CN112797511B - Rotary dehumidification unit and control method thereof - Google Patents
Rotary dehumidification unit and control method thereof Download PDFInfo
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- CN112797511B CN112797511B CN202011561547.0A CN202011561547A CN112797511B CN 112797511 B CN112797511 B CN 112797511B CN 202011561547 A CN202011561547 A CN 202011561547A CN 112797511 B CN112797511 B CN 112797511B
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F3/00—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems
- F24F3/12—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling
- F24F3/14—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F11/00—Control or safety arrangements
- F24F11/0008—Control or safety arrangements for air-humidification
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F11/00—Control or safety arrangements
- F24F11/62—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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F11/00—Control or safety arrangements
- F24F11/70—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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F3/00—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems
- F24F3/12—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling
- F24F3/14—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification
- F24F2003/1458—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 using regenerators
- F24F2003/1464—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 using regenerators using rotating regenerators
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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
- F24F2110/00—Control inputs relating to air properties
- F24F2110/10—Temperature
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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
- F24F2110/00—Control inputs relating to air properties
- F24F2110/20—Humidity
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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
- F24F2203/00—Devices or apparatus used for air treatment
- F24F2203/10—Rotary wheel
- F24F2203/1032—Desiccant wheel
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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
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Abstract
The invention relates to the field of air conditioning equipment and discloses a rotary wheel dehumidification unit and a control method thereof, wherein the rotary wheel dehumidification unit comprises an air supply system, a rotary wheel and a regeneration air system; the air supply system comprises a first evaporator, a first compressor, a first condenser and a first expansion valve; the first evaporator is arranged in front of the moisture absorption area of the rotating wheel and used for adjusting the temperature of air before dehumidification; the first condenser is arranged behind the moisture absorption area of the rotating wheel and used for adjusting the temperature of the dehumidified air. The invention has wider temperature and humidity range, quicker response to the demand change of the regulated space, high dehumidification efficiency, stable control of the temperature and the humidity of the air supply and better constant temperature and humidity; meanwhile, the pipeline arrangement is simple, and the pipeline arrangement device is suitable for occasions with limited space.
Description
Technical Field
The invention relates to the field of air conditioning equipment, in particular to a rotary wheel dehumidification unit and a control method thereof.
Background
The rotary dehumidifier belongs to an important branch of the air conditioning field and is a typical representative of temperature control dehumidification. In a common condensation type dehumidifier, in a low-temperature and high-humidity environment, the temperature of an evaporator end is lower than the room temperature, so that the surface of the common condensation type dehumidifier is very easy to frost, once the common condensation type dehumidifier frosts, the working efficiency of a heat exchanger is greatly reduced, and the common condensation type dehumidifier is not suitable for the low-temperature environment. The dehumidification principle of the rotary wheel type dehumidifier is that moisture in air (namely air supply) sent into a regulated space is removed through a moisture absorption rotary wheel which continuously rotates, then moisture on a rotary disc is taken away through high-temperature dry air (namely regeneration air), an area for absorbing the moisture in the air supply on the rotary wheel is a moisture absorption area, and an area for passing the regeneration air is a regeneration area. The rotary dehumidifier has the greatest advantage that the dehumidifying capacity is not limited by the temperature and the humidity of the environment, and the scene that a condensation type dehumidifier cannot be used can be made up.
However, the rotary wheel type dehumidifier has the defects that the dehumidification process depends on the rotation of the rotary wheel, the energy consumption is high, the dehumidification efficiency is lower than that of a condensation type dehumidifier, meanwhile, the temperature response is not timely, the rotary wheel type dehumidifier cannot be suitable for scenes with rapidly changed adjusted parameters, the control on the temperature and the humidity of the supplied air is weak, and the rotary wheel type dehumidifier is easily influenced by air leakage and sudden load change.
Disclosure of Invention
The present invention is directed to overcoming at least one of the disadvantages of the related art, and to providing a rotary dehumidifier unit and a control method thereof.
The rotating wheel dehumidification unit comprises an air supply system, a rotating wheel and a regeneration air system, wherein the rotating wheel is arranged between the air supply system and the regeneration air system and used for exchanging air moisture of the air supply system and the regeneration air system; the rotating wheel comprises a moisture absorption area and a regeneration area; the system comprises an air supply system, an air compressor, a condenser and an expansion valve, wherein the air supply system is arranged in the air supply system and comprises a first evaporator, a first compressor, a first condenser and a first expansion valve which are sequentially connected through pipelines to form circulation; the air supply direct expansion system also comprises a refrigerant proportion regulating valve and a reserve condenser, the first compressor is connected with the first expansion valve through two ports of the refrigerant proportion regulating valve, the other port of the refrigerant proportion regulating valve is connected with an outlet of the reserve condenser through a pipeline, and an inlet of the reserve condenser is connected with an outlet of the first compressor through a pipeline; the first evaporator is arranged in front of the moisture absorption area of the rotating wheel and used for adjusting the temperature of air before dehumidification; the first condenser is arranged behind the moisture absorption area of the rotating wheel and used for adjusting the temperature of the dehumidified air. The air supply direct expansion system serves the air supply system, the refrigerant of the air supply direct expansion system directly exchanges heat with air supply at the first evaporator and/or the first condenser, no intermediate heat exchange medium (secondary refrigerant) exists, the heat exchange efficiency is high, the air supply temperature can be adjusted more quickly, the whole dehumidification and drying process is accelerated, and the temperature and humidity adjusting range of the whole rotary wheel dehumidification unit is widened. The air supply direct expansion system has the advantages that the space is also embodied, no intermediate heat exchange medium is used for reducing the number of pipelines, the pipeline circuit is simpler, the whole air supply direct expansion system can be arranged in the air supply system, the cross-system arrangement is not needed, and the space for arranging the pipelines is reduced.
