CN114893851B - Laboratory fresh air handling unit based on double-evaporation-temperature refrigerating system - Google Patents

Laboratory fresh air handling unit based on double-evaporation-temperature refrigerating system Download PDF

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Publication number
CN114893851B
CN114893851B CN202210567852.3A CN202210567852A CN114893851B CN 114893851 B CN114893851 B CN 114893851B CN 202210567852 A CN202210567852 A CN 202210567852A CN 114893851 B CN114893851 B CN 114893851B
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temperature
fresh air
air
low
valve
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CN114893851A (en
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李钊
童吉华
张蕾
陈剑波
陆雨
肖竣仁
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University of Shanghai for Science and Technology
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University of Shanghai for Science and Technology
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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
    • F24F7/00—Ventilation
    • F24F7/04—Ventilation with ducting systems, e.g. by double walls; with natural circulation
    • F24F7/06—Ventilation with ducting systems, e.g. by double walls; with natural circulation with forced air circulation, e.g. by fan positioning of a ventilator in or against a conduit
    • F24F7/08—Ventilation with ducting systems, e.g. by double walls; with natural circulation with forced air circulation, e.g. by fan positioning of a ventilator in or against a conduit with separate ducts for supplied and exhausted air with provisions for reversal of the input and output systems
    • 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
    • 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
    • F24F11/74—Control systems characterised by their outputs; Constructional details thereof for controlling the supply of treated air, e.g. its pressure for controlling air flow rate or air velocity
    • F24F11/77—Control systems characterised by their outputs; Constructional details thereof for controlling the supply of treated air, e.g. its pressure for controlling air flow rate or air velocity by controlling the speed of ventilators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/70—Control systems characterised by their outputs; Constructional details thereof
    • F24F11/80—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air
    • F24F11/83—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers
    • F24F11/84—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers using valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/70—Control systems characterised by their outputs; Constructional details thereof
    • F24F11/80—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air
    • F24F11/86—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling compressors within refrigeration or heat pump circuits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F12/00—Use of energy recovery systems in air conditioning, ventilation or screening
    • F24F12/001—Use of energy recovery systems in air conditioning, ventilation or screening with heat-exchange between supplied and exhausted air
    • F24F12/002—Use of energy recovery systems in air conditioning, ventilation or screening with heat-exchange between supplied and exhausted air using an intermediate heat-transfer fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F13/00—Details common to, or for air-conditioning, air-humidification, ventilation or use of air currents for screening
    • F24F13/28—Arrangement or mounting of filters
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F13/00—Details common to, or for air-conditioning, air-humidification, ventilation or use of air currents for screening
    • F24F13/30—Arrangement or mounting of heat-exchangers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F3/00—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems
    • F24F3/12—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling
    • F24F3/14—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification
    • F24F3/1405—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 in which the humidity of the air is exclusively affected by contact with the evaporator of a closed-circuit cooling system or heat pump circuit
    • 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
    • F24F3/16—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 purification, e.g. by filtering; by sterilisation; by ozonisation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F5/00—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater
    • F24F5/0007—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater cooling apparatus specially adapted for use in air-conditioning
    • F24F5/001—Compression cycle type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F7/00—Ventilation
    • F24F7/003—Ventilation in combination with air cleaning
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F8/00—Treatment, e.g. purification, of air supplied to human living or working spaces otherwise than by heating, cooling, humidifying or drying
    • F24F8/10—Treatment, e.g. purification, of air supplied to human living or working spaces otherwise than by heating, cooling, humidifying or drying by separation, e.g. by filtering
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/31—Expansion valves
    • F25B41/34—Expansion valves with the valve member being actuated by electric means, e.g. by piezoelectric actuators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • 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
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Combustion & Propulsion (AREA)
  • Chemical & Material Sciences (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Signal Processing (AREA)
  • Sustainable Development (AREA)
  • Fuzzy Systems (AREA)
  • Mathematical Physics (AREA)
  • Fluid Mechanics (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Central Air Conditioning (AREA)

Abstract

The invention relates to a laboratory fresh air handling unit based on a double-evaporation temperature refrigerating system, which comprises: the fresh air duct is provided with a fresh air filter, an air inlet heat recovery heat exchange coil, a high-temperature evaporator, a low-temperature evaporator, a moisture content transmitter, a condensation heat recovery device, a temperature sensor and a fresh air machine; the exhaust air duct is provided with an exhaust filter, an exhaust heat recovery heat exchange coil, an air speed sensor and an exhaust fan; the double-evaporation temperature refrigerating system module comprises a double-suction compressor, a high-temperature electronic expansion valve, a low-temperature electronic expansion valve, a high-temperature side gas-liquid separator, a low-temperature side gas-liquid separator, an electric regulating valve, an electromagnetic valve, a check valve, a condenser, a condensation heat recoverer and a high-temperature evaporator and a low-temperature evaporator; the glycol exhaust heat recovery circulation module comprises an air inlet and exhaust heat recovery heat exchange coil and a solution circulation loop; the air supply quantity and air supply state control module comprises a fan frequency converter, a compressor frequency converter and a main controller connected with the moisture content transmitter, the temperature sensor, the air speed sensor, the fan frequency converter, the compressor frequency converter and the electric regulating valve.

