WO2012139248A1 - Heat and cold sources of temperature and humidity independent control air conditioning system - Google Patents
Heat and cold sources of temperature and humidity independent control air conditioning system Download PDFInfo
- Publication number
- WO2012139248A1 WO2012139248A1 PCT/CN2011/000642 CN2011000642W WO2012139248A1 WO 2012139248 A1 WO2012139248 A1 WO 2012139248A1 CN 2011000642 W CN2011000642 W CN 2011000642W WO 2012139248 A1 WO2012139248 A1 WO 2012139248A1
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- Prior art keywords
- heat
- evaporator
- compressor
- expansion valve
- condenser
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
- F25D17/00—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces
- F25D17/02—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces for circulating liquids, e.g. brine
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
- F25B1/04—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type
- F25B1/053—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type of turbine type
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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
- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/30—Expansion means; Dispositions thereof
- F25B41/385—Dispositions with two or more expansion means arranged in parallel on a refrigerant line leading to the same evaporator
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
- F25B5/02—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in parallel
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B6/00—Compression machines, plants or systems, with several condenser circuits
- F25B6/04—Compression machines, plants or systems, with several condenser circuits arranged in series
Definitions
- the first expansion valve 4 is further used for adjusting the temperature of the outlet chilled water of the first evaporator 6.
- the present invention provides heat and cold sources of the THIC air conditioning system, in which a centrifugal refrigerator is used as a compressor for removing the indoor sensible heat and the indoor latent heat, so as to meet the heat and cold sources requirement of a small-scale THIC air conditioning system (the total cooling capacity is less than 250kW); the present invention further provides another heat and cold sources of the THIC air conditioning system, in which at least two centrifugal refrigerators are used as compressors for respectively removing the indoor sensible heat and the indoor latent heat independently, so as to meet the heat and cold sources requirement of a large-scale THIC air conditioning system (the total cooling capacity is greater than 500kW).
- the outlet refrigerant of the second condenser 3 is divided into two flows which are adjusted respectively by the first expansion valve 4 and the second expansion valve 5; one of the two flows enters into the first cycle branch and passes through the first expansion valve 4 to flow into the first evaporator 6, so as to cool the high temperature (18 ⁇ 21 ° C) chilled water which flows on the other side of the first evaporator 6 in reverse direction from the refrigerant; the other flow enters into the second cycle branch and passes through the second expansion valve 5 to flow into the second evaporator 7, so as to cool the diluted solution which flows on the other side of the second evaporator 7 in reverse direction from the refrigerant.
- the outlet refrigerants of the first cycle branch and the second cycle branch, i.e. of the first evaporator 6 and the second evaporator 7 are mixed into a stream of refrigerant and return back to the compressor 1, and then the refrigerant enters the next cycle after being processed.
- the compressor 1 of the heat and cold sources of the THIC air conditioning system is a centrifugal compressor, for example, a centrifugal compressor with the cooling capacity of 175kW (Wang Jia et al., Performance analysis on micro centrifugal chillers, Heating, Ventilating & Air Conditioning, 2009, 39 ( 5 ) : 104-108).
- the one or more refrigerators a are independently controlled respectively.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Air Conditioning Control Device (AREA)
- Other Air-Conditioning Systems (AREA)
Abstract
Heat and cold sources of a temperature and humidity independent control air conditioning system comprise a compressor (1), a first condenser (2) and a second condenser (3), which are connected successively. A first expansion valve (4) and a second expansion valve (5) are respectively connected to the second condenser (3). A first evaporator (6) and a second evaporator (7) are respectively connected to the compressor (1). The first evaporator (6) is connected to the first expansion valve (4) to form a first cycle branch while the second evaporator (7) is connected to the second expansion valve (5) to form a second cycle branch. The first cycle branch and the second cycle branch are connected in parallel. The heat and cold sources of the temperature and humidity independent control air conditioning system have a relatively high refrigeration efficiency so as to significantly reduce energy consumption and protect environment.