Further, the first evaporator is arranged adjacent to the moisture absorption area of the rotating wheel and used for enabling air to enter the moisture absorption area of the rotating wheel immediately after being processed by the first evaporator. The operation that adjusts the temperature before the air supply moisture absorption is carried out by first evaporimeter, and the air supply is direct and the refrigerant heat transfer in the first evaporimeter, can accomplish the cooling fast, makes the water analysis in the air supply in the short time, and quick response is adjusted the humidity demand change in space, improves the moisture absorption effect in moisture absorption district, and the humidity variation of the range control air supply of accessible cooling is favorable to maintaining the invariable humidity in adjusted space simultaneously.
Furthermore, the first condenser is arranged at the tail end of the air supply system and is used for enabling the last temperature adjustment operation before air is sent out to be carried out by the first condenser. The first condenser is used as the last temperature adjusting device for sending air into the adjusted space, so that the air supply temperature range of the unit is expanded, the temperature demand change of the adjusted space can be responded quickly, the influence of sudden load is reduced, and the constant temperature of the adjusted space is maintained stably.
Further, the air supply system comprises an air feeder and at least three surface coolers; the blower is used for driving air in the air supply system to flow to the regulated space along the pipeline; the at least three surface coolers are distributed in the extending direction of the pipeline of the air supply system and used for adjusting the temperature of air in different pipe sections of the air supply system.
Further, the system also comprises a regenerative wind direct expansion system; the regeneration air direct expansion system is arranged in the regeneration air system and comprises a second evaporator, a second compressor, a second condenser and a second expansion valve which are sequentially connected through pipelines to form circulation; the second evaporator and the second condenser are used for adjusting the temperature of the regenerated air, and the regenerated air firstly passes through the second evaporator and then passes through the second condenser. The regenerative wind direct expansion system reduces the overall energy consumption, and uses the heater 22 with high energy consumption as a backup option, and the main heat load of the regenerative wind is borne by the second condenser 53.
Further, the device also comprises a filter; the filter is arranged at the head end of the air supply system pipeline, and/or at the tail end of the air supply system pipeline, and/or at the head end of the regeneration air system pipeline. A filter is arranged in front of the air supply direction of the first surface cooler to remove dust particles and the like in fresh air and keep the cleanliness of pipelines of an air supply system; a filter is arranged behind the air supply direction of the first condenser, impurities attached to the air in the flowing process of the air supply system are removed, and the cleanliness of the air sent into the conditioned space is improved; and a filter is arranged in front of the flow direction of the regeneration air of the second evaporator, so that most impurities of the regeneration air are filtered, and the cleanliness of a pipeline of a regeneration air system is kept.
The control method applied to the rotary wheel dehumidification unit comprises the following steps of: presetting adjustment standards delta t1, delta t2 and delta t3, wherein delta t1 and delta t2 are more than delta t3 at 2 ℃; receiving a dew point temperature of a demand of a conditioned space; acquiring the instant dew point temperature in the regulated space, calculating the difference delta t between the instant dew point temperature and the required dew point temperature, and regulating the output capacity of the first compressor according to the delta t: if the delta t is less than the delta t1, stopping the first compressor to enable the output capacity of the first compressor to be zero; if the delta t is more than or equal to delta t1 and less than the delta t2, the first compressor is adjusted to operate at the first output capacity; if the delta t is more than or equal to delta t2 and less than the delta t3, the first compressor is adjusted to operate at a second output capacity; if the delta t3 is less than or equal to the delta t, adjusting the first compressor to operate at a third output capacity; wherein the first output capacity is less than the second output capacity and less than the third output capacity; presetting a reference dew point temperature; comparing the instant dew point temperature in the room to be conditioned with the reference dew point temperature, if the former is greater than the latter, collecting the dry bulb temperature of the air to be treated by the first condenser, and controlling the opening degree of a port of the refrigerant proportion regulating valve, which is connected with the first condenser, so that the dry bulb temperature of the air treated by the first condenser is kept to be greater than or equal to the instant dew point temperature in the room to be conditioned; if the former is less than the latter, the maximum air supply dry bulb temperature is determined by the dew point temperature required by the regulated space, and the air processing equipment in the air supply system is controlled to ensure that the temperature of the air sent into the regulated space is less than or equal to the maximum air supply dry bulb temperature.
The dew point temperature of the conditioned space demand is indicative of the dehumidification demand, the lower the dew point temperature demand. The first compressor operates according to different regulation standards and different output capacities, when the difference between the instant dew point temperature and the required dew point temperature is large, the dehumidifying capacity of the regulated space is large, the output capacity increased by the first compressor operates, the refrigerating capacity of the first evaporator is increased, the instant dew point temperature of the regulated space is rapidly reduced and approaches the required dew point temperature, and the unit performs rapid dehumidification in a short time. In order to prevent the air supply from frosting at the air outlet of the adjusted space, a reference dew point temperature is preset, if the instant dew point temperature in the adjusted room is greater than the reference dew point temperature, which indicates that the air supply is likely to be frosted at the air outlet, the heating quantity of the first condenser is controlled by controlling the opening degree of the opening of the port of the refrigerant proportion adjusting valve connected with the first condenser, the dry bulb temperature of the air supply is always greater than or equal to the instant dew point temperature in the adjusted room, and the frosting is avoided. On the contrary, if the instant dew point temperature in the conditioned room is less than the reference dew point temperature, which indicates that the air supply part does not frost, the maximum air supply dry bulb temperature capable of meeting the dehumidification requirement of the conditioned space can be determined according to the dehumidification requirement of the conditioned room, the dry bulb temperature of the fed air is less than or equal to the maximum air supply dry bulb temperature by controlling the air processing equipment, and the lower the dry bulb temperature of the fed air is, the faster the dehumidification is. The first compressor and the refrigerant proportion adjusting valve are used as a control execution main body, and the control effect is instant, so that the response time of the whole rotary wheel dehumidification unit is further shortened, the temperature and the humidity of air supply are effectively controlled, and various use scenes are responded. The control method can quickly reduce the dew point temperature of the regulated space, achieve the effect of quick dehumidification and prevent frosting at the same time.
