CN113339901A - Control system and method for adjusting indoor air temperature and humidity in humid area - Google Patents
Control system and method for adjusting indoor air temperature and humidity in humid area Download PDFInfo
- Publication number
- CN113339901A CN113339901A CN202110527715.2A CN202110527715A CN113339901A CN 113339901 A CN113339901 A CN 113339901A CN 202110527715 A CN202110527715 A CN 202110527715A CN 113339901 A CN113339901 A CN 113339901A
- Authority
- CN
- China
- Prior art keywords
- air
- heat
- humidity
- exchanger
- fresh air
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- 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
- F24F3/147—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 with both heat and humidity transfer between supplied and exhausted air
-
- 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
- F24F11/65—Electronic processing for selecting an operating mode
-
- 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
- F24F11/72—Control systems characterised by their outputs; Constructional details thereof for controlling the supply of treated air, e.g. its pressure
-
- 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
-
- 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]
- Y02B30/54—Free-cooling systems
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Signal Processing (AREA)
- Physics & Mathematics (AREA)
- Fuzzy Systems (AREA)
- Mathematical Physics (AREA)
- Central Air Conditioning (AREA)
Abstract
According to the control system for adjusting the temperature and humidity of the indoor air in the humid area, provided by the invention, outdoor fresh air is dehumidified by the solution dehumidifying device to form dry fresh air, the dry fresh air enters the heat and humidity exchange loop in the control system to perform heat and humidity exchange with high-temperature cold source water at the temperature of 12-18 ℃, and the high-temperature cold source water is cooled to the temperature of 10-13 ℃ and is used as regulation spray water in the heat and humidity regulation exchanger; the indoor return air is extracted from the room and is dehumidified by the solution dehumidifying device to be dry return air; the dry return air is subjected to heat-moisture exchange with the regulation spray water in the heat-moisture regulation exchanger, the temperature of the dry return air is regulated to 10-18 ℃ of the wet bulb temperature of dry air at the air inlet side of the heat-moisture regulation exchanger, the humidity of the dry return air reaches 40-60%, and when the indoor air supply requirement is met, the dry return air is supplied to the indoor through the air outlet of the heat-moisture regulation exchanger; the invention provides a control method applying the control system. The control system and the control method provided by the invention overcome the technical defects that the dry-wet bulb temperature of air in a high-humidity area is very close, the evaporative cooling efficiency is extremely low, and the energy consumption is high in the prior art.
Description
Technical Field
The invention belongs to the field of air index control, and particularly relates to a control system and a control method for adjusting the temperature and humidity of indoor air in a humid area.
Background
In reality, an air conditioning system is often adopted for air temperature and humidity adjustment, but the air conditioning system has the following problems: 1. the compressor is required to continuously generate compression work to promote evaporative cooling, and the energy consumption is overlarge; 2. in a dry area, the air in the area is dry, the moisture content is low, and the water can be directly evaporated and cooled to obtain lower water temperature for regulating the indoor temperature and humidity; however, in wet and humid areas, the dry-wet bulb temperature of air is very close, so that the evaporative cooling efficiency is extremely low, and the energy consumption is large; 3. sensible heat and latent heat ratio of air treatment are difficult to match with changes of indoor heat-humidity ratio, air is cooled and dehumidified in a condensation mode, the absorbed sensible heat and latent heat ratio can only change within a certain range, the actual heat-humidity ratio of a building is large in change, when the requirements of temperature and humidity cannot be met simultaneously, the control of humidity is generally sacrificed, the indoor relative humidity is too high or too low, the too high result is uncomfortable, the temperature needs to be reduced to improve the comfort level, the energy consumption is increased, and the too low humidity can cause the increase of indoor and outdoor enthalpy difference to increase the energy consumption of fresh air treatment; 4. the moist surfaces resulting from condensation and dehumidification are the best locations for indoor mold growth, and growth and mold propagation in air conditioning systems is a major cause of possible health problems for air conditioners.
The evaporative cooling device is a novel system capable of adjusting the temperature and the humidity of air by using a high-temperature cold source, and the air is cooled by using the heat and mass exchange principle of unsaturated air and water, so that the temperature of the air can reach lower temperature without consuming compression work. Has the advantages that: 1. the initial investment cost is low, which is about half of the traditional compression refrigeration, and the cost recovery period is greatly shortened; 2. the power consumption is low, the power required by the evaporative cooling system mainly comprises a fan and a water pump, a refrigeration compressor is not provided, the energy efficiency ratio COP value is higher, and the electricity is saved by about 80%; 3. the air conditioner runs in full air, has air filtering (cleaning) and humidifying functions, can continuously input fresh air, ensures that indoor harmful gas is discharged outdoors by positive pressure conveying, and does not generate air pollution caused by mildew indoors due to a cold water system; 4, the environment is protected, the pollution is zero, the evaporative cooling device takes water and air as media, and the evaporative cooling device does not contain Freon and has no pollution to the atmosphere; 5. the maintenance is simple and the maintenance cost is low. However, in the prior art, the problems of large humidity of an air conditioning area, limited temperature drop, low application efficiency of a region with large humidity and even inapplicability exist in practical application, and the like, so that the evaporative cooling device is generally only suitable for low-humidity regions and medium-humidity regions (Harbin-Taiyuan-Baoji-West Chang-Kunming West region).
In summary, a control system and a method suitable for indoor air temperature and humidity regulation in a humid area, low dehumidification temperature rise, no low-temperature cold source and no compressor work are urgently needed to be developed.
Disclosure of Invention
In view of the above-mentioned disadvantages of the prior art, the present invention provides a control system for adjusting the temperature and humidity of the indoor air in a humid area to overcome the technical defects of the prior art that the dry-wet bulb temperature of the air in a high-humidity area is very close, the efficiency of evaporative cooling is extremely low, and the energy consumption is large;
the invention also aims to provide a control method suitable for regulating the temperature and the humidity of the indoor air in the humid area;
in order to achieve the above and other related purposes, the invention provides a control system for regulating the temperature and humidity of indoor air in a humid area, outdoor fresh air is dehumidified by a solution dehumidifying device into dry fresh air, the dry fresh air enters a heat and humidity exchange loop in the control system to perform heat and humidity exchange with high-temperature cold source water at the temperature of 12-18 ℃, and the high-temperature cold source water is cooled to 10-13 ℃ and is used as regulating spray water in a heat and humidity regulating and controlling exchanger; the indoor return air is extracted from the room and is dehumidified by the solution dehumidifying device to be dry return air; and the dry return air is subjected to heat-moisture exchange with the regulation spray water in the heat-moisture regulation exchanger 8, the temperature of the dry return air is regulated to 10-18 ℃ of the wet bulb temperature of dry air at the air inlet side of the heat-moisture regulation exchanger, the humidity of the dry return air reaches 40-60%, and when the requirement of indoor air supply is met, the dry return air is supplied to the indoor air through the air outlet of the heat-moisture regulation exchanger.
