to the straight expansion part 200, the shell refrigerant pipeline interfaces are a first shell refrigerant pipeline interface 120 and a second shell refrigerant pipeline interface 121 respectively, the inner end of the first shell refrigerant pipeline interface 120 is connected with the output end of the refrigeration part, the outer end of the first shell refrigerant pipeline interface 120 is communicated to a No. 3 coil pipe 24 through a pipeline, the outer end of the second shell refrigerant pipeline interface 121 is connected to a No. 2 coil pipe 23 through a pipeline, the No. 2 coil pipe 23 and the No. 3 coil pipe 24 are connected through a No. 3 electronic expansion valve 122, a fresh air inlet in the fresh air dehumidification unit 2, an air filter 21, a No. 1 coil pipe 22, a No. 2 coil pipe 23, a No. 3 coil pipe 24, a water baffle 25, a humidifier 26 and a fresh air.
The water system part 100 specifically comprises a water system compressor 11, a first four-way reversing valve 12, a first air-cooled heat exchanger 14 provided with a first fan 13, a first receiver 15, a first drying filter 16, a first liquid viewing mirror 17 and a plate heat exchanger 19, an exhaust pipe of a water system compressor 11 is connected with a D port of a first four-way reversing valve 12, a C port of the first four-way reversing valve 12 is connected with a first air-cooled heat exchanger 14, the first air-cooled heat exchanger 14 is respectively connected with a first receiver 14, a first receiver 15, a first drying filter 16, a first liquid viewing mirror 17 and a No. 1 electronic expansion valve 18 in sequence through a refrigerator pipeline and then is connected with a refrigerant pipe of a plate heat exchanger 19, a refrigerant outlet interface of the plate heat exchanger 19 is connected with an E interface of the first four-way reversing valve 12, and an S interface of the first four-way reversing valve 12 is communicated with an air suction pipe of the water system compressor 11 to form a complete water-cooled refrigeration system;
the water inlet pipe 6 is connected to the water inlet of the plate heat exchanger 19 through the shell water pipe inlet 110, and the water inlet pipe 6 is used as a water supply and return pipe interface of high-temperature chilled water or hot water; the water return pipe 7 is connected to a water outlet of the plate heat exchanger 19 through a shell water pipe outlet 111, and in a main water system part, the water system is divided into two paths for supplying water, wherein firstly, one path is sent to the coil pipe 22 No. 1 of the multifunctional fresh air dehumidifying unit 2, namely a water coil pipe, so as to pretreat fresh air; the other water supply pipe is connected with the indoor radiation tail end 5, so that the air temperature in the regulation and control space can be controlled by using high-temperature chilled water or hot water;
the straight expansion part 200 specifically comprises a straight expansion compressor 112, a second four-way reversing valve 113, a second heat exchanger 115 provided with a second fan 114, a second receiver 116, a second drying filter 117, a second liquid viewing mirror 118, a No. 2 electronic expansion valve 119, an exhaust pipe of the straight expansion compressor 112 is connected with a port D of a second four-way reversing valve 113, a port C of the second four-way reversing valve 113 is connected with a second air-cooled heat exchanger 115, the second air-cooled heat exchanger 115 is respectively connected with a second receiver 115, a second receiver 116, a second drying filter 117, a second liquid viewing mirror 118 and a No. 2 electronic expansion valve 119 in sequence through refrigerator pipelines and then is connected to a No. 3 coil 24 through pipelines, an outlet of the No. 2 coil 23 is connected with a port E of the second four-way reversing valve 113 through a pipeline, and a port S of the second four-way reversing valve 113 is connected with an air suction pipe of the straight expansion compressor 112 to form a complete straight expansion refrigeration system;
the direct expansion refrigeration system is provided with a No. 2 electronic expansion valve 119 and a No. 3 electronic expansion valve 122 which respectively correspond to the No. 2 coil 23 and the No. 3 coil 24, when the No. 2 electronic expansion valve 119 is fully opened, no throttling function is realized, the No. 3 coil 24 connected with the direct expansion refrigeration system is used as a subcooler, the supercooling degree of a refrigerant at the outlet of the No. 3 coil 24 is improved, the system energy efficiency can be effectively improved, the No. 3 coil 24 has a reheating function on the air supply of the fresh air dehumidifier unit 2, the No. 3 electronic expansion valve 122 connected between the No. 2 coil 23 and the No. 3 coil 24 is used as a throttling device, and the superheat degree of the system is controlled through the opening; when the electronic expansion valve 119 No. 2 performs opening degree adjustment to control the moisture content of the outlet air of the coil pipe 24 No. 3, the electronic expansion valve 119 No. 2 serves as a primary throttling device, the electronic expansion valve 122 No. 3 connected between the coil pipe 23 No. 2 and the coil pipe 24 No. 3 serves as a secondary throttling device, and the superheat degree of the system is adjusted and controlled by utilizing the opening degree;
the temperature and humidity control system can be flexibly applied to small and medium-sized residences and office buildings, and independent temperature and humidity control is realized in annual operation by adopting a system form of combining a fresh air dehumidifier unit and a radiation tail end. Specifically, the main modes of operation of the host include, but are not limited to: transition season working conditions, summer high temperature and high humidity working conditions and winter working conditions.