More specifically, the air equipment arranged in the air supply system of the rotary wheel dehumidification unit comprises an air feeder and at least three surface coolers; the blower is used for driving air in the air supply system to flow to the regulated space along the pipeline; the at least three surface coolers are distributed in the extending direction of the pipeline of the air supply system and are used for adjusting the temperature of air in different pipe sections of the air supply system; if Δ t < Δ t1 further includes: controlling the flow of chilled water in a surface cooler in an air supply system to maintain the instant dew point temperature in the regulated space; comparing the instantaneous dew point temperature in the conditioned room with the reference dew point temperature, and if the former is less than the latter, further comprising: the flow of the chilled water in the surface cooler in the air supply system is controlled so that the temperature of the air sent into the conditioned space is less than or equal to the maximum air supply dry bulb temperature.
Furthermore, after the dehumidification requirement is met, the positive pressure of the conditioned room needs to be maintained, and air supply caused by the influence of the air supply density and the air return density is reduced. When the delta t is less than 2 ℃, performing a positive pressure maintaining mode; the positive pressure maintaining mode specifically comprises the following steps: collecting the dry bulb temperature of air at the outlet of a moisture absorption area of the rotating wheel and the instant dry bulb temperature of the air in a regulated space; if the dry bulb temperature of the air at the outlet of the rotating wheel moisture absorption area is 2 ℃ or more higher than the instant dry bulb temperature of the air in the regulated space, the flow rate of the chilled water in the third surface cooler is increased to cool the air at the outlet of the rotating wheel moisture absorption area; and if the dry bulb temperature of the air at the outlet of the rotating wheel moisture absorption area is lower than the instant dry bulb temperature of the air in the adjusted space by 2 ℃ or more, increasing the opening degree of a port of the refrigerant proportion adjusting valve connected with the first condenser to heat the air at the outlet of the rotating wheel moisture absorption area.
Compared with the prior art, the invention has the beneficial effects that: the temperature and humidity range which can be reached is wider, the response to the demand change of the regulated space is quicker, the dehumidification efficiency is high, the control on the temperature and the humidity of the air supply is stable, and the constant temperature and the constant humidity are better realized; meanwhile, the pipeline arrangement is simple, and the pipeline arrangement device is suitable for occasions with limited space.
Drawings
FIG. 1 is a partial schematic structural view of the present invention.
Fig. 2 is a diagram of the air supply direct expansion system of the invention.
FIG. 3 is a diagram of a regenerative wind direct expansion system of the present invention.
Fig. 4 is a complete structural schematic diagram of the present invention.
FIG. 5 is a flowchart illustrating the overall control method of the present invention.
Fig. 6 is a specific dehumidification flow chart of the present invention.
FIG. 7 is a flow chart of an exemplary positive pressure maintenance mode of the present invention.
Description of reference numerals: a first surface cooler 11; a second surface cooler 12; a third surface cooler 13; a blower 14; a chilled water inlet pipe 15; a chilled water outlet line 16; a regenerative fan 21; a heater 22; a runner 30; the first evaporator 41; a first compressor 42; a first condenser 43; a first expansion valve 44; a refrigerant ratio adjusting valve 45; a reserve condenser 46; a gas-liquid separator 47; a drying filter 48; a reservoir 49; a second evaporator 51; a second compressor 52; a second condenser 53; a second expansion valve 54; a first filter 61; a second filter 62; and a third filter 63.
Detailed Description
The drawings are only for purposes of illustration and are not to be construed as limiting the invention. For a better understanding of the following embodiments, certain features of the drawings may be omitted, enlarged or reduced, and do not represent the size of an actual product; it will be understood by those skilled in the art that certain well-known structures in the drawings and descriptions thereof may be omitted.
Example 1
As shown in fig. 1 and 4, the present embodiment provides a rotary wheel dehumidifier unit, in which a part of the pipes and components of the air supply direct expansion system in fig. 1 are omitted, and fig. 4 is a structural diagram of a complete rotary wheel dehumidifier unit, the rotary wheel dehumidifier unit includes an air supply system, a rotary wheel 30, a regeneration air system and an air supply direct expansion system, and the rotary wheel 30 is disposed between the air supply system and the regeneration air system for exchanging air moisture between the air supply system and the regeneration air system. Wherein air supply system includes forced draught blower 14 and the first surface cooler 11, second surface cooler 12, the third surface cooler 13 that connects gradually through the pipeline, and first surface cooler 11 is arranged in adjusting the temperature to the new trend in the pipeline, and second surface cooler 12 is used for adjusting the temperature to the mixed wind, and third surface cooler 13 is used for adjusting the temperature to the air after runner is handled. The runner 30 is divided into a moisture absorption zone and a regeneration zone; the regeneration air system comprises a regeneration fan 21 and a heater 22; as shown in fig. 2, the air supply direct expansion system includes a first evaporator 41, a first compressor 42, a first condenser 43, and a first expansion valve 44, which are connected in sequence by pipes, and a refrigerant ratio adjusting valve 45 and a reserve condenser 46 are provided on the pipes.