Description

Laboratory fresh air handling unit based on double-evaporation-temperature refrigerating system
Technical Field
The invention relates to a fresh air system, in particular to a laboratory fresh air unit based on a double-evaporation-temperature refrigerating system.
Background
Some toxic or polluting gaseous pollutants are generated in the operation process of a plurality of types of laboratories, so that the laboratory has high requirements on ventilation and air conditioning systems, and particularly high requirements on ventilation systems. The specificity of the laboratory requires that the indoor air inlet in the ventilation system is full fresh air, and the ventilation system can ensure that the indoor pressure state is negative pressure while ensuring that the indoor air exchange times are large. In addition, the exhaust air quantity of the laboratory is dynamically changed according to different working conditions of the exhaust cabinet, so that the ventilation air-conditioning system of the laboratory is a variable air quantity system for ensuring the negative pressure of the laboratory and saving energy. At present, the laboratory ventilation air conditioning system combined with variable air volume mainly has two forms: a direct-current VAV fresh air system is characterized in that the fresh air system is required to bear indoor heat and humidity load, and the system means that a laboratory ventilation system and an air conditioning system are combined. The other is that the VAV fresh air system and the air conditioning system bearing indoor heat and humidity load are respectively arranged, the fresh air is processed to indoor state points, the indoor load is not borne, and the fresh air is only used for meeting the corresponding indoor personnel sanitation, ventilation times and negative pressure requirements.
At present, most laboratories often adopt air conditioning modes respectively set by a VAV fresh air system (fresh air is processed to an indoor state point and does not bear indoor load) and an air conditioning system bearing indoor heat and humidity load, wherein the air conditioning system bearing indoor load is mainly a split air conditioner. The split air conditioner generally adopts a compressor to start and stop to carry out coupling control on indoor temperature and humidity, the main control object is the indoor temperature, the humidity control is only a cooling byproduct, and the indoor humidity condition under the laboratory air conditioning system mode is generally poor. Most laboratory users are more concerned about the quality of a laboratory ventilation system, and the indoor ventilation quality is concerned, and meanwhile, the temperature and humidity control requirements for indoor air are often ignored or met. For the laboratory with higher indoor temperature and humidity control requirements (particularly some laboratories with constant temperature and humidity requirements), a direct-current full fresh air variable air volume air conditioning system mode bearing indoor loads is adopted, compared with a laboratory air conditioning mode respectively set by a VAV fresh air system and an air conditioning system bearing indoor thermal and humidity loads. The laboratory air conditioning system mode has higher requirements on air supply parameters, is more reliable in temperature and humidity control on a laboratory room, and can meet the requirements on indoor personnel sanitation, ventilation times and negative pressure.
As before, the laboratory generally has negative pressure requirements (the negative pressure requirements of the laboratory room are mainly realized by adopting an air volume tracking control method for controlling the difference of air supply and exhaust or a direct pressure control method for directly monitoring the indoor pressure at present, when adopting the air volume tracking control method, attention needs to be paid to the fact that if the fresh air volume calculated according to the difference of the air supply and exhaust is smaller than the fresh air volume required by the indoor personnel hygiene, the fresh air volume is determined according to the minimum fresh air volume required by the personnel hygiene at the moment, and meanwhile, an air outlet is additionally arranged for ensuring the indoor negative pressure. If the direct-current type fresh air variable air volume air conditioning system mode for bearing indoor load is adopted, when the working condition of the indoor exhaust cabinet is changed, the air supply volume of the fresh air machine is correspondingly changed in order to ensure the pressure difference between the indoor and the outdoor, and the moisture content and the temperature of the air supply state point are also necessarily changed, so that the dynamic air supply state parameter puts high demands on the automatic control part of the fresh air unit.
The refrigerating/heating system with double evaporating temperatures is well applied to small and medium-sized buildings at present, and compared with the conventional refrigerating/heating system, the novel refrigerating/heating system has higher unit energy efficiency ratio and remarkable energy-saving benefit. However, in general, laboratories are mostly located in small and medium-sized houses and office buildings, and it is considered to apply the cooling/heating system with double evaporation temperatures to a fresh air handling unit of a laboratory. If the refrigerating and heating machine set is used for treating fresh air sent into a laboratory, the energy consumption of cold energy transmission and distribution of cold water treatment is avoided, and the COP of the machine set is improved, so that compared with the traditional method for treating the fresh air by using chilled water or a common direct expansion machine set, the machine set has remarkable energy-saving benefit theoretically.
However, due to the dynamic change characteristic of the air supply state of the fresh air unit in the laboratory, if the double-evaporation temperature refrigeration/heating system is matched with the direct-current fresh air variable air volume air conditioning system for bearing the indoor load, the requirements of ventilation and air conditioning in the laboratory are met, and how to dynamically adjust the moisture content and the air supply temperature in the air supply state is two problems to be solved. The existing methods for regulating the moisture content mainly comprise two methods: one is to adjust the frequency of the double-suction compressor, and the surface temperature of the high-low temperature evaporator coil is adjusted by changing the frequency of the compressor so as to adjust the moisture content of the air supply, and the other is to adjust the moisture content of the air supply by adjusting the opening degree of the high-low temperature expansion valve. There are studies at present that when the compressor is fixed in frequency and the opening degree of the high-temperature electronic expansion valve is fixed, as the opening degree of the low-temperature electronic expansion valve is increased (the opening degree of the low-temperature electronic expansion valve is within a certain range), the refrigerating capacity of the high-temperature plate exchanger is kept stable, and the refrigerating and dehumidifying capacity of the low-temperature plate exchanger is reduced after the first step (if the capacity of the compressor is matched with the capacity of the high-temperature plate exchanger, the refrigerating capacity of the low-temperature plate exchanger is positively correlated with the opening degree of the low-temperature electronic expansion valve). This phenomenon shows that as the opening of the low-temperature electronic expansion valve increases, the high-temperature plate exchanger can provide stable sensible cooling capacity and the cooling and dehumidifying capacity of the low-temperature plate exchanger increases when the compressor is fixed in frequency and the opening of the high-temperature electronic expansion valve is fixed. The air supply temperature is mainly adjusted by adjusting the reheating quantity of fresh air after cooling and dehumidifying.
In addition, the conventional laboratory fresh air system has the function of exhaust heat recovery, so that part of cold energy carried by low-temperature low-humidity air is wasted.
In addition, no matter whether the fresh air system is required to bear corresponding indoor load or not, the fresh air needs to be subjected to reheating treatment after being cooled and dehumidified in order to meet the requirement of the air supply state point of the fresh air unit. The electric heating mode can lead to cold and hot offset to cause energy waste, and how to recover waste heat for reheating fresh air is a problem worthy of research.
Disclosure of Invention
The invention aims to solve the problems, and aims to provide a laboratory fresh air handling unit based on a double-evaporation-temperature refrigerating system.
The invention provides a laboratory fresh air handling unit based on a double-evaporation-temperature refrigerating system, which is used for controlling the temperature and the humidity in a laboratory and has the characteristics that: the fresh air duct is used for feeding fresh air into the room, and a fresh air filter, an air inlet heat recovery heat exchange coil, a high-temperature evaporator, a low-temperature evaporator, a moisture content transmitter, a condensation heat recoverer, a temperature sensor and a fresh air fan are sequentially arranged in the fresh air duct along the flow direction of the fresh air; the exhaust air duct is stacked above the fresh air duct and is used for indoor exhaust, and an exhaust filter, an exhaust heat recovery heat exchange coil, an air speed sensor and an exhaust fan are sequentially arranged in the exhaust air duct along the exhaust air flowing direction; the double-evaporation temperature refrigerating system module comprises a double-suction compressor, a high-temperature electronic expansion valve, a low-temperature electronic expansion valve, a high-temperature side gas-liquid separator, a low-temperature side gas-liquid separator, an electric regulating valve, a first electromagnetic valve, a check valve, a condenser, a condensation heat recoverer, a high-temperature evaporator and a low-temperature evaporator; the glycol exhaust heat recovery circulation module comprises an air inlet heat recovery heat exchange coil, an exhaust heat recovery heat exchange coil and a solution circulation loop for connecting the air inlet heat recovery heat exchange coil and the exhaust heat recovery heat exchange coil, wherein the solution circulation loop comprises an expansion valve, a liquid supplementing valve, a second electromagnetic valve, a solution circulation pump, a third electromagnetic valve, a fourth electromagnetic valve, a fifth electromagnetic valve, a standby solution circulation pump, a sixth electromagnetic valve and a liquid discharge valve; the air supply quantity and air supply state control module comprises a fan frequency converter connected with a fresh air fan and arranged outside a fresh air duct, a compressor frequency converter connected with a double-suction air compressor and a main controller connected with a moisture content transmitter, a temperature sensor, an air speed sensor, the fan frequency converter, the compressor frequency converter and an electric regulating valve, wherein an input flow direction of the double-suction air compressor is connected with the high-temperature evaporator and the low-temperature evaporator, an output flow direction of the double-suction air compressor is connected with a condensation heat recoverer and a condenser, the output flow direction of the double-suction air compressor is split by the electric regulating valve and a first electromagnetic valve, the split flow is correspondingly connected with the condensation heat recoverer and the condenser, the input flow direction is correspondingly connected with the high-temperature evaporator and the low-temperature evaporator by a high-temperature side air-liquid separator, the high-temperature side air-liquid separator is arranged in a pipe section of the double-suction air compressor, the low-temperature side air-liquid separator is arranged in a pipe section of the double-suction air compressor, the condenser is connected with the high-temperature evaporator and the low-temperature evaporator in the output flow direction, the condenser is correspondingly connected with the condensation heat recoverer and the first electromagnetic valve in the output flow direction, the double-suction air compressor is correspondingly connected with the condensation heat recoverer and the condenser in the high-suction air compressor through the high-temperature evaporator and the high-temperature evaporator, and the high-temperature evaporator and the low-suction air compressor flow is simultaneously arranged in the common air compressor and the two-suction air compressor flow direction and the high-pressure evaporator and the low-suction air compressor flow and the high-level flow and the low-pressure evaporator.
The laboratory fresh air handling unit based on the double-evaporation-temperature refrigerating system provided by the invention can also have the following characteristics: in the double evaporation temperature refrigerating system module, after refrigerant flows through a double suction compressor and is isentropically compressed into high-temperature high-pressure refrigerant steam, the refrigerant steam is divided into two paths through an electric regulating valve and a first electromagnetic valve, one path of superheated steam flows to a condensation heat recoverer and is used for reheating fresh air, the other path of superheated steam directly flows to a condenser, after sensible heat exchange is carried out on the superheated steam flowing to the condenser heat recoverer and the cooled and dehumidified fresh air, the superheated steam is converged with the superheated steam directly flowing to the condenser through a common refrigerant pipeline through a check valve and flows to the condenser, the mixed superheated steam is condensed and released by the condenser and then becomes liquid refrigerant, the liquid refrigerant output by the condenser is divided into two paths, one path of the liquid refrigerant flows to the high-temperature evaporator after being throttled and depressurized by a high-temperature electronic expansion valve, flows to a high-temperature side gas-liquid separator after the heat absorption evaporation of the high-temperature evaporator, the other path of superheated steam flows to a low-temperature evaporator after the throttle and is depressurized by a low-temperature electronic expansion valve, flows to the low-temperature side gas-liquid separator after the evaporation of the low-temperature evaporator, and then flows to the low-temperature side gas-liquid separator after the heat absorption of the low-temperature evaporator.
The laboratory fresh air handling unit based on the double-evaporation-temperature refrigerating system provided by the invention can also have the following characteristics: and a condensed water tray for collecting condensed water on the surface of the coil is further arranged below the high-temperature evaporator and the low-temperature evaporator, and a condensed water drain pipe arranged outside the fresh air pipeline is arranged at the bottom end of the condensed water tray to drain the condensed water.
The laboratory fresh air handling unit based on the double-evaporation-temperature refrigerating system provided by the invention can also have the following characteristics: in the solution circulation loop, an expansion valve, a fluid supplementing valve, a second electromagnetic valve, a solution circulation pump, a third electromagnetic valve and a fourth electromagnetic valve are sequentially arranged on a pipe section flowing from the exhaust heat recovery heat exchange coil to the intake heat recovery heat exchange coil, a branch is further arranged behind the fluid supplementing valve, one end of the branch is arranged between the fluid supplementing valve and the second electromagnetic valve, the other end of the branch is arranged between the third electromagnetic valve and the fourth electromagnetic valve, a fifth electromagnetic valve, a standby solution circulation pump and a sixth electromagnetic valve are sequentially arranged in the branch along the flowing direction, and in the solution circulation loop, a liquid discharging valve is arranged on the pipe section flowing from the intake heat recovery coil to the exhaust heat recovery coil.