1) Transition season working conditions: the water system part of the integrated unit operates according to a refrigeration mode, the plate heat exchanger is used as an evaporator to prepare high-temperature chilled water at the temperature of 17 ℃, one branch of the water is sent to a coil pipe 1 of the fresh air dehumidifying unit to be used as a fresh air precooling treatment cold source, and the other branch of the water is sent to the indoor radiation tail end through a water supply pump to control the indoor temperature; meanwhile, the direct-expansion system part of the integrated unit operates according to a refrigeration mode, the No. 2 electronic expansion valve is fully opened at the moment, and the No. 3 coil of the fresh air unit carries out reheating treatment on fresh air subjected to cooling and dehumidifying treatment.
2) Summer high-temperature high-humidity working condition: the running mode of the water system part of the integrated unit is consistent with that of the integrated unit 1), and in the direct expansion part of the integrated unit, the electronic expansion valve No. 2 performs primary throttling, the coil pipe No. 3 operates as a direct expansion evaporator, fresh air is further cooled and dehumidified, the electronic expansion valve No. 3 performs secondary throttling, the surface temperature of the coil pipe of the direct expansion refrigerant No. 2 is further reduced, the fresh air is deeply dehumidified, the moisture content of the fresh air is low enough, and therefore indoor high humidity load is borne. The No. 2 electronic expansion valve is used for opening degree adjustment to control the moisture content of fresh air supply, and the No. 3 electronic expansion valve is used for opening degree adjustment to control the superheat degree of the system.
3) Working conditions in winter: the water system part of integral type unit is according to the mode operation that heats, through the switching-over of four-way reversing valve, and plate heat exchanger moves as the condenser, prepares hot water, and fresh air unit preheats as winter new trend is sent into in a branch road, and another branch road sends into indoor radiation end through mixing water governing valve and working shaft, carries out indoor temperature control. Meanwhile, the direct expansion type part of the integrated unit operates according to a heating mode and is reversed through a four-way reversing valve, the coil pipe No. 2 operates as a condenser to heat fresh air, the electronic expansion valve No. 3 is fully opened and does not play a throttling role, the coil pipe No. 3 also operates as a condenser to further heat the fresh air, the electronic expansion valve No. 2 plays a throttling role, and the superheat degree of the opening degree adjusting system is passed through.
It cools down the dehumidification to the new trend through new trend dehumidifier group, handles the new trend to lower moisture content to undertake indoor moisture load, carry out humidity control to the room air, along new trend air inlet direction in proper order be air cleaner, No. 1 coil pipe, No. 2 coil pipes, No. 3 coil pipes, breakwater, humidifier and forced draught blower, corresponding with the host computer operational mode, the new trend unit has different functions under different operational mode. In the working condition of a transition season, fresh air is filtered, is pretreated by high-temperature chilled water through a No. 1 coil pipe, is cooled and dehumidified through a No. 2 coil pipe, is reheated by a No. 3 coil pipe and is sent into a room; in the working condition of high temperature and high humidity in summer, fresh air is deeply dehumidified by the coil pipe No. 2 after being filtered and precooled by the coil pipe No. 1, and is further cooled and dehumidified at the coil pipe No. 3, so that the dehumidification effect of the fresh air is ensured; in winter working conditions, fresh air is filtered and preheated by the coil pipe No. 1, is respectively heated by the coil pipes No. 2 and No. 3, and is sent into a room after being humidified.
