CN112460696A - Temperature and humidity independent control air conditioning system - Google Patents
Temperature and humidity independent control air conditioning system Download PDFInfo
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- CN112460696A CN112460696A CN202011360621.2A CN202011360621A CN112460696A CN 112460696 A CN112460696 A CN 112460696A CN 202011360621 A CN202011360621 A CN 202011360621A CN 112460696 A CN112460696 A CN 112460696A
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F3/00—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems
- F24F3/12—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling
- F24F3/14—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification
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- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F13/00—Details common to, or for air-conditioning, air-humidification, ventilation or use of air currents for screening
- F24F13/28—Arrangement or mounting of filters
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F13/00—Details common to, or for air-conditioning, air-humidification, ventilation or use of air currents for screening
- F24F13/30—Arrangement or mounting of heat-exchangers
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- 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
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- 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
- F25B49/00—Arrangement or mounting of control or safety devices
- F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F2221/00—Details or features not otherwise provided for
- F24F2221/34—Heater, e.g. gas burner, electric air heater
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- 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
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
- F25B2313/02742—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using two four-way valves
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
- Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
- Y02B30/12—Hot water central heating systems using heat pumps
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Central Air Conditioning (AREA)
Abstract
The invention relates to a temperature and humidity independent control air conditioning system, which comprises a refrigerant flow path X, a refrigerant flow path Y, a waterway flow path and an air flow path; a plurality of water channel valves are arranged in the water channel in parallel and/or in series, and the distribution of cold/hot water output by the refrigerant channel X and the refrigerant channel Y in the water coil is realized by the opening and closing of the water channel valves, so that cold water generated by the refrigerant channel X in summer is only supplied to mixed air for deep dehumidification, and cold water generated by the refrigerant channel Y is supplied to mixed air for precooling and indoor refrigeration; in winter, the hot water generated in the refrigerant flow path X is supplied to the indoor heating in addition to the mixed air heating, and the hot water generated in the refrigerant flow path Y is supplied to the mixed air heating and the indoor heating. Compared with the prior art, the air conditioning system solves the problem that fresh air in summer and winter and indoor refrigeration and heating loads of the temperature and humidity independent control air conditioning system are unbalanced, can give consideration to the requirements of fresh air in summer and winter and indoor sensible heat and latent heat, reasonably and stepwisely utilizes heat, and improves the energy efficiency ratio of the unit.
Description
Technical Field
The invention relates to an air conditioning system, in particular to an air conditioning system capable of independently controlling temperature and humidity.
Background
Along with the development of air conditioning systems and the attention degree of people to health is also higher and higher, the independent temperature and humidity control system has come up with the turn, and indoor temperature is adjusted by the radiation end promptly, and indoor humidity is adjusted by the new trend after handling to this system has combined radiation system and new trend system to reach the purpose of temperature, humidity independent control, has avoided the comfort level problem that conventional air conditioner heat and humidity combined processing brought.
However, the fresh air system bears all indoor wet loads in summer, the requirement on the capacity of the fresh air system is high, the indoor radiation tail end bears indoor sensible heat loads, the capacity of the radiation tail end is relatively small, the fresh air system does not have wet loads in winter, only indoor air needs to be heated, the heat supply capacity of the radiation system is insufficient, the fresh air volume is small, the fresh air system cannot bear the indoor sensible heat loads, and the problem that the loads are not matched under the refrigerating and heating conditions exists. On the basis of energy conservation and environmental protection, a brand-new system for improving the load imbalance under the refrigeration and heating conditions is provided, and is a problem to be solved urgently.
Disclosure of Invention
The invention aims to overcome the defects in the prior art, provides the independent temperature and humidity control air conditioning system, solves the problem that fresh air in summer and winter and indoor refrigeration and heating loads of the independent temperature and humidity control air conditioning system are unbalanced, can meet the requirements of fresh air in summer and winter and indoor sensible heat and latent heat, reasonably and stepwisely utilizes heat, and improves the energy efficiency ratio of a unit.
The purpose of the invention can be realized by the following technical scheme:
the invention relates to a temperature and humidity independent control air conditioning system, which comprises a refrigerant flow path X, a refrigerant flow path Y, a waterway flow path, a heat pipe and an air flow path;
the refrigerant flow path X and the refrigerant flow path Y are both closed cycles;
the refrigerant flow path X and the refrigerant flow path Y are respectively thermally coupled with a water path flow path;
the waterway flow path is thermally coupled to the air flow path by a plurality of water coils;
the waterway flow path is connected with the indoor tail end;
the water channel is a closed cycle, wherein a plurality of water channel valves are arranged in parallel and/or in series, and the distribution of cold/hot water output by the refrigerant channel X and the refrigerant channel Y in the water coil is realized by the opening and closing of the water channel valves, so that:
in summer, cold water generated by the refrigerant flow path X is only supplied to mixed air for deep dehumidification, and cold water generated by the refrigerant flow path Y is supplied to mixed air for precooling and indoor refrigeration;
in winter, the hot water generated in the refrigerant flow path X is supplied to the indoor heating in addition to the mixed air heating, and the hot water generated in the refrigerant flow path Y is supplied to the mixed air heating and the indoor heating.
The heat pipe is provided with a liquid channel and an air channel, and the filled liquid can be a refrigerant or an antifreeze. The liquid channel of heat pipe A end and heat pipe B end is connected through connecting pipe, pump, and the air channel of heat pipe A end passes through wind channel intercommunication second water coil pipe in the air flow path, and the air channel of heat pipe B end passes through wind channel intercommunication first water coil pipe air passage in the air flow path, sends into indoor through electric heating unit, fan.
Furthermore, an air filter, a heat pipe, an electric heating unit and a fan are arranged in the air flow path;
the mixed air is mixed by outdoor fresh air and indoor return air in front of an air filter, then passes through the air filter, the end A of the heat pipe, the second water coil, the first water coil, the end B of the heat pipe, the electric heating unit and the fan, and finally is sent into the room.
In the refrigerant flow path:
in the refrigerant flow path X, a refrigerant passes through a refrigerant connecting pipe and sequentially passes through a first compressor, a first four-way reversing valve, a first outdoor heat exchanger, a first throttling device and a first plate type heat exchanger on the refrigerant side to form closed circulation;
the refrigerant flow path X is on the first plate heat exchanger water side: cold water at 7-12 deg.c is produced in summer and hot water at 40-45 deg.c is produced in winter.
In the refrigerant flow path Y, a refrigerant passes through a refrigerant connecting pipe and sequentially passes through a second compressor, a second four-way reversing valve, a second outdoor heat exchanger, a second throttling device and a second plate heat exchanger on the refrigerant side to form closed circulation;
the refrigerant flow path Y is on the second plate heat exchanger water side: cold water at 18-20 deg.c is produced in summer and hot water at 30-35 deg.c is produced in winter.
Furthermore, the first compressor is communicated with the first outdoor heat exchanger and the first plate heat exchanger through a refrigerant connecting pipe, a first four-way reversing valve and a first throttling device.
Furthermore, the second compressor is communicated with the second outdoor heat exchanger and the second plate heat exchanger through a refrigerant connecting pipe, a second four-way reversing valve and a second throttling device.
Further, the first outdoor heat exchanger is characterized by being provided with a refrigerant passage and an air passage. The refrigerant channel of the first outdoor heat exchanger is communicated with the first compressor and the first throttling device through a refrigerant connecting pipe in the refrigerant circulating loop.
Further, the second outdoor heat exchanger is characterized by being provided with a refrigerant passage and an air passage. And the refrigerant channel of the second outdoor heat exchanger is communicated with the second compressor and the second throttling device through a refrigerant connecting pipe in the refrigerant circulating loop.
Further, the first plate heat exchanger is characterized by being provided with a refrigerant channel and a water channel. The refrigerant channel of the first plate heat exchanger is communicated with the first compressor and the first throttling device through a refrigerant connecting pipe in a refrigerant circulating loop, and the waterway channel of the first plate heat exchanger is communicated with the first water pump and the first water coil pipe through a water connecting pipe in the waterway circulating loop.
Further, the second plate heat exchanger includes a refrigerant passage and a water passage. And a refrigerant channel of the second plate heat exchanger is communicated with the second compressor and the second throttling device through a refrigerant connecting pipe in the refrigerant circulating loop. Under the refrigeration working condition, a waterway channel of the second plate type heat exchanger is communicated with a second waterway valve, a second water pump, a second water coil and an indoor tail end in a waterway circulation loop through a water connecting pipe. Under the working condition of heating, the waterway channel of the second plate heat exchanger is communicated with the water side channel of the first plate heat exchanger, the second water coil pipe and the indoor tail end in the waterway circulation loop through the water connecting pipe.
Furthermore, the first four-way reversing valve changes the switching of the refrigerant flow paths under different working conditions by controlling the valve. Under the refrigeration working condition, the exhaust end of the first compressor is communicated with the first outdoor heat exchanger through a refrigerant connecting pipe; and under the heating working condition, the first four-way reversing valve is switched, and the exhaust end of the first compressor is communicated with the first plate heat exchanger through the refrigerant connecting pipe.
Furthermore, the second four-way reversing valve changes the switching of the refrigerant flow paths under different working conditions by controlling the valve. Under the refrigeration working condition, the exhaust end of the second compressor is communicated with the second outdoor heat exchanger through a refrigerant connecting pipe; and under the heating working condition, the second four-way reversing valve is switched, and the exhaust end of the second compressor is communicated with the second plate heat exchanger through a refrigerant connecting pipe.
Further, the first throttling device can be a capillary tube, a short tube, an electronic expansion valve and other refrigeration system throttling devices, and the first throttling device is communicated with the first outdoor heat exchanger and the first plate heat exchanger through a refrigerant connecting pipe in the refrigerant circulation loop.
The second throttling device can be a capillary tube, a short tube, an electronic expansion valve and other throttling devices of the refrigeration system, and is communicated with the second outdoor heat exchanger and the second plate heat exchanger through a refrigerant connecting pipe in the refrigerant circulation loop.
In the waterway flow path:
the water is communicated with the water path side of the first plate type heat exchanger, the water path side of the second plate type heat exchanger, the first water pump, the first water coil, the first water path valve, the second water pump, the second water coil and the indoor tail end through the water path connecting pipe;
the switching of the refrigeration/heating working conditions is realized through the opening and closing of the first water path valve and the second water path valve.
Furthermore, a water channel and an air channel are arranged in the first water coil, the water channel of the first water coil is communicated with the first water pump and the water side of the first plate heat exchanger through a water connecting pipe in water circulation, and a fan is arranged at the downstream of the air flow path in the air channel of the first water coil;
and the water channel of the second water coil is communicated with the water side of the second water pump and the water side of the second plate heat exchanger through water connecting pipes in water circulation, and the air channel of the second water coil is communicated with the air channel of the first water coil in an air flow path through an air channel.
Further, the indoor end is a series/parallel combination of one or more of a radiation ceiling, a dry-type coil pipe and a floor heating coil pipe.
Further, under the refrigeration operating mode, in the water route flow path, first water route valve is closed, and the second water route valve is opened, and the cold water that flows out from second plate heat exchanger divides into two tunnel:
the first path of cold water is connected with the water side of the first plate heat exchanger, and the cold water flowing out of the first plate heat exchanger is connected with the first water coil pipe through the first water pump to deeply dehumidify the mixed air;
and the second path of cold water is divided into two paths through a second water path valve and a second water pump, one path of cold water is connected with the second water coil pipe and used for precooling mixed air, and the other path of cold water is connected with the indoor tail end and used for providing cold energy indoors.
Further, under the operating mode of heating, in the water route flow path, first water route valve is opened, and second water route valve is closed, and the hot water that flows out from second plate heat exchanger divides into two the tunnel:
the first path of hot water is connected with the first water coil pipe through the first water pump to heat mixed air, the second path of hot water is divided into two paths through the first water path valve and the second water pump, the second water coil pipe is connected with the first path of hot water to preheat mixed air, and the other path of hot water is connected with the indoor tail end to provide heat for the indoor space.
The main working process of the invention is as follows: under the refrigeration working condition, the first waterway valve is closed, and the second waterway valve is opened. The first and second plate heat exchangers correspond to evaporators. The refrigerant flow path X has low evaporation temperature to prepare low-temperature cold water at 7-12 ℃, the low-temperature cold water from the first plate heat exchanger is only sent to the first water coil pipe to deeply dehumidify the air, the refrigerant flow path Y has high evaporation temperature to prepare high-temperature cold water at 18-20 ℃, the high-temperature cold water from the second plate heat exchanger is divided into two paths by the second water path valve and the second water pump, one path of cold water is led to the second water coil pipe to pre-cool the mixed air before deep dehumidification, and the other path of cold water is led to the indoor tail end to cool the indoor air, so that the refrigeration purpose is achieved.
Under the refrigeration working condition, the heat pipe is used for saving energy and reheating air, liquid in the heat pipe enters the end B of the heat pipe under the driving of the pump and is used for recovering cold energy in the air after deep dehumidification and reheating the air (an electric heating unit is used when heating is insufficient), so that the temperature of the liquid is higher than the indoor dew point temperature, and the condensation on the outer surface of an air supply pipe is avoided; the cooled liquid at the end B of the heat pipe is sent to the end A of the heat pipe for precooling air, so that the cooling and dehumidifying loads of the first water coil and the second water coil are reduced, and energy conservation is realized.
Under the heating working condition, the first water way valve is opened, and the second water way valve is closed. The first plate heat exchanger and the second plate heat exchanger are equivalent to a condenser, and the first plate heat exchanger and the second plate heat exchanger heat a waterway flow path together. The hot water heated by the second plate heat exchanger and the first plate heat exchanger is divided into two paths, the first path is sent to the first water coil pipe to heat the air and finally returns to the water path of the first plate heat exchanger, the second path is divided into two paths by the first water path valve and the second water pump, the first path is passed through the second water coil pipe to heat the air, the other path is led to the indoor tail end to heat the indoor air, the heating purpose is achieved, and the heated air is led to the second plate heat exchanger after being converged.
Under the heating condition, the heat pipe has the function of preventing the water coil pipe from frost cracking in a low-temperature heat exchange environment, if the temperature of air entering the first water coil pipe is detected to be lower than 0 ℃, a heat pipe circulating pump is started, the problem that liquid in the heat pipe is lifted by utilizing the heat absorption of the end B of the heat pipe is solved, the air entering the second water coil pipe is preheated by the end A of the heat pipe, and the problem that the air entering the second water coil pipe is locally frost cracking due to too low temperature is avoided. When the air is not heated enough, the electric heating unit is started to supplement heat.
Compared with the prior art, the invention has the following advantages:
1. the problem of unbalanced load under the refrigeration and heating conditions of the temperature and humidity independent control air conditioning system is solved;
2. only 18-20 ℃ cold water is needed for treating indoor sensible heat in summer, so that the running energy consumption of the unit is greatly reduced, and the energy is saved and the environment is protected;
3. the temperature of the water supply in summer is higher than the dew point temperature of the indoor air, so that the indoor tail end has no condensation risk;
4. only water pipelines are arranged indoors, and construction is simple.
Drawings
FIG. 1 is a schematic flow chart of example 1.
Fig. 2 is a schematic diagram of an operation flow of the temperature and humidity independent control air conditioning system in the invention under a refrigeration working condition in summer.
Fig. 3 is a schematic view of an operation flow of the independent temperature and humidity control air conditioning system according to the present invention under a winter heating condition.
In the figure, X denotes a first refrigerant flow path, and Y denotes a second refrigerant flow path. 1 is a first compressor, 11 is a second compressor, 3 is a first four-way reversing valve, A, B, C and D are four interfaces of the first four-way reversing valve, 13 is a second four-way reversing valve, E, F, G and H are four interfaces of the second four-way reversing valve, 5 is a first outdoor heat exchanger, 15 is a second outdoor heat exchanger, 7 is a first throttling device, 17 is a second throttling device, 8 is a first plate heat exchanger, 18 is a second plate heat exchanger, 23 is a first water pump, 32 is a second water pump, 29 is a first water path valve, 39 is a second water path valve, 25 is a first water coil, 34 is a second water coil, 44 is a fan, 42 is an indoor tail end, 46 is an air filter, 47-51 is an air flow path, 52, 53 and 54 form a heat pipe system, 52 is a heat pipe end A, 53 is a heat pipe end B, 54 is a pump, 55 is an electric heating unit, 2, 4 and 6 are respectively, 9. 10, 12, 14, 16, 19 and 20 are refrigerant connecting pipelines, and the rest are water connecting pipelines.
Detailed Description
The invention is described in detail below with reference to the figures and specific embodiments.
According to the invention, the two water path valves are arranged on the water path flow path, the opening and closing states of the water path valves under different working conditions are adjusted, the cold energy generated by the refrigerant flow path X in summer is only provided for fresh air to carry out deep dehumidification, the cold energy generated by the refrigerant flow path Y is provided for fresh air pre-cooling and indoor refrigeration, the heat generated by the refrigerant flow path X in winter is also provided for indoor heating besides heating the fresh air, and the heat generated by the refrigerant flow path Y is provided for fresh air heating and indoor heating, so that the problem of unbalanced load distribution under the refrigeration and heating conditions is balanced.
The invention relates to a temperature and humidity independent control air conditioning system, which comprises a refrigerant flow path X, a refrigerant flow path Y, a water path flow path and an air flow path; the refrigerant flow path X and the refrigerant flow path Y are both closed cycles; the refrigerant flow path X and the refrigerant flow path Y are thermally coupled to the water path flow path; the water path flow path is thermally coupled with the air flow path through a plurality of water coils; the waterway flow path is connected to the indoor end 42; the water channel flow path is a closed cycle, wherein a plurality of water channel valves are arranged in parallel and/or in series, and the distribution of cold/hot water output by the refrigerant flow path X and the refrigerant flow path Y in the water coil is realized by the opening and closing of the water channel valves, so that: in summer, cold water generated by the refrigerant flow path X is only supplied to mixed air for deep dehumidification, and cold water generated by the refrigerant flow path Y is supplied to mixed air for precooling and indoor refrigeration; in winter, the hot water generated in the refrigerant flow path X is supplied to the indoor heating in addition to the mixed air heating, and the hot water generated in the refrigerant flow path Y is supplied to the mixed air heating and the indoor heating.
An air filter 46, a heat pipe, an electric heating unit 55 and a fan 44 are provided in the air flow path. The mixed air is mixed by outdoor fresh air and indoor return air before the air filter 46, then passes through the air filter 46, the heat pipe A end 52, the second water coil 34, the first water coil 25, the heat pipe B end 53, the electric heating unit 55 and the fan 44, and finally is sent into the room.
In the refrigerant flow path X, the refrigerant passes through the first compressor 1, the first four-way selector valve 3, the first outdoor heat exchanger 5, the first throttle device 7, and the first plate heat exchanger 8 in this order via the refrigerant connection pipe, and a closed cycle is formed. The refrigerant flow path X is on the water side of the first plate heat exchanger 8: cold water at 7-12 deg.c is produced in summer and hot water at 40-45 deg.c is produced in winter. In the refrigerant flow path Y, the refrigerant passes through the refrigerant connecting pipe sequentially on the refrigerant side of the second compressor 11, the second four-way reversing valve 13, the second outdoor heat exchanger 15, the second throttling device 17 and the second plate heat exchanger 18 to form a closed cycle; the refrigerant flow path Y is on the water path side of the second plate heat exchanger 18: cold water at 18-20 deg.c is produced in summer and hot water at 30-35 deg.c is produced in winter.
The water is communicated with the water path side of the first plate heat exchanger 8, the water path side of the second plate heat exchanger 18, the first water pump 23, the first water coil 25, the first water path valve 29, the second water path valve 39, the second water pump 32, the second water coil 34 and the indoor tail end 42 through water path connecting pipes; the switching of the cooling/heating conditions is realized by opening and closing the first and second water passage valves 29 and 39. A water channel and an air channel are arranged in the first water coil 25, the water channel of the first water coil 25 is communicated with the first water pump 23 and the water side of the first plate heat exchanger 8 through a water connecting pipe in water circulation, and the air channel of the first water coil 25 is provided with a fan 44 at the downstream of the air flow path; the second water coil 34 is provided with a water channel and an air channel, the water channel of the second water coil 34 is communicated with the water side of the second water pump 32 and the second plate heat exchanger 18 through a water connecting pipe in water circulation, and the air channel of the second water coil 34 is communicated with the first water coil air channel through an air channel in an air flow path.
The indoor end 42 is a series/parallel combination of one or more of a radiant ceiling, dry coil, floor heating coil.
Example 1
The structure and the flow of the air conditioning system with medium temperature and humidity independently controlled in this embodiment are shown in fig. 1, and the main structure includes a first refrigerant flow path X, a second refrigerant flow path Y, a first compressor 1, a second compressor 11, a first four-way reversing valve 3, a second four-way reversing valve 13, a first outdoor heat exchanger 5, a second outdoor heat exchanger 15, a first throttling device 7, a second throttling device 17, a first plate heat exchanger 8, a second plate heat exchanger 18, a first water pump 23, a second water pump 32, a first water path valve 29, a second water path valve 39, a first water coil 25, a second water coil 34, a fan 44, an indoor end 42, an air filter 46, refrigerant connecting lines 2, 4, 6, 9, 10, 12, 14, 16, 19, 20, water connecting lines 21, 22, 24, 26, 27. 28, 30, 31, 33, 35, 36, 37, 38, 40, 41, 43.
The temperature and humidity independent control air conditioning system has the following two working conditions.
1. Under the refrigeration working condition, in a first refrigerant flow path X, an exhaust port of a first compressor 1 on a refrigerant side is connected with a first four-way reversing valve 3 through a connecting pipe 2, interfaces A and B of the first four-way reversing valve 3 are communicated and connected with a first outdoor heat exchanger 5 through a connecting pipe 4, the first outdoor heat exchanger 5 is connected with a first throttling device 7 through a connecting pipe 6, an outlet of the first throttling device 7 is connected with the refrigerant side of a first plate type heat exchanger 8, refrigerant coming out of the first plate type heat exchanger 8 is connected with the first four-way reversing valve 3 through a connecting pipe 9, and an interface D of the first four-way reversing valve 3 is connected with an air suction port of the first compressor 1 through a connecting pipe 10. In the second refrigerant flow path Y, the exhaust port of the second compressor 11 is connected to the second four-way selector valve 13 through the connection pipe 12, the interface E of the second four-way selector valve 13 is communicated with the interface F, the second four-way selector valve 13 is connected to the second outdoor heat exchanger 15 through the connection pipe 14, the second outdoor heat exchanger 15 is connected to the second throttling device 17 through the connection pipe 16, the outlet of the second throttling device 17 is connected to the refrigerant side of the second plate heat exchanger 18, the refrigerant from the second plate heat exchanger 18 is connected to the second four-way selector valve 13 through the connection pipe 19, and the interface H of the second four-way selector valve 13 is connected to the suction port of the second compressor 11 through the connection pipe 20.
In the water path, the first water path valve 29 is closed, the second water path valve 39 is opened, the water connection pipe 36 is connected to the water side of the second plate heat exchanger 18, and the cold water flowing out of the second plate heat exchanger 18 is divided into two paths by the water connection pipe 37. The first path is connected with the water side of the first plate heat exchanger 8 through a water connecting pipe 27, cold water coming out of the first plate heat exchanger 8 is connected with a first water coil 25 through water connecting pipes 21 and 22, a first water pump 23 and a water connecting pipe 24 to carry out deep dehumidification for mixed air, and an outlet of the first water coil 25 is connected with a water connecting pipe 26 and is connected with the water connecting pipe 27 to form a loop. The second path is divided into two paths through a water connecting pipe 38, a second water path valve 39, water connecting pipes 40 and 31 and a second water pump 32, one path is connected with a second water coil pipe 34 through a water connecting pipe 33 for precooling for air mixing, and the outlet of the second water coil pipe 34 is connected with a water connecting pipe 35. The other path is connected with the indoor tail end 42 through a water connecting pipe 41 to provide cold energy indoors, and the cold energy is converged with the other path through a water connecting pipe 43 and returns to the second plate heat exchanger 18 through a water connecting pipe 36 to complete water path circulation.
In the air flow path, fresh air 47 and indoor return air 48 are mixed through an air door 45, then precooled through an air filter 46, a heat pipe A end 52 and a second water coil 34, deeply dehumidified through a first water coil 25, reheated at a heat pipe B end 53, and finally sent into the room through a fan 44. When the outdoor temperature is low in summer, if the air supply temperature requirement cannot be met only by using the heat pipe, the electric heating unit 55 can be turned on to heat the air.
2. Under the heating working condition, in a first refrigerant flow path X, an exhaust port of a first compressor 1 on a refrigerant side is connected with a first four-way reversing valve 3 through a connecting pipe 2, interfaces A and D of the first four-way reversing valve 3 are communicated and are connected with a refrigerant side of a first plate type heat exchanger 8 through a connecting pipe 9, an outlet of the first plate type heat exchanger 8 is connected with a first throttling device 7, and is connected with a first outdoor heat exchanger 5 through a connecting pipe 6 and is connected with the first four-way reversing valve 3 through a connecting pipe 4, and an interface C of the first four-way reversing valve 3 is connected with an air suction port of the first compressor 1 through a connecting pipe 10. In the second refrigerant flow path Y, the exhaust port of the second compressor 11 is connected to the second four-way selector valve 13 through the connecting pipe 12, the ports E and H of the second four-way selector valve 13 are communicated with each other and connected to the refrigerant side of the second plate heat exchanger 18 through the connecting pipe 19, the outlet of the second plate heat exchanger 18 is connected to the second throttling device 17, to the second outdoor heat exchanger 15 through the connecting pipe 16 and connected to the second four-way selector valve 13 through the connecting pipe 14, and the port G of the second four-way selector valve 13 is connected to the suction port of the first compressor 11 through the connecting pipe 20.
