CN114198829A - Humidity adjusting system - Google Patents
Humidity adjusting system Download PDFInfo
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- CN114198829A CN114198829A CN202111420313.9A CN202111420313A CN114198829A CN 114198829 A CN114198829 A CN 114198829A CN 202111420313 A CN202111420313 A CN 202111420313A CN 114198829 A CN114198829 A CN 114198829A
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- 238000005057 refrigeration Methods 0.000 claims abstract description 49
- 238000001179 sorption measurement Methods 0.000 claims abstract description 38
- 238000010438 heat treatment Methods 0.000 claims description 51
- 239000003507 refrigerant Substances 0.000 claims description 36
- 238000001816 cooling Methods 0.000 claims description 11
- 230000003750 conditioning effect Effects 0.000 claims description 10
- 238000001704 evaporation Methods 0.000 claims description 8
- 238000009833 condensation Methods 0.000 claims description 5
- 230000005494 condensation Effects 0.000 claims description 5
- 230000008020 evaporation Effects 0.000 claims description 5
- 230000002596 correlated effect Effects 0.000 claims description 2
- 238000007791 dehumidification Methods 0.000 abstract description 47
- 238000003795 desorption Methods 0.000 abstract description 33
- 238000000034 method Methods 0.000 abstract description 31
- 238000004378 air conditioning Methods 0.000 abstract description 4
- 238000005457 optimization Methods 0.000 abstract description 2
- 230000000694 effects Effects 0.000 description 9
- 239000007788 liquid Substances 0.000 description 8
- 238000010586 diagram Methods 0.000 description 7
- 238000004781 supercooling Methods 0.000 description 7
- 230000001276 controlling effect Effects 0.000 description 5
- 239000013526 supercooled liquid Substances 0.000 description 5
- 239000007789 gas Substances 0.000 description 4
- 238000007599 discharging Methods 0.000 description 3
- CURLTUGMZLYLDI-UHFFFAOYSA-N Carbon dioxide Chemical compound O=C=O CURLTUGMZLYLDI-UHFFFAOYSA-N 0.000 description 2
- 239000000463 material Substances 0.000 description 2
- QVGXLLKOCUKJST-UHFFFAOYSA-N atomic oxygen Chemical compound [O] QVGXLLKOCUKJST-UHFFFAOYSA-N 0.000 description 1
- 229910002092 carbon dioxide Inorganic materials 0.000 description 1
- 239000001569 carbon dioxide Substances 0.000 description 1
- 230000002349 favourable effect Effects 0.000 description 1
- 229910052760 oxygen Inorganic materials 0.000 description 1
- 239000001301 oxygen Substances 0.000 description 1
- 238000006467 substitution reaction Methods 0.000 description 1
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Classifications
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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
- F24F5/00—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater
- F24F5/0007—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater cooling apparatus specially adapted for use in air-conditioning
- F24F5/001—Compression cycle type
-
- 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
- F24F11/62—Control or safety arrangements characterised by the type of control or by internal processing, e.g. using fuzzy logic, adaptive control or estimation of values
- F24F11/63—Electronic processing
- F24F11/64—Electronic processing using pre-stored data
-
- 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
- F24F11/70—Control systems characterised by their outputs; Constructional details thereof
- F24F11/80—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air
- F24F11/83—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers
- F24F11/84—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers using valves
-
- 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
- F24F11/70—Control systems characterised by their outputs; Constructional details thereof
- F24F11/80—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air
- F24F11/86—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling compressors within refrigeration or heat pump circuits
-
- 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
- F24F13/24—Means for preventing or suppressing noise
-
- 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
-
- 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
- F24F3/1411—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 by absorbing or adsorbing water, e.g. using an hygroscopic desiccant
- F24F3/1423—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 by absorbing or adsorbing water, e.g. using an hygroscopic desiccant with a moving bed of solid desiccants, e.g. a rotary wheel supporting solid desiccants
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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
- F25B41/00—Fluid-circulation arrangements
- F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
-
- 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
- F25B41/00—Fluid-circulation arrangements
- F25B41/30—Expansion means; Dispositions thereof
- F25B41/31—Expansion valves
- F25B41/34—Expansion valves with the valve member being actuated by electric means, e.g. by piezoelectric actuators
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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
- F24F13/24—Means for preventing or suppressing noise
- F24F2013/247—Active noise-suppression
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F2110/00—Control inputs relating to air properties
- F24F2110/10—Temperature
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F2110/00—Control inputs relating to air properties
- F24F2110/20—Humidity
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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]
- Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Signal Processing (AREA)
- Sustainable Development (AREA)
- Life Sciences & Earth Sciences (AREA)
- Fuzzy Systems (AREA)
- Mathematical Physics (AREA)
- Central Air Conditioning (AREA)
- Air Conditioning Control Device (AREA)
Abstract
The invention relates to a humidity adjusting system, which comprises a heat pump air conditioning system and an adsorption type rotating wheel, and realizes the humidity adjustment of fresh air, wherein a first heat exchanger and a second heat exchanger are connected in series in the refrigeration and dehumidification process, indoor return air firstly flows through the first heat exchanger, and the first heat exchanger and air realize sufficient high temperature difference heat exchange to improve the front desorption temperature of the rotating wheel, so that the high-efficiency performance of the rotating wheel in the refrigeration and dehumidification process is realized; and the system loop optimization of the fresh air dehumidifying air-conditioning system with the rotating wheel is realized.