After adopting this system, it has following beneficial effect:
1. according to the air conditioning system, independent control of indoor temperature and humidity of a building is achieved by combining fresh air dehumidification with radiation tail end, the problems of indoor blowing feeling and uneven temperature distribution caused by a traditional air conditioning mode can be effectively solved, the thermal comfort of indoor users is effectively improved, and the filtered and dehumidified (humidified) fresh air can effectively regulate and control indoor humidity, so that the indoor air quality is guaranteed;
2. two cold source air source heat pump host computers of system cold source host computer formula as an organic whole in this application, its water system part provides high temperature refrigerated water or hot water for radiation end and new trend preliminary treatment, therefore refrigerating system's evaporating temperature can improve greatly to effectively improve refrigeration cycle's efficiency, and the formula system part of directly expanding of host computer utilizes the direct and air heat transfer of refrigerant coil pipe, has reduced the loss that many times of heat transfer caused, and heat exchange efficiency improves, can reduce unit installed capacity, effective reduce cost.
3. The direct-expansion system part of the integrated double-cold-source air source heat pump host machine can realize the function of recovering partial condensation heat and reduce the energy consumption of the unit through the matching of different operation conditions of the two electronic expansion valves.
It will be evident to those skilled in the art that the invention is not limited to the details of the foregoing illustrative embodiments, and that the present invention may be embodied in other specific forms without departing from the spirit or essential attributes thereof. The present embodiments are therefore to be considered in all respects as illustrative and not restrictive, the scope of the invention being indicated by the appended claims rather than by the foregoing description, and all changes which come within the meaning and range of equivalency of the claims are therefore intended to be embraced therein. Any reference sign in a claim should not be construed as limiting the claim concerned.
Furthermore, it should be understood that although the present description refers to embodiments, not every embodiment may contain only a single embodiment, and such description is for clarity only, and those skilled in the art should integrate the description, and the embodiments may be combined as appropriate to form other embodiments understood by those skilled in the art.
Claims (7)
1. The utility model provides an use family formula humiture independent control system of double cold source heat pump host computer which characterized in that: the integrated double-cold-source air source heat pump comprises an integrated double-cold-source air source heat pump host, a fresh air dehumidifying unit, a three-way regulating valve, a water pump and a radiation tail end, wherein the radiation tail end is arranged indoors, a fresh air outlet end of the fresh air dehumidifying unit is communicated to a fresh air inlet in the room through a pipeline, the integrated double-cold-source air source heat pump host comprises a water system part and a straight expansion part, a shell water pipe inlet and a shell water pipe outlet are arranged on a shell part of the integrated double-cold-source air source heat pump host corresponding to the water system part, the radiation tail end is communicated with the shell water pipe inlet through a water inlet pipe, two interfaces of the three-way regulating valve are integrated on the water inlet pipe, the radiation tail end is communicated with the shell water pipe outlet through a water return pipe, the water pump is integrated on the water return pipe, the water pump is fed into the radiation tail end when the, the pipeline part of the water inlet pipe, which is close to the inlet of the shell water pipe, is connected to the coil pipe No. 1 of the fresh air dehumidifying unit through a first branch, the pipeline part of the water return pipe, which is close to the outlet of the shell water pipe, is connected to the coil pipe No. 1 through a second branch, the shell part is provided with two shell refrigerant pipeline interfaces corresponding to the straight expansion part, namely a first shell refrigerant pipeline interface and a second shell refrigerant pipeline interface, the inner end of the first shell refrigerant pipeline interface is connected with the output end of the refrigerating part, the outer end of the first shell refrigerant pipeline interface is communicated to the coil pipe No. 3 through a pipeline, the outer end of the second shell refrigerant pipeline interface is connected to the coil pipe No. 2 through a pipeline, the coil pipe No. 2 and the coil pipe No. 3 are connected through an electronic expansion valve No. 3, and a fresh air inlet, an air filter, no. 1 coil pipe, No. 2 coil pipe, No. 3 coil pipe, breakwater, humidifier, new trend forced draught blower arrange in order.