Preferably, the heat and moisture exchange circuit comprises an indirect heat and moisture exchanger for performing equal-humidity cooling on the dry fresh air and a direct heat and moisture exchanger for performing direct evaporative cooling on high-temperature cold source water by using the equal-humidity cooled dry fresh air to manufacture cooling water.
Preferably, the dry fresh air enters the indirect heat and humidity exchanger and is cooled by high-temperature cold source water and the like to form primary indirect evaporative cooling fresh air, the primary indirect evaporative cooling fresh air enters the direct heat and humidity exchanger to directly evaporate and absorb heat of indirect cold drainage discharged from the indirect heat and humidity exchanger to form a saturated primary exhaust air discharge heat and humidity exchange loop; the cooled indirect cooling drainage becomes cooling water for use by a heat and humidity regulation exchanger; the primary indirect evaporative cooling fresh air and the dry return air enter the mixing chamber to be mixed into fresh return air, then enter the heat and humidity regulation and control exchanger to carry out heat and humidity exchange with cooling water used for regulating and controlling spray water, and after the requirement of indoor air supply is met, air is supplied to the indoor space through the air outlet of the heat and humidity regulation and control exchanger.
Preferably, there are two direct heat and moisture exchangers, the first direct heat and moisture exchanger and the second direct heat and moisture exchanger are connected in series, and the serial connection position is arranged on the serial circulation pump 9 b; the dry fresh air is divided into two paths: treat to mix the new trend and treat the evaporative cooling new trend, treat the evaporative cooling new trend and shunt again into two tunnel: the primary fresh air to be evaporated and the secondary fresh air to be evaporated respectively enter the heat-moisture exchange loop; wherein, the primary fresh air to be evaporated enters the indirect heat-moisture exchanger and is cooled by the circulating high-temperature cold source water in an equal humidity manner to become primary indirect evaporation cooling fresh air; high-temperature cold source water enters a primary direct heat-moisture exchanger to be directly evaporated and cooled by the secondary fresh air to be evaporated, and then enters a secondary direct heat-moisture exchanger to be directly evaporated and cooled again by the primary indirect evaporative cooling fresh air to form cooling water; the secondary fresh air to be evaporated is directly evaporated and absorbed to become saturated secondary exhaust air which is discharged out of the heat-moisture exchange loop; the primary indirect evaporative cooling fresh air is directly evaporated and absorbed to become saturated primary exhaust air which is discharged out of the heat-moisture exchange loop; cooling water is divided into circulating high-temperature cold source water and regulation spray water which respectively enter the indirect heat-humidity exchanger and the heat-humidity regulation exchanger; pipelines for conveying fresh air to be mixed, fresh air to be evaporated and cooled, primary fresh air to be evaporated and secondary fresh air to be evaporated are respectively provided with a fresh air valve to be mixed, a fresh air valve to be evaporated and cooled, a primary fresh air valve to be evaporated and a secondary fresh air valve to be evaporated; the dry return air and the fresh air to be mixed enter the mixing chamber to be mixed into fresh return air, the fresh return air enters the heat and humidity regulation and control exchanger to carry out heat and humidity exchange with the regulation and control spray water, and after the requirements of indoor air supply are met, the air is supplied to the indoor through the air outlet of the heat and humidity regulation and control exchanger; and a new mixed air return valve is arranged on the pipeline for conveying new mixed air.
Preferably, the solution dehumidifying device comprises a cross-flow plate type heat exchanger, an upper return air outlet cavity, an upper fresh air outlet cavity, a lower return air inlet cavity, a lower fresh air inlet cavity, a dehumidifying spray pipe and a louver liquid baffle plate, wherein the cross-flow plate type heat exchanger is arranged in the solution dehumidifying device and isolates the air channel of the solution dehumidifying device; the cross flow plate type heat exchanger is a cube; the outdoor fresh air and the indoor return air respectively enter the lower fresh air inlet cavity and the lower return air inlet cavity after being subjected to cross wall type mutual heat exchange through respective independent channels arranged in the solution dehumidifying device; the bottoms of the lower fresh air inlet cavity and the lower return air inlet cavity are arc-shaped to form an arc-shaped air channel; and the dehumidifying agent falling into a liquid collecting tank at the bottom of the solution dehumidifying device is used as dehumidifying backwater and is pumped into the dehumidifying spray pipe from the dehumidifying circulating pipe through the dehumidifying circulating pump to circularly dehumidify the gas in the air duct.
Preferably, the dehumidified backwater flows through the gas-liquid heat exchanger through the regenerated water supply pipe, enters the regenerator, is heated and concentrated, then flows back to the gas-liquid heat exchanger to perform non-contact heat exchange with primary exhaust air, and finally flows back to a liquid collecting tank at the bottom of the solution dehumidifying device; the regeneration water supply pipe is provided with a regeneration circulating pump.
Preferably, outdoor fresh air and the indoor return air firstly enter the air-air heat exchanger to perform mutual non-contact heat exchange and then respectively enter the solution dehumidifying device, and a return air inlet valve is arranged at the indoor return air inlet of the air-air heat exchanger; the indoor return air is also exhausted to the outside atmosphere through an outside exhaust pipe; and the external exhaust pipe is provided with an external exhaust air valve.
Preferably, circulating cold water discharged from a water outlet of the heat and humidity regulation exchanger or/and the indirect heat and humidity exchanger is collected and enters a high-temperature cold water pipe through a circulating cold water pipe, and then enters the control system as high-temperature cold water; the high-temperature cold water pipe is also connected with a water supplementing pipe, and a water supplementing control valve is arranged on the water supplementing pipe; a circulating cold water circulating pump is arranged on the circulating cold water pipe; a spraying regulation control valve is arranged on the pipeline for conveying the regulation spray water; the pipeline for discharging the cooling water is provided with a cooling water circulating pump.