Description
Heat and Cold Sources of Temperature and Humidity Independent Control Air Conditioning System
Technical Field
The present invention generally relates to refrigeration and air conditioning equipments technology fields, and more particularly, to heat and cold sources of Temperature and Humidity Independent Control (THIC) air conditioning system.
Background Art
The THIC air conditioning system is directed to an air conditioning system composed of an independent sensible heat processing system for indoor temperature control and an independent latent heat processing system for indoor humidity control. Due to its advantages on improving performance of conditioning system, reducing energy consumption, improving indoor air quality, and protecting atmosphere, the THIC air conditioning system is more and more widely applied in recent years. China patent CNl 862123 A provides high efficiency liquid desiccant fresh air handling units driven by heat pump. On one hand, the fresh air units cool the desiccant concentrated solution with an evaporator of a heat pump so as to improve the solution's capability of moisture absorption and remove the latent heat released during the moisture absorption process; on the other hand, the fresh air units heat the regenerated dilute solution with a condenser of the same heat pump, and the solution is concentrated into regenerated solution by performing a total heat exchange with the exhaust air of total heat recovery. The energy efficiency ratio (EER) of the heat pump driven liquid desiccant fresh air units provided by China patent CNl 862123 A is relatively high, thus the fresh air units has very good prospects for application. In the THIC air conditioning system mentioned below, the liquid desiccant fresh air units refers to the heat pump driven liquid desiccant fresh air units provided by China patent CNl 862123 A.
Fig. 1 is a schematic diagram illustrating the working principle of the THIC air conditioning system in the prior art. The indoor sensible heat is removed by high temperature(around 18°C) chilled water from refrigerator 1, and the indoor latent heat is removed by the dry and cool fresh air from the liquid desiccant fresh air units. In the liquid desiccant fresh air units, the cooling capacity required by the liquid dehumidifier and the heating capacity required by the liquid regenerator are provided by refrigerator 2. The refrigerator 1 and refrigerator 2 can be regarded as the heat and cold sources of the THIC air conditioning system. For the heat and cold sources of the THIC air conditioning system in the prior art, the refrigerator 1 is usually a centrifugal or screw refrigerator with a relatively large cooling capacity, and the refrigerator 2 is usually a vortex refrigerator with a relatively small cooling capacity. A centrifugal refrigerator is not used as the refrigerator 2, since the cooling capacity of a conventional centrifugal refrigerator is thousands of kilowatts and the cooling capacity required by the refrigerator 2 is usually below 200 kw according to the usual fresh air requirement (below 18000 m per hour). However, the refrigeration efficiency of a vortex refrigerator is usually lower than that of a centrifugal refrigerator; the rated value of a vortex refrigerator is usually 3~4 while the refrigeration efficiency rated value of a centrifugal refrigerator may be 5~6. If a centrifugal refrigerator can be made small enough with the cooling capacity level of a vortex refrigerator, the original vortex refrigerator may be replaced by a centrifugal refrigerator.
To sum up, the refrigeration efficiency of the heat and cold sources of the prior THIC air conditioning system is relatively low, and it is disadvantaged to reduce energy consumption and protect atmospheric environment.
Contents of the Invention
(1) The technical problem to be solved
The technical problem to be solved according to the present invention is how
to provide heat and cold sources of the THIC air conditioning system with higher refrigeration efficiency in response to the above defects, so as to reduce energy consumption and protect atmospheric environment.
(2) The technical solution
To solve the above technical problem, the present invention provides heat and cold sources of the THIC air conditioning system, comprising: a compressor 1, a first condenser 2 and a second condenser 3, which are connected successively; a first expansion valve 4 and a second expansion valve 5 respectively connected to the second condenser 3; a first evaporator 6 and a second evaporator 7 respectively connected to the compressor 1; the first evaporator 6 is connected to the first expansion valve 4 to form a first cycle branch; the second evaporator 7 is connected to the second expansion valve 5 to form a second cycle branch; the first cycle branch and the second cycle branch which are connected in parallel connect the second condenser 3 and the compressor 1.
Preferably, the compressor 1 is a centrifugal compressor.
Preferably, the first expansion valve 4 is further used for adjusting the temperature of the outlet chilled water of the first evaporator 6.
Preferably, the second expansion valve 5 is further used for adjusting the temperature of the outlet diluted solution of the second evaporator 7.
The present invention further provides heat and cold sources of the THIC air conditioning system, comprising: one or more refrigerators a and one or more refrigerators b, wherein,
The refrigerator a comprises: a first compressor la, a first condenser 2a, a first expansion valve 3a and a first evaporator 4a, which are connected together to form a ring;
The refrigerator b comprises: a second compressor lb, a second condenser 2b, a second expansion valve 3b and a second evaporator 4b, which are connected together to form a ring.
Preferably, both the first compressor la and the second compressor lb are centrifugal compressors.
Preferably, the one or more refrigerators a are independently controlled respectively; the one or more refrigerators b are independently controlled respectively.
(3) The advantageous effects
The present invention provides heat and cold sources of the THIC air conditioning system, in which a centrifugal refrigerator is used as a compressor for removing the indoor sensible heat and the indoor latent heat, so as to meet the heat and cold sources requirement of a small-scale THIC air conditioning system (the total cooling capacity is less than 250kW); the present invention further provides another heat and cold sources of the THIC air conditioning system, in which at least two centrifugal refrigerators are used as compressors for respectively removing the indoor sensible heat and the indoor latent heat independently, so as to meet the heat and cold sources requirement of a large-scale THIC air conditioning system (the total cooling capacity is greater than 500kW). Compared with the original vortex refrigerator, a centrifugal refrigerator has an obvious advantage on the refrigeration efficiency, thus the total refrigeration efficiency may be improved by taking a centrifugal refrigerator as heat and cold sources of the THIC air conditioning system. Therefore, it is possible to significantly reduce energy consumption and protect atmosphere environment.
Description of Figures
Fig. 1 is a schematic diagram illustrating the working principle of the THIC air conditioning system in the prior art;
Fig. 2 is a structure schematic diagram illustrating the heat and cold sources of the THIC air conditioning system according to embodiment 1 of the present invention;
Fig. 3 is a structure schematic diagram illustrating the heat and cold sources of the THIC air conditioning system according to embodiment 2 of the present invention.
Specific Mode for Carrying out the Invention
The specific mode for carrying out the invention is hereinafter described in detail with reference to the accompanying figures and embodiments. The following embodiments are provided by way of explanation of the invention, not limitation of the scope of the invention.
Embodiment 1
Fig. 2 is a structure schematic diagram illustrating the heat and cold sources of the THIC air conditioning system according to embodiment 1 of the present invention; as shown in fig. 2, the heat and cold sources of the THIC air conditioning system comprises: a compressor 1, a first condenser 2 and a second condenser 3, which are connected successively; a first expansion valve 4 and a second expansion valve 5 respectively connected to the second condenser 3; a first evaporator 6 and a second evaporator 7 respectively connected to the compressor 1; the first evaporator 6 is connected to the first expansion valve 4 to form a first cycle branch; the second evaporator 7 is connected to the second expansion valve 5 to form a second cycle branch; the first cycle branch and the second cycle branch which are connected in parallel connect the second condenser 3 and the compressor 1.
The outlet refrigerant with higher temperature (greater than 45 °C ) from the compressor 1 firstly flows into the first condenser 2 to heat the concentrated solution which flows on the other side of the first condenser 2 in reverse direction from the refrigerant. Then, the outlet refrigerant from the first condenser 2 flows into the second condenser 3 and removes the extra condensing heat with the cooling water which flows on the other side of the second condenser 3 in reverse
direction from the refrigerant. The outlet refrigerant of the second condenser 3 is divided into two flows which are adjusted respectively by the first expansion valve 4 and the second expansion valve 5; one of the two flows enters into the first cycle branch and passes through the first expansion valve 4 to flow into the first evaporator 6, so as to cool the high temperature (18~21 °C) chilled water which flows on the other side of the first evaporator 6 in reverse direction from the refrigerant; the other flow enters into the second cycle branch and passes through the second expansion valve 5 to flow into the second evaporator 7, so as to cool the diluted solution which flows on the other side of the second evaporator 7 in reverse direction from the refrigerant. The outlet refrigerants of the first cycle branch and the second cycle branch, i.e. of the first evaporator 6 and the second evaporator 7 are mixed into a stream of refrigerant and return back to the compressor 1, and then the refrigerant enters the next cycle after being processed.
In this embodiment, the compressor 1 of the heat and cold sources of the THIC air conditioning system is a centrifugal compressor, for example, a centrifugal compressor with the cooling capacity of 175kW (Wang Jia et al., Performance analysis on micro centrifugal chillers, Heating, Ventilating & Air Conditioning, 2009, 39 ( 5 ) : 104-108).
In this embodiment, the concentrated solution entering the first condenser 2 through a concentrated solution inlet 9 is heated to around 45 °C by the refrigerant, and then it is sent to a regenerator through a concentrated solution outlet 8.
The chilled water entering the first evaporator 6 through a chilled water inlet 12 is cooled to around 18°C by the refrigerant, and then it is sent to an indoor sensible heat terminal through a chilled water outlet 13.
The diluted solution entering the second evaporator 7 through a diluted solution inlet 14 is cooled to around 14°C by the refrigerant, and then it is sent to the dehumidifier through a diluted solution outlet 15.
In this embodiment, the outlet chilled water temperature of the first
evaporator 6 and the outlet diluted solution temperature of the second evaporator 7 are respectively adjusted by the first expansion valve 4 and the second expansion valve 5, so that the cooling capacities of the first evaporator 6 and the second evaporator 7 respectively meet the requirements of themselves.
In this embodiment, the frequency or the guide vane angle of compressor 1 is adjusted according to the superheat degree of the outlet refrigerants of the first evaporator 6 and the second evaporator 7 to adjust the total refrigerant flow, so that the total cooling capacity of refrigerator meets the requirement of removing the sensible heat and the latent heat.
In this embodiment, the condensing temperature is adjusted by adjusting the temperature or flow of the cooling water entering the second condenser 3 through a cooling water inlet 11, so that the outlet concentrated solution temperature of the first condenser 2 is adjusted to meet the requirement of the concentrated solution.
Embodiment 2
Fig. 3 is a structure schematic diagram illustrating the heat and cold sources of the THIC air conditioning system according to embodiment 2 of the present invention; as shown in fig. 3, the heat and cold sources of the THIC air conditioning system comprises one or more refrigerators a and one or more refrigerators b, wherein, the refrigerator a comprises: a first compressor la, a first condenser 2a, a first expansion valve 3a and a first evaporator 4a, which are connected together to form a ring; the refrigerator b comprises: a second compressor lb, a second condenser 2b, a second expansion valve 3b and a second evaporator 4b, which are connected together to form a ring.
In the refrigerator a, the outlet refrigerant of the first compressor la first flows into the first condenser 2a to remove the condensing heat generated by the refrigerator a with the cooling water which flows on the other side of the first condenser 2a in reverse direction from the refrigerant. The outlet refrigerant from the first condenser 2a passes through the first expansion valve 3a to flow into the
first evaporator 4a, so as to cool the high temperature chilled water which flows on the other side of the first evaporator 4a in reverse direction from the refrigerant; the outlet refrigerant of the first evaporator 4a flows into the first compressor la, and then enters the next cycle after being processed.
In the refrigerator b, the outlet refrigerant of the second compressor lb first flows into the second condenser 2b to heat the concentrated solution which flows on the other side of the second condenser 2b in reverse direction from the refrigerant by the higher temperature of the refrigerant. The outlet refrigerant of the second condenser 2b passes through the second expansion valve 3b to flow into the second evaporator 4b, so as to cool the diluted solution which flows on the other side of the second evaporator 4b in reverse direction from the refrigerant. The outlet refrigerant of the second evaporator 4b flows into the second compressor lb, and then enters the next cycle after being processed.
In this embodiment, both the first compressor la and the second compressor lb are centrifugal compressors, for example, a centrifugal compressor with the cooling capacity of 175kW (Wang Jia et al., Performance analysis on micro centrifugal chillers, Heating, Ventilating & Air Conditioning, 2009, 39 ( 5 ) : 104-108).
In this embodiment, the high temperature chilled water entering the first evaporator 4a through a chilled water inlet 7 is cooled to around 18°C by the refrigerant, and then it is sent to an indoor sensible heat terminal through a chilled water outlet 8.
In this embodiment, the concentrated solution entering the second condenser 2b through a concentrated solution inlet 10 is heated to around 45 °C by the refrigerant, and then it is sent to a regenerator through a concentrated solution outlet 9.
In this embodiment, the diluted solution entering the second evaporator 4b through a diluted solution inlet 11 is cooled to around 14°C by the refrigerant, and
then it is sent to the dehumidifier through a diluted solution outlet 12.
In this embodiment, the one or more refrigerators a are independently controlled respectively.
In this embodiment, the one or more refrigerators b are independently controlled respectively.
The above embodiments are only used for explaining the present invention, but not for limiting its protection scope. Those skilled in the art may conduct various changes and variations without departing from the spirit and scope of the present invention. Therefore, all equivalent technical solutions shall fall into the protection scope of the present invention which is defined by the attached claims.
INDUSTRIAL APPLICABILITY
To sum up, the present invention provides heat and cold sources of the THIC air conditioning system, in which a centrifugal refrigerator is used as a compressor for removing both the indoor sensible heat and the indoor latent heat so as to meet the requirement of heat and cold sources of a small-scale THIC air conditioning system (the total cooling capacity is less than 250kW); the present invention further provides another heat and cold sources of the THIC air conditioning system, in which at least two centrifugal refrigerators are used as compressors for respectively removing the indoor sensible heat and the indoor latent heat independently so as to meet the requirement of heat and cold sources of a large-scale THIC air conditioning system (the total cooling capacity is greater than 500kW). Compared with the original vortex refrigerator, a centrifugal refrigerator has an obvious advantage on the refrigeration efficiency, thus the total refrigeration efficiency may be improved by taking a centrifugal refrigerator as a heat and cold sources of the THIC air conditioning system. Therefore, it is possible to significantly reduce energy consumption and protect atmosphere environment.
Claims
1. Heat and cold sources of the temperature and humidity independent control air conditioning system, comprising: a compressor (1), a first condenser (2) and a second condenser (3), which are connected successively; a first expansion valve (4) and a second expansion valve (5) respectively connected to the second condenser (3); a first evaporator (6) and a second evaporator (7) respectively connected to the compressor (1); the first evaporator (6) is connected to the first expansion valve (4) to form a first cycle branch; the second evaporator (7) is connected to the second expansion valve (5) to form a second cycle branch; the first cycle branch and the second cycle branch which are connected in parallel connect the second condenser (3) and the compressor (1).
2. The heat and cold sources of claim 1 , wherein the compressor (1) is a centrifugal compressor.
3. The heat and cold sources of claim 1 , wherein, the first expansion valve (4) is further used for adjusting the temperature of the outlet chilled water of the first evaporator (6).
4. The heat and cold sources of claim 1, wherein, the second expansion valve (5) is further used for adjusting the temperature of the outlet diluted solution of the second evaporator (7).
5. Heat and cold sources of the temperature and humidity independent control air conditioning system, comprising: one or more refrigerators (a) and one or more refrigerators (b), wherein
the refrigerator (a) comprises: a first compressor (la), a first condenser (2a), a first expansion valve (3 a) and a first evaporator (4a), which are connected together to form a ring;
the refrigerator (b) comprises: a second compressor (lb), a second condenser (2b), a second expansion valve (3b) and a second evaporator (4b), which are connected together to form a ring.
6. The heat and cold sources of claim 5, wherein both the first compressor (la) and the second compressor (lb) are centrifugal compressors.
7. The heat and cold sources of claim 5, wherein,
the one or more refrigerators (a) are independently controlled respectively; the one or more refrigerators (b) are independently controlled respectively.
Priority Applications (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| PCT/CN2011/000642 WO2012139248A1 (en) | 2011-04-12 | 2011-04-12 | Heat and cold sources of temperature and humidity independent control air conditioning system |
| JP2013509427A JP2013519066A (en) | 2011-04-12 | 2011-04-12 | Heat source and cold source of air conditioning system with independent control of temperature and humidity |
| CN201180070064.3A CN103562657B (en) | 2011-04-12 | 2011-04-12 | The Cooling and Heat Source of humiture independence control air conditioner system |
| US13/319,231 US20130111940A1 (en) | 2011-04-12 | 2011-04-12 | Heat and cold sources of temperature and humidity independent control air conditioning system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| PCT/CN2011/000642 WO2012139248A1 (en) | 2011-04-12 | 2011-04-12 | Heat and cold sources of temperature and humidity independent control air conditioning system |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| WO2012139248A1 true WO2012139248A1 (en) | 2012-10-18 |
Family
ID=47008765
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| PCT/CN2011/000642 WO2012139248A1 (en) | 2011-04-12 | 2011-04-12 | Heat and cold sources of temperature and humidity independent control air conditioning system |
Country Status (4)
| Country | Link |
|---|---|
| US (1) | US20130111940A1 (en) |
| JP (1) | JP2013519066A (en) |
| CN (1) | CN103562657B (en) |
| WO (1) | WO2012139248A1 (en) |
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|---|---|---|---|---|
| CN103994601A (en) * | 2014-06-05 | 2014-08-20 | 上海理工大学 | Independent temperature and humidity control air-conditioning system with heat recovery function |
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| CN104908919B (en) * | 2015-05-26 | 2017-11-07 | 浙江海洋学院 | A kind of air-conditioning device of ship cabin |
| CN105758056B (en) * | 2016-04-22 | 2018-08-17 | 广东美的制冷设备有限公司 | Air-conditioning system and air conditioner with it |
| CN105928098A (en) * | 2016-06-16 | 2016-09-07 | 珠海格力电器股份有限公司 | Air conditioner |
| CN108105795B (en) * | 2017-07-10 | 2023-04-18 | 昊姆（上海）节能科技有限公司 | Compression type and absorption type heat pump coupling flue gas treatment equipment |
| CN107560019A (en) * | 2017-09-30 | 2018-01-09 | 佛山市耐堡电气有限公司 | Dehumidifier |
| CN108518736A (en) * | 2018-04-04 | 2018-09-11 | 珠海格力电器股份有限公司 | Machine, constant temperature and humidity system and its control method in constant temperature and humidity |
| CN110425761A (en) * | 2019-09-02 | 2019-11-08 | 珠海冰恬环境科技有限公司 | A kind of comprehensive Cooling and Heat Source supply Optimization of Energy Saving system and its control method |
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- 2011-04-12 US US13/319,231 patent/US20130111940A1/en not_active Abandoned
- 2011-04-12 CN CN201180070064.3A patent/CN103562657B/en not_active Expired - Fee Related
- 2011-04-12 WO PCT/CN2011/000642 patent/WO2012139248A1/en active Application Filing
- 2011-04-12 JP JP2013509427A patent/JP2013519066A/en active Pending
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| CN103994601A (en) * | 2014-06-05 | 2014-08-20 | 上海理工大学 | Independent temperature and humidity control air-conditioning system with heat recovery function |
Also Published As
| Publication number | Publication date |
|---|---|
| US20130111940A1 (en) | 2013-05-09 |
| JP2013519066A (en) | 2013-05-23 |
| CN103562657B (en) | 2016-05-18 |
| CN103562657A (en) | 2014-02-05 |
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