2. The household independent temperature and humidity control system using the dual cold source heat pump host machine according to claim 1, characterized in that: the water system part comprises a water system compressor, a first four-way reversing valve, a first air-cooled heat exchanger provided with a first fan, a first receiver, a first drying filter, a first liquid viewing mirror and a plate heat exchanger, the exhaust pipe of the water system compressor is connected with the D port of the first four-way reversing valve, the C port of the first four-way reversing valve is connected with the first air-cooled heat exchanger, the first air-cooled heat exchanger is connected with a first receiver, a first drying filter, a first liquid viewing mirror and a No. 1 electronic expansion valve in sequence through a refrigerator pipeline and then is connected with a refrigerant pipe of the plate heat exchanger, the refrigerant outlet interface of the plate heat exchanger is connected with the interface E of the first four-way reversing valve, and an S port of the first four-way reversing valve is communicated to an air suction pipe of the water system compressor to form a complete water-cooling refrigerating system.
3. The household independent temperature and humidity control system using the dual cold source heat pump host machine according to claim 2, characterized in that: the water inlet pipe is connected to a water inlet of the plate heat exchanger through a shell water pipe inlet, and the water inlet pipe is used as a water supply and return pipe interface of high-temperature chilled water or hot water; the water return pipe is connected to a water outlet of the plate heat exchanger through a shell water pipe outlet, and in a main water system part, the water system is divided into two paths for supplying and returning water, wherein firstly, one path is sent to a No. 1 coil pipe of a multifunctional fresh air dehumidifying unit, namely a water coil pipe, and the fresh air is pretreated; the other water supply pipe is connected with the indoor radiation tail end.
4. The household independent temperature and humidity control system using the dual cold source heat pump host machine according to claim 3, characterized in that: the direct expansion part specifically comprises a direct expansion compressor, a second four-way reversing valve, a second heat exchanger provided with a second fan, a second receiver, a second drying filter, a second liquid viewing mirror and a No. 2 electronic expansion valve, wherein an exhaust pipe of the direct expansion compressor is connected with a port D of the second four-way reversing valve, a port C of the second four-way reversing valve is connected with the second air-cooling heat exchanger, the second air-cooling heat exchanger is sequentially connected with the second receiver, the second drying filter, the second liquid viewing mirror and the No. 2 electronic expansion valve through refrigerator pipelines and then is connected to a No. 3 coil pipe through a pipeline, an outlet of the No. 2 coil pipe is connected with a port E of the second four-way reversing valve through a pipeline, and a port S of the second four-way reversing valve is connected with an air suction pipe of the direct expansion compressor to form a complete direct expansion refrigeration system.
5. The system of claim 4, wherein the system comprises: the direct expansion refrigeration system is provided with a No. 2 electronic expansion valve and a No. 3 electronic expansion valve which respectively correspond to the No. 2 coil pipe and the No. 3 coil pipe, when the No. 2 electronic expansion valve is fully opened, the throttling function is not achieved, the No. 3 coil pipe connected with the direct expansion refrigeration system serves as a subcooler, the supercooling degree of a refrigerant at the outlet of the No. 3 coil pipe is improved, the system energy efficiency can be effectively improved, the No. 3 coil pipe plays a role in reheating air supply of a fresh air dehumidifying unit, the No. 3 electronic expansion valve connected between the No. 2 coil pipe and the No. 3 coil pipe serves as a throttling device, and the superheat degree of the system is controlled through the; when the No. 2 electronic expansion valve performs opening degree adjustment to control the moisture content of the outlet air of the No. 3 coil pipe, the No. 2 electronic expansion valve is used as a primary throttling device, and the No. 3 electronic expansion valve connected between the No. 2 coil pipe and the No. 3 coil pipe is used as a secondary throttling device.
6. The system of claim 5, wherein the system is used in small and medium-sized residential and office buildings, and adopts a system form of combining a fresh air dehumidifier unit and a radiation end to realize independent temperature and humidity control in annual operation, and the main modes of operation include, but are not limited to: transition season working conditions, summer high-temperature high-humidity working conditions and winter working conditions;
1) transition season working conditions: the water system part of the integrated unit operates according to a refrigeration mode, the plate heat exchanger is used as an evaporator to prepare high-temperature chilled water at the temperature of 17 ℃, one branch of the water is sent to a coil pipe 1 of the fresh air dehumidifying unit to be used as a fresh air precooling treatment cold source, and the other branch of the water is sent to the indoor radiation tail end through a water supply pump to control the indoor temperature; meanwhile, the direct-expansion system part of the integrated unit operates according to a refrigeration mode, the No. 2 electronic expansion valve is fully opened at the moment, and the No. 3 coil of the fresh air unit carries out reheating treatment on fresh air subjected to cooling and dehumidifying treatment.