Preferably, the gas-liquid heat exchanger is a coil pipe surface type heat exchanger or a surface type heat exchanger with fins; the gas-gas heat exchanger is a dividing wall plate type heat exchanger; the indirect heat and moisture exchanger is an indirect evaporative cooler; the direct heat and moisture exchanger is a direct evaporative cooler; the heat and humidity regulation and control exchanger is an indirect evaporative cooler or a direct evaporative cooler.
A control method applying the control system,
a. opening a return air inlet air valve, a fresh air valve to be steamed and cooled, a fresh air return mixing air valve, a primary fresh air valve to be steamed and a secondary fresh air valve to be steamed, and closing an external air exhaust air valve and a fresh air valve to be mixed; opening all circulating pumps, opening a spraying regulation control valve, and closing a water replenishing control valve; only indoor return air enters the control system, and the control system enters a full return air circulation mode:
b. opening an external air exhaust air valve, a fresh air valve to be mixed, a fresh air mixing air valve, a fresh air return mixing air valve, a secondary fresh air valve to be steamed and a primary fresh air valve to be steamed, and closing a return air inlet air valve; opening all circulating pumps, opening a spraying regulation control valve, and closing a water replenishing control valve; only outdoor fresh air enters the control system, and the control system enters a full fresh air circulation mode;
c. opening all air valves, all circulating pumps and the spraying regulation control valve; closing the water replenishing control valve; and adjusting the opening degrees of a return air inlet air valve and a fresh air valve to be mixed, allowing outdoor fresh air and indoor return air to enter the control system simultaneously, and allowing the control system to enter a fresh air and return air mixed circulation mode.
d. Closing an external exhaust valve and a fresh air valve to be mixed, and opening other air valves; closing all the control valves, opening all the circulating pumps, independently dehumidifying indoor return air by the control system, and entering an independent dehumidification mode by the control system;
and when the water content in the control system is lower than a threshold value, opening a water supplementing control valve to supplement water to the control system.
The control system and the method for adjusting the temperature and the humidity of the indoor air in the humid area have the following beneficial effects:
1) the traditional evaporative cooling air conditioner is mainly suitable for dry areas, the air in the dry areas is dry, the moisture content is low, and the lower water temperature can be obtained by direct evaporative cooling; however, in wet areas, the efficiency of the evaporative cooling air conditioner is extremely low due to the fact that the dry-wet bulb temperature of air is very close, and the control system can be used for well solving the problem.
2) The control system does not need to provide compression work, and is energy-saving and environment-friendly;
3) the control system is provided with a plurality of energy recovery loops, so that the energy-saving efficiency is further improved;
4) the control system can realize free switching of the mode in all the conditions, and meet the requirements of different working conditions;
5) in the prior art, dehumidification is usually carried out by using a solid adsorbent for adsorption and dew point temperature dehumidification, but the adsorbent is solid and cannot flow in a pipeline, so that extra power with more weight is required in the operation process, a great blocking effect on the flow of air is achieved, and meanwhile, the temperature rise caused in the solid dehumidification process is great, and the extra load of an adjusting system is increased; dew point dehumidification needs low temperature cold source cooling air, and to the constant temperature difference air supply system, the air after the dehumidification still need reheat to air supply state point, has increased governing system's energy consumption, and adopts the dehumidification liquid dehumidification in this case, can effectively restrain the temperature rise of dehumidification in-process, need not low temperature cold source cooling air, practiced thrift system energy consumption.
Drawings
FIG. 1 is a schematic view of a control system according to embodiment 1 of the present invention;
FIG. 2 is a schematic diagram of a control system according to embodiment 2 of the present invention
FIG. 3 is a schematic view of a solution dehumidification apparatus according to the present invention;
FIG. 4 is a block diagram of a solution dehumidifier according to the present invention;
fig. 5 is a diagram of the air handling state of the control system in the full return air circulation mode according to embodiment 3 of the present invention;
FIG. 6 is a diagram of the air treatment status of the control system in the fresh air circulation mode according to embodiment 3 of the present invention;
fig. 7 is an air handling state diagram of the control system in a fresh air and return air mixed circulation mode according to embodiment 3 of the present invention;
fig. 8 is a diagram illustrating an air handling state during a dehumidification process of a solution dehumidification device in a control system according to embodiment 3 of the present invention;
wherein: 1-a regenerator; 2-gas-liquid heat exchanger; 3-a gas-gas heat exchanger; 4-a mixing chamber; 5-solution dehumidification device; 501-cross flow plate heat exchanger; 502-upper return air outlet cavity; 503-installing a fresh air outlet cavity; 504-lower return air inlet chamber; 505-lower fresh air inlet cavity; 506-a dehumidifying spray pipe; 507-louver liquid baffle plates; 508-fresh air inlet channel; 509-return air inlet channel; 6-an indirect heat and moisture exchanger; 7-direct heat and moisture exchanger; 701-primary direct heat and moisture exchanger; 702-a secondary direct heat and moisture exchanger; 8-a thermo-hygrothermal regulation exchanger; 9 a-a dehumidification circulation pump; 9 b-series circulation pump; 9 c-regeneration of the circulation pump; 9 d-circulating cold water circulating pump; 9 e-cooling water circulation pump; 10 a-a fresh air valve to be mixed; 10 b-a fresh air valve to be steamed and cooled; 10 c-a primary fresh air valve to be steamed; 10 d-a secondary fresh air valve to be steamed; 10 e-new return air mixing air valve; 10 f-a return air inlet valve; 10 g-external air exhaust air valve; 11 a-a water replenishing control valve; 11 b-a spray regulating control valve; 12-primary indirect evaporative cooling of fresh air; 13-primary air exhaust; 14-secondary air exhaust; 15-indoor air return; 16-outdoor fresh air; 17-an exhaust fan; 18-high temperature cold source water; 19-cooling water; 20-circulating cold water; and 21-circulating high-temperature cold source water.
Detailed Description
The following description of the embodiments of the present invention is provided for illustrative purposes, and other advantages and effects of the present invention will become apparent to those skilled in the art from the present disclosure.
Referring to fig. 1 to 8, the structures, the ratios, the sizes, and the like shown in the drawings attached to the present specification are only used for matching with the disclosure of the specification, so as to be understood and read by those skilled in the art, and are not used to limit the conditions under which the present invention can be implemented, so that the present invention has no technical essence, and any structural modification, ratio relationship change, or size adjustment should still fall within the scope of the present invention without affecting the efficacy and the achievable purpose of the present invention. In addition, the terms such as "top", "bottom", "upper", "lower", "inner" and "outer" used in the present specification are for clarity of description, and are not intended to limit the scope of the present invention, and changes or modifications of the relative relationship may be made without substantial technical changes.
Example 1:
as shown in figure 1, the invention provides a control system for regulating the temperature and humidity of indoor air in a humid area, outdoor fresh air 16 is dehumidified by a solution dehumidifier 5 into dry fresh air, the dry fresh air enters a heat and humidity exchange loop in the control system to carry out heat and humidity exchange with high-temperature cold source water 18 at the temperature of 12-18 ℃, and the high-temperature cold source water 18 is cooled to the temperature of 10-13 ℃ and is used as regulation spray water in a heat and humidity regulation exchanger 8; the indoor return air 15 is extracted from the room and dehumidified by the solution dehumidifying device 5 to become dry return air; and the dry return air is subjected to heat-moisture exchange with the regulated spray water in the heat-moisture regulation exchanger 8, the temperature of the dry return air is regulated to 10-18 ℃ of the wet bulb temperature of dry air at the air inlet side of the heat-moisture regulation exchanger 8, the humidity of the dry return air reaches 40-60%, and when the requirement of indoor air supply is met, the dry return air is supplied to the indoor air through the air outlet of the heat-moisture regulation exchanger.
The heat and humidity exchange loop comprises an indirect heat and humidity exchanger 6 for carrying out equal humidity cooling on the dry fresh air and a direct heat and humidity exchanger 7 for utilizing the equal humidity cooled dry fresh air to carry out direct evaporative cooling on high temperature cold source water 18 to manufacture cooling water 19, wherein the dry fresh air enters the indirect heat and humidity exchanger 6 and is subjected to equal humidity cooling by the high temperature cold source water 18 to become primary indirect evaporative cooling fresh air 12 which enters the direct heat and humidity exchanger 7 to carry out direct evaporative heat absorption on indirect cold exhaust water discharged from the indirect heat and humidity exchanger 6 to become saturated primary exhaust air 13 which is discharged out of the heat and humidity exchange loop; the cooled indirect cooling drainage becomes cooling water 19 for use by the heat and humidity regulation and control exchanger 8; the primary indirect evaporative cooling fresh air 12 and the dry return air enter the mixing chamber 4 to be mixed into new return mixed air, then enter the heat and humidity regulation and control exchanger 8 to perform heat and humidity exchange with cooling water 19 used as regulation and control spray water, and when the requirement of indoor air supply is met, the air is supplied to the indoor through an air outlet of the heat and humidity regulation and control exchanger.
As shown in fig. 3 and 4, the solution dehumidifying device 5 includes a cross-flow plate heat exchanger 501, an upper return air outlet cavity 502, an upper fresh air outlet cavity 503, a lower return air inlet cavity 504, a lower fresh air inlet cavity 505, a dehumidifying spray pipe 506 and a louver liquid baffle 507, wherein the cross-flow plate heat exchanger 501 is erected in the solution dehumidifying device 5 to isolate the air duct of the solution dehumidifying device from the air duct; the cross flow plate type heat exchanger 501 is a cube; the outdoor fresh air 16 and the indoor return air 15 exchange heat with each other in a cross-dividing wall type through respective independent channels (a fresh air inlet channel 508 and a return air inlet channel 509) arranged in the solution dehumidifying device 5, and then respectively enter the lower fresh air inlet cavity 505 and the lower return air inlet cavity 504; the bottom of the lower fresh air inlet cavity 505 and the bottom of the lower return air inlet cavity are arc-shaped to form an arc-shaped air channel; the dehumidifying agent falling into the liquid collecting tank at the bottom of the solution dehumidifying device is used as dehumidifying backwater and is pumped into the dehumidifying spray pipe 506 from the dehumidifying circulating pipe through the dehumidifying circulating pump 9a to circularly dehumidify the gas in the air duct.
The dehumidification return water also flows through the gas-liquid heat exchanger 2 through a regeneration water supply pipe, enters the regenerator 1, is heated and concentrated, then flows back to the gas-liquid heat exchanger 2 to perform non-contact heat exchange with the primary exhaust 13, and finally flows back to a liquid collecting tank at the bottom of the solution dehumidification device; the regeneration water supply pipe is provided with a regeneration circulating pump 9 c.
Outdoor fresh air 16 and the indoor return air 15 firstly enter the air-air heat exchanger 3 to perform mutual non-contact heat exchange and then respectively enter the solution dehumidifying device 5, and a return air inlet valve 10f is arranged at the indoor return air inlet of the air-air heat exchanger 3; the indoor return air 15 is also exhausted to the outside atmosphere through an outside exhaust pipe; and the external exhaust pipe is provided with an external exhaust air valve.
Circulating cold water 20 which is discharged from a water outlet of the heat and humidity control exchanger and collected into a high-temperature cold water pipe enters a control system as high-temperature cold water after entering the high-temperature cold water pipe through a circulating cold water pipe; the high-temperature cold water pipe is also connected with a water supplementing pipe, and a water supplementing control valve 11a is arranged on the water supplementing pipe; a circulating cold water circulating pump 9d is arranged on the circulating cold water pipe; a spraying regulation control valve 11b is arranged on the pipeline for conveying the regulation and control spraying water; a cooling water circulation pump 9e is provided on the pipe for discharging the cooling water 19.
The gas-liquid heat exchanger 2 is a coil pipe surface type heat exchanger or a surface type heat exchanger with fins; the gas-gas heat exchanger 3 is a dividing wall plate type heat exchanger; the indirect heat and moisture exchanger 6 is an indirect evaporative cooler; the direct heat and moisture exchanger 7 is a direct evaporative cooler; the heat and humidity control exchanger 8 is an indirect evaporative cooler or a direct evaporative cooler.
Example 2:
the heat and moisture exchange loop of embodiment 1 is adjusted, and the number of the direct heat and moisture exchangers is increased to two, as shown in fig. 2, a primary direct heat and moisture exchanger 701 and a secondary direct heat and moisture exchanger 702 are connected in series, and the series connection position is arranged on the series circulating pump 9 b; the dry fresh air is divided into two paths: treat to mix the new trend and treat the evaporative cooling new trend, treat the evaporative cooling new trend and shunt again into two tunnel: the primary fresh air to be evaporated and the secondary fresh air to be evaporated respectively enter the heat-moisture exchange loop; wherein, the primary fresh air to be evaporated enters the indirect heat and humidity exchanger 6 and becomes primary indirect evaporative cooling fresh air 12 after being cooled by humidity such as circulating high-temperature cold source water 21 and the like; the high-temperature cold source water 18 enters the primary direct heat-moisture exchanger 701 to be directly evaporated and cooled by the secondary fresh air to be evaporated, and then enters the secondary direct heat-moisture exchanger 702 to be directly evaporated and cooled again by the primary indirect evaporative cooling fresh air 12 to form cooling water 19; the secondary fresh air to be evaporated is directly evaporated to absorb heat to become saturated secondary exhaust air 14 which is discharged out of the heat and humidity exchange loop; the primary indirect evaporative cooling fresh air 12 is directly evaporated and absorbed to become saturated primary exhaust air 13 and is discharged out of the heat-moisture exchange loop; the cooling water 19 is divided into circulating high-temperature cold source water 21 and regulation spray water which respectively enter the indirect heat and humidity exchanger 6 and the heat and humidity regulation and control exchanger 8; pipelines for conveying fresh air to be mixed, fresh air to be evaporated and cooled, primary fresh air to be evaporated and secondary fresh air to be evaporated are respectively provided with a fresh air valve to be mixed, a fresh air valve to be evaporated and cooled 10b, a primary fresh air valve to be evaporated and cooled 10c and a secondary fresh air valve to be evaporated and evaporated 10 d; the dry return air and the fresh air to be mixed enter the mixing chamber 4 to be mixed into fresh return air, the fresh return air enters the heat and humidity regulation and control exchanger 8 to carry out heat and humidity exchange with the regulation and control spray water, and when the requirements of indoor air supply are met, the air is supplied to the indoor through an air outlet of the heat and humidity regulation and control exchanger; a new mixed air return valve 10e is arranged on the pipeline for conveying new mixed air; circulating cold water 20 which is discharged from the water outlets of the heat and humidity control exchanger and the indirect heat and humidity exchanger 6 and collected enters the high-temperature cold water pipe through the circulating cold water pipe and then enters the control system as high-temperature cold water.
Example 3:
a control method to which the control system of embodiment 2 is applied:
a. opening a return air inlet air valve 10f, a fresh air valve 10b to be steamed and cooled, a fresh air mixing air valve 10e, a primary fresh air valve 10c to be steamed and a secondary fresh air valve to be steamed, and closing an external air outlet air valve 10g and a fresh air valve 10a to be mixed; opening all circulating pumps, opening the spraying regulation control valve 11b, and closing the water replenishing control valve 11 a; only the indoor return air 15 enters the control system which enters the full return air circulation mode, as shown in fig. 5:
indoor air is subjected to internal circulation, the temperature and the humidity are increased, and after being extracted by an exhaust fan 17, indoor return air 15(i (the state point, the same below) is formed, the temperature is 24-28 ℃, and the humidity is more than 60%), exchanging heat with outdoor fresh air 16(w: temperature 35-40 ℃, humidity 80%) in a gas-gas heat exchanger 3 (the temperature of indoor return air 15 is lower than that of outdoor fresh air, the temperature is slightly raised after heat exchange, the moisture content is unchanged), dehumidifying by a solution dehumidifying device 5 to become dry return air (g: temperature about 32 ℃, 10-30%) with normal temperature and low humidity, enters a heat and humidity regulation exchanger 8 through a mixing chamber 4, and after the temperature and humidity of the air enters the indoor air supply requirement by regulating a spraying regulation control valve 11b and a new air return mixing valve 10e, the air is supplied to the indoor air through an air outlet of the heat and humidity regulation exchanger (o: the temperature is 13 (lowest) to 18 ℃ and 40-65%);
b. opening an external air exhaust air valve 10g, a fresh air valve to be mixed 10a, a fresh air mixing air valve, a fresh air back mixing air valve 10e, a secondary fresh air valve to be steamed and a primary fresh air valve to be steamed 10c, and closing a return air inlet air valve 10 f; opening all circulating pumps, opening the spraying regulation control valve 11b, and closing the water replenishing control valve 11 a; only outdoor fresh air 16 enters the control system, and the control system enters a fresh air circulation mode, as shown in fig. 6:
outdoor fresh air 16(w: temperature 35-40 ℃, humidity 80%) enters a solution dehumidifying device 5 through a gas-gas heat exchanger 3, and is dehumidified by a dehumidifying agent, and latent heat in the outdoor fresh air is taken away to form dry fresh air (n: 30-35 ℃, 20-30%); the dry fresh air is divided into two paths by the fresh air valve 10a to be mixed and the fresh air valve 10b to be evaporated and cooled: and (3) after the fresh air to be mixed and the fresh air to be evaporated and cooled, the fresh air to be mixed enters the heat and humidity regulation and control exchanger 8 through the mixing chamber 4 and the fresh air backmixing air valve 10e (h) to carry out heat and humidity exchange with the regulation and control spray water, the wet bulb temperature of the dry air at the point h (the temperature is 13 (lowest) to 18 ℃ and 40% -65%) is reached by regulating the spray regulation control valve 11b and the fresh air backmixing air valve 10e, and the air is supplied to the room through the air outlet (o) of the heat and humidity regulation and control exchanger after the indoor air supply requirement is met.
c. Opening all air valves, all circulating pumps and the spraying adjusting control valve 11 b; closing the water replenishing control valve 11 a; adjust return air inlet blast gate 10f and treat the aperture that mixes new trend blast gate 10a, outdoor new trend 16, outdoor return air get into simultaneously among the control system, control system gets into new trend return air mixed cycle mode, as shown in fig. 7: w is the temperature of 35-40 ℃ and the humidity of 80%; m: about 30 ℃, 70%; n: about 33 ℃, 20% -30%; g about 30 ℃, 20% -30%; (ii) a h about 31 ℃, 20% -30%; o, i and f are the same as above;
d. closing the external exhaust valve and the fresh air valve to be mixed 10a, and opening the other air valves; closing all control valves, opening all circulating pumps, independently dehumidifying indoor return air 15 by the control system, entering an independent dehumidification mode by the control system, and removing indoor waste heat by high-temperature cold source water of other equipment (such as a dry air disc) if needed;
wherein, when the water content in the control system is lower than the threshold value, the water supplementing control valve 11a is opened to supplement water to the control system.
In each mode, the fresh air to be subjected to evaporative cooling is divided into two paths: the primary fresh air to be steamed and the secondary fresh air to be steamed respectively enter the heat and humidity exchange loop, and the functions of the primary fresh air to be steamed and the secondary fresh air to be steamed are that cooling water 19 is manufactured by cooling each evaporation cooler in the heat and humidity exchange loop and is used as regulation spray water of the heat and humidity regulation exchanger 8 to regulate and control the temperature and humidity of the fresh air and the mixed air for heat absorption and humidification, and the specific process comprises the following steps: the secondary fresh air to be evaporated enters a primary direct heat-moisture exchanger 701 (a direct evaporation cooler) and high-temperature cold source water (cold water is supplemented or circulated 20 from a water supplementing pipe) to be directly evaporated and cooled to take away a large amount of latent heat and sensible heat, the high-temperature cold source water 18 is cooled to the wet bulb temperature of n points (about 18 ℃), and the secondary fresh air to be evaporated is changed into hot and wet (close to saturation) secondary exhaust air 14 after heat-mass exchange and then is discharged; the primary fresh air to be evaporated firstly enters an air channel of an indirect heat and humidity exchanger 6 (indirect evaporative cooler), cold water (circulating high-temperature cold source water 21, about 13 ℃) sprayed from the top of the indirect heat and humidity exchanger flows through the cold water channel, two fluids are not contacted with each other and exchange heat by the wall surfaces of the respective channels in a reverse flow manner, the primary fresh air to be evaporated and the like are cooled to about 20 ℃, primary indirect evaporative cooling fresh air 12(j state point) with the humidity of 35% continues to enter a secondary direct heat and humidity exchanger 702 (direct heat and humidity exchanger, direct evaporative cooler) and contact and cool the moisture in the secondary direct heat and humidity exchanger, a large amount of moisture is evaporated to enter the primary indirect evaporative cooling fresh air 12 to obtain cooling water 19 with the temperature of about 13 ℃ close to the temperature of an air wet bulb at the j point, the cooling water 19 is divided into circulating high-temperature cold source water 21, and regulation and control spray water respectively enter the indirect heat and humidity exchanger 6, the heat and humidity regulation and control exchanger 8 carries out respective heat and humidity exchange; the primary indirect evaporative cooling fresh air 12 reaches a saturated state after obtaining sensible heat and latent heat in the secondary direct heat and humidity exchanger 702, and is discharged out of the secondary direct heat and humidity exchanger 702 to become wet and cold primary exhaust air 13(p point) to be discharged out of the heat and humidity exchange loop; the primary exhaust 13 and the dehumidification return water (regeneration liquid) sent into the heat exchanger and dehumidified by the regenerator 1 at high temperature are discharged (point q) after heat exchange;
since the water is directly contacted with the air in the primary and secondary direct evaporative coolers, a large amount of water is evaporated and taken away by the secondary air and the primary air in the evaporative cooling process, and the water lost from the water replenishing pipe is replenished through adjusting the water replenishing control valve 11 a.
As shown in fig. 8, in the solution dehumidifying apparatus 5, a high-concentration dehumidifying agent (calcium chloride, lithium bromide solution, etc.) is ejected via the dehumidifying shower pipe 506 into two passages (not shown) of the cross-flow type plate heat exchanger (now available): the return air channel and the fresh air channel respectively dehumidify return air and fresh air, and air in the two channels simultaneously exchanges heat through the partition plates of the plate heat exchanger; the diluted desiccant falls into a liquid collecting tank at the bottom of the solution dehumidifying device and is pumped into a dehumidifying spray pipe 506 from a dehumidifying circulating pipe through a dehumidifying circulating pump 9a as dehumidifying return water to circularly dehumidify the gas in the air duct; when the concentration of the diluted dehumidifying agent (dehumidifying return water) is too low, the dehumidifying agent is pumped into the gas-liquid heat exchanger 2 through the regenerating circulating pump 9c and enters the regenerator 1, high-temperature dehumidification is carried out through the regenerator 1 to form a regenerated liquid, the regenerated liquid is cooled and exchanged in the gas-liquid heat exchanger 2 by adopting saturated wet and cold primary exhaust 13 due to higher temperature, and the regenerated liquid after concentration and temperature reduction is sent into a liquid collecting tank at the bottom of the solution dehumidifying device again for circulation.
The foregoing embodiments are merely illustrative of the principles and utilities of the present invention and are not intended to limit the invention. Any person skilled in the art can modify or change the above-mentioned embodiments without departing from the spirit and scope of the present invention. Accordingly, it is intended that all equivalent modifications or changes which can be made by those skilled in the art without departing from the spirit and technical spirit of the present invention be covered by the claims of the present invention.
Claims (10)
1. A control system for adjusting the temperature and humidity of indoor air in a humid area is characterized in that outdoor fresh air is dehumidified by a solution dehumidifying device to form dry fresh air, the dry fresh air enters a heat and humidity exchange loop in the control system to perform heat and humidity exchange with high-temperature cold source water at the temperature of 12-18 ℃, and the high-temperature cold source water is cooled to the temperature of 10-13 ℃ and serves as regulation spray water in a heat and humidity regulation exchanger;
the indoor return air is extracted from the room and is dehumidified by the solution dehumidifying device to be dry return air;
and the dry return air is subjected to heat-moisture exchange with the regulation spray water in the heat-moisture regulation exchanger, the temperature of the dry return air is regulated to 10-18 ℃ of the wet bulb temperature of dry air at the air inlet side of the heat-moisture regulation exchanger, the humidity of the dry return air reaches 40-60%, and when the dry return air meets the requirement of indoor air supply, the air is supplied to the indoor through the air outlet of the heat-moisture regulation exchanger.
2. The system as claimed in claim 1, wherein the heat and moisture exchange circuit includes an indirect heat and moisture exchanger for cooling the dry fresh air with equal humidity and a direct heat and moisture exchanger for producing cooling water by direct evaporative cooling of the high temperature cold source water with the dry fresh air cooled with equal humidity.
3. The system as claimed in claim 2, wherein the dry fresh air enters the indirect heat and humidity exchanger and is cooled by the high temperature cold source water, and then enters the direct heat and humidity exchanger to directly evaporate and absorb heat to the indirect cold exhaust water discharged from the indirect heat and humidity exchanger to become a saturated primary exhaust air discharge heat and humidity exchange loop; the cooled indirect cooling drainage becomes cooling water for use by a heat and humidity regulation exchanger;
the primary indirect evaporative cooling fresh air and the dry return air enter the mixing chamber to be mixed into fresh return air, then enter the heat and humidity regulation and control exchanger to carry out heat and humidity exchange with cooling water used for regulating and controlling spray water, and after the requirement of indoor air supply is met, air is supplied to the indoor space through the air outlet of the heat and humidity regulation and control exchanger.