Description
Technical Field
The invention relates to the technical field of humidity adjustment, in particular to a humidity adjustment system.
Background
The existing indoor air is generally subjected to temperature regulation through an air conditioner, after a period of time, the oxygen concentration in the closed indoor space is reduced, the carbon dioxide concentration is increased, and the indoor comfort level is deteriorated, so that outdoor fresh air needs to be introduced.
Disclosure of Invention
The invention provides a humidity adjusting system, which solves the technical problem that the dehumidification/humidification capacity of an adsorption type rotating wheel cannot be improved to the maximum extent by adjusting the temperature through a total heat exchanger in the prior art.
In order to achieve the purpose, the invention adopts the following technical scheme:
a humidity conditioning system comprising:
the heat exchanger comprises a compressor, a four-way valve, a first heat exchanger, a second heat exchanger, a throttling element and a third heat exchanger which are sequentially connected through a refrigerant pipeline, wherein the third heat exchanger is connected with the four-way valve;
the valve unit is used for being controlled to be switched to a state that the first heat exchanger and the second heat exchanger are connected in series when the four-way valve is switched to a refrigeration state, the first heat exchanger and the second heat exchanger are condensers, and the third heat exchanger is an evaporator;
a total heat exchanger;
an adsorption type runner;
the air exhaust fan is used for discharging indoor return air to the outside after sequentially flowing through the total heat exchanger, the first heat exchanger, the adsorption type rotating wheel adsorption and the second heat exchanger;
and the air supply fan is used for sequentially passing outdoor fresh air through the total heat exchanger, the third heat exchanger and the adsorption type rotating wheel for desorption and then sending the fresh air into the room.
Compared with the prior art, the technical scheme of the invention has the following technical effects: the humidity adjusting system comprises a heat pump air conditioning system and an adsorption type rotating wheel, the humidity adjustment of fresh air is realized, a first heat exchanger and a second heat exchanger are connected in series in the refrigeration and dehumidification process, indoor return air firstly flows through the first heat exchanger, the first heat exchanger and air exchange with sufficient high temperature difference is realized, and the front desorption temperature of the rotating wheel is increased, so that the high-efficiency performance of the rotating wheel in the refrigeration and dehumidification process is realized; and the system loop optimization of the fresh air dehumidifying air-conditioning system with the rotating wheel is realized.
Drawings
In order to more clearly illustrate the technical solutions of the embodiments of the present invention, the drawings needed to be used in the description of the embodiments are briefly introduced below, and it is obvious that the drawings in the following description are only some embodiments of the present invention, and it is obvious for those skilled in the art to obtain other drawings based on these drawings without creative efforts.
FIG. 1 is a schematic view of the air side treatment process of the present invention.
Fig. 2 is a schematic diagram of a system cycle of a refrigeration and dehumidification process according to a first embodiment of the present invention.
Fig. 3 is a schematic system cycle of a heating and humidifying process according to a first embodiment of the present invention.
Fig. 4 is a schematic diagram of a refrigeration and dehumidification process according to the first embodiment of the invention.
Fig. 5 is a schematic diagram of a heating and humidifying process according to a first embodiment of the present invention.
Fig. 6 is a schematic diagram of a system cycle of a refrigeration and dehumidification process according to a second embodiment of the present invention.
Fig. 7 is a schematic diagram of a system cycle of a heating and humidifying process according to a second embodiment of the present invention.
Fig. 8 is a schematic view of a heating and humidifying process according to a second embodiment of the present invention.
1. A compressor;
2. a four-way valve;
3. a first heat exchanger;
4. a first on-off element;
5. a second heat exchanger;
6. a third break-through element;
7. a throttling element;
8. a reservoir;
9. a third heat exchanger;
10. a second switching element;
11. a total heat exchanger;
12. an adsorption type runner;
13. an exhaust fan;
14. an air supply fan;
in particular, if the cost is sufficient, all the check valves in the figure can be replaced by other devices capable of controlling the on-off direction of the flow path, such as a solenoid valve.
OA: outdoor fresh air RA: and (4) indoor air return SA: sending out fresh air EA: and discharging dirty air.
The A/B/C/D is the air state point of the fresh air loop, and the E/F/G/H is the air state point of the return air loop.
Detailed Description
The technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.
In the description of the present invention, it should be noted that, unless otherwise explicitly specified or limited, the terms "mounted," "connected," and "connected" are to be construed broadly, e.g., as meaning either a fixed connection, a removable connection, or an integral connection; may be directly connected or indirectly connected through an intermediate. The specific meanings of the above terms in the present invention can be understood in specific cases to those skilled in the art. In the foregoing description of embodiments, the particular features, structures, materials, or characteristics may be combined in any suitable manner in any one or more embodiments or examples.
The terms "first", "second" and "first" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of the present invention, "a plurality" means two or more unless otherwise specified.
In order to conveniently describe the technical principles and the realization effects of refrigeration dehumidification and heating humidification of the invention, the temperature and the moisture content of outdoor fresh air OA are assumed to be higher than those of indoor return air RA during refrigeration dehumidification in the following description; the temperature and the moisture content of the outdoor fresh air OA are lower than those of the indoor return air RA during heating and humidifying.
Example one
A humidity conditioning system comprising:
the system comprises a compressor 1, a four-way valve 2, a first heat exchanger 3, a second heat exchanger 5, a throttling element 7 and a third heat exchanger 9 which are sequentially connected through a refrigerant pipeline, wherein the third heat exchanger 9 is connected with the four-way valve 2;
the valve unit is used for being controlled to be switched to a state that the first heat exchanger 3 and the second heat exchanger 5 are connected in series when the four-way valve 2 is switched to a refrigeration state, the first heat exchanger 3 and the second heat exchanger 5 are condensers, and the third heat exchanger 9 is an evaporator;
the total heat exchanger 11;
an adsorption type runner 12;
the exhaust fan 13 is used for discharging indoor return air RA out of the room after sequentially passing through the total heat exchanger 11, the first heat exchanger 3, the adsorption runner 12 and the second heat exchanger 5;
and the air supply fan 14 is used for enabling outdoor fresh air OA to sequentially flow through the total heat exchanger 11, the third heat exchanger 9 and the adsorption type rotating wheel 12 for desorption and then sending the outdoor fresh air OA into the room.
The valve unit is used for being controlled to be switched to a state that the second heat exchanger 5 is connected with the first heat exchanger 3 in parallel when the four-way valve 2 is switched to a heating state, the first heat exchanger 3 and the second heat exchanger 5 are evaporators, and the third heat exchanger 9 is a condenser.
Wherein, the valve unit includes:
the first on-off element 4 can be a solenoid valve 4, is not limited to the solenoid valve 4, and is positioned between the first heat exchanger 3 and the second heat exchanger 5;
the second on-off element 10 is a one-way valve 10, one end of the second on-off element 10 is connected between the second heat exchanger 5 and the first on-off element 4, and the other end of the second on-off element 10 is connected between the four-way valve 2 and the first heat exchanger 3;
the third on-off element 6 is an electronic expansion valve 6, one end of the third on-off element 6 is connected between the first on-off element 4 and the first heat exchanger 3, and the other end of the third on-off element 6 is connected between the second heat exchanger 5 and the third heat exchanger 9;
when the four-way valve 2 is switched to a refrigeration state, the first on-off element 4 is switched on, the second on-off element 10 is switched off, and the third on-off element 6 is switched off; when the four-way valve 2 is switched to the heating state, the first on-off element 4 is turned off, the second on-off element 10 is turned on, and the third on-off element 6 is turned on.
The third shut-off element 6 is an electronic expansion valve and is used for controllably adjusting the opening degree so as to ensure that the first heat exchanger 3 achieves the maximum refrigerating capacity under the condition of no condensation when the four-way valve 2 is switched to the heating state.
A reservoir 8 is arranged between the third heat exchanger 9 and the restriction element 7.
The heat exchange area of the first heat exchanger 3 is larger than that of the second heat exchanger 5.
When the four-way valve 2 is switched to a refrigeration state, the running frequency of the compressor is controlled by the difference value of the evaporation temperature of the third heat exchanger 9 and the dew point temperature of a state point B after outdoor fresh air flows through the total heat exchanger 11; when the four-way valve 2 is switched to a heating state, the operation frequency of the compressor is controlled by the difference between the evaporating temperature of the second heat exchanger 5 and the dew point temperature of the state point H after the indoor return air passes through the adsorption runner 12 for adsorption.
Wherein the difference is positively correlated with the frequency and ensures that the evaporation temperature is not less than the frosting temperature.
Cooling and dehumidifying mode of the present embodiment:
the operation and component control of the cooling and dehumidifying of the present embodiment will be described with reference to fig. 1, fig. 2, and fig. 4.
As shown in fig. 1, the refrigeration and dehumidification process: a) the outdoor fresh air OA and the indoor return air RA are subjected to heat-mass exchange through the total heat exchanger 11, the temperature and the moisture content of the outdoor fresh air are reduced to be state points B, and the temperature and the moisture content of the indoor return air are increased to be state points F; b) the air is cooled and dehumidified by a state point B of the full heat exchanger 11, and exchanges heat with a third heat exchanger 9 (an evaporator) to be further cooled and dehumidified, so that the temperature and the moisture content are further reduced to a state point C, the relative humidity of the air outlet at the point C is very high (more than 90 percent, and certain difference exists according to different structures of the heat exchangers), and the adsorption and dehumidification requirements of the runner 12 are met; c) heat exchange is carried out between the state point F of temperature rise and humidification of the total heat exchanger 11 and the first heat exchanger 3 (condenser), the temperature rises, the moisture content is unchanged, the relative humidity is reduced to be a state point G, and the desorption requirements of the adsorption type rotating wheel 12 are met by lower relative humidity and higher temperature; d) the state point G of the fresh air loop with high temperature and low relative humidity and the state point C with low temperature and high relative humidity respectively enter the desorption side and the adsorption side of the rotating wheel, the state point C is subjected to adsorption dehumidification at the adsorption side of the rotating wheel, the adsorption heat generated in the adsorption process heats the state point C, the state point D with increased temperature and reduced moisture content is changed, and fresh air SA is sent out, while the state point G is subjected to desorption humidification at the desorption side of the rotating wheel, the heat of the state point C is absorbed in the desorption process, and the state point H with reduced temperature and increased moisture content is changed; e) in order to further improve the energy efficiency of the system, the air outlet H at the desorption side of the rotating wheel and the second heat exchanger 5 (condenser) further exchange heat and recover energy, and the dirty air EA is discharged when the moisture content of the state point H is unchanged and the temperature is increased to be a state point I.
As shown in fig. 2, a) a compressor 1 compresses suction gas into discharge gas of high temperature and high pressure and discharges it into a first heat exchanger 3 through a four-way valve 2; b) the first heat exchanger 3 exchanges heat with a state point F which finishes heat and mass exchange and has increased temperature and moisture content through the total heat exchanger 11 and the outdoor fresh air OA, and a refrigerant at the outlet of the first heat exchanger 3 is cooled into a high-pressure two-phase state or a high-pressure supercooled liquid state with low supercooling degree by high-temperature high-pressure exhaust; c) at the moment, the electromagnetic valve 4 is opened, the electronic expansion valve 6 is in a fully closed state, the refrigerant enters the second heat exchanger 5 and exchanges heat with a state point H at the outlet of the desorption side, and the refrigerant is further cooled into high-pressure supercooled liquid; d) the high-pressure supercooled liquid refrigerant is throttled and decompressed into a low-pressure two-phase refrigerant by a throttling element 7 (an electronic expansion valve 7) and enters a liquid storage device 8; e) and a low-pressure two-phase refrigerant flows out of the liquid accumulator 8, enters the third heat exchanger 9 and exchanges heat with the state point B, absorbs heat and evaporates into a low-pressure overheat state, and enters the compressor 1 through the four-way valve 2.
From the above process, the contribution components for implementing the fresh air moisture load dehumidification treatment include the total heat exchanger 11, the evaporator 9 and the rotating wheel 12 for adsorption dehumidification. In the total heat exchanger 11, the fresh air and the return air are subjected to heat-mass exchange, so that the moisture content of the outlet air is reduced (state point B); in the evaporator 9, evaporative cooling dehumidification is achieved by lowering the air temperature to below the dew point temperature (state point C); the runner 12 adsorbs the side, and the fresh air with higher relative humidity is dehumidified (state point D) through the adsorption material effect.
Heating and humidifying mode of the present embodiment:
the operation and component control of heating and humidifying in the present embodiment will be described with reference to fig. 1, fig. 3, and fig. 5.
As shown in fig. 1, the heating and humidifying process: a) the outdoor fresh air OA and the indoor return air RA are subjected to heat-mass exchange through the total heat exchanger 11, the temperature and the moisture content of the outdoor fresh air are increased to be state points B, and the temperature and the moisture content of the indoor return air are reduced to be state points F; b) after heat exchange is carried out by the state point B of temperature rise and humidification of the total heat exchanger 11 and the third heat exchanger 9 (condenser), the temperature is increased, the moisture content is unchanged, the relative humidity is reduced to be the state point C, and the lower relative humidity (for example, about 20 percent) meets the desorption requirement of the runner 12; c) exchanging heat with the first heat exchanger 3 (evaporator) through the state point F of the state point of temperature reduction and humidity reduction of the total heat exchanger 11, wherein the state point G is formed by temperature reduction, constant moisture content and relative humidity increase; d) the fresh air loop state point C is desorbed at the desorption side of the rotating wheel 12, the moisture content is increased, humidification is realized, fresh air SA is sent out when the desorption process absorbs air heat and the temperature is reduced to a state point D, the return air loop state point G is absorbed at the adsorption side of the rotating wheel 12, the moisture content is reduced, and the adsorption heat generated in the adsorption process heats the air and the temperature is increased to a state point H; e) the rotating wheel adsorption side air-out state point H and the second heat exchanger 5 (evaporator) further exchange heat, and the temperature is reduced to a state point I, namely the dirty air EA is discharged out of the room.
As shown in fig. 3, a) a compressor 1 compresses suction gas into discharge gas of high temperature and high pressure and discharges it into a third heat exchanger 9 through a four-way valve 2; b) the third heat exchanger 9 exchanges heat with the state point B, and the refrigerant at the outlet of the third heat exchanger 9 is cooled into a high-pressure supercooled liquid state by high-temperature and high-pressure exhaust and enters the liquid reservoir 8; c) the high-pressure liquid refrigerant flows out of the liquid reservoir 8 and is divided into two paths, one path of the high-pressure liquid refrigerant enters the second heat exchanger 5 through the throttling element 7 to exchange heat with a state point H of the return air loop, absorbs heat and evaporates to form a low-pressure superheated refrigerant, the other path of the high-pressure liquid refrigerant enters the first heat exchange 3 through the electronic expansion valve 6 to exchange heat with a state point F of the return air loop, and the low-pressure superheated refrigerant is absorbed heat and evaporated to form the low-pressure superheated refrigerant; d) at this time, the electromagnetic valve 4 is in a fully closed state, and the refrigerant after heat exchange by the second heat exchanger 5 is converged by the check valve 10 and the refrigerant from the first heat exchanger 3 and then enters the compressor 1 through the four-way valve 2.
According to the process, the contribution component for realizing the fresh air humidity load humidifying treatment comprises a total heat exchanger 11 and a runner 12 for desorption and humidification. In the total heat exchanger 11, the fresh air and the return air are subjected to heat-mass exchange to realize the increase of the moisture content of the outlet air (state point B); in the runner 12, the moisture of the return air (state point G) is recovered through the runner adsorption side, and then the fresh air (state point C) with lower relative humidity is desorbed through the runner desorption side, so that humidification (state point D) is realized.
Component function and control:
total heat exchanger 11: carrying out heat-mass exchange between outdoor fresh air OA and indoor return air RA, and carrying out refrigeration and dehumidification: the temperature reduction and the humidity reduction of outdoor fresh air OA are realized, and the heating and humidifying are as follows: the temperature rise and the humidity increase of outdoor fresh air OA are realized;
first heat exchanger 3: the refrigeration and dehumidification are used as a condenser to provide high desorption temperature and low relative humidity air for the rotating wheel 12 so that the rotating wheel can exert dehumidification high performance;
the second heat exchanger 9: refrigeration and dehumidification are used as condensers, the energy of air is recovered, the high pressure of the system is further reduced, and the energy efficiency is improved;
the third heat exchanger 5: the refrigeration and dehumidification evaporator is used for dehumidifying air through evaporative cooling on one hand, and providing low-temperature and high-relative-humidity air for the rotating wheel 12 so as to bring the rotating wheel into play of dehumidification high performance on the other hand;
the rotating wheel 12: refrigerating and dehumidifying to dehumidify the fresh air, and heating and humidifying to humidify the fresh air;
the air supply fan 14: the fan of the fresh air loop sucks fresh air OA to supply air SA to the user room;
discharge fan 13: the fan of the return air loop sucks the return air RA and discharges the dirty air EA outdoors;
the compressor 1: the low-pressure overheat inspiration is compressed into high-pressure high-temperature exhaust, the difference between the evaporation temperature of the third heat exchanger 9 and the dew point temperature of the state point B is controlled during refrigeration and dehumidification, the dehumidification capacity of the evaporator is guaranteed, the evaporator is not lower than 0 ℃, and the difference between the evaporation temperature of the second heat exchanger 5 and the dew point temperature of the state point H is controlled during heating and humidification, so that the capacity of the evaporator is guaranteed to be exerted, and the evaporator is not frosted;
four-way valve 2: the switching of a refrigerant circulation loop is realized, the four-way valve is OFF during refrigeration and dehumidification, and the four-way valve is ON during heating and humidification;
and (4) electromagnetic valve: the electromagnetic valve is opened during refrigeration and dehumidification to realize series connection between the first heat exchanger 3 and the second heat exchanger 5, and the electromagnetic valve is closed during heating and humidification to realize parallel connection between the first heat exchanger 3 and the second heat exchanger 5;
electronic expansion valve 6: closing the first heat exchanger during refrigeration and dehumidification, and controlling the opening degree of the first heat exchanger during heating and humidification to ensure that the first heat exchanger can fully exert capacity under the condition of no condensation, particularly controlling the superheat degree of an outlet of the first heat exchanger;
the throttling element 7: controlling the exhaust superheat degree of the compressor 1 in a reasonable range during refrigeration and dehumidification, and controlling the exhaust superheat degree of the compressor 1 in a reasonable range during heating and humidification;
the reservoir 8: generally, the refrigerant quantity for cooling/heating in the refrigerant circulation system is balanced, and the state of the refrigerant in the accumulator is a two-phase state during cooling and dehumidifying, and the state of the refrigerant in the accumulator is a supercooled liquid state during heating and humidifying. The main reason is that the first heat exchanger 3 and the second heat exchanger 5 are both condensers when the system is used for refrigerating, only the third heat exchanger 9 is used for heating, high-pressure liquid in the condensers is more, and the quantity of stored refrigerants is large, so that the refrigerant quantity required by the refrigerating system is larger than that for heating, and the refrigerating/heating refrigerant quantity is balanced by the demand reservoir;
the check valve 10: when heating is realized, the two loops of the first heat exchanger 3 and the second heat exchanger 5 are connected in parallel.
The technical points and the realization effects of the embodiment are as follows:
under the refrigeration and dehumidification working condition, two condensers, namely a first heat exchanger 3 and a second heat exchanger 5, are connected in series, under the heating and humidification working condition, two evaporators, namely the first heat exchanger 3 and the second heat exchanger 5, are connected in parallel, and the control of an electromagnetic valve 4 and an electronic expansion valve 6 and the arrangement of a one-way valve 10 are adopted to realize the refrigeration and dehumidification working condition, so that the dehumidification/humidification capacity of the dehumidifier and the system energy efficiency are ensured to exert the optimal effect. The realization effect is as follows: 1) the runner 12 is a component for realizing deep dehumidification of the third plate block after the total heat exchanger 11 and the third heat exchanger 9 in the refrigeration and dehumidification process, and according to the prior known knowledge, the most important influencing factors are the high desorption temperature and the low relative humidity of the state point G on the desorption side, in addition to the easily realized factors of the optimal rotation speed, the low temperature of the state point C on the inlet side and the high relative humidity, of the capacity of the runner 12. The system adopts the serial connection of the first heat exchanger 3 and the second heat exchanger 5 during refrigeration and dehumidification, and ensures that the refrigerant in the first heat exchanger 3 is in a state of no or little high-pressure high-temperature superheat section, two-phase section and supercooling section, thereby realizing the high-temperature state in the first heat exchanger 3, ensuring the high heat exchange temperature difference between the first heat exchanger 3 and a state point F, improving the sufficient heat exchange between the first heat exchanger 3 and the F, realizing the high desorption temperature and the low relative humidity of a rotor desorption inlet state point G, and realizing the high-efficiency performance exertion of the rotor 12 during refrigeration and dehumidification; 2) from the energy efficiency of the refrigeration system, the second heat exchanger 5 is connected with the first heat exchanger 3 in series, and the refrigerant of the second heat exchanger 5 is in a high-pressure two-phase state and a supercooled state, so that the realization of high supercooling degree in front of the throttling element 7 (electronic expansion valve) is facilitated, on one hand, the supercooling degree in front of a valve is promoted, and the noise problem of the electronic expansion valve is avoided, on the other hand, the dryness of the refrigerant entering the third heat exchanger 9, namely an evaporator, is reduced, the refrigeration capacity of the system is promoted, and the refrigerating capacity and the dehumidifying capacity of the third heat exchanger 9 are improved; 3) and under the heating and humidifying working condition, the first heat exchanger 3 and the second heat exchanger 5 are connected in parallel, so that on one hand, the capacities of the two heat exchangers are fully utilized to improve the heating capacity of the system and transfer heat to the third heat exchanger 9, on the other hand, the desorption side inlet state point C, namely the outlet air temperature of the third heat exchanger 9, is as high as possible, and the efficient performance of the humidifying performance of the runner is realized.
Secondly, in order to realize the capacity matching of the first heat exchanger 3 and the second heat exchanger 5 in refrigeration dehumidification and heating humidification, the area of the heat exchanger of the first heat exchanger 3 is required to be larger than that of the second heat exchanger 5, so that the energy of the third heat exchanger 9 and the energy of the compressor 1 in the refrigeration system under the refrigeration and dehumidification working conditions are ensured to be in the first heat exchanger 3 as much as possible, and the desorption temperature of the runner is increased, so that the performance is improved.
In the heating and humidifying process of the embodiment, the electronic expansion valve 6 controls the superheat degree of the first heat exchanger 3, the heat exchange capacity of the first heat exchanger is fully exerted under the condition of ensuring that the first heat exchanger is not condensed, on one hand, the capacity of the first heat exchanger can be fully exerted, the capacity of a condenser is improved, the humidifying capacity of the runner is improved by desorbing the inlet temperature of the runner 12, on the other hand, the capacity of the first heat exchanger is improved under the condition of ensuring that the first heat exchanger is not condensed, the relative humidity of the inlet state point G of the runner 12 can be improved, the humidifying capacity of the runner 12 is improved, the first heat exchanger 3 is controlled not to be condensed finally, the purpose is to recover the moisture from the indoor return air at the adsorption side of the runner 12 for the maximum, and therefore the humidifying capacity of the runner 12 is improved.
In the refrigeration and dehumidification process, the first heat exchanger and the second heat exchanger are connected in series, and the first heat exchanger and the air exchange with sufficient high temperature difference are realized through the area matching of the two heat exchangers to increase the front desorption temperature of the rotating wheel; in the heating and humidifying process, the first heat exchanger and the second heat exchanger are connected in parallel, and the heating capacity is fully exerted under the condition that the first heat exchanger is controlled not to be condensed, so that the high relative humidity of air at an adsorption inlet of the runner is realized, and the high desorption temperature at a desorption inlet of the runner is realized, thereby improving the heating and humidifying performance of the runner.
The air side sensor includes:
OA outdoor fresh air temperature sensor Toa;
RA indoor return air temperature sensor Tra and relative humidity sensor Hra;
SA fresh air supply temperature sensor Tsa and relative humidity sensor Ha;
the air inlet of the second heat exchanger is Tba in the state B, and the relative humidity sensor Hba;
the inlet air of the third heat exchanger is Tha in the state H, and the relative humidity sensor Hha;
the operation mode is as follows:
1) the user sets a "target temperature" and a "target relative humidity";
2) the controller of the unit can calculate the target air moisture content doa by using the "target temperature" and the "target relative humidity" and calculate the indoor return air moisture content dra by using the return air temperature sensor Tra and the relative humidity sensor Hra;
3) when the unit is stopped, comparing the difference value delta d = doa-dra between the target air moisture content and the indoor return air moisture content, if delta d is larger than a, operating the heating and humidifying mode, and if delta d is smaller than-a, operating the cooling and dehumidifying mode. Delta d is more than or equal to a, the difference between the moisture content of the target air and the moisture content of the current indoor return air is considered to be smaller, and the unit is kept out of operation;
4) in the running of the unit, if the heating and humidifying process is executed, stopping the unit when delta d is less than or equal to 0; if the refrigeration and dehumidification process is executed, stopping the machine when delta d is more than or equal to 0.
Example two
The present embodiment differs from the first embodiment in that the valve unit of the present embodiment lacks the third shut-off element 6.
The valve unit is used for being controlled to be switched to a state that a refrigerant flows through the second heat exchanger 5 and does not flow through the first heat exchanger 3 when the four-way valve 2 is switched to a heating state, the first heat exchanger 3 and the second heat exchanger 5 are evaporators, and the third heat exchanger 9 is a condenser.
Specifically, the valve unit includes:
a first on-off element 4 located between the first heat exchanger 3 and the second heat exchanger 5;
one end of the second on-off element 10 is connected between the second heat exchanger 5 and the first on-off element 4, and the other end of the second on-off element 10 is connected between the four-way valve 2 and the first heat exchanger 3;
when the four-way valve 2 is switched to a refrigeration state, the first on-off element 4 is switched on, and the second on-off element 10 is switched off; when the four-way valve 2 is switched to the heating state, the first on-off element 4 is turned off and the second on-off element 10 is turned on.
As shown in fig. 6 and 7, it is a system cycle diagram of cooling, dehumidifying, heating and humidifying in the present embodiment.
Fig. 4 and 8 are schematic diagrams of the cooling, dehumidifying, heating and humidifying processes of the embodiment.
In contrast to the first embodiment, the present embodiment eliminates the electronic expansion valve 6. The refrigeration and dehumidification process is the same as the first embodiment, and the heating and humidification process is different from the first embodiment in that: the refrigerant from the reservoir 8 enters the second heat exchanger 5 after being throttled and depressurized only by the throttling element 7, and then enters the four-way valve 2 through the check valve 10 to return to the compressor 1, and at this time, the electromagnetic valve 4 is closed.
The advantages of this embodiment are: 1) one electronic expansion valve 6 is saved, and the cost is reduced; 2) the heating and humidifying process omits the control of the electronic expansion valve 6, and the control is simpler.
The technical points and the realization effects of the embodiment are as follows:
under the refrigeration and dehumidification working condition, two condensers, namely a first heat exchanger 3 and a second heat exchanger 5, are connected in series, under the heating and humidification working condition, the electromagnetic valve 4 is closed, and the refrigerant only flows through the second heat exchanger 5 and returns to the compressor 1 through the one-way valve 10. The realization effect is as follows: 1) the runner 12 is a component for realizing deep dehumidification of the third plate block after the total heat exchanger 11 and the third heat exchanger 9 in the refrigeration and dehumidification process, and according to the prior known knowledge, the most important influencing factors are the high desorption temperature and the low relative humidity of the state point G on the desorption side, in addition to the easily realized factors of the optimal rotation speed, the low temperature of the state point C on the inlet side and the high relative humidity, of the capacity of the runner 12. The system adopts the serial connection of the first heat exchanger 3 and the second heat exchanger 5 during refrigeration and dehumidification, and ensures that the refrigerant in the first heat exchanger 3 is in a state of no or little high-pressure high-temperature superheat section, two-phase section and supercooling section, thereby realizing the high-temperature state in the first heat exchanger 3, ensuring the high heat exchange temperature difference between the first heat exchanger 3 and a state point F, improving the sufficient heat exchange between the first heat exchanger 3 and the F, realizing the high desorption temperature and the low relative humidity of a rotor desorption inlet state point G, and realizing the high-efficiency performance exertion of the rotor 12 during refrigeration and dehumidification; 2) from the energy efficiency of the refrigeration system, the second heat exchanger 5 is connected with the first heat exchanger 3 in series, and the refrigerant of the second heat exchanger 5 is in a high-pressure two-phase state and a supercooled state, so that the realization of high supercooling degree in front of the throttling element 7 (electronic expansion valve) is facilitated, on one hand, the supercooling degree in front of a valve is promoted, and the noise problem of the electronic expansion valve is avoided, on the other hand, the dryness of the refrigerant entering the third heat exchanger 9, namely an evaporator, is reduced, the refrigeration capacity of the system is promoted, and the refrigerating capacity and the dehumidifying capacity of the third heat exchanger 9 are improved; 3) heating humidification operating mode only adopts second heat exchanger 5, adopts this scheme, though abandoned the ability of first heat exchanger 3, but control is simple, avoid the condensation risk, in the embodiment one if electronic expansion valve 6 control aperture is too big, easily lead to first heat exchanger 3 ability too high, lead to with the wind temperature reduction of first heat exchanger 3 heat transfer too much, thereby the condensation leads to the moisture content of the air of the preceding adsorption side of runner 12 to reduce, retrieve the moisture that comes from indoor return air from runner 12 adsorption side and reduce, thereby the guide runner desorption side humidification effect is poor.
Secondly, in order to realize the capacity matching of the first heat exchanger 3 and the second heat exchanger 5 in refrigeration dehumidification and heating humidification, the area of the heat exchanger of the first heat exchanger 3 is required to be larger than that of the second heat exchanger 5, so that the energy of the third heat exchanger 9 and the energy of the compressor 1 in the refrigeration system under the refrigeration and dehumidification working conditions are ensured to be in the first heat exchanger 3 as much as possible, and the desorption temperature of the runner 12 is increased, thereby improving the performance.
The first embodiment is a preferable embodiment, and the second embodiment is lower in cost and simple in control, but the heat of the first heat exchanger 3 is not fully utilized, the inlet temperature of the desorption side of the runner 12 is low, and the relative humidity of the air before adsorption of the runner 12 is also low, which is not favorable for the performance of the humidifying capability of the runner 12.
The above description is only for the specific embodiments of the present invention, but the scope of the present invention is not limited thereto, and any changes or substitutions that can be easily conceived by those skilled in the art within the technical scope of the present invention are included in the scope of the present invention. Therefore, the protection scope of the present invention shall be subject to the protection scope of the claims.
Claims (10)
1. A humidity conditioning system, comprising:
the heat exchanger comprises a compressor (1), a four-way valve (2), a first heat exchanger (3), a second heat exchanger (5), a throttling element (7) and a third heat exchanger (9) which are sequentially connected through a refrigerant pipeline, wherein the third heat exchanger (9) is connected with the four-way valve (2);
the valve unit is used for being controlled to be switched to a state that the first heat exchanger (3) and the second heat exchanger (5) are connected in series when the four-way valve (2) is switched to a refrigeration state, the first heat exchanger (3) and the second heat exchanger (5) are condensers, and the third heat exchanger (9) is an evaporator;
a total heat exchanger (11);
an adsorption runner (12);
the air exhaust fan (13) is used for enabling indoor return air to sequentially flow through the total heat exchanger (11), the first heat exchanger (3), the adsorption type rotating wheel (12) for adsorption and the second heat exchanger (5) and then be discharged outdoors;
and the air supply fan (14) is used for delivering the fresh outdoor air into the room after passing through the total heat exchanger (11), the third heat exchanger (9) and the adsorption rotating wheel (12) in sequence and being desorbed.
2. The humidity adjustment system according to claim 1, wherein the valve unit is configured to be controlled to switch to a state where a refrigerant flows through the second heat exchanger (5) and does not flow through the first heat exchanger (3) when the four-way valve (2) is switched to a heating state, the first heat exchanger (3) and the second heat exchanger (5) are evaporators, and the third heat exchanger (9) is a condenser.
3. The humidity conditioning system of claim 2, wherein said valve unit comprises:
a first on-off element (4) located between the first heat exchanger (3) and the second heat exchanger (5);
a second on-off element (10), one end of the second on-off element (10) is connected between the second heat exchanger (5) and the first on-off element (4), and the other end of the second on-off element (10) is connected between the four-way valve (2) and the first heat exchanger (3);
when the four-way valve (2) is switched to a refrigeration state, the first on-off element (4) is switched on, and the second on-off element (10) is switched off; when the four-way valve (2) is switched to a heating state, the first on-off element (4) is cut off, and the second on-off element (10) is switched on.
4. A humidity conditioning system according to claim 1, wherein the valve unit is adapted to be controlled to switch to a state in which the second heat exchanger (5) and the first heat exchanger (3) are connected in parallel when the four-way valve (2) is switched to a heating state, the first heat exchanger (3) and the second heat exchanger (5) being evaporators and the third heat exchanger (9) being a condenser.
5. The humidity conditioning system of claim 4, wherein said valve unit comprises:
a first on-off element (4) located between the first heat exchanger (3) and the second heat exchanger (5);
a second on-off element (10), one end of the second on-off element (10) is connected between the second heat exchanger (5) and the first on-off element (4), and the other end of the second on-off element (10) is connected between the four-way valve (2) and the first heat exchanger (3);
one end of the third on-off element (6) is connected between the first on-off element (4) and the first heat exchanger (3), and the other end of the third on-off element (6) is connected between the second heat exchanger (5) and the third heat exchanger (9);
when the four-way valve (2) is switched to a refrigeration state, the first on-off element (4) is switched on, the second on-off element (10) is switched off, and the third on-off element (6) is switched off; when the four-way valve (2) is switched to a heating state, the first on-off element (4) is turned off, the second on-off element (10) is turned on, and the third on-off element (6) is turned on.
6. A humidity conditioning system according to claim 5, characterized in that the third shut-off element (6) is an electronic expansion valve for controlled adjustment of the opening to ensure that the first heat exchanger (3) reaches maximum cooling capacity without condensation when the four-way valve (2) is switched to the heating state.
7. A humidity conditioning system according to claim 1, characterized in that a reservoir (8) is provided between the third heat exchanger (9) and the throttling element (7).
8. A humidity conditioning system according to claim 1, characterized in that the heat exchange area of the first heat exchanger (3) is larger than the heat exchange area of the second heat exchanger (5).
9. A humidity adjusting system according to any one of claims 1 to 8, characterized in that when the four-way valve (2) is switched to a cooling state, the operation frequency of the compressor is controlled by the difference between the evaporating temperature of the third heat exchanger (9) and the dew point temperature of the state point B after outdoor fresh air passes through the total heat exchanger (11); when the four-way valve (2) is switched to a heating state, the running frequency of the compressor is controlled through the difference between the evaporating temperature of the second heat exchanger (5) and the dew point temperature of a state point H after indoor return air passes through the adsorption type rotating wheel (12) for adsorption.
10. The humidity conditioning system of claim 9, wherein said difference is positively correlated to said frequency and ensures that said evaporation temperature is not below frosting temperature.
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