2) Summer high-temperature high-humidity working condition: the running mode of the water system part of the integrated unit is consistent with that of the integrated unit 1), and in the direct expansion part of the integrated unit, the electronic expansion valve No. 2 performs primary throttling, the coil pipe No. 3 operates as a direct expansion evaporator, fresh air is further cooled and dehumidified, the electronic expansion valve No. 3 performs secondary throttling, the surface temperature of the coil pipe of the direct expansion refrigerant No. 2 is further reduced, the fresh air is deeply dehumidified, the moisture content of the fresh air is low enough, and therefore indoor high humidity load is borne. The No. 2 electronic expansion valve is used for opening degree adjustment to control the moisture content of fresh air supply, and the No. 3 electronic expansion valve is used for opening degree adjustment to control the superheat degree of the system.
3) Working conditions in winter: the water system part of integral type unit is according to the mode operation that heats, through the switching-over of four-way reversing valve, and plate heat exchanger moves as the condenser, prepares hot water, and fresh air unit preheats as winter new trend is sent into in a branch road, and another branch road sends into indoor radiation end through mixing water governing valve and working shaft, carries out indoor temperature control. Meanwhile, the direct expansion type part of the integrated unit operates according to a heating mode and is reversed through a four-way reversing valve, the coil pipe No. 2 operates as a condenser to heat fresh air, the electronic expansion valve No. 3 is fully opened and does not play a throttling role, the coil pipe No. 3 also operates as a condenser to further heat the fresh air, the electronic expansion valve No. 2 plays a throttling role, and the superheat degree of the opening degree adjusting system is passed through.
7. The system of claim 6, wherein the system comprises: the fresh air dehumidifier unit is used for cooling and dehumidifying fresh air, treating the fresh air to lower moisture content so as to bear indoor moisture load and control the humidity of indoor air, and the fresh air dehumidifier unit comprises an air filter, a coil pipe 1, a coil pipe 2, a coil pipe 3, a water baffle, a humidifier and a blower in sequence along the fresh air inlet direction, corresponds to a host machine operation mode, and has different functions under different operation modes; in the working condition of a transition season, fresh air is filtered, is pretreated by high-temperature chilled water through a No. 1 coil pipe, is cooled and dehumidified through a No. 2 coil pipe, is reheated by a No. 3 coil pipe and is sent into a room; in the working condition of high temperature and high humidity in summer, fresh air is deeply dehumidified by the coil pipe No. 2 after being filtered and precooled by the coil pipe No. 1, and is further cooled and dehumidified at the coil pipe No. 3, so that the dehumidification effect of the fresh air is ensured; in winter working conditions, fresh air is filtered and preheated by the coil pipe No. 1, is respectively heated by the coil pipes No. 2 and No. 3, and is sent into a room after being humidified.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202011276025.6A CN112378061B (en) | 2020-11-16 | 2020-11-16 | Household independent temperature and humidity control system using double-cold-source heat pump host |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202011276025.6A CN112378061B (en) | 2020-11-16 | 2020-11-16 | Household independent temperature and humidity control system using double-cold-source heat pump host |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN112378061A true CN112378061A (en) | 2021-02-19 |
| CN112378061B CN112378061B (en) | 2022-06-14 |
Family
ID=74584068
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202011276025.6A Active CN112378061B (en) | 2020-11-16 | 2020-11-16 | Household independent temperature and humidity control system using double-cold-source heat pump host |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN112378061B (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113390183A (en) * | 2021-05-14 | 2021-09-14 | 广东奥伯特节能设备有限公司 | High-temperature water source heat pump air heater |
| CN114135948A (en) * | 2021-11-26 | 2022-03-04 | 珠海格力电器股份有限公司 | Air conditioning system for cardiac surgery operating room and control method thereof |
| CN114263997A (en) * | 2021-12-23 | 2022-04-01 | 上海朗绿建筑科技股份有限公司 | Temperature and humidity separately-controlled household air conditioning system |
Citations (17)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB9311239D0 (en) * | 1992-06-02 | 1993-07-21 | Toshiba Kk | Air conditioning apparatus having a dehumidifying operation |
| JP2000043563A (en) * | 1998-07-31 | 2000-02-15 | Calsonic Corp | Air-conditioning and heating equipment for automobile |
| EP2246208A2 (en) * | 2009-04-29 | 2010-11-03 | Behr GmbH & Co. KG | Motor vehicle air conditioning |
| CN202024421U (en) * | 2011-04-23 | 2011-11-02 | 郑文伟 | Water-cooling refrigerant direct-expansion variable air volume air handling unit |
| CN102705920A (en) * | 2012-05-24 | 2012-10-03 | 吕智 | Double-cold-source heat pump total heat recovery humidity regulating and temperature controlling fresh air unit and control method thereof |
| DE102012205200A1 (en) * | 2011-04-04 | 2012-10-04 | Denso Corporation | Refrigerant cycle device |
| CN103411278A (en) * | 2013-08-23 | 2013-11-27 | 机械工业第三设计研究院 | Fresh air handling unit suitable for air conditioning system allowing independent temperature and humidity control |
| CN103900184A (en) * | 2014-04-25 | 2014-07-02 | 荣国华 | Water cooling medium three-pipe refrigerating and heating air-conditioning system |
| CN105091231A (en) * | 2015-08-11 | 2015-11-25 | 青岛海尔空调器有限总公司 | Air conditioner and method for switching air conditioner from refrigeration mode to constant-temperature dehumidification mode |
| CN206234930U (en) * | 2016-11-28 | 2017-06-09 | 中机中联工程有限公司 | A kind of warm and humid sub-control Fresh air handling units based on high temperature chilled water |
| CN207907434U (en) * | 2018-01-15 | 2018-09-25 | 广东省建筑科学研究院集团股份有限公司 | A kind of double low-temperature receiver depth dehumidifying fresh air treatment systems |
| CN108679747A (en) * | 2018-07-23 | 2018-10-19 | 珠海格力电器股份有限公司 | Fresh air dehumidification air conditioning system |
| CN109405325A (en) * | 2018-11-30 | 2019-03-01 | 上海朗绿建筑科技股份有限公司 | Double cold source fresh air dehumidification units |
| CN109595703A (en) * | 2018-12-10 | 2019-04-09 | 江苏致远高科能源科技有限公司 | A kind of multistage cold source swimming pool heat pump dehumidifier and its working method |
| CN109724175A (en) * | 2019-02-20 | 2019-05-07 | 中国人民解放军63921部队 | The energy-saving fresh freeze drying system of low dew-point air supply |
| CN208936579U (en) * | 2018-06-20 | 2019-06-04 | 江苏三六五室内环境科技有限公司 | A kind of fresh air conditioner system of independent temperature-humidity control |
| CN110617567A (en) * | 2019-08-30 | 2019-12-27 | 江苏致远高科能源科技有限公司 | Method for designing double-cold-source fresh air dehumidifier according to cold quantity division ratio |
-
2020
- 2020-11-16 CN CN202011276025.6A patent/CN112378061B/en active Active
Patent Citations (17)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB9311239D0 (en) * | 1992-06-02 | 1993-07-21 | Toshiba Kk | Air conditioning apparatus having a dehumidifying operation |
| JP2000043563A (en) * | 1998-07-31 | 2000-02-15 | Calsonic Corp | Air-conditioning and heating equipment for automobile |
| EP2246208A2 (en) * | 2009-04-29 | 2010-11-03 | Behr GmbH & Co. KG | Motor vehicle air conditioning |
| DE102012205200A1 (en) * | 2011-04-04 | 2012-10-04 | Denso Corporation | Refrigerant cycle device |
| CN202024421U (en) * | 2011-04-23 | 2011-11-02 | 郑文伟 | Water-cooling refrigerant direct-expansion variable air volume air handling unit |
| CN102705920A (en) * | 2012-05-24 | 2012-10-03 | 吕智 | Double-cold-source heat pump total heat recovery humidity regulating and temperature controlling fresh air unit and control method thereof |
| CN103411278A (en) * | 2013-08-23 | 2013-11-27 | 机械工业第三设计研究院 | Fresh air handling unit suitable for air conditioning system allowing independent temperature and humidity control |
| CN103900184A (en) * | 2014-04-25 | 2014-07-02 | 荣国华 | Water cooling medium three-pipe refrigerating and heating air-conditioning system |
| CN105091231A (en) * | 2015-08-11 | 2015-11-25 | 青岛海尔空调器有限总公司 | Air conditioner and method for switching air conditioner from refrigeration mode to constant-temperature dehumidification mode |
| CN206234930U (en) * | 2016-11-28 | 2017-06-09 | 中机中联工程有限公司 | A kind of warm and humid sub-control Fresh air handling units based on high temperature chilled water |
| CN207907434U (en) * | 2018-01-15 | 2018-09-25 | 广东省建筑科学研究院集团股份有限公司 | A kind of double low-temperature receiver depth dehumidifying fresh air treatment systems |
| CN208936579U (en) * | 2018-06-20 | 2019-06-04 | 江苏三六五室内环境科技有限公司 | A kind of fresh air conditioner system of independent temperature-humidity control |
| CN108679747A (en) * | 2018-07-23 | 2018-10-19 | 珠海格力电器股份有限公司 | Fresh air dehumidification air conditioning system |
| CN109405325A (en) * | 2018-11-30 | 2019-03-01 | 上海朗绿建筑科技股份有限公司 | Double cold source fresh air dehumidification units |
| CN109595703A (en) * | 2018-12-10 | 2019-04-09 | 江苏致远高科能源科技有限公司 | A kind of multistage cold source swimming pool heat pump dehumidifier and its working method |
| CN109724175A (en) * | 2019-02-20 | 2019-05-07 | 中国人民解放军63921部队 | The energy-saving fresh freeze drying system of low dew-point air supply |
| CN110617567A (en) * | 2019-08-30 | 2019-12-27 | 江苏致远高科能源科技有限公司 | Method for designing double-cold-source fresh air dehumidifier according to cold quantity division ratio |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113390183A (en) * | 2021-05-14 | 2021-09-14 | 广东奥伯特节能设备有限公司 | High-temperature water source heat pump air heater |
| CN114135948A (en) * | 2021-11-26 | 2022-03-04 | 珠海格力电器股份有限公司 | Air conditioning system for cardiac surgery operating room and control method thereof |
| CN114263997A (en) * | 2021-12-23 | 2022-04-01 | 上海朗绿建筑科技股份有限公司 | Temperature and humidity separately-controlled household air conditioning system |
Also Published As
| Publication number | Publication date |
|---|---|
| CN112378061B (en) | 2022-06-14 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN201652636U (en) | Double-cold-source heat recovery constant temperature and humidity air conditioning unit | |
| CN112378061B (en) | Household independent temperature and humidity control system using double-cold-source heat pump host | |
| CN203177357U (en) | Domestic fresh air dehumidifier | |
| CN112254209A (en) | Two-pipe refrigerating and condensing reheating fresh air system and control method thereof | |
| CN112460696B (en) | Temperature and humidity independent control air conditioning system | |
| CN101294755A (en) | Air-conditioning unit with constant temperature and humidity | |
| CN101216225A (en) | Double temperature cold water/cold air unit | |
| CN113048587B (en) | Freezing and rotating wheel dehumidification coupling heat recovery temperature and humidity separation control air treatment system | |
| CN111442448A (en) | Combined air conditioning unit for independently cooling and dehumidifying fresh air | |
| CN110966696B (en) | Refrigerant radiation wall integrated air conditioning system with solar energy injection function and air conditioner | |
| CN103363711B (en) | Air conditioner capable of controlling temperature and humidity separately | |
| CN114087743B (en) | Heat pipe fresh air machine, control method thereof and computer readable storage medium | |
| CN104566720A (en) | Precision machine room air condition compressor fluorine pump refrigerating cycle system | |
| CN104315633A (en) | Water chiller unit, operating method and refrigerant for air-conditioner refrigeration field | |
| CN110749018A (en) | Single-machine two-stage compression middle air exhaust heat recovery fresh air processing device | |
| CN108105917B (en) | Combined air conditioner | |
| KR100926480B1 (en) | Air Conditioner | |
| CN110160180B (en) | Composite energy air treatment unit | |
| CN210688501U (en) | Two-pipe double-cold-source all-year-round operation constant-temperature and constant-humidity air conditioning unit | |
| CN209819742U (en) | Variable-frequency multi-connected radiation heating and refrigerating air conditioning system | |
| CN113776220B (en) | Room air conditioner and control method thereof | |
| KR102257544B1 (en) | Energy enhanced air-conditioning system and control method thereof | |
| CN104089350B (en) | A kind of warm and humid independent control soil natural source capillary tube air conditioning system | |
| CN203478699U (en) | Air conditioning system with fresh air processed by two states and temperature and humidity controlled separately | |
| CN109520046B (en) | Air-cooled compression type refrigeration and evaporation refrigeration combined double-cold-source device |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |