WO2013026255A1 - 蒸汽压缩式制冷与转轮除湿耦合空调装置 - Google Patents

蒸汽压缩式制冷与转轮除湿耦合空调装置 Download PDF

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Publication number
WO2013026255A1
WO2013026255A1 PCT/CN2012/000794 CN2012000794W WO2013026255A1 WO 2013026255 A1 WO2013026255 A1 WO 2013026255A1 CN 2012000794 W CN2012000794 W CN 2012000794W WO 2013026255 A1 WO2013026255 A1 WO 2013026255A1
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WO
WIPO (PCT)
Prior art keywords
fan
regeneration
air
runner
heat exchanger
Prior art date
Application number
PCT/CN2012/000794
Other languages
English (en)
French (fr)
Inventor
马军
Original Assignee
Ma Jun
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Priority claimed from CN201110246146.0A external-priority patent/CN102322675B/zh
Priority claimed from CN201110359277XA external-priority patent/CN102401430B/zh
Priority claimed from CN2012100489748A external-priority patent/CN102589193A/zh
Application filed by Ma Jun filed Critical Ma Jun
Publication of WO2013026255A1 publication Critical patent/WO2013026255A1/zh
Priority to US14/187,358 priority Critical patent/US9534798B2/en

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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
    • F24F3/1411—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification by absorbing or adsorbing water, e.g. using an hygroscopic desiccant
    • F24F3/1423—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification by absorbing or adsorbing water, e.g. using an hygroscopic desiccant with a moving bed of solid desiccants, e.g. a rotary wheel supporting solid desiccants
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B01—PHYSICAL OR CHEMICAL PROCESSES OR APPARATUS IN GENERAL
    • B01D—SEPARATION
    • B01D53/00—Separation of gases or vapours; Recovering vapours of volatile solvents from gases; Chemical or biological purification of waste gases, e.g. engine exhaust gases, smoke, fumes, flue gases, aerosols
    • B01D53/02—Separation of gases or vapours; Recovering vapours of volatile solvents from gases; Chemical or biological purification of waste gases, e.g. engine exhaust gases, smoke, fumes, flue gases, aerosols by adsorption, e.g. preparative gas chromatography
    • B01D53/06—Separation of gases or vapours; Recovering vapours of volatile solvents from gases; Chemical or biological purification of waste gases, e.g. engine exhaust gases, smoke, fumes, flue gases, aerosols by adsorption, e.g. preparative gas chromatography with moving adsorbents, e.g. rotating beds
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B01—PHYSICAL OR CHEMICAL PROCESSES OR APPARATUS IN GENERAL
    • B01D—SEPARATION
    • B01D53/00—Separation of gases or vapours; Recovering vapours of volatile solvents from gases; Chemical or biological purification of waste gases, e.g. engine exhaust gases, smoke, fumes, flue gases, aerosols
    • B01D53/26—Drying gases or vapours
    • B01D53/261—Drying gases or vapours by adsorption
    • 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
    • F24F5/00—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater
    • F24F5/0007—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater cooling apparatus specially adapted for use in air-conditioning
    • F24F5/0017—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater cooling apparatus specially adapted for use in air-conditioning using cold storage bodies, e.g. ice
    • F24F5/0021—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater cooling apparatus specially adapted for use in air-conditioning using cold storage bodies, e.g. ice using phase change material [PCM] for storage
    • 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
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E60/00—Enabling technologies; Technologies with a potential or indirect contribution to GHG emissions mitigation
    • Y02E60/14—Thermal energy storage

Definitions

  • the present invention relates to a refrigerating air conditioner, and more particularly to an air conditioning apparatus in which a vapor compression type refrigeration and a wheel dehumidification are coupled.
  • the prior art prior art load of the air conditioner includes two aspects of heat load and wet load, wherein the wet load accounts for 20-40% of the total air conditioner load.
  • the conventional air conditioning device includes an evaporator, a compressor, a condenser, an expansion valve, and a refrigerant. The evaporator reduces the temperature of the air, and the moisture in the air also condenses, and the heat load and the wet load are simultaneously processed.
  • the object of the present invention is to provide an air conditioning apparatus for coupling operation of vapor compression refrigeration and rotary dehumidification in response to the above problems and disadvantages.
  • the coupling device of the present invention is characterized in that the vapor compression refrigeration system can be operated Producing high temperature air with a temperature above 70'C directly serves as the energy source for dehumidification of the rotor.
  • a further object of the present invention is to separate the heat load from the wet load.
  • the vapor compression refrigeration system is not responsible for removing moisture from the air.
  • the vapor compression refrigeration system saves energy due to dehumidification and at the same time, the evaporation temperature is higher than The evaporation temperature of the ordinary vapor compression refrigeration system, the refrigeration efficiency is about 30% higher than that of the ordinary vapor compression refrigeration.
  • a vapor compression refrigeration and a rotary dehumidification coupling air conditioner comprising a rotary dehumidification system and a vapor compression refrigeration system connected by a pipeline
  • the vapor compression refrigeration system is an evaporator, a compressor, a condenser, a closed circuit composed of an expansion valve
  • the rotary dehumidification system comprises a revolving wheel having a regeneration zone and a treatment zone, a processing fan, a regenerative fan and a motor for rotating the revolving wheel, and the processing fan and the regenerative fan are provided with an exhaust vent
  • the condenser comprises a phase Variable condensing heat exchange and subcooling heat exchanger and refrigerant gas cooler
  • the refrigerant gas cooler is mainly responsible for cooling the superheated refrigerant discharged from the compressor into a saturated refrigerant, and the structure thereof is tube-fin heat exchange , consisting of heat exchange tubes and fins, refrig
  • the temperature of the heated air is higher than the saturated condensation temperature of the refrigerant in the refrigeration system.
  • the phase change condensation heat transfer and the subcooling heat exchanger are mainly responsible for condensing the refrigerant from the gaseous state. In the liquid state, after the refrigerant is completely condensed in the heat exchanger, it is further cooled to a supercooled state, and the energy required for the regeneration of the runner is derived from the heat released by the refrigeration process.
  • the phase change condensing heat transfer and the subcooling heat exchanger may be air-cooled heat exchangers, and the structure thereof is a tube-fin heat exchanger, which is composed of a heat exchange tube and fins, and the rotor dehumidification system further includes a front regenerative fan.
  • the air to be treated a is connected to the evaporator, the runner processing area and the processing fan through the pipeline in sequence, and the regeneration air e is sequentially connected to the pre-regeneration fan through the pipeline, the phase change condensation heat exchange and the supercooling heat exchanger, and the refrigerant gas cooling.
  • the evaporator may also be located between the rotor processing zone and the processing fan.
  • the air to be treated a is connected to the runner processing zone, the evaporator and the processing fan through the pipeline in sequence.
  • the flow rate of the pre-regeneration fan is greater than the flow rate of the regenerative fan, the heat transfer area of the phase change condensing heat transfer and the subcooling heat exchanger is larger than the heat exchange area of the refrigerant gas cooler, and the air volume of the pre-regeneration fan is regulated by the temperature measurement and the controller.
  • the pre-regeneration fan makes the air flow through the phase change condensation heat transfer and the subcooling heat exchanger, part of the wind is used as the waste hot air from the phase change condensation heat exchange and between the subcooling heat exchanger and the refrigerant gas cooler.
  • the exhaust vents are discharged to the atmosphere.
  • the regenerative fan heats some of the air that has undergone phase change condensation heat exchange and the supercooled heat exchanger to continue to flow through the refrigerant gas cooler, thereby obtaining high temperature air.
  • the temperature measurement and controller are used to control the air volume of the front fan.
  • the flow rate of the front fan is reduced by adjusting the frequency or voltage of the front fan.
  • the vapor compression refrigeration system is two sets, including the main compression refrigeration system and the secondary compression refrigeration system, the main supercooling heat exchanger and the secondary refrigerant gas cooler. There is an air outlet between the rooms.
  • the air to be treated a is connected to the secondary evaporator, the runner processing zone, the main evaporator and the processing fan through the pipeline, and the regeneration air e is sequentially connected to the pre-regeneration fan through the pipeline, the secondary phase change condensation heat transfer and the Cold heat exchanger, main phase change condensing heat transfer and subcooling heat exchanger, secondary refrigerant gas cooler, main refrigerant gas cooler, runner regeneration zone and regenerative fan.
  • the air to be treated a is sequentially connected to the secondary evaporator, the runner processing area and the processing fan through the pipeline, and the regeneration air e is sequentially connected to the pre-regeneration fan, the secondary phase change condensation heat exchange and the supercooling heat exchange through the pipeline.
  • main phase change condensing heat transfer and subcooling heat exchanger secondary refrigerant gas cooler, main refrigerant gas cooler, runner regeneration zone, main evaporator and regeneration fan.
  • the air to be treated a is connected to the runner processing zone, the main evaporator, the secondary evaporator and the pipeline through the pipeline.
  • Processing fan, regeneration air e is connected to the pre-regeneration fan, sub-phase change condensation heat transfer and subcooling heat exchanger, main phase change condensation heat transfer and subcooling heat exchanger, secondary refrigerant gas cooler, main through the pipeline Refrigerant gas cooler, runner regeneration zone and regenerative fan.
  • phase change condensing heat exchange and the subcooling heat exchanger can be a water-cooled heat exchanger
  • the phase change condensing heat exchange and the subcooling heat exchanger are a shell-and-tube heat exchanger or a plate heat exchanger
  • the variable condensing heat exchange and one side of the supercooled heat exchanger pass the refrigerant, and the other side passes the cooling water.
  • the rotary dehumidification system further includes a cooler, and the air to be treated a is sequentially connected to the runner processing area through the pipeline, and is cooled.
  • the evaporator, the evaporator and the processing fan, and the regeneration air e are sequentially connected to the refrigerant gas cooler, the runner regeneration zone and the regeneration fan through the pipeline.
  • the air a flows through the runner processing zone, the moisture in the air a is adsorbed by the runner, the air becomes dry, and then sequentially passes through the cooler, the evaporator and the processing fan, and is then taken out by the exhaust fan b of the processing fan;
  • the air e is heated by the refrigerant gas cooler, the temperature thereof is higher than the saturated condensation temperature of the refrigerant of the refrigeration system, the hot air flows through the processing area of the runner, and the moisture adsorbed on the runner is taken away by the hot air, and the runner is regenerated.
  • the energy required is derived from the heat released by the refrigerant gas cooler during the refrigeration process, and then discharged from the exhaust vent f to the atmosphere by the regenerative fan, and the adsorbent material on the runner recovers the adsorption capacity.
  • the runner is a two-stage runner
  • the cooler is a two-stage cooler
  • the two-stage runner is rotated by the respective motors, and the air a is processed to be sequentially connected through the pipeline.
  • Regeneration air e is diverted through the refrigerant gas cooler through the pipeline, one through the Class I
  • the regenerative zone is connected to the Class I regenerative fan, and the other stream is connected to the Class II regenerative fan through the ⁇ -stage regenerator.
  • the invention combines a vapor compression refrigeration system with a rotary dehumidification system, and by setting a two-stage condenser, on one hand, the refrigerant is cooled to a supercooled state, and at the same time, the refrigeration system releases a large amount of energy; on the other hand, the revolver is required for dehumidification.
  • the energy is completely derived from the heat released by the refrigeration process, and the temperature is above 70 ⁇ .
  • the heat load and the wet load are separately treated. Since the refrigeration system does not need to be responsible for removing the moisture in the air, the evaporation temperature of the evaporator during operation of the refrigeration system is higher than that of the ordinary refrigeration system.
  • the evaporating temperature during operation is high, and the evaporating temperature of the refrigerating evaporator is about 2-10 ⁇ higher than that of the ordinary refrigerating system.
  • the ratio of the evaporating pressure and the condensing pressure of the evaporative compression refrigeration system is low, and the power consumed by the compressor is low.
  • the vapor compression refrigeration system has high cooling efficiency and low energy consumption.
  • the flow rate of the pre-regeneration fan is greater than the flow rate of the regenerative fan.
  • the condensing heat of the cooling is greater than the cooling capacity generated by the cooling.
  • the air volume used for cooling the condenser is generally the air volume of the cooling process through the evaporator. More than double.
  • the air volume of the fan passing through the treatment zone is generally more than three times that of the regeneration zone.
  • the special airflow design and the distribution of the air volume ensure that the system ensures the cooling efficiency at the same time. Dehumidification efficiency with the runner.
  • the phase change condensing heat transfer and the heat exchange area of the supercooled heat exchanger are larger than the heat exchange area of the refrigerant gas cooler, and the condensation process is basically carried out under normal pressure conditions.
  • the condensation process is divided into a variable temperature condensation process and a normal temperature condensation process.
  • the temperature change condensation process is a refrigerant in which the refrigerant in the superheated state is cooled to a saturated state.
  • the heat released by the process is high, but the heat emitted by the process only accounts for the heat released by the condensation process. 15-20%;
  • the normal temperature condensation process is under constant temperature and constant pressure conditions, the refrigerant is condensed from a gaseous state into a liquid state, and the heat released by this process accounts for 80-85% of the heat of condensation.
  • the supercooled heat exchanger is responsible for releasing a large amount of low-temperature cooling heat, so the required heat exchange area is large, and the refrigerant gas cooler is responsible for releasing the residual heat generated during the cooling process, and this part of the residual heat is occupied by the cooling waste heat.
  • the ratio is low, so the heat exchange area of the refrigerant gas cooler is smaller than that of the supercooled heat exchanger.
  • the temperature measurement and controller are used to control the air volume of the front fan.
  • the temperature of the cooling air after the cooling air passes through the front heat exchanger is as high as possible without affecting the cooling efficiency.
  • the ambient temperature is constantly changing. In the case where the ambient temperature is lowered, the amount of cooling air must be reduced in order to obtain the temperature.
  • Figure 1 is a schematic structural view of the present invention
  • FIG. 2 is a schematic view showing a second structure of the present invention.
  • Figure 3 is a third structural schematic view of the present invention.
  • Figure 4 is a schematic view showing the structure added to Figure 3;
  • Figure 5 is a schematic view of the structure added to Figure 1 ⁇
  • Figure 6 is a schematic view showing the structure added to Figure 1;
  • Fig. 7 is a schematic view showing the structure added to Fig. 2.
  • the invention relates to a vapor compression refrigeration and a rotary dehumidification coupling air conditioner, which comprises a rotor dehumidification system and a vapor compression refrigeration system connected by a pipeline.
  • the vapor compression refrigeration system is a closed loop composed of an evaporator 2, a compressor 3, a phase change condensation heat exchange and a subcooling heat exchanger 4, a refrigerant gas cooler 6, and an expansion valve 5,
  • the variable condensation heat exchange and the structure of the supercooled heat exchanger 4 are tube-fin heat exchangers, which are composed of heat exchange tubes and fins.
  • the rotor dehumidification system includes a reel having a regeneration zone 10 and a treatment zone 8, a processing fan 1, a pre-regeneration fan 13, a regenerative fan 11, and a motor 12 that rotates the reel.
  • the refrigerant gas cooler 6 is mainly responsible for cooling the superheated refrigerant discharged from the compressor 3 into a saturated refrigerant.
  • the structure is a tube-fin heat exchanger composed of a heat exchange tube and fins, and the refrigerant is in the tube.
  • the air flowing and cooling the refrigerant flows outside the tube, the temperature of the heated air is higher than the saturated condensation temperature of the refrigerant of the refrigeration system, the phase change condensation heat exchange and the supercooling heat exchanger 4 are mainly responsible for condensing the refrigerant from the gaseous state into The liquid is liquid and the refrigerant is further cooled to a supercooled state in the phase change condensation heat exchange and subcooling heat exchanger 4, and the energy required for the regeneration of the rotor is derived from the heat released by the vapor compression refrigeration process.
  • the air a flows through the evaporator 2, and then passes through the rotor processing area 8 and the processing fan 1 in sequence, and is discharged from the exhaust port b of the processing fan 1; the regeneration air e passes through the pre-regeneration fan 13, phase change condensation heat transfer and supercooling
  • the heat exchanger 4, the refrigerant gas cooler 6, the runner regeneration zone 10, and the regeneration fan 11, are discharged from the exhaust port f to the atmosphere, the phase change condensation heat exchange, and the supercooling heat exchanger 4 and the refrigerant gas cooler 6 There is an air outlet between them.
  • the evaporator 2 is adjusted between the runner processing area 8 and the processing fan 1, and the air a flows through the runner processing area 8, and then sequentially passes through the evaporator 2 and processes.
  • the fan 1 is discharged by the exhaust port b of the processing fan 1.
  • the phase change condensing heat exchange and the subcooling heat exchanger 4 are a shell-and-tube heat exchanger or a plate heat exchanger, a phase change condensing heat exchange and a side pass refrigerant of the supercooling heat exchanger 4. , the other side is connected to cooling water,
  • the rotor dehumidification system includes a rotor having a regeneration zone 10 and a treatment zone 8, a treatment fan 1, a cooler 7, a regeneration fan 11, and a motor 12 that drives the rotation of the wheel.
  • the air a flows through the rotor processing zone 8, and is sequentially discharged through the cooler 7, the evaporator 2, the processing fan 1, and the exhaust port b; the regeneration air e passes through the refrigerant gas cooler 6, the regeneration zone 10, and the regeneration
  • the fan 11 is discharged from the air outlet f to the atmosphere.
  • the present invention adds a set of runners and cooling to the basis of FIG.
  • the rotor dehumidification system includes a Class I runner, a Class II runner, a processing fan 1, a Class I runner regeneration zone 17, a Class I cooler 14, a Class II regeneration fan 11, and a Class II cooling. 7 and the motor, the two-stage runner rotates under the respective motors, and the air a flows through the I-stage runner processing zone 18, the class I cooler 14, the class II runner processing zone 8, and the class II cooler 7 in sequence.
  • the regeneration air e is heated by the refrigerant gas cooler 6 and then branched, and one flow passes through the I-stage regenerator regeneration zone 17 and the I-stage regeneration fan 20, and then The exhaust port g is discharged to the atmosphere, and the other stream flows through the second-stage runner regeneration zone 10 and the class II regeneration fan 11, and is then mixed from the exhaust port f to the atmosphere.
  • the vapor compression refrigeration system is two sets, including the main compression refrigeration system and the secondary compression refrigeration system, the main phase change condensation heat transfer and the supercooling heat exchanger 41 and An exhaust vent is provided between the secondary refrigerant gas coolers 62.
  • the air a is sequentially connected to the secondary evaporator 22, the rotary processing zone 8, the main evaporator 21 and the processing fan 1 through the pipeline, and is discharged by the exhaust vent b, and the regeneration air e is sequentially connected to the front through the pipeline.
  • Regenerative fan 13 secondary phase change condensing heat exchange and subcooling heat exchanger 42, main phase change condensing heat exchange and subcooling heat exchanger 41, secondary refrigerant gas cooler 62, main refrigerant gas cooler 61, runner
  • the regeneration zone 10 and the regeneration fan 11 are discharged from the exhaust port f to the atmosphere.
  • the air a is sequentially connected to the secondary evaporator 22, the rotary treatment zone 8 and the processing fan 1 through the pipeline, and is discharged by the exhaust vent b, and the regeneration air e is sequentially connected to the pre-regeneration fan 13 through the pipeline.
  • the evaporator 21 and the regeneration fan 11 are discharged to the atmosphere from the exhaust port f.
  • the air to be treated a is sequentially connected to the rotor processing area 8, the main evaporator 21, the secondary evaporator 22, and the processing fan 1 through the pipeline, and is discharged by the exhaust port b, and the regeneration air e is sequentially passed through the pipeline.
  • the pre-regeneration fan 13 is connected, the secondary phase change condensation heat exchange and subcooling heat exchanger 42, the main phase change condensation heat exchange and the subcooling heat exchanger 41, the secondary refrigerant gas cooler 62, and the main refrigerant gas cooler 61
  • the runner regeneration zone 10 and the regeneration fan 11 are discharged from the exhaust vent f to the atmosphere.

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Abstract

一种蒸汽压缩式制冷与转轮除湿耦合空调装置，包括通过管道连接的转轮除湿系统和压缩制冷系统。蒸汽压缩式制冷系统包括蒸发器（2）、压缩机（3）、相变冷凝换热及过冷换热器（4）、制冷剂气体冷却器（6）和膨胀阀（5）。转轮除湿系统包括具有再生区（10）和处理区（8）的转轮、处理风机（1）、再生风机（11）和带动转轮旋转的电机（12）。本申请中转轮除湿所需的能源完全来自制冷过程释放的热量，从而降低能耗，同时将热负荷和湿负荷分开作业，蒸汽压缩式制冷系统无需负责除去空气中的水分。

Description

蒸汽 縮式制冷与转轮除绿耦食空调装囂 _ 本发明所屑技术领墚 本发明涉及制冷空调， 具体是蒸汽压缩式制冷与转轮除湿耦合运行的空调装置。 在本发明之前的现有技术 空调装置的负荷包括热负荷和湿负荷两个方面， 其中湿负荷在总的空调负荷中占 2 0-40%。 传统的空调装置包括蒸发器、 压缩机、 冷凝器、 膨胀阀及制冷剂， 蒸发器使空气 温度降低的同时空气中的水分也会出现冷凝， 实现热负荷和湿负荷同时处理， 这中情况 下压缩机消耗的功率高， 蒸汽压缩式制冷系统的制冷效率低； 而冷凝器则散发出大量热 量， 通常情况下这些热空气直接排向大气。 本发明目的 本发明的目的在于针对上述存在的问题和不足， 提供一种蒸汽压缩式制冷与转轮除湿 耦合运行的空调装置， 本发明耦合装置的特征在于， 蒸汽压縮式制冷系统工作时可以产生 温度在 70'C以上的高温空气直接作为转轮除湿所需的能源。
本发明的进一步目的是将热负荷和湿负荷分开作业， 蒸汽压缩式制冷系统无需负责除 去空气中的水分， 由此， 蒸汽压缩式制冷系统节省了由于除湿消耗的能源， 同时， 蒸发温 度高于普通的蒸汽压缩式制冷系统的蒸发温度， 制冷效率比普通蒸汽压缩式制冷效率高 30%左右 c 本发明釆用的找术方案
本发明的技术方案如下： 蒸汽压缩制冷与转轮除湿耦合空调装置， 包括通过管道连接的转轮除湿系统和蒸汽 压缩制冷系统， 其中， 蒸汽压缩制冷系统是由蒸发器、 压缩机、 冷凝器、 膨胀阀组成的 闭合回路， 转轮除湿系统包括具有再生区和处理区的转轮、 处理风机、 再生风机及带动 转轮旋转的电机， 处理风机与再生风机设有排风口； 冷凝器包括相变冷凝换热以及过冷 换热器和制冷剂气体冷却器， 制冷剂气体冷却器主要负责将从压缩机排出的过热的制冷 剂冷却成饱和的制冷剂， 其结构形式是管翅式换热器， 由换热管与翅片组成， 制冷剂在 管内流动而冷却制冷剂的空气在管外流动， 被加热的空气温度高于制冷系统的制冷剂的 饱和冷凝温度， 相变冷凝换热以及过冷换热器主要负责将制冷剂从气态冷凝成液态， 制 冷剂在换热器中完全冷凝后， 被进一步冷却到过冷状态， 转轮再生需要的能源来源于制 冷过程释放的热量。
相变冷凝换热以及过冷换热器可以是风冷换热器， 其结构形式是管翅式换热器， 由 换热管与翅片组成， 转轮除湿系统还包括有前置再生风机， 需处理空气 a通过管道依序 连接蒸发器、 转轮处理区与处理风机， 再生空气 e通过管道依序连接前置再生风机、 相 变冷凝换热以及过冷换热器、 制冷剂气体冷却器、 转轮再生区及再生风机， 相变冷凝换 热以及过冷换热器与制冷剂气体冷却器之间设有排风口； 蒸发器也可以位于转轮处理区 与处理风机之间， 需处理空气 a通过管道依序连接转轮处理区、 蒸发器与处理风机。
前置再生风机流量大于再生风机流量， 相变冷凝换热以及过冷换热器换热面积大于 制冷剂气体冷却器的换热面积， 前置再生风机的风量由温度测量与控制器调控。 前置再 生风机使空气流过过相变冷凝换热以及过冷换热器后， 部分风作为废热空气从相变冷凝 换热以及过冷换热器与制冷剂气体冷却器之间设有的排风口排向大气。 再生风机使部分 经过相变冷凝换热以及过冷换热器加热后的空气继续流过制冷剂气体冷却器加热， 由此 获得高温空气。
温度测量与控制器用于控制前置风机的风量， 当测量得到的温度低于设定值的时候， 通过调节前置风机的频率或者电压使前置风机的流速降低
为了使再生温度更高， 整个体统具有更好的运行效率， 蒸汽压縮制冷系统为两套， 包括主压缩制冷系统与次压缩制冷系统， 主过冷换热器与次制冷剂气体冷却器之间设有 排风口。
一种方式， 需处理空气 a通过管道依序连接次蒸发器、 转轮处理区、 主蒸发器与处 理风机， 再生空气 e通过管道依序连接前置再生风机、 次相变冷凝换热以及过冷换热器、 主相变冷凝换热以及过冷换热器、 次制冷剂气体冷却器、 主制冷剂气体冷却器、 转轮再 生区及再生风机。
另一种方式， 需处理空气 a通过管道依序连接次蒸发器、 转轮处理区与处理风机， 再生空气 e通过管道依序连接前置再生风机、 次相变冷凝换热以及过冷换热器、 主相变 冷凝换热以及过冷换热器、 次制冷剂气体冷却器、 主制冷剂气体冷却器、 转轮再生区、 主蒸发器及再生风机。
再一种方式， 需处理空气 a通过管道依序连接转轮处理区、 主蒸发器、 次蒸发器与 处理风机， 再生空气 e通过管道依序连接前置再生风机、 次相变冷凝换热以及过冷换热 器、 主相变冷凝换热以及过冷换热器、 次制冷剂气体冷却器、 主制冷剂气体冷却器、 转 轮再生区及再生风机。
进一步的技术方案是， 相变冷凝换热以及过冷换热器可以是水冷换热器， 相变冷凝 换热以及过冷换热器是管壳式换热器或者是板式换热器， 相变冷凝换热以及过冷换热器 的一側通制冷剂， 另外一側通冷却水， 转轮除湿系统还包括有冷却器， 需要处理的空气 a通过管道依序连接转轮处理区、冷却器、蒸发器与处理风机， 再生空气 e通过管道依序 连接制冷剂气体冷却器、 转轮再生区及再生风机。 空气 a流经过转轮处理区后， 空气 a 中的水分被转轮吸附， 空气变得干燥， 再依序经冷却器、 蒸发器与处理风机后， 由处理 风机排风口 b拌出； 再生空气 e经制冷剂气体冷却器加热后， 其温度高于制冷系统的制 冷剂的饱和冷凝温度， 热空气流过转轮处理区， 吸附在转轮上的水分被热空气带走， 转 轮再生需要的能源来源于制冷剂气体冷却器制冷过程释放的热量， 再经再生风机从排风 口 f排向大气， 转轮上的吸附材料恢复吸附能力。
如果空气 a中的水分含量比较高， 进一步的， 转轮为双级转轮， 冷却器为双级冷却 器， 双级转轮在各自的电机带动下旋转， 需处理空气 a通过管道依序连接 I级转轮处理 区、 I级冷却器、 II级转轮处理区、 II级冷却器、 蒸发器与处理风机； 再生空气 e通过 管道经制冷剂气体冷却器后分流、一支流经 I级转轮再生区与 I级再生风机连通， 另一 支流经 Π级转轮再生区与 II级再生风机连通。
本发明将蒸汽压缩制冷系统与转轮除湿系统联合作业， 通过设置两级冷凝器， 一方 面实现制冷剂冷却到过冷状态， 同时制冷系统释放大量的能源； 另一方面转轮除湿所需 的能源完全来源于制冷过程释放的热量， 温度在 70Ό以上。 通过设置制冷系统与转轮除 湿系统各个部件的位置， 将热负荷和湿负荷分开处理， 由于制冷系统无需要负责除去空 气中的水分， 制冷系统运行时其蒸发器的蒸发温度比普通的制冷系统运行时的蒸发温度 高， 制冷机蒸发器蒸发温度比普通制冷系统的蒸发温度大约高 2-10Ό, 由此， 蒸发压缩 式制冷系统的蒸发压力与冷凝压力之比值低， 压缩机消耗的功率低， 蒸汽压缩式制冷系 统的制冷效率高， 能耗低。
前置再生风机流量大于再生风机流量， 普通的制冷过程中， 制冷冷凝热量大于制冷 产生的冷量， 为了保证制冷效率足够高， 用于冷却冷凝器的风量一般是制冷过程通过蒸 发器风量的 1倍以上。 但是在转轮除湿过程中， 经过处理区的风机风量一般是通过再生 区风量的 3倍以上， 特殊的风量流动设计与风量的分配保证了本系统同时保证制冷效率 与转轮除湿效率。
相变冷凝换热以及过冷换热器换热面积大于制冷剂气体冷却器的换热面积， 冷凝过 程基本是在常压条件下进行。 冷凝过程分成变温冷凝过程与常温冷凝过程， 变温冷凝过 程是过热状态的制冷剂冷却成饱和状态的制冷剂， 此过程释放的热量温度高， 但是此过 程散发出的热量只占冷凝过程释放热量的 15-20%;常温冷凝过程是在恒温与恒压条件下， 制冷剂从气态冷凝成液态， 此过程释放出来的热量占冷凝热的 80~85%。 过冷换热器负责 释放大量的低温的制冷热量， 所以要求的换热面积大， 而制冷剂气体冷却器负责释放制 冷过程中产生的髙温余热， 而由于该部分余热在制冷余热中所占比例低， 所以， 制冷剂 气体冷却器的换热面积比过冷换热器的换热面积小。
温度測量与控制器用于控制前置风机的风量， 为了保证获得高温， 在不影响制冷效 率的前提下， 冷却空气通过前置换热器后冷却空气的温度要求尽可能地高。 但是环境温 度是不断变化的， 在环境温度降低的情况下， 为了获得髙温必须将冷却风风量降低。
下面结合附图对本发明作进一步的说明。
mm
图 1为本发明的一种结构示意图；
图 2为本发明的第二种结构示意图；
图 3为本发明的第三种结构示意图；
图 4为针对图 3增加的结构示意图；
图 5为针对图 1增加的结构示意图 ·，
图 6为针对图 1增加的结构示意图；
图 7为针对图 2增加的结构示意图。
【主要组件符号说明】
I -处理风机， 2-蒸发器， 3-压缩机，
4 -相变冷凝换热以及过冷换热器， 5-膨胀阀， 6-制冷剂气体冷却器
7- II级冷却器， 8- II级转轮处理区， 10- II级转轮再生区，
II- 11级再生风机， 12-电机， 13-再生风机，
14- 1级冷却器， 17- I级转轮再生区， 18- I级转轮处理区，
20- I级再生风机 21-主蒸发器， 31-主压缩机，
41 -主相变冷凝换热以及过冷换热器， 51-主膨胀阀，
6卜主制冷剂气体冷却器 22-次蒸发器， 32-次压缩机， 42 -次相变冷凝换热以及过冷换热器， 52-次膨胀阀，
62-次制冷剂气体冷却器
实摊例
本发明为蒸汽压缩制冷与转轮除湿耦合空调装置， 包括通过管道连接的转轮除湿系 统和蒸汽压缩制冷系统。
如图 1所示， 蒸汽压縮制冷系统是由蒸发器 2、 压缩机 3、 相变冷凝换热以及过冷 换热器 4、 制冷剂气体冷却器 6、 膨胀阀 5组成的闭合回路， 相变冷凝换热以及过冷换热 器 4的结构形式是管翅式换热器， 由换热管与翅片组成。
转轮除湿系统包括具有再生区 10和处理区 8的转轮、 处理风机 1、 前置再生风机 13、 再生风机 11及带动转轮旋转的电机 12。
制冷剂气体冷却器 6主要负责将从压缩机 3排出的过热的制冷剂冷却成饱和的制冷 剂， 其结构形式是管翅式换热器， 由换热管与翅片组成， 制冷剂在管内流动而冷却制冷 剂的空气在管外流动， 被加热的空气温度高于制冷系统的制冷剂的饱和冷凝温度， 相变 冷凝换热以及过冷换热器 4主要负责将制冷剂从气态冷凝成液态并且使制冷剂在相变冷 凝换热以及过冷换热器 4中被进一步冷却到过冷状态， 转轮再生需要的能源来源于蒸汽 压縮式制冷过程释放的热量。
空气 a流经蒸发器 2，再依序经转轮处理区 8与处理风机 1， 由处理风机 1排风口 b 排出； 再生空气 e经前置再生风机 13、 相变冷凝换热以及过冷换热器 4、 制冷剂气体冷 却器 6、 转轮再生区 10及再生风机 11， 从排风口 f排向大气， 相变冷凝换热以及过冷换 热器 4与制冷剂气体冷却器 6之间设有排风口。
如图 2所示， 在图 1的基础上， 将蒸发器 2调于转轮处理区 8与处理风机 1之间， 空气 a流经转轮处理区 8，再依序经蒸发器 2与处理风机 1，由处理风机 1排风口 b排出。
如图 3所示， 相变冷凝换热以及过冷换热器 4是管壳式换热器或者是板式换热器， 相变冷凝换热以及过冷换热器 4的一側通制冷剂， 另外一側通冷却水，
转轮除湿系统包括具有再生区 10和处理区 8的转轮、 处理风机 1、冷却器 7、 再生 风机 11及带动转轮旋转的电机 12。
空气 a流经转轮处理区 8，再依序经冷却器 7、蒸发器 2与处理风机 1,排风口 b排 出； 再生空气 e经制冷剂气体冷却器 6、转轮再生区 10及再生风机 11, 从排风口 f排向 大气。
针对空气 a中的水分含量较大的情况，本发明在图 3的基础上增加一套转轮与冷却 器， 如图 4所示， 转轮除湿系统包括 I级转轮、 II级转轮、处理风机 1、 I级转轮再生区 17、 I级冷却器 14、 II级再生风机 11、 II级冷却器 7及电机， 双级转轮在各自的电机带 动下旋转， 空气 a依序流经 I级转轮处理区 18、 I级冷却器 14、 II级转轮处理区 8、 II 级冷却器 7、蒸发器 2与处理风机 1之后， 由排风口 b排出， 再生空气 e经制冷剂气体冷 却器 6加热后分流， 一支流过 I级转轮再生区 17与 I级再生风机 20后， 从排风口 g排 向大气， 另一支流经 II级转轮再生区 10与 II级再生风机 11后， 从排风口 f拌向大气。
为了使再生温度更高， 整个体统具有更好的运行效率， 蒸汽压缩制冷系统为两套， 包括主压缩制冷系统与次压縮制冷系统， 主相变冷凝换热以及过冷换热器 41与次制冷剂 气体冷却器 62之间设有排风口。
如图 5所示， 空气 a通过管道依序连接次蒸发器 22、 转轮处理区 8、 主蒸发器 21 与处理风机 1, 由排风口 b排出， 再生空气 e通过管道依序连接前置再生风机 13、 次相 变冷凝换热以及过冷换热器 42、主相变冷凝换热以及过冷换热器 41、 次制冷剂气体冷却 器 62、 主制冷剂气体冷却器 61、 转轮再生区 10及再生风机 11, 从排风口 f排向大气。
如图 6所示， 空气 a通过管道依序连接次蒸发器 22、 转轮处理区 8与处理风机 1， 由排风口 b排出， 再生空气 e通过管道依序连接前置再生风机 13、 次相变冷凝换热以及 过冷换热器 42、主相变冷凝换热以及过冷换热器 41、次制冷剂气体冷却器 62、主制冷剂 气体冷却器 61、 转轮再生区 10、 主蒸发器 21及再生风机 11, 从排风口 f排向大气。
如图 7所示， 需处理空气 a通过管道依序连接转轮处理区 8、 主蒸发器 21、 次蒸发 器 22与处理风机 1，， 由排风口 b排出， 再生空气 e通过管道依序连接前置再生风机 13、 次相变冷凝换热以及过冷换热器 42、 主相变冷凝换热以及过冷换热器 41、 次制冷剂气体 冷却器 62、 主制冷剂气体冷却器 61、 转轮再生区 10及再生风机 11, 从排风口 f排向大 气。
上述实施例为本发明较佳的实施方式， 但本发明的实施方式并不受上述实施例的限 制， 其他的任何未背离本发明的精神实质与原理下所作的改变、 修饰、 替代、 组合、 简 化， 均应为等效的置换方式， 都包含在本发明的保护范围之内。

Claims

权 利 要 求 书
1、 蒸汽压缩式制冷与转轮除湿耦合空调装置, 包括通过管道连接的转轮除湿系统和 蒸汽压缩式制冷系统， 其中， 蒸汽压缩式制冷系统是由蒸发器（2)、压缩机（3)、冷凝器、 膨胀阀（5)组成的闭合回路， 转轮除湿系统包括具有再生区（10)和处理区（8)的转轮、 处理风机（1 )、 再生风机（11 )及带动转轮旋转的电机（12)， 处理风机（1 )与再生风机 ( 11 )设有排风口， 其特征在于： 冷凝器包括相变冷凝换热以及过冷换热器（4)和制冷 剂气体冷却器（6)， 制冷剂气体冷却器（6)主要负责将从压缩机 (3)排出的过热的制冷 剂冷却成饱和的制冷剂， 其结构形式是管翅式换热器， 由换热管与翅片组成， 制冷剂在管 内流动而冷却制冷剂的空气在管外流动， 被加热的空气温度高于制冷剂的饱和冷凝温度， 相变冷凝换热以及过冷换热器（4)将制冷剂从气态冷凝成液态并且使制冷剂在相变冷凝 换热以及过冷换热器（4) 中被进一步冷却到过冷状态， 转轮再生需要的能源来源于蒸汽 压缩式制冷过程释放的热量。
2.根据权利要求 1所述的耦合空调装置， 其特征在于： 相变冷凝换热以及过冷换热器 (4) 的结构形式是管翅式换热器， 由换热管与翅片组成， 转轮除湿系统还包括有前置再 生风机（13)， 需处理空气 a通过管道依序连接蒸发器（2)、 转轮处理区 （8)与处理风机 ( 1 ),再生空气 e通过管道依序连接前置再生风机（ 13)、相变冷凝换热以及过冷换热器 (4)、 制冷剂气体冷却器（6)、 转轮再生区 （10)及再生风机（11 ), 相变冷凝换热以及过冷换 热器（4)与制冷剂气体冷却器（6)之间设有排风口。
3.根据权利要求 2述的耦合空调装置， 其特征在于： 蒸发器（2)位于转轮处理区（8) 与处理风机（1 )之间， 需处理空气 a通过管道依序连接转轮处理区 （8)、 蒸发器（2) 与 处理风机（1 )。
4.根据权利要求 2或 3所述的耦合空调装置， 其特征在于： 前置再生风机（13)流量大 于再生风机（11 )流量， 相变冷凝换热以及过冷换热器（4)换热面积大于制冷剂气体冷 却器（6)的换热面积， 前置再生风机（13)的风量由温度测量与控制器调控。
5、 根据权利要求 1所述的耦合空调装置， 其特征在于： 相变冷凝换热以及过冷换热器 (4)是管壳式换热器或者是板式换热器， 相变冷凝换热以及过冷换热器（4)的一侧通制 冷剂， 另外一側通冷却水， 转轮除湿系统还包括有冷却器（7〉， 所述需要处理的空气 a通 过管道依序连接转轮处理区（8)、 冷却器（7)、 蒸发器（2)与处理风机 ( 1 ), 再生空气 e 通过管道依序连接制冷剂气体冷却器（6)、 转轮再生区（10)及再生风机（11 )。
6、 根据权利要求 5所述的耦合空调装置， 其特征在于： 转轮为双级转轮， 冷却器为双 级冷却器， 双级转轮在各自的电机带动下旋转， 需处理空气 a通过管道依序连接 I级转轮 处理区 （18)、 I级冷却器（14)、 II级转轮处理区 （8)、 II级冷却器（7)、蒸发器（2) 与处理风机（1); 再生空气 e通过管道经制冷剂气体冷却器（6)后分流、一支流经 I级转 轮再生区（17)与 I级再生风机（20)连通， 另一支流经 II级转轮再生区（10)与 II级再 生风机 (11)连通。
7、 根据权利要求 2或 3所述的耦合空调装置， 其特征在于： 蒸汽压缩式制冷系统为两 套， 包括主压缩制冷系统与次压缩制冷系统， 主相变冷凝换热以及过冷换热器（41)与次 制冷剂气体冷却器（62)之间设有排风口。
8、根据权利要求 7所述的耦合空调装置， 其特征在于:所述需处理空气 a通过管道依序 连接次蒸发器（22)、 转轮处理区 （8)、 主蒸发器（21)与处理风机（1)， 再生空气 e通过 管道依序连接前置再生风机（13)、 次相变冷凝换热以及过冷换热器（42)、 主相变冷凝换 热以及过冷换热器（41 )、 次制冷剂气体冷却器（62)、 主制冷剂气体冷却器（61 )、 转轮 再生区（10)及再生风机（11)。
9、 根据权利要求 7所述的耦合空调装置， 其特征在于:所述需处理空气 a通过管道依序 连接次蒸发器（22)、 转轮处理区（8)与处理风机（1), 再生空气 e通过管道依序连接前 置再生风机（13)、 次相变冷凝换热以及过冷换热器（42)、 主相变冷凝换热以及过冷换热 器（41)、 次制冷剂气体冷却器（62)、 主制冷剂气体冷却器（61)、 转轮再生区（10)、 主 蒸发器 (21)及再生风机（11)。
10、 根据权利要求 7所述的耦合空调装置， 其特征在于:所述需处理空气 a通过管道依 序连接转轮处理区（8)、 主蒸发器（21)、 次蒸发器（22)与处理风机（1)， 再生空气 e通 过管道依序连接前置再生风机（13)、 次相变冷凝换热以及过冷换热器（42)、 主相变冷凝 换热以及过冷换热器（41)、 次制冷剂气体冷却器（62)、 主制冷剂气体冷却器（61)、 转 轮再生区（10)及再生风机（11)。
PCT/CN2012/000794 2011-08-25 2012-06-11 蒸汽压缩式制冷与转轮除湿耦合空调装置 WO2013026255A1 (zh)

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