In the air supply system, the position of the air feeder 14 in the air supply system is not limited, and the air feeder is used for driving the air in the air supply system to flow along the pipeline to the direction of the conditioned space, and the embodiment is preferably arranged on the pipeline connecting the first surface air cooler 11 and the second surface air cooler 12, the return air of the conditioned space is mixed with the unprocessed fresh air in the pipeline, and the fan 14 can effectively and quickly mix the return air and the fresh air, so that the return air and the fresh air can be subjected to forced heat exchange to form mixed air with uniform temperature and pass through the next pipeline. The first surface air cooler 11, the second surface air cooler 12 and the third surface air cooler 13 use chilled water as a cold source, and the chilled water continuously circulates through the inlet pipeline 15 and the outlet pipeline 16. The air of process is cooled down to three surface cooler, wherein the moisture absorption district of runner 30 locates between second surface cooler 12 and the third surface cooler 13, first surface cooler 11 is used for the precooling new trend, second surface cooler 12 is used for reducing the temperature of the mixed wind that new trend and return air mix and form, the mixed wind is absorbed most moisture behind the moisture absorption district of runner 30, humidity drops, third surface cooler 13 is used for adjusting the temperature of mixed wind behind the moisture absorption district of runner 30, if the mixed wind temperature after the moisture absorption is lower than the air temperature in the space of being transferred, then can open third surface cooler 13 and cool down.
In the regeneration air system, the setting position of the regeneration fan 21 in the regeneration air system is not limited, and it is used to drive the air in the regeneration air system to flow along the direction of the pipeline, in this embodiment, preferably, the regeneration fan 21 is set behind the regeneration air flow direction of the regeneration area of the rotating wheel 30, the air in the pipeline is heated by the heater 22 first, the moisture absorption capacity is enhanced, and then the air moisture in the air supply system is absorbed by the regeneration area of the rotating wheel 30, the position of the air suction side of the regeneration fan 21 is adjacent to the rotating wheel 30, the air coming out of the regeneration area of the rotating wheel 30 is sucked away quickly, the pressure difference between the two sides of the rotating wheel 30 is increased, the flow rate of the air entering the rotating wheel 30 is also increased, the air passes through the regeneration area of the rotating wheel 30 quickly, and the moisture absorption effect is enhanced.
The air supply direct expansion system is arranged in the air supply system and used for quickly adjusting and stabilizing the air temperature in the air supply system. The first evaporator 41, the first compressor 42, the first condenser 43 and the first expansion valve 44 are connected in sequence by pipes for circulating a refrigerant, which may be a common refrigerant such as R22 or R134 a. Wherein, a refrigerant proportion regulating valve 45 is arranged on a pipeline between the first condenser 43 and the first expansion valve 44, two ports of the refrigerant proportion regulating valve 45 are respectively led to the first condenser 43 and the first expansion valve 44, the remaining one port is connected with an outlet of a reserve condenser 46 through a pipeline, an inlet of the reserve condenser 46 is connected with an outlet of a compressor through a pipeline, the reserve condenser 46 and the first condenser 43 are connected in parallel with the first compressor 42, the high-temperature refrigerant coming out of the first compressor 42 flows in two ways, one part flows to the reserve condenser 46, the rest flows to the first condenser 43, the proportion of the two ways of distributed refrigerants is controlled through the refrigerant proportion regulating valve 45, the refrigerant proportion regulating valve 45 and the reserve condenser 46 are used for controlling the first condenser 43 to heat the air processed by the moisture absorption area of the runner 30, when the heating is not needed, the refrigerant proportion regulating valve 45 distributes all high-temperature refrigerants coming out of the first compressor 42 of the air supply direct expansion system to the reserve condenser 46, the refrigeration cycle in the air supply direct expansion system is normally carried out, and the first condenser 43 does not heat passing air; when heating is required, the refrigerant proportion adjusting valve 45 adjusts the opening degree of the port connected with the first condenser 43 and the port connected with the reserve condenser 46, high-temperature refrigerants coming out of the first compressor 42 are distributed according to different proportions, when the maximum heating effect is required, the port of the refrigerant proportion adjusting valve 45 connected with the reserve condenser 46 is completely closed, all the high-temperature refrigerants flow to the first condenser 43 to rapidly heat the supplied air, and the first condenser 43 can be arranged in front of or behind the third surface cooler 13. The whole air supply direct expansion system serves as an air supply system, the first evaporator 41 further cools the air (mixed air) passing through the second surface air cooler 12, and the first condenser 43 further adjusts the temperature of the air to be supplied to the adjusted space, so that the air can be prevented from frosting after being supplied to a room. The refrigerant of the two-process air supply direct expansion system directly exchanges heat with air supply without an intermediate heat exchange medium (secondary refrigerant), so that the heat exchange efficiency is high, the air supply temperature is adjusted more quickly, the whole dehumidification and drying process is accelerated, and the temperature and humidity adjusting range of the whole rotary wheel dehumidification unit is widened. The air supply direct expansion system has the advantages that the air supply direct expansion system is embodied in space, no middle heat exchange medium is used for reducing the number of pipelines, the first evaporator 41 and the first condenser 43 exchange heat with air in the air supply system, pipeline lines are simpler, and the whole air supply direct expansion system can be arranged in the air supply system without cross-system arrangement.
Further, the present embodiment further includes a regeneration wind direct expansion system provided in the regeneration wind system, as shown in fig. 3, which includes a second evaporator 51, a second compressor 52, a second condenser 53 and a second expansion valve 54 connected in sequence by pipes. The second evaporator 51 and the second condenser 53 are sequentially provided on a duct before the regeneration air of the heater of the regeneration air system flows, and the regeneration air sequentially passes through the second evaporator 51, the second condenser 53 and the heater 22 of the regeneration air system in the duct. The refrigerant in the second evaporator 51 is in a low temperature state, and the temperature of the regeneration air is reduced by the second evaporator 51, most of the moisture is removed, and the humidity is reduced; the second compressor 52 sends the high-temperature refrigerant having undergone heat exchange in the second evaporator 51 to the second condenser 53, and the high-temperature refrigerant exchanges heat with the passing regeneration air in the second condenser 53, and the regeneration air changes from a low-temperature and low-humidity state to a high-temperature and low-humidity state, thereby enhancing the moisture absorption capacity. When the temperature of the regeneration air is still not high enough after passing through the second condenser 53, the standby heater 22 may be turned on to supplement the surplus, and the heater 22 may be in the form of electric heating, steam heating, gas heating, heat transfer oil, or the like. The main energy consumption of the rotary dehumidifier lies in the regeneration energy consumption, in the existing rotary dehumidifier unit, the heat required by regeneration mainly adopts heating modes such as electric heating, steam heating, fuel gas heating, industrial waste heat and the like, the rotary dehumidifier unit of the embodiment utilizes a regeneration air direct expansion system to reduce the overall energy consumption, a heater with high energy consumption is used as a standby option, and the main heat load of the regeneration air is borne by a second condenser. Meanwhile, the system is the same as the air supply direct expansion system, the regeneration air direct expansion system does not have an intermediate heat exchange medium (secondary refrigerant), the heat exchange efficiency is high, the pipeline circuit is simple, and the arrangement space is saved.