4. The control system for regulating the temperature and humidity of the indoor air in a humid area according to claim 2, wherein there are two direct heat and humidity exchangers, the first direct heat and humidity exchanger and the second direct heat and humidity exchanger are connected in series, and the series connection is arranged on the series circulating pump; the dry fresh air is divided into two paths: treat to mix the new trend and treat the evaporative cooling new trend, treat the evaporative cooling new trend and shunt again into two tunnel: the primary fresh air to be evaporated and the secondary fresh air to be evaporated respectively enter the heat-moisture exchange loop; wherein the content of the first and second substances,
the primary fresh air to be evaporated enters the indirect heat-moisture exchanger and is subjected to equal-humidity temperature reduction by circulating high-temperature cold source water to form primary indirect evaporative cooling fresh air;
high-temperature cold source water enters a primary direct heat-moisture exchanger to be directly evaporated and cooled by the secondary fresh air to be evaporated, and then enters a secondary direct heat-moisture exchanger to be directly evaporated and cooled again by the primary indirect evaporative cooling fresh air to form cooling water; the secondary fresh air to be evaporated is directly evaporated and absorbed to become saturated secondary exhaust air which is discharged out of the heat-moisture exchange loop; the primary indirect evaporative cooling fresh air is directly evaporated and absorbed to become saturated primary exhaust air which is discharged out of the heat-moisture exchange loop; cooling water is divided into circulating high-temperature cold source water and regulation spray water which respectively enter the indirect heat-humidity exchanger and the heat-humidity regulation exchanger;
pipelines for conveying fresh air to be mixed, fresh air to be evaporated and cooled, primary fresh air to be evaporated and secondary fresh air to be evaporated are respectively provided with a fresh air valve to be mixed, a fresh air valve to be evaporated and cooled, a primary fresh air valve and a secondary fresh air valve to be evaporated;
the dry return air and the fresh air to be mixed enter the mixing chamber to be mixed into fresh return air, the fresh return air enters the heat and humidity regulation and control exchanger to carry out heat and humidity exchange with the regulation and control spray water, and after the requirements of indoor air supply are met, the air is supplied to the indoor through the air outlet of the heat and humidity regulation and control exchanger; and a new mixed air return valve is arranged on the pipeline for conveying new mixed air.
5. The control system for regulating the temperature and humidity of indoor air in a humid area according to any one of claims 1 to 4, wherein the solution dehumidifying device comprises a cross-flow plate type heat exchanger, an upper return air outlet cavity, an upper fresh air outlet cavity, a lower return air inlet cavity, a lower fresh air inlet cavity, a dehumidifying spray pipe and a louver liquid baffle plate, wherein the cross-flow plate type heat exchanger is erected in the solution dehumidifying device and isolates the air flue of the solution dehumidifying device; wherein the content of the first and second substances,
the cross flow plate type heat exchanger is a cube; the outdoor fresh air and the indoor return air respectively enter the lower fresh air inlet cavity and the lower return air inlet cavity after being subjected to cross wall type mutual heat exchange through respective independent channels arranged in the solution dehumidifying device; the bottoms of the lower fresh air inlet cavity and the lower return air inlet cavity are arc-shaped to form an arc-shaped air channel;
and the dehumidifying agent falling into a liquid collecting tank at the bottom of the solution dehumidifying device is used as dehumidifying backwater and is pumped into the dehumidifying spray pipe from the dehumidifying circulating pipe through the dehumidifying circulating pump to circularly dehumidify the gas in the air duct.
6. The control system for adjusting the temperature and humidity of the indoor air in the humid area according to claim 5, wherein the dehumidified return water flows through the air-liquid heat exchanger through the regeneration water supply pipe, enters the regenerator, is heated and concentrated, then flows back to the air-liquid heat exchanger to perform non-contact heat exchange with primary exhaust air, and finally flows back to a liquid collecting tank at the bottom of the solution dehumidifying device; the regeneration water supply pipe is provided with a regeneration circulating pump.
7. The system of claim 6, wherein the fresh outdoor air and the return indoor air enter the air-to-air heat exchanger for mutual non-contact heat exchange and then enter the solution dehumidifier respectively, and a return air inlet valve is disposed at the inlet of the return indoor air of the air-to-air heat exchanger; the indoor return air is also exhausted to the outside atmosphere through an outside exhaust pipe; and the external exhaust pipe is provided with an external exhaust air valve.
8. The control system for regulating the temperature and humidity of the indoor air in the humid region according to claim 7, wherein the circulating cold water discharged from the water discharge port of the heat and humidity regulating exchanger or/and the indirect heat and humidity exchanger is collected to enter the high-temperature cold water pipe through the circulating cold water pipe and then enters the control system as the high-temperature cold water; the high-temperature cold water pipe is also connected with a water supplementing pipe, and a water supplementing control valve is arranged on the water supplementing pipe; a circulating cold water circulating pump is arranged on the circulating cold water pipe; a spraying regulation control valve is arranged on the pipeline for conveying the regulation spray water; the pipeline for discharging the cooling water is provided with a cooling water circulating pump.
9. The control system for regulating the temperature and humidity of air in a humid area interior according to claim 8, wherein said gas-liquid heat exchanger is a coiled tube surface heat exchanger or a finned surface heat exchanger; the gas-gas heat exchanger is a dividing wall plate type heat exchanger; the indirect heat and moisture exchanger is an indirect evaporative cooler; the direct heat and moisture exchanger is a direct evaporative cooler; the heat and humidity regulation and control exchanger is an indirect evaporative cooler or a direct evaporative cooler.
10. A control method using the control system according to claim 9,
a. opening a return air inlet air valve, a fresh air valve to be steamed and cooled, a fresh air return mixing air valve, a primary fresh air valve to be steamed, a secondary fresh air valve to be steamed, closing an external air exhaust air valve and a fresh air valve to be mixed; opening all circulating pumps, opening a spraying regulation control valve, and closing a water replenishing control valve; only indoor return air enters the control system, and the control system enters a full return air circulation mode:
b. opening an external air exhaust air valve, a fresh air valve to be mixed, a fresh air mixing air valve, a fresh air return mixing air valve, a secondary fresh air valve to be steamed and a primary fresh air valve to be steamed, and closing a return air inlet air valve; opening all circulating pumps, opening a spraying regulation control valve, and closing a water replenishing control valve; only outdoor fresh air enters the control system, and the control system enters a full fresh air circulation mode;
c. opening all air valves, all circulating pumps and the spraying regulation control valve; closing the water replenishing control valve; adjusting the opening degrees of a return air inlet air valve and a fresh air valve to be mixed, simultaneously feeding outdoor fresh air and indoor return air into the control system, and feeding the control system into a fresh air and return air mixed circulation mode;
d. closing an external exhaust valve and a fresh air valve to be mixed, and opening other air valves; closing all the control valves, opening all the circulating pumps, independently dehumidifying indoor return air by the control system, and entering an independent dehumidification mode by the control system; and when the water content in the control system is lower than a threshold value, opening a water supplementing control valve to supplement water to the control system.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110527715.2A CN113339901B (en) | 2021-05-14 | 2021-05-14 | Control system and method for adjusting indoor air temperature and humidity in humid area |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110527715.2A CN113339901B (en) | 2021-05-14 | 2021-05-14 | Control system and method for adjusting indoor air temperature and humidity in humid area |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN113339901A true CN113339901A (en) | 2021-09-03 |
| CN113339901B CN113339901B (en) | 2022-05-31 |
Family
ID=77470044
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202110527715.2A Active CN113339901B (en) | 2021-05-14 | 2021-05-14 | Control system and method for adjusting indoor air temperature and humidity in humid area |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN113339901B (en) |
Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101769575A (en) * | 2010-01-07 | 2010-07-07 | 西安工程大学 | Evaporating semi-centralized air-conditioning system combined with usual cold water machine set as cold source |
| CN201615718U (en) * | 2008-07-23 | 2010-10-27 | 杨泰和 | Double-flow circuit heat exchange device for periodic positive and reverse directional pumping |
| EP2339252A1 (en) * | 2009-12-21 | 2011-06-29 | Universita' degli Studi di Genova | Air conditioning and dehumidification integrated system |
| CN104833014A (en) * | 2015-05-03 | 2015-08-12 | 江苏格瑞力德空调制冷设备有限公司 | Solution type all-air air conditioning unit provided with all cold and heat sources and capable of transferring refrigerant and heating medium |
| CN105953322A (en) * | 2016-05-12 | 2016-09-21 | 东南大学 | Heat source tower based heat pump air-conditioning system and method taking fresh air into consideration |
| WO2017088400A1 (en) * | 2015-11-24 | 2017-06-01 | 东南大学 | Independent temperature and humidity processing air conditioning system driven by low-level thermal energy |
| CN107869789A (en) * | 2016-09-23 | 2018-04-03 | 江苏科技大学 | A kind of air purifier and its implementation |
-
2021
- 2021-05-14 CN CN202110527715.2A patent/CN113339901B/en active Active
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN201615718U (en) * | 2008-07-23 | 2010-10-27 | 杨泰和 | Double-flow circuit heat exchange device for periodic positive and reverse directional pumping |
| EP2339252A1 (en) * | 2009-12-21 | 2011-06-29 | Universita' degli Studi di Genova | Air conditioning and dehumidification integrated system |
| CN101769575A (en) * | 2010-01-07 | 2010-07-07 | 西安工程大学 | Evaporating semi-centralized air-conditioning system combined with usual cold water machine set as cold source |
| CN104833014A (en) * | 2015-05-03 | 2015-08-12 | 江苏格瑞力德空调制冷设备有限公司 | Solution type all-air air conditioning unit provided with all cold and heat sources and capable of transferring refrigerant and heating medium |
| WO2017088400A1 (en) * | 2015-11-24 | 2017-06-01 | 东南大学 | Independent temperature and humidity processing air conditioning system driven by low-level thermal energy |
| CN105953322A (en) * | 2016-05-12 | 2016-09-21 | 东南大学 | Heat source tower based heat pump air-conditioning system and method taking fresh air into consideration |
| CN107869789A (en) * | 2016-09-23 | 2018-04-03 | 江苏科技大学 | A kind of air purifier and its implementation |
Also Published As
| Publication number | Publication date |
|---|---|
| CN113339901B (en) | 2022-05-31 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN100476308C (en) | Humidity controller | |
| US9810439B2 (en) | Energy exchange system for conditioning air in an enclosed structure | |
| CN1890508B (en) | Air conditioner | |
| CN100432553C (en) | Air conditioner | |
| US20120167610A1 (en) | Indirect air-side economizer for removing heat from enclosed spaces with high internal heat generation | |
| JP6147537B2 (en) | Air conditioner | |
| CN103370579A (en) | Method and apparatus for conditioning air | |
| CN205383723U (en) | Energy -saving evaporation cooling formula central air conditioning unit | |
| JP2008070097A (en) | Dehumidifying air conditioner | |
| KR100904592B1 (en) | Humidity controller | |
| CN211503040U (en) | Heat-humidity ratio adjustable solution auxiliary type heat pump system | |
| JP2001241693A (en) | Air conditioner | |
| KR20040026242A (en) | Liquid dessicant cooling system using heat pump | |
| CN107246681A (en) | A kind of small-sized household formula solution humidifying Fresh air handling units of external low-temperature receiver | |
| CN105737302A (en) | Central air-conditioning based on dry air energy | |
| CN205957353U (en) | Air treatment device | |
| CN105020807B (en) | It crosses cold mould heat-pump-type solution humidifying and evaporates cooling combined air-conditioning system | |
| CN110173776A (en) | A kind of Fresh air handing device of pre-cooling type runner humidifying | |
| CN107575967A (en) | A kind of heat pump type air conditioning system and its operation method suitable for annual operating mode | |
| CN108224628A (en) | With reference to heat pump driven standpipe indirect evaporating-cooling and the air-conditioner set of solution dehumidification | |
| CN204880414U (en) | Air conditioning unit suitable for in subway | |
| JP2018021711A (en) | Water evaporation cooler | |
| CN212108844U (en) | Air conditioning unit based on rotary wheel type heat recovery, indirect evaporative cooling and mechanical refrigeration | |
| CN100458292C (en) | Refrigerating unit of air condition by dehumidifying, evaporative cooling solution | |
| CN113339901B (en) | Control system and method for adjusting indoor air temperature and humidity in humid area |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |