CN114198829B - Humidity regulating system - Google Patents
Humidity regulating system Download PDFInfo
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- CN114198829B CN114198829B CN202111420313.9A CN202111420313A CN114198829B CN 114198829 B CN114198829 B CN 114198829B CN 202111420313 A CN202111420313 A CN 202111420313A CN 114198829 B CN114198829 B CN 114198829B
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- heat exchanger
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- rotating wheel
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- 230000001105 regulatory effect Effects 0.000 title abstract description 4
- 238000001179 sorption measurement Methods 0.000 claims abstract description 37
- 238000010438 heat treatment Methods 0.000 claims description 49
- 239000003507 refrigerant Substances 0.000 claims description 32
- 238000001704 evaporation Methods 0.000 claims description 10
- 230000008020 evaporation Effects 0.000 claims description 10
- 230000003750 conditioning effect Effects 0.000 claims description 7
- 238000009833 condensation Methods 0.000 claims description 5
- 230000005494 condensation Effects 0.000 claims description 5
- 238000001816 cooling Methods 0.000 claims description 5
- 238000010521 absorption reaction Methods 0.000 claims description 4
- 238000007599 discharging Methods 0.000 claims description 4
- 230000002596 correlated effect Effects 0.000 claims description 2
- 238000003795 desorption Methods 0.000 abstract description 33
- 238000000034 method Methods 0.000 abstract description 29
- 238000004378 air conditioning Methods 0.000 abstract description 4
- 238000005457 optimization Methods 0.000 abstract description 2
- 238000007791 dehumidification Methods 0.000 description 42
- 238000005057 refrigeration Methods 0.000 description 33
- 238000010586 diagram Methods 0.000 description 8
- 230000000694 effects Effects 0.000 description 8
- 239000007789 gas Substances 0.000 description 7
- 239000007788 liquid Substances 0.000 description 7
- 238000004781 supercooling Methods 0.000 description 7
- 239000013526 supercooled liquid Substances 0.000 description 5
- 230000001276 controlling effect Effects 0.000 description 3
- CURLTUGMZLYLDI-UHFFFAOYSA-N Carbon dioxide Chemical compound O=C=O CURLTUGMZLYLDI-UHFFFAOYSA-N 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 2
- 238000005516 engineering process Methods 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
- 229910052760 oxygen Inorganic materials 0.000 description 1
- 239000001301 oxygen Substances 0.000 description 1
- 239000010865 sewage Substances 0.000 description 1
- 238000006467 substitution reaction Methods 0.000 description 1
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
-
- 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
Abstract
The invention relates to a humidity regulating system, which comprises a heat pump air conditioning system and an adsorption type rotating wheel, wherein the humidity regulation of fresh air is realized, a first heat exchanger and a second heat exchanger are connected in series in the refrigerating and dehumidifying process, and indoor return air firstly flows through the first heat exchanger, so that the first heat exchanger and air are subjected to high-temperature difference heat exchange to raise the desorption temperature before the rotating wheel, and the high-efficiency performance of the rotating wheel in refrigerating and dehumidifying is realized; and the optimization of a system loop 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, the temperature and the humidity are generally regulated through a total heat exchanger and an adsorption type rotating wheel, and the dehumidifying/humidifying capacity of the adsorption type rotating wheel cannot be improved to the greatest extent only through the total heat exchanger.
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 above purpose, the invention adopts the following technical scheme:
a humidity conditioning system comprising:
the compressor, the four-way valve, the first heat exchanger, the second heat exchanger, the throttling element and the third heat exchanger are sequentially connected through a refrigerant pipeline, and the third heat exchanger is connected with the four-way valve;
the valve unit is used for being controlled to switch 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 refrigerating 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 rotating wheel;
the exhaust fan is used for sequentially flowing the indoor return air through the total heat exchanger, the first heat exchanger, the adsorption type rotating wheel adsorption and the second heat exchanger and then discharging the indoor return air out of the room;
and the air supply fan is used for sequentially enabling outdoor fresh air to flow through the total heat exchanger, the third heat exchanger and the adsorption rotating wheel for desorption and then to be sent into a room.
Compared with the prior art, the technical scheme of the invention has the following technical effects: the humidity control system comprises a heat pump air conditioning system and an adsorption type rotating wheel, so that the humidity control of fresh air is realized, a first heat exchanger and a second heat exchanger are connected in series in the refrigerating and dehumidifying process, and indoor return air firstly flows through the first heat exchanger, so that the first heat exchanger and air are subjected to heat exchange with a sufficiently high temperature difference to raise the desorption temperature before the rotating wheel, and the high-efficiency performance of the rotating wheel in refrigerating and dehumidifying is realized; and the optimization of a system loop 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 required for the description of the embodiments will be briefly described below, and it is obvious that the drawings in the following description are only some embodiments of the present invention, and other drawings may be obtained according to these drawings without inventive effort for a person skilled in the art.
FIG. 1 is a schematic illustration of the air side process of the present invention.
Fig. 2 is a schematic system cycle diagram of a refrigeration and dehumidification process according to a first embodiment of the present invention.
Fig. 3 is a schematic system cycle diagram of a heating and humidification process according to a first embodiment of the present invention.
Fig. 4 is a schematic diagram of a refrigeration and dehumidification process according to one/two embodiment of the present 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 system cycle diagram of a refrigeration and dehumidification process according to a second embodiment of the present invention.
Fig. 7 is a schematic system cycle diagram of a heating and humidifying process according to a second embodiment of the present invention.
Fig. 8 is a schematic diagram 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 switching element;
7. a throttle element;
8. a reservoir;
9. a third heat exchanger;
10. a second switching element;
11. a total heat exchanger;
12. an adsorption type rotating wheel;
13. an exhaust fan;
14. an air supply fan;
in particular, if the cost is abundant, 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 electromagnetic valves.
OA: outdoor fresh air RA: indoor return air SA: sending fresh air EA: and discharging the polluted air.
A/B/C/D is the air state point of the fresh air loop, and E/F/G/H is the air state point of the return air loop.
Detailed Description
The following description of the embodiments of the present invention will be made clearly and completely with reference to the accompanying drawings, in which it is apparent that the embodiments described are only some embodiments of the present invention, but not all embodiments. All other embodiments, which can be made by those skilled in the art based on the embodiments of the invention without making any inventive effort, are intended to be within the scope of the invention.
In the description of the present invention, it should be noted that, unless explicitly specified and limited otherwise, the terms "mounted," "connected," and "connected" are to be construed broadly, and may be either fixedly connected, detachably connected, or integrally connected, for example; can be directly connected or indirectly connected through an intermediate medium. The specific meaning of the above terms in the present invention will be understood in specific cases by those of ordinary skill in the art. In the description of the above embodiments, 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 the like, 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 defining "a first" or "a second" may explicitly or implicitly include one or more such feature. In the description of the present invention, unless otherwise indicated, the meaning of "a plurality" is two or more.
For convenience in describing the technical principles and realization effects of refrigeration, dehumidification, heating and humidification of the invention, the following description assumes that the temperature and moisture content of outdoor fresh air OA are higher than indoor return air RA during refrigeration and dehumidification; the temperature and moisture content of the outdoor fresh air OA are lower than those of the indoor return air RA when heating and humidifying.
Example 1
A humidity conditioning system comprising:
the compressor 1, the four-way valve 2, the first heat exchanger 3, the second heat exchanger 5, the throttling element 7 and the third heat exchanger 9 are sequentially connected through refrigerant pipelines, and the third heat exchanger 9 is connected with the four-way valve 2;
the valve unit is used for being controlled to switch 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 refrigerating 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 rotor 12;
the exhaust fan 13 is used for sequentially passing the indoor return air RA through the total heat exchanger 11, the first heat exchanger 3, the adsorption type runner 12 and the second heat exchanger 5 and then discharging the indoor return air RA out of the room;
and the air supply fan 14 is used for desorbing outdoor fresh air OA sequentially flowing through the total heat exchanger 11, the third heat exchanger 9 and the adsorption rotating wheel 12 and then sending the desorbed fresh air OA into a room.
The valve unit is used for being controlled when the four-way valve 2 is switched to a heating state, and is switched to a state that the second heat exchanger 5 and the first heat exchanger 3 are connected in parallel, wherein 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 may be an electromagnetic valve 4, not limited to the electromagnetic valve 4, and is located between the first heat exchanger 3 and the second heat exchanger 5;
the second switching element 10 is a one-way valve 10, one end of the second switching element 10 is connected between the second heat exchanger 5 and the first switching element 4, and the other end of the second switching 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 refrigerating state, the first on-off element 4 is turned on, the second on-off element 10 is turned off, and the third on-off element 6 is turned 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 switching-off element 6 is an electronic expansion valve for controlled adjustment of the opening degree to ensure that the first heat exchanger 3 reaches the maximum refrigerating capacity without 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 throttling element 7.
The heat exchange area of the first heat exchanger 3 is larger than the heat exchange area of the second heat exchanger 5.
When the four-way valve 2 is switched to a refrigerating state, the operation frequency of the compressor is controlled through the difference value between the evaporation temperature of the third heat exchanger 9 and the dew point temperature of the state point B of the outdoor fresh air after flowing 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 through the difference between the evaporation temperature of the second heat exchanger 5 and the dew point temperature of the state point H after the indoor return air is absorbed by the absorption type rotating wheel 12.
Wherein the difference is positively correlated to the frequency and ensures that the evaporation temperature is not lower than the frosting temperature.
Refrigeration dehumidification mode of this embodiment:
the operation and the control of the components of the refrigeration and dehumidification of the present embodiment are described with reference to fig. 1, 2, and 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 outdoor fresh air temperature and the moisture content are reduced to be a state point B, and the indoor return air temperature is increased and the moisture content is increased to be a state point F; b) The temperature and moisture reduction state point B passes through the total heat exchanger 11 to exchange heat with the third heat exchanger 9 (evaporator), the temperature and moisture content are further reduced to the 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 the structure of the heat exchanger) so as to meet the adsorption and dehumidification requirements of the rotating wheel 12; c) Heat exchange is carried out through the state point F of temperature rise and humidification of the total heat exchanger 11 and the first heat exchanger 3 (condenser), the temperature is increased, the moisture content is unchanged, the relative humidity is reduced to the state point G, and the desorption requirement of the adsorption rotating wheel 12 is 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 adsorbed and dehumidified on the adsorption side of the rotating wheel, 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 into a state point D with new air SA sent out, the state point G is desorbed and humidified on the desorption side of the rotating wheel, the heat of the state point C is absorbed in the desorption process, and the state point G with reduced temperature and increased moisture content is changed into a state point H; 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, the moisture content of the state point H is unchanged, and the temperature is increased to the state point I, namely the sewage air EA is discharged.
As shown in fig. 2, a) the compressor 1 compresses suction gas into high-temperature and high-pressure exhaust gas and discharges the exhaust gas into the first heat exchanger 3 through the four-way valve 2; b) The first heat exchanger 3 exchanges heat with a state point F at which the heat mass exchange is finished through the total heat exchanger 11 and the outdoor fresh air OA, the temperature is increased, the moisture content is increased, and the refrigerant at the outlet of the first heat exchanger 3 is cooled into a high-pressure two-phase state or a supercooled liquid state with very low high pressure and supercooling degree by high-temperature high-pressure exhaust; c) At this time, the electromagnetic valve 4 is opened, the electronic expansion valve 6 is fully closed, the refrigerant enters the second heat exchanger 5 and exchanges heat with the state point H of the desorption side outlet, and the refrigerant is further cooled into high-pressure supercooled liquid; d) The high-pressure supercooled liquid refrigerant is throttled and depressurized by a throttling element 7 (an electronic expansion valve 7) to be low-pressure two-phase refrigerant, and the low-pressure two-phase refrigerant enters a liquid reservoir 8; e) The low-pressure two-phase refrigerant flowing out of the liquid storage 8 enters the third heat exchanger 9 and exchanges heat with the state point B, the refrigerant absorbs heat and evaporates into a low-pressure overheat state, and the refrigerant enters the compressor 1 through the four-way valve 2.
The above process shows that the contribution parts for realizing the fresh air wet load dehumidification treatment comprise three parts, namely a total heat exchanger 11, an evaporator 9 and a rotating wheel 12 for adsorption dehumidification. In the total heat exchanger 11, fresh air is subjected to heat and mass exchange with return air to reduce the moisture content of the outlet air (state point B); in the evaporator 9, evaporative cooling dehumidification is achieved by lowering the air temperature below the dew point temperature (state point C); the adsorption side of the rotating wheel 12 is used for dehumidifying fresh air with relatively high humidity through the action of the adsorption material (state point D).
Heating humidification mode of the present embodiment:
the operation of heating and humidification and the control of the components of this embodiment are described with reference to fig. 1, 3, and 5.
As shown in fig. 1, the heating and humidification 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 outdoor fresh air temperature and the moisture content are increased to be a state point B, the indoor return air temperature is reduced, and the moisture content is reduced to be a state point 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 the state point C, and the lower relative humidity (for example, about 20 percent) meets the desorption requirement of the rotating wheel 12; c) The temperature is reduced, the humidity is reduced, the state point F is a state point G when the temperature is reduced, the humidity is reduced, the relative humidity is increased through the temperature reduction of the total heat exchanger 11 and the heat exchange between the total heat exchanger 11 and the first heat exchanger 3 (evaporator); 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, the desorption process absorbs air heat, the temperature is reduced to the state point D, namely fresh air SA is sent out, the return air loop state point G is adsorbed 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 the state point H; e) The air outlet state point H of the adsorption side of the rotating wheel exchanges heat with the second heat exchanger 5 (evaporator), and the temperature is reduced to the state point I, namely the discharged dirty air EA is discharged outside.
As shown in fig. 3, a) the compressor 1 compresses the suction gas into high-temperature high-pressure exhaust gas and discharges the exhaust gas to the third heat exchanger 9 through the 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 high-pressure exhaust gas and enters the liquid reservoir 8; c) The high-pressure liquid refrigerant flows out of the liquid storage 8 and is divided into two paths, one path enters the second heat exchanger 5 through the throttling element 7 and exchanges heat with a state point H of the return air loop, the heat absorption and evaporation are low-pressure overheat refrigerant, and the other path enters the first heat exchange 3 through the electronic expansion valve 6 and exchanges heat with a state point F of the return air loop, and the heat absorption and evaporation are low-pressure overheat refrigerant; d) At this time, in the fully closed state of the electromagnetic valve 4, the refrigerant subjected to heat exchange by the second heat exchanger 5 passes through the one-way valve 10 and the refrigerant from the first heat exchanger 3, and then enters the compressor 1 through the four-way valve 2.
The above process shows that the contribution parts for realizing the fresh air wet load humidification treatment comprise a total heat exchanger 11 and a rotating wheel 12 for desorption and humidification. In the total heat exchanger 11, fresh air performs heat and mass exchange with return air to increase the moisture content of the outlet air (state point B); in the rotating wheel 12, moisture in return air (state point G) is recovered through the rotating wheel adsorption side, and then desorption is performed through the rotating wheel desorption side by using fresh air (state point C) with low relative humidity, thereby realizing humidification (state point D).
Component function and control:
total heat exchanger 11: the outdoor fresh air OA and the indoor return air RA perform heat and mass exchange, and the refrigeration and dehumidification are performed: realize the temperature reduction and humidity reduction of outdoor fresh air OA, heat humidification: the temperature rise and the humidity increase of outdoor fresh air OA are realized;
the first heat exchanger 3: the refrigeration and dehumidification serves as a condenser, and provides high desorption temperature and low relative humidity air for the rotating wheel 12 so that the rotating wheel can play a role in dehumidification and high performance;
the second heat exchanger 9: the refrigeration dehumidification is used as a condenser, the energy of the air is recovered, the high pressure of the system is further reduced, and the energy efficiency is improved;
the third heat exchanger 5: refrigeration dehumidification serves as an evaporator, on one hand, dehumidifies air through evaporative cooling, and on the other hand, provides low-temperature and high-relative-humidity air for the rotating wheel 12 so that the rotating wheel can perform dehumidification with high performance;
wheel 12: the refrigeration and dehumidification dehumidifies the fresh air, and the heating and humidification is the fresh air humidification;
air blower 14: the fan of the fresh air loop sucks fresh air OA, and supplies air SA for the indoor of a user;
the exhaust fan 13: a fan of the return air loop sucks return air RA and discharges dirty air EA outdoors;
compressor 1: the low-pressure overheat air suction 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 ensured, the evaporator is not lower than 0 ℃, 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, the exertion of the capacity of the evaporator is ensured, 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;
solenoid valve 4: the electromagnetic valve is opened during refrigeration and dehumidification, so that the first heat exchanger 3 and the second heat exchanger 5 are connected in series, the electromagnetic valve is closed during heating and humidification, and the first heat exchanger 3 and the second heat exchanger 5 are connected in parallel;
electronic expansion valve 6: closing the first heat exchanger during refrigeration and dehumidification, controlling the opening degree of the first heat exchanger during heating and humidification to ensure that the first heat exchanger fully plays a role under the condition of no condensation, and particularly controlling the superheat degree of an outlet of the first heat exchanger;
throttling element 7: the exhaust superheat degree of the compressor 1 is controlled within a reasonable range during refrigeration and dehumidification, and the exhaust superheat degree of the compressor 1 is also controlled within a reasonable range during heating and humidification;
reservoir 8: in general, the state of the refrigerant in the accumulator is in a two-phase state during refrigeration and dehumidification, and the state of the refrigerant in the accumulator is in a supercooled liquid state during heating and humidification. The main reason is that when the system is used for refrigerating, the first heat exchanger 3 and the second heat exchanger 5 are both condensers, and only the third heat exchanger 9 is used for heating, so that the condenser is more in high-pressure liquid state and more in refrigerant storage capacity, the refrigerant capacity required by the refrigerating system is larger than that required for heating, and the accumulator is required to balance the refrigerating/heating refrigerant capacity;
check valve 10: when heating is realized, two loops of the first heat exchanger 3 and the second heat exchanger 5 are connected in parallel.
The technical point and the realization effect of the embodiment are as follows:
(1) the two condensers, namely the first heat exchanger 3 and the second heat exchanger 5 are connected in series under the refrigeration and dehumidification working condition, and the two evaporators, namely the first heat exchanger 3 and the second heat exchanger 5 are connected in parallel under the heating and humidification working condition and are realized through the control of the electromagnetic valve 4 and the electronic expansion valve 6 and the arrangement of the one-way valve 10 so as to ensure the dehumidification/humidification capability of the dehumidifier and the optimal effect of the system energy efficiency. The realization effect is as follows: 1) In the refrigerating and dehumidifying process, the rotating wheel 12 is a part for realizing deep dehumidification of the third plate following the total heat exchanger 11 and the third heat exchanger 9, and according to the prior known technology, the most important influencing factors are the high desorption temperature and the low relative humidity of the state point G at the desorption side besides the factors which are easy to realize such as the optimal rotation speed, the low temperature and the high relative humidity of the state point C at the inlet of the adsorption side, and the like, of the capability of the rotating wheel 12. The first heat exchanger 3 and the second heat exchanger 5 are connected in series during refrigeration and dehumidification, so that the refrigerant in the first heat exchanger 3 is in a state of no or little of a high-pressure high-temperature super-heated section, a two-phase section and a super-cooled section, the high-temperature state in the first heat exchanger 3 is realized, the high heat exchange temperature difference between the first heat exchanger 3 and a state point F is ensured, the sufficient heat exchange between the first heat exchanger 3 and the first heat exchanger F is improved, the high desorption temperature and the low relative humidity of a rotating wheel desorption inlet state point G are realized, and the high-efficiency performance exertion of the rotating wheel 12 during refrigeration and dehumidification is realized; 2) From the aspect of the energy efficiency of the refrigerating system, the second heat exchanger 5 is connected with the first heat exchanger 3 in series, the refrigerant of the second heat exchanger 5 is in a high-pressure two-phase state and a supercooling state, so that the high supercooling degree in front of the throttling element 7 (electronic expansion valve) is realized, on one hand, the supercooling degree in front of the lifting valve is facilitated, the noise problem of the electronic expansion valve is avoided, on the other hand, the dryness fraction entering the third heat exchanger 9, namely the evaporator, is reduced, the refrigerating capacity of the system is improved, and the refrigerating capacity and the dehumidifying capacity of the third heat exchanger 9 are improved; 3) The heating and humidifying working condition is that the first heat exchanger 3 and the second heat exchanger 5 are connected in parallel, on one hand, the capacities of the two heat exchangers are fully utilized to improve the heating capacity of the system and the heat transferred to the third heat exchanger 9, on the other hand, the desorption side inlet state point C, namely the air outlet temperature of the third heat exchanger 9 is as high as possible, and the high-efficiency exertion of the humidifying performance of the rotating wheel is realized.
(2) In order to achieve capacity matching of the first heat exchanger 3 and the second heat exchanger 5 in refrigeration dehumidification and heating humidification in (1), the heat exchanger area of the first heat exchanger 3 is required to be larger than that of the second heat exchanger 5, so that energy of the third heat exchanger 9 and the compressor 1 in the refrigeration system under refrigeration dehumidification working conditions is ensured to be in the first heat exchanger 3 as much as possible, and the desorption temperature of the rotating wheel is improved, so that performance is improved.
(3) In the heating and humidifying process of this embodiment, the electronic expansion valve 6 controls the superheat degree of the first heat exchanger 3, and fully exerts its heat exchange capability under the condition of ensuring that it does not condense, on one hand, fully exerts its capability to raise the capability of the condenser, and the desorption inlet temperature of the rotating wheel 12 raises the humidification capability of the rotating wheel, and on the other hand, raises its capability under the condition of ensuring that it does not condense, and can raise the relative humidity of the adsorption inlet state point G of the rotating wheel 12, thereby being beneficial to raising the humidification capability of the rotating wheel 12, and finally, the first heat exchanger 3 is required to be controlled so as to furthest raise the humidification capability of the rotating wheel 12 by recovering the moisture from indoor return air from the adsorption side of the rotating wheel 12.
In the embodiment, the first heat exchanger and the second heat exchanger are connected in series in the refrigeration and dehumidification process, and the area matching of the two heat exchangers realizes that the first heat exchanger and the air are subjected to heat exchange with a sufficiently high temperature difference to raise the desorption temperature before the rotating wheel; the first heat exchanger and the second heat exchanger are connected in parallel in the heating and humidifying process, 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 the air at the adsorption inlet of the rotating wheel is realized, the desorption inlet of the rotating wheel is high in desorption temperature, and the heating and humidifying performance of the rotating wheel is further improved.
The air side sensor includes:
an OA outdoor fresh air temperature sensor Toa;
RA indoor return air temperature sensor Tra, relative humidity sensor hrs;
SA fresh air supply temperature sensor Tsa, relative humidity sensor Has;
the inlet air of the second heat exchanger is Tba of the state B, and the relative humidity sensor Hba;
the air intake of the third heat exchanger is the Tha of the state H, and the relative humidity sensor Hha;
operation mode:
1) The user sets "target temperature" and "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 a return air temperature sensor Tra and a relative humidity sensor Hra;
3) When the machine set is stopped, the difference Deltad= doa-dra between the target air moisture content and the indoor return air moisture content is compared, if Deltad is more than a, the heating and humidifying mode is operated, and if Deltad is less than-a, the refrigerating and dehumidifying mode is operated. A is more than or equal to Deltad and less than or equal to a, the difference between the target air moisture content and the current indoor return air moisture content is considered to be smaller, and the unit is kept to be inoperative;
4) In the running of the unit, if the heating and humidifying process is executed, the Deltad is less than or equal to 0 and is stopped; if the refrigerating and dehumidifying process is executed, the Deltad is more than or equal to 0 and the machine is stopped.
Example two
The present embodiment differs from the first embodiment in that the valve unit of the present embodiment lacks the third break element 6.
The valve unit is used for being controlled when the four-way valve 2 is switched to a heating state, the state is switched to a state that the refrigerant flows through the second heat exchanger 5 and does not flow through the first heat exchanger 3, 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;
a second switching element 10, one end of the second switching element 10 is connected between the second heat exchanger 5 and the first switching element 4, and the other end of the second switching 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 refrigerating state, the first on-off element 4 is turned on, and the second on-off element 10 is turned 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, the system cycle chart of the present embodiment for cooling, dehumidifying, heating, and humidifying is shown.
As shown in fig. 4 and 8, the present embodiment is a schematic diagram of the cooling, dehumidifying and heating humidification process.
Compared with 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 liquid reservoir 8 only enters the second heat exchanger 5 after being throttled and depressurized by the throttling element 7, then enters the four-way valve 2 through the one-way valve 10 and returns to the compressor 1, and the state of the electromagnetic valve 4 is closed at the moment.
The advantage of this embodiment is that: 1) One electronic expansion valve 6 is saved, and the cost is reduced; 2) The control of the electronic expansion valve 6 is omitted in the heating and humidifying process, and the control is simpler.
The technical point and the realization effect of the embodiment are as follows:
(1) the two condensers, namely the first heat exchanger 3 and the second heat exchanger 5, are connected in series under the refrigeration and dehumidification working condition, the electromagnetic valve 4 is closed under the heating and humidification working condition, 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) In the refrigerating and dehumidifying process, the rotating wheel 12 is a part for realizing deep dehumidification of the third plate following the total heat exchanger 11 and the third heat exchanger 9, and according to the prior known technology, the most important influencing factors are the high desorption temperature and the low relative humidity of the state point G at the desorption side besides the factors which are easy to realize such as the optimal rotation speed, the low temperature and the high relative humidity of the state point C at the inlet of the adsorption side, and the like, of the capability of the rotating wheel 12. The first heat exchanger 3 and the second heat exchanger 5 are connected in series during refrigeration and dehumidification, so that the refrigerant in the first heat exchanger 3 is in a state of no or little of a high-pressure high-temperature super-heated section, a two-phase section and a super-cooled section, the high-temperature state in the first heat exchanger 3 is realized, the high heat exchange temperature difference between the first heat exchanger 3 and a state point F is ensured, the sufficient heat exchange between the first heat exchanger 3 and the first heat exchanger F is improved, the high desorption temperature and the low relative humidity of a rotating wheel desorption inlet state point G are realized, and the high-efficiency performance exertion of the rotating wheel 12 during refrigeration and dehumidification is realized; 2) From the aspect of the energy efficiency of the refrigerating system, the second heat exchanger 5 is connected with the first heat exchanger 3 in series, the refrigerant of the second heat exchanger 5 is in a high-pressure two-phase state and a supercooling state, so that the high supercooling degree in front of the throttling element 7 (electronic expansion valve) is realized, on one hand, the supercooling degree in front of the lifting valve is facilitated, the noise problem of the electronic expansion valve is avoided, on the other hand, the dryness fraction entering the third heat exchanger 9, namely the evaporator, is reduced, the refrigerating capacity of the system is improved, and the refrigerating capacity and the dehumidifying capacity of the third heat exchanger 9 are improved; 3) The heating and humidifying working condition only adopts the second heat exchanger 5, and by adopting the scheme, the capacity of the first heat exchanger 3 is abandoned, but the control is simple, the condensation risk is avoided, and in the first embodiment, if the control opening of the electronic expansion valve 6 is too large, the capacity of the first heat exchanger 3 is easily too high, the air temperature exchanging heat with the first heat exchanger 3 is reduced too much, the condensation is caused, the moisture content of the air at the adsorption side before the rotating wheel 12 is reduced, the moisture from indoor return air is recovered from the adsorption side of the rotating wheel 12 is reduced, and the desorption side of the guiding wheel is poor in humidifying effect.
(2) In order to achieve capacity matching of the first heat exchanger 3 and the second heat exchanger 5 in refrigeration dehumidification and heating humidification in (1), the heat exchanger area of the first heat exchanger 3 is required to be larger than that of the second heat exchanger 5, so that energy of the third heat exchanger 9 and the compressor 1 in the refrigeration system under refrigeration dehumidification working conditions is ensured to be in the first heat exchanger 3 as much as possible, and desorption temperature of the rotating wheel 12 is improved, so that performance is improved.
The first embodiment is a preferred solution, and the second embodiment has lower cost and simple control, but the heat of the first heat exchanger 3 is not fully utilized, the inlet temperature of the desorption side of the rotating wheel 12 is low, and the relative humidity of the air before the rotating wheel 12 is adsorbed is also low, which is not beneficial to the utilization of the humidifying capacity of the rotating wheel 12.
The foregoing is merely illustrative of the present invention, and the present invention is not limited thereto, and any changes or substitutions easily contemplated by those skilled in the art within the scope of the present invention should be included in the scope of the present invention. Therefore, the protection scope of the invention is subject to the protection scope of the claims.
Claims (7)
1. A humidity conditioning system, comprising:
the device 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 switch 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 refrigerating state, the first heat exchanger (3) and the second heat exchanger (5) are condensers, and the third heat exchanger (9) is an evaporator; the valve unit is used for being controlled to switch to a state that 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) are evaporators, and the third heat exchanger (9) is a condenser;
a total heat exchanger (11);
an adsorption rotor (12);
the exhaust fan (13) is used for sequentially flowing the indoor return air through the total heat exchanger (11), the first heat exchanger (3), the adsorption rotating wheel (12) and the second heat exchanger (5) and then discharging the indoor return air out of the room;
the air supply fan (14) is used for sequentially desorbing outdoor fresh air through the total heat exchanger (11), the third heat exchanger (9) and the adsorption rotating wheel (12) and then sending the desorbed fresh air into a room;
when the four-way valve (2) is switched to a refrigerating state, the operation frequency of the compressor is controlled through the difference value between the evaporation temperature of the third heat exchanger (9) and the dew point temperature of a state point B of the outdoor fresh air flowing 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 through the difference value between the evaporation temperature of the second heat exchanger (5) and the dew point temperature of the state point H of the indoor return air after being absorbed by the absorption rotating wheel (12); the difference is positively correlated to the frequency and ensures that the evaporation temperature is not lower than the frosting temperature.
2. Humidity control system according to claim 1, characterized in that the valve unit is adapted to be controlled to switch to a state in which the refrigerant flowing through the second heat exchanger (5) 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) being evaporators, and the third heat exchanger (9) being condensers.
3. The humidity conditioning system of claim 2, wherein the valve unit comprises:
the first on-off element (4) is positioned between the first heat exchanger (3) and the second heat exchanger (5);
a second switching element (10), wherein one end of the second switching element (10) is connected between a second heat exchanger (5) and the first switching element (4), and the other end of the second switching 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 refrigerating state, the first on-off element (4) is turned on, and the second on-off element (10) is turned off; when the four-way valve (2) is switched to a heating state, the first on-off element (4) is turned off, and the second on-off element (10) is turned on.
4. The humidity conditioning system of claim 1, wherein the valve unit comprises:
the first on-off element (4) is positioned between the first heat exchanger (3) and the second heat exchanger (5);
a second switching element (10), wherein one end of the second switching element (10) is connected between a second heat exchanger (5) and the first switching element (4), and the other end of the second switching element (10) is connected between the four-way valve (2) and the first heat exchanger (3);
a third on-off element (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 refrigerating state, the first on-off element (4) is turned on, the second on-off element (10) is turned off, and the third on-off element (6) is turned 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.
5. Humidity control system according to claim 4, characterized in that the third shut-off element (6) is an electronic expansion valve for controlled adjustment of the opening degree 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.
6. Humidity conditioning system according to claim 1, characterized in that a reservoir (8) is arranged between the third heat exchanger (9) and the throttling element (7).
7. 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).
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