In this embodiment, the air supply direct expansion system further preferably includes a gas-liquid separator 47, a drying filter 48, and a reservoir 49. The gas-liquid separator 47 is connected to the first evaporator 41 and the first compressor 42 through pipes, and the gas-liquid separator 47, the first evaporator 41, and the first compressor 42 are connected in series in a pipe of the air blowing direct expansion system. The gas-liquid separator 47 is used to separate the liquid-phase refrigerant and the gas-phase refrigerant from the first evaporator 41, to prevent liquid impact on the first compressor 42, and to protect the first compressor 42. The dry filter 48 and the accumulator 49 are provided in a pipe between the first condenser 43 and the first expansion valve 44, and the dry filter 48, the accumulator 49 and the refrigerant ratio adjusting valve 45 are connected in series. The dry filter 48 is used for filtering impurities of the refrigerant in the air supply direct expansion system and protecting the first expansion valve 44; the accumulator 49 serves to prevent the compressor from sucking liquid refrigerant and causing liquid slugging.
Further, the rotary wheel dehumidification unit of the present embodiment further includes filters, including a first filter 61, a second filter 62, and a third filter 63, in the air supply system and the regeneration air system. The first filter 61 is arranged in a pipeline in the air supply system in front of the air supply direction of the first surface cooler 11 and used for removing fresh air impurities and ensuring the air cleanliness of the air supply system; the second filter 62 is arranged at the tail end of a pipeline in the air supply system and is used for cleaning before inputting air to the regulated space, so that the air supply cleanliness is ensured; the third filter 63 is disposed at the head end of the pipeline in the regeneration air system, and is used for removing air impurities at the inlet of the regeneration air system and ensuring the air cleanliness of the regeneration air system.
The whole dehumidification process of the rotary wheel dehumidification unit of the embodiment is as follows:
the new trend gets into air supply system's pipeline, at first through first filter 61, and first filter 61 goes on removing the impurity to the new trend and handles, guarantees the air cleanliness factor in the follow-up pipeline. Then, the fresh air passes through the first surface air cooler 11, the first surface air cooler 11 pre-cools the fresh air, return air with parameters similar to the air parameters of the conditioned space is introduced into a pipeline behind the first surface air cooler 11, the pipeline is close to the suction side of the air feeder 14, and the fresh air and the return air are quickly mixed and transfer heat under the action of the air feeder 14 to form mixed air with uniform temperature distribution. The mixed air is discharged from the blower 14 and passes through the second surface air cooler 12, and the second surface air cooler 12 carries out large-amplitude temperature reduction treatment on the mixed air, so that the moisture absorption capacity of the mixed air is reduced, and water in the mixed air is easy to separate out. The mixed air processed by the second surface air cooler 12 is provided with a first evaporator 41 on a pipeline before being sent to the runner 30, and the first evaporator 41 belongs to an air supply direct expansion system and is used for further cooling the mixed air passing through to make up for the cooling allowance of the first surface air cooler 41. The mixed air passes through the next pipeline, the next pipeline is provided with a moisture absorption area of the rotating wheel 30, moisture of the mixed air is absorbed on the moisture absorption area, the humidity of the passing mixed air is greatly reduced and changed into low-temperature and low-humidity air, the mixed air passes through the rear rotating wheel to rotate, the original moisture absorption area rotates to a pipeline in a regeneration air system, and the rotating wheel part in the pipeline of the air supply system is called as a new moisture absorption area. The runner air-out is through third surface cooler 13 and is handled by the cooling of third surface cooler 13, reaches first condenser 43 in the air supply direct expansion system, and whether first condenser 43 selects to heat the air supply and selects the heating degree to the air supply according to the needs in the space of transferring, and the air supply is sent to the space of transferring after further filtering impurity through second filter 62 at last, and whole process forced draught blower 14 is operated ceaselessly, guarantees that the air in the air supply system flows.
The treatment of the regenerated air is performed synchronously with the treatment of the fresh air, and the regenerated air enters a pipeline of the regenerated air system, passes through the third filter 63 firstly, is filtered and then is conveyed to the next pipeline. The next pipeline is provided with a second evaporator 51 of the regeneration direct expansion system, the second evaporator 51 carries out temperature reduction treatment on the regeneration air and simultaneously removes most moisture of the regeneration air, and then a second condenser 53 of the regeneration direct expansion system reheats the regeneration air so as to improve the moisture absorption capacity of the regeneration air. The regeneration air is then transported to the heater 22, and the heater 22 selects whether to heat the regeneration air and the heating degree of the regeneration air according to the needs of the conditioned space. After passing through the heater 22, the regeneration air enters the pipeline of the regeneration area provided with the rotating wheel 30, the regeneration area of the rotating wheel 30 is provided with the moisture absorbed by the rotating wheel 30 from the air supply system, the regeneration air carries away the moisture and is conveyed to the next pipeline to be discharged, the regeneration fan 21 does not stop operating in the whole process, and the air flow in the regeneration air system is ensured.
The above-mentioned pipes include a pipe for carrying refrigerant and a pipe for carrying air, and those skilled in the art can easily distinguish between the above and below, and thus the distinguishing description is omitted for the sake of brevity.
Example 2
As shown in fig. 5, this embodiment provides a control method for a rotating wheel dehumidifier unit according to embodiment 1, where the control method requires to acquire air parameters at different pipeline positions of the rotating wheel dehumidifier unit, and preferably, a dew point temperature of a return air pipeline of the rotating wheel dehumidifier unit is acquired as an instant dew point temperature in a conditioned space; collecting the dry bulb temperature of the air in the air supply pipeline behind the first condenser as the dry bulb temperature of the air fed into the regulated space; the collecting process can be carried out by arranging a temperature sensor or other collecting and measuring means in the pipeline; in different embodiments, those skilled in the art can collect corresponding temperatures according to corresponding pipe arrangements and obtain the instant dew point temperature in the conditioned space and the dry bulb temperature of the air fed into the conditioned space through an enthalpy-humidity relationship, which are not listed here, and the specific processes are as follows:
presetting adjustment standards delta t1, delta t2 and delta t3, wherein delta t1 and delta t2 are more than delta t3 at 2 ℃; the adjustment standards Δ t1, Δ t2, and Δ t3 are dehumidification demand gradients, the units perform dehumidification of different degrees under different gradients, in this embodiment, Δ t1 is 0 ℃, Δ t2 is 5, and Δ t3 is 10, this dehumidification demand gradient can meet the requirements of most comfort air conditioners, and other embodiments can be set in a matching manner according to actual application scenarios.
Receiving a dew point temperature of a demand of a conditioned space; the user can set the dew point temperature required by the regulated space through a remote controller and other terminals or other common means, and the rotating wheel dehumidification unit receives the dew point temperature;
acquiring the instant dew point temperature in the regulated space, calculating the difference delta t between the instant dew point temperature and the required dew point temperature, and regulating the output capacity of the first compressor according to the delta t: if Δ t is less than Δ t1, stopping the first compressor to make its output capacity zero, and in this embodiment, maintaining the instant dew point temperature in the conditioned space by controlling the flow rate of the chilled water in the surface cooler in the air supply system; if the delta t is more than or equal to delta t1 and less than the delta t2, the first compressor is adjusted to operate at the first output capacity; if the delta t is more than or equal to delta t2 and less than the delta t3, the first compressor is adjusted to operate at a second output capacity; if the delta t3 is less than or equal to the delta t, adjusting the first compressor to operate at a third output capacity; wherein the first output capacity is less than the second output capacity and less than the third output capacity; the smaller Δ t represents the smaller amount of dehumidification required by the conditioned room, and the humidity of the conditioned room before conditioning is already close to the required humidity. The output capacity of the first compressor is controlled to adjust the cooling capacity of the first evaporator, so that the air entering the rotating wheel reaches a proper low temperature and is matched with different dehumidification requirements. The first output capacity, the second output capacity and the third output capacity of the embodiment are respectively 25%, 50% and 100%, and when the Δ t3 is less than or equal to Δ t, the first compressor operates at full load, so that the unit performs rapid dehumidification. In other embodiments the output capacity may use a different output capacity gradient.
Presetting a reference dew point temperature;
comparing the instant dew point temperature in the room to be conditioned with the reference dew point temperature, if the former is greater than the latter, collecting the dry bulb temperature of the air to be treated by the first condenser, and controlling the opening degree of a port of the refrigerant proportion regulating valve, which is connected with the first condenser, so that the dry bulb temperature of the air treated by the first condenser is kept to be greater than or equal to the instant dew point temperature in the room to be conditioned; if the former is less than the latter, the maximum supply dry bulb temperature is determined by the dew point temperature required by the conditioned space, and the specific determination method is well known to those skilled in the art, and the air handling equipment in the air supply system is controlled to make the dry bulb temperature of the air supplied to the conditioned space less than or equal to the maximum supply dry bulb temperature.
In this embodiment, after reaching the dew point temperature required by the conditioned space, the positive pressure maintaining mode is started: collecting the dry bulb temperature of air at the outlet of a moisture absorption area of the rotating wheel and the instant dry bulb temperature of the air in a regulated space; if the dry bulb temperature of the air at the outlet of the rotating wheel moisture absorption area is 2 ℃ or more higher than the instant dry bulb temperature of the air in the regulated space, the flow rate of the chilled water in the third surface cooler is increased to cool the air at the outlet of the rotating wheel moisture absorption area; and if the dry bulb temperature of the air at the outlet of the rotating wheel moisture absorption area is lower than the instant dry bulb temperature of the air in the adjusted space by 2 ℃ or more, increasing the opening degree of a port of the refrigerant proportion adjusting valve connected with the first condenser to heat the air at the outlet of the rotating wheel moisture absorption area. In other embodiments, the dry bulb temperature of the air at the outlet of the rotary wheel moisture absorption area is determined to be a few degrees greater than the instant dry bulb temperature of the air in the conditioned space according to local climate conditions and ambient air parameters, so that the flow of the chilled water and the adjustment of the refrigerant proportion adjusting valve are carried out, and the condition of 2 ℃ is not a limiting condition.
Preferred embodiments of this embodiment are shown in FIGS. 5-7:
s1: presetting Δ t1, Δ t2, Δ t3 and reference dew point temperature; s2: receiving a dew point temperature of a demand of a conditioned space; s3: collecting the instant dew point temperature in the regulated space; s4: comparing whether the dew point temperature required by the regulated space is equal to the instant dew point temperature or not; if not, go to S5; if not, go to S6; s5: dehumidifying; s6: the maintenance positive pressure mode is initiated.