In the waterway flow path, the first waterway valve 29 is opened, the second waterway valve 39 is closed, the water connecting pipe 36 is connected with the water side of the second plate heat exchanger 18, and the hot water coming out of the second plate heat exchanger 18 is connected with the water side of the first plate heat exchanger 8 through the water connecting pipes 37 and 27 for heating, and is divided into two paths through the water connecting pipe 21. The first path is connected with a first water coil 25 through a water connecting pipe 22, a first water pump 23 and a water connecting pipe 24 to heat the mixed air, and the outlet of the first water coil 25 is connected with a water connecting pipe 26 to form a loop with a water connecting pipe 27. The second path is divided into two paths through a water connecting pipe 28, a first water path valve 29, water connecting pipes 30 and 31 and a second water pump 32, one path is connected with a second water coil pipe 34 through a water connecting pipe 33 and is preheated for mixing air, and the outlet of the second water coil pipe 34 is connected with a water connecting pipe 35. The other path is connected with the indoor tail end 42 through a water connecting pipe 41 to provide heat for the indoor, and is converged with the other path through a water connecting pipe 43 and returned to the second plate heat exchanger 18 through a water connecting pipe 36 to complete water path circulation.
In the air flow path, fresh air 47 and indoor return air 48 are mixed through an air door 45, then pass through an air filter 46, are preheated through the second water coil 34, are heated through the first water coil 25, and finally are sent into the room through a fan 44. In severe winter conditions, if it is detected that the temperature of the mixed air 49 is too low, the pump 54 can be turned on to preheat the air through the heat pipe a end 52, thereby preventing the second water coil 34 from freezing.
The terms "first," "second," and the like are used herein to define components, as one skilled in the art would know: the use of the words "first", "second", etc. is merely for convenience in describing the differences between the components. Unless otherwise stated, the above words have no special meaning.
In the above embodiments, all components of the refrigerant cycle are not completely shown, in the implementation process, the refrigerant circuit is provided with common refrigeration accessories such as a liquid reservoir, a gas-liquid separator, an oil separator, a filter, a dryer, a check valve, a stop valve, a liquid separator and the like, and the fresh air duct is provided with air treatment accessories such as a filter, a silencer, a humidifier, a heater, a sterilization device and the like, which cannot be regarded as substantial improvements to the present invention, and shall belong to the protection scope of the present invention.
The embodiments described above are described to facilitate an understanding and use of the invention by those skilled in the art. It will be readily apparent to those skilled in the art that various modifications to these embodiments may be made, and the generic principles described herein may be applied to other embodiments without the use of the inventive faculty. Therefore, the present invention is not limited to the above embodiments, and those skilled in the art should make improvements and modifications within the scope of the present invention based on the disclosure of the present invention.
Claims (10)
1. An air conditioning system with independent temperature and humidity control is characterized by comprising a refrigerant flow path X, a refrigerant flow path Y, a water path flow path and an air flow path;
the refrigerant flow path X and the refrigerant flow path Y are both closed cycles;
the refrigerant flow path X and the refrigerant flow path Y are respectively thermally coupled with a water path flow path;
the waterway flow path is thermally coupled to the air flow path by a plurality of water coils;
the waterway flow path is connected with an indoor tail end (42);
the water channel is a closed cycle, wherein a plurality of water channel valves are arranged in parallel and/or in series, and the distribution of cold/hot water output by the refrigerant channel X and the refrigerant channel Y in the water coil is realized by the opening and closing of the water channel valves, so that:
in summer, cold water generated by the refrigerant flow path X is only supplied to mixed air for deep dehumidification, and cold water generated by the refrigerant flow path Y is supplied to mixed air for precooling and indoor refrigeration;
in winter, the hot water generated in the refrigerant flow path X is supplied to the indoor heating in addition to the mixed air heating, and the hot water generated in the refrigerant flow path Y is supplied to the mixed air heating and the indoor heating.
2. The air conditioning system with independent temperature and humidity control according to claim 1, wherein an air filter (46), a heat pipe, a water coil, an electric heating unit (55) and a fan (44) are arranged in the air flow path;
the mixed air is mixed by outdoor fresh air and indoor return air in front of an air filter (46), then passes through the air filter (46), a heat pipe A end (52), a second water coil (34), a first water coil (25), a heat pipe B end (53), an electric heating unit (55) and a fan (44), and finally is sent into the room.
3. The air conditioning system with independent temperature and humidity control according to claim 1, wherein in the refrigerant flow path X, the refrigerant passes through a first compressor (1), a first four-way reversing valve (3), a first outdoor heat exchanger (5), a first throttling device (7) and a first plate heat exchanger (8) in sequence through a refrigerant connecting pipe to form a closed cycle;
the refrigerant flow path X is arranged on the water side of the first plate heat exchanger (8): cold water at 7-12 deg.c is produced in summer and hot water at 40-45 deg.c is produced in winter.
4. The air conditioning system with independent temperature and humidity control according to claim 3, wherein in the refrigerant flow path Y, the refrigerant passes through a refrigerant connecting pipe sequentially from the refrigerant side of the second compressor (11), the second four-way reversing valve (13), the second outdoor heat exchanger (15), the second throttling device (17) and the second plate heat exchanger (18) to form a closed cycle;
the refrigerant flow path Y is arranged on the water side of the second plate heat exchanger (18): cold water at 18-20 deg.c is produced in summer and hot water at 30-35 deg.c is produced in winter.
5. The air conditioning system with independent temperature and humidity control according to claim 1, wherein in the waterway flow path, water is communicated with the water path side of the first plate heat exchanger (8), the water path side of the second plate heat exchanger (18), the first water pump (23), the first water coil (25), the first water path valve (29), the second water path valve (39), the second water pump (32), the second water coil (34) and the indoor end (42) through a waterway connecting pipe;
the switching of the refrigeration/heating working conditions is realized through the opening and closing of the first water path valve (29) and the second water path valve (39).
6. The air conditioning system with independent temperature and humidity control according to claim 5, wherein a water channel and an air channel are arranged in the first water coil (25), the water channel of the first water coil (25) is communicated with the first water pump (23) and the water side of the first plate heat exchanger (8) through a water connecting pipe in a water circulation, and a fan (44) is arranged at the downstream of the air channel of the first water coil (25);
the water pump is characterized in that a water channel and an air channel are arranged in the second water coil (34), the water channel of the second water coil (34) is communicated with a water side of the second water pump (32) and the second plate heat exchanger (18) through water connecting pipes in water circulation, and the air channel of the second water coil (34) is communicated with the air channel of the first water coil through an air channel in an air flow path.
7. The independent temperature and humidity control air conditioning system according to claim 1, wherein the indoor end (42) is a series/parallel combination of one or more of a radiant ceiling, a dry coil, and a floor heating coil.
8. The air conditioning system with independent temperature and humidity control according to claim 6, wherein under a refrigeration condition, the first water path valve (29) is closed, the second water path valve (39) is opened, and cold water flowing out of the second plate heat exchanger (18) is divided into two paths:
the first path of cold water is connected with the water side of the first plate type heat exchanger (8), and the cold water flowing out of the first plate type heat exchanger (8) is connected with the first water coil pipe (25) through the first water pump (23) to deeply dehumidify the mixed air;
and the second path of cold water is divided into two paths through a second water path valve (39) and a second water pump (32), one path of cold water is connected with a second water coil pipe (34) to pre-cool the mixed air, and the other path of cold water is connected with an indoor tail end (42) to provide cold energy indoors.
9. The air conditioning system with independent temperature and humidity control according to claim 6, wherein in a heating working condition, in a water path, the first water path valve (29) is opened, the second water path valve (39) is closed, and hot water flowing out of the second plate heat exchanger (18) is divided into two paths:
the first path of hot water is connected with a first water coil pipe (25) through a first water pump (23) and is used for heating mixed air, the second path of hot water is divided into two paths through a first water path valve (29) and a second water pump (32), one path of second water coil pipe (34) is connected and is used for preheating mixed air, and the other path of hot water is connected with an indoor tail end (42) and is used for providing heat indoors.
10. The air conditioning system with independent temperature and humidity control according to claim 4, wherein the first throttling device (7) and the second throttling device (17) are both one of capillary tubes, short tubes or electronic expansion valves.
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