As shown in fig. 6, the S5 is specifically divided into S51 and S52, S51 is used for realizing rapid dehumidification, S52 is used for ensuring that the air supply outlet does not frost during dehumidification, and S51 and S52 are performed synchronously.
Wherein, S51: calculating the difference delta t between the instant dew point temperature and the required dew point temperature; s511: judging whether the delta t is smaller than the delta t 1; if yes, go to S512; if not, go to S513; s512: stopping the first compressor; s513: judging whether the delta t is smaller than the delta t 2; if yes, go to S514; if not, go to S515; s514: adjusting the first compressor to operate at a first output capacity; s515: judging whether the delta t is smaller than the delta t 3; if yes, go to S516; if not, executing S517; s516: adjusting the first compressor to operate at a second output capacity; s517: the first compressor is regulated to operate at a third output capacity.
S52: judging whether the instant dew point temperature in the regulated room is greater than the reference dew point temperature; if yes, the process is carried out by the paths of S521 and S522; if not, the process is carried out by paths of 525, S526 and S527; s521: collecting the dry bulb temperature of air to be treated by a first condenser; s522: judging whether the dry bulb temperature of the air treated by the first condenser is greater than or equal to the instant dew point temperature in the room to be conditioned; if yes, go to S523; if not, go to S524; s523: reducing the opening degree of a port of the refrigerant proportion regulating valve, which is connected with the first condenser; s524: the opening degree of a port of the refrigerant proportion regulating valve, which is connected with the first condenser, is increased; s525: determining the maximum air supply dry bulb temperature; s526: collecting the dry bulb temperature of the air supply pipeline behind the first condenser; if not, go to S528; if yes, S529 is carried out; s528: the output cold quantity of the air treatment equipment is reduced; s529: the output cold quantity of the air treatment equipment is improved.
As shown in fig. 7, the S6 specifically includes:
s61: collecting the dry bulb temperature of the air at the outlet of the moisture absorption area of the rotating wheel and the instant dry bulb temperature of the air in the regulated space; s62: judging whether the dry bulb temperature of the air at the outlet of the moisture absorption area of the rotating wheel is higher than the instant dry bulb temperature of the air in the regulated space or not; if yes, go to S63; if not, go to S64; s63: increasing the flow of chilled water in a third surface cooler; s64: the opening degree of the opening of the refrigerant proportion adjusting valve connected with the first condenser is increased. The air supply amount and the air return amount are balanced in the process, the pressure state of the regulated space is stabilized, the air supply density is indirectly controlled by using the refrigerant proportion regulating valve 45, the amount of the high-temperature refrigerant flowing into the first condenser 43 is controlled by regulating the opening degree of the opening of the refrigerant proportion regulating valve 45 connected with the first condenser 43, the heating amount is regulated, and the residual high-temperature refrigerant flows into the storage condenser 46 to release heat. In other embodiments, the mode of maintaining positive pressure may not be enabled, and a common means of supplementing fresh air may be used instead.
It should be understood that the above-mentioned embodiments of the present invention are only examples for clearly illustrating the technical solutions of the present invention, and are not intended to limit the specific embodiments of the present invention. Any modification, equivalent replacement, and improvement made within the spirit and principle of the present invention claims should be included in the protection scope of the present invention claims.
Claims (9)
1. A rotary wheel dehumidification unit comprises an air supply system, a rotary wheel and a regeneration air system, wherein air treatment equipment is arranged in the air supply system and the regeneration air system; the rotating wheel is arranged between the air supply system and the regeneration air system and is used for exchanging air moisture of the air supply system and the regeneration air system; the rotating wheel comprises a moisture absorption area and a regeneration area;
it is characterized in that the preparation method is characterized in that,
the system comprises an air supply system, an air compressor, a condenser and an expansion valve, wherein the air supply system is arranged in the air supply system and comprises a first evaporator, a first compressor, a first condenser and a first expansion valve which are sequentially connected through pipelines to form circulation;
the air supply direct expansion system also comprises a refrigerant proportion regulating valve and a reserve condenser, the first compressor is connected with the first expansion valve through two ports of the refrigerant proportion regulating valve, the other port of the refrigerant proportion regulating valve is connected with an outlet of the reserve condenser through a pipeline, and an inlet of the reserve condenser is connected with an outlet of the first compressor through a pipeline;
the first evaporator is arranged in front of the moisture absorption area of the rotating wheel and used for adjusting the temperature of air before dehumidification;
the first condenser is arranged behind the moisture absorption area of the rotating wheel and is used for adjusting the temperature of the dehumidified air;
the first compressor is configured to: when the delta t is less than the delta t1, stopping the operation; when the delta t1 is more than or equal to the delta t < delta t2, the operation is carried out with the first output capacity; when the delta t2 is more than or equal to the delta t < delta t3, the operation is carried out by a second output capacity; when the delta t3 is less than or equal to delta t, the operation is carried out by a third output capacity; wherein, the delta t1, the delta t2 and the delta t3 are preset adjusting standards, and the delta t1 is more than the delta t2 is more than the delta t3 at the temperature of 2 ℃; the first output capacity is less than the second output capacity and less than the third output capacity;
the refrigerant proportion regulating valve is set as follows: when the instant dew point temperature in the room to be conditioned is higher than the preset reference dew point temperature, adjusting the opening degree of a port connected with the first condenser so as to keep the dry bulb temperature of the air treated by the first condenser to be higher than or equal to the instant dew point temperature in the room to be conditioned;
the air treatment device is provided with: when the instant dew point temperature in the room to be conditioned is less than the preset reference dew point temperature, the dry bulb temperature of the air sent into the conditioned space is less than or equal to the maximum air supply dry bulb temperature.
2. The rotary dehumidifier assembly of claim 1,
the first evaporator is arranged adjacent to the moisture absorption area of the rotating wheel and used for enabling air to enter the moisture absorption area of the rotating wheel after being processed by the first evaporator.
3. The rotary dehumidifier assembly of claim 1,
the first condenser is arranged at the tail end of the air supply system and is used for carrying out final temperature adjustment operation before air is sent out.
4. The rotary dehumidifier assembly of claim 1,
the air equipment arranged in the air supply system comprises an air feeder and at least three surface coolers;
the blower is used for driving air in the air supply system to flow to the regulated space along the pipeline;
the at least three surface coolers are distributed in the extending direction of the pipeline of the air supply system and used for adjusting the temperature of air in different pipe sections of the air supply system.
5. The rotary dehumidifier assembly of claim 1,
the device also comprises a regenerative wind direct-expansion system; the regeneration air direct expansion system is arranged in the regeneration air system and comprises a second evaporator, a second compressor, a second condenser and a second expansion valve which are sequentially connected through pipelines to form circulation;
the second evaporator and the second condenser are used for adjusting the temperature of the regenerated air, and the regenerated air firstly passes through the second evaporator and then passes through the second condenser.
6. The rotary dehumidifier assembly of claim 1,
the device also comprises a filter;
the filter is arranged at the head end of the air supply system pipeline, and/or at the tail end of the air supply system pipeline, and/or at the head end of the regeneration air system pipeline.
7. A control method is applied to the rotary wheel dehumidification unit as claimed in any one of claims 1 to 6, and is characterized by comprising the following steps of:
presetting adjustment standards delta t1, delta t2 and delta t3, wherein delta t1 and delta t2 are more than delta t3 at 2 ℃;
receiving a dew point temperature of a demand of a conditioned space;
acquiring the instant dew point temperature in the regulated space, calculating the difference delta t between the instant dew point temperature and the required dew point temperature, and regulating the output capacity of the first compressor according to the delta t: if the delta t is less than the delta t1, stopping the first compressor to enable the output capacity of the first compressor to be zero, and controlling air processing equipment in the air supply system to keep the instant dew point temperature of the adjusted space; if the delta t is more than or equal to delta t1 and less than the delta t2, the first compressor is adjusted to operate at the first output capacity; if the delta t is more than or equal to delta t2 and less than the delta t3, the first compressor is adjusted to operate at a second output capacity; if the delta t3 is less than or equal to the delta t, adjusting the first compressor to operate at a third output capacity; wherein the first output capacity is less than the second output capacity and less than the third output capacity;
presetting a reference dew point temperature;
comparing the instant dew point temperature in the room to be conditioned with the reference dew point temperature, if the former is greater than the latter, collecting the dry bulb temperature of the air to be treated by the first condenser, and controlling the opening degree of a port of the refrigerant proportion regulating valve, which is connected with the first condenser, so that the dry bulb temperature of the air treated by the first condenser is kept to be greater than or equal to the instant dew point temperature in the room to be conditioned; if the former is less than the latter, the maximum air supply dry bulb temperature is determined by the dew point temperature required by the regulated space, and the air processing equipment in the air supply system is controlled to ensure that the dry bulb temperature of the air sent into the regulated space is less than or equal to the maximum air supply dry bulb temperature.
8. A control method according to claim 7,
the air supply system of the rotary wheel dehumidification unit is provided with air equipment comprising an air feeder and at least three surface coolers;
the blower is used for driving air in the air supply system to flow to the regulated space along the pipeline;
the at least three surface coolers are distributed in the extending direction of the pipeline of the air supply system and are used for adjusting the temperature of air in different pipe sections of the air supply system;
if Δ t < Δ t1 further includes: controlling the flow of chilled water in a surface cooler in an air supply system to maintain the instant dew point temperature in the regulated space;
comparing the instantaneous dew point temperature in the conditioned room with the reference dew point temperature, and if the former is less than the latter, further comprising: the flow of the chilled water in the surface cooler in the air supply system is controlled so that the temperature of the air sent into the conditioned space is less than or equal to the maximum air supply dry bulb temperature.
9. A control method according to claim 8,
when the delta t is less than 2 ℃, performing a positive pressure maintaining mode; the positive pressure maintaining mode specifically comprises the following steps:
collecting the dry bulb temperature of air at the outlet of a moisture absorption area of the rotating wheel and the instant dry bulb temperature of the air in a regulated space;
if the dry bulb temperature of the air at the outlet of the rotating wheel moisture absorption area is 2 ℃ or more higher than the instant dry bulb temperature of the air in the regulated space, the flow rate of the chilled water in the third surface cooler is increased to cool the air at the outlet of the rotating wheel moisture absorption area; and if the dry bulb temperature of the air at the outlet of the rotating wheel moisture absorption area is lower than the instant dry bulb temperature of the air in the adjusted space by 2 ℃ or more, increasing the opening degree of a port of the refrigerant proportion adjusting valve connected with the first condenser to heat the air at the outlet of the rotating wheel moisture absorption area.
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| CN113932448A (en) * | 2021-11-22 | 2022-01-14 | 广州奥斯德科技有限公司 | Energy coupling recovery type low dew point high temperature unit |
| CN114777226A (en) * | 2022-04-29 | 2022-07-22 | 广东申菱环境系统股份有限公司 | Dehumidifying unit capable of realizing constant temperature and constant humidity and control method thereof |
| CN115875815B (en) * | 2022-11-18 | 2024-06-28 | 珠海格力电器股份有限公司 | Control method and device of rotary dehumidifier, rotary dehumidifier and storage medium |
| CN116795152A (en) * | 2023-05-29 | 2023-09-22 | 深圳市华图测控系统有限公司 | Constant humidity control method and system applied to cultural relic storage cabinet showcase |
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| CN110513784A (en) * | 2019-09-17 | 2019-11-29 | 江苏塔菲尔新能源科技股份有限公司 | A kind of Double-working-condition rotary dehumidifier |
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