The laboratory fresh air handling unit based on the double-evaporation-temperature refrigerating system provided by the invention can also have the following characteristics: in the glycol exhaust heat recovery circulation module, glycol solution is arranged in an air inlet heat recovery heat exchange coil and an exhaust heat recovery heat exchange coil for heat exchange, circulation of the glycol solution is carried out between the air inlet heat recovery heat exchange coil and the exhaust heat recovery heat exchange coil through a solution circulation loop, the glycol solution in the exhaust heat recovery heat exchange coil absorbs low-temperature low-humidity cold energy from exhaust air, a solution circulation pump distributes the glycol solution carrying the low-temperature low-humidity cold energy to the air inlet heat recovery heat exchange coil, then the glycol solution releases the low-temperature cold energy to fresh air in the air inlet heat recovery heat exchange coil to pre-cool the fresh air, and the heated glycol solution flows back to the exhaust heat recovery heat exchange coil again to be cooled by the low-temperature cold energy of exhaust air, so that heat recovery circulation is formed.
The laboratory fresh air handling unit based on the double-evaporation-temperature refrigerating system provided by the invention can also have the following characteristics: wherein in the air supply quantity and air supply state control module, a fan frequency converter is used for adjusting the frequency of a fresh air fan, a compressor frequency converter is used for adjusting the frequency of a double-suction compressor, an electric adjusting valve is used for adjusting the heating capacity of a condensation heat recovery device to fresh air, a high-temperature electronic expansion valve and a low-temperature electronic expansion valve are used for correspondingly adjusting the processing capacity of the high-temperature evaporator and the low-temperature evaporator to the fresh air, a main controller is used for obtaining the induction data of a moisture content transmitter, a temperature sensor and an air speed sensor through a control method combining feedforward control and feedback control, after the actually required fresh air quantity, air supply moisture content and air supply temperature are calculated through a control algorithm, the fan frequency converter, the compressor frequency converter and an electric adjusting valve are correspondingly controlled, and meanwhile, the opening degrees of the high-temperature electronic expansion valve and the low-temperature electronic expansion valve are manually adjusted, the feedforward control is used for controlling the fresh air quantity, the air supply moisture content and the temperature under the variation of the air exhaust quantity, under the feedforward control, the main controller calculates the air exhaust quantity according to the air speed in the air exhaust duct monitored by the air speed sensor in real time, and adopts an air quantity tracking method for controlling the fresh air quantity and the air exhaust quantity difference to ensure the indoor negative pressure requirement, the calculated fresh air quantity required for ensuring the indoor and outdoor pressure difference is calculated by a control algorithm, the main controller compares the calculated fresh air quantity with the minimum fresh air quantity meeting the indoor personnel sanitary requirement, if the calculated fresh air quantity is larger than the minimum fresh air quantity, the indoor actual required fresh air quantity is determined according to the calculated fresh air quantity, otherwise, the indoor actual required fresh air quantity is determined according to the minimum fresh air quantity, after the actual required fresh air quantity is determined, the main controller controls the fresh air quantity fed into a room by controlling the frequency of the fresh air machine through controlling the fan frequency converter, simultaneously, the main controller calculates the moisture content and the temperature of an air supply state point at the fresh air machine after the fresh air quantity is regulated to the actual required fresh air quantity through a control algorithm, correspondingly controls the compressor frequency converter and the electric regulating valve, simultaneously, the opening of the high-temperature electronic expansion valve and the low-temperature electronic expansion valve is manually regulated to correspondingly regulate the moisture content and the temperature of the air supply state point after the fresh air quantity is changed, the feedback control is used for controlling the moisture content and the temperature of the air supply under the condition that the outdoor fresh air state is changed or the feedforward control precision is not high, the moisture content transmitter and the temperature sensor monitor the moisture content of the fresh air after the fresh air flows through the low-temperature evaporator and the temperature after the condensation heat recoverer in real time under the feedback control, the main controller receives monitoring signals, the real-time monitoring values are obtained, the real-time monitoring values are compared with the calculated values obtained through the control algorithm under the actual required fresh air quantity, and the real-time monitoring values of the moisture content and the temperature are correspondingly regulated to the opening of the electric compressor and the high-temperature electronic expansion valve through controlling the electric compressor frequency converter and the electric compressor, and the opening of the air supply temperature is regulated to the actual required electronic expansion valve under the condition that the real-time temperature is regulated.
Effects and effects of the invention
According to the laboratory fresh air handling unit based on the double-evaporation-temperature refrigerating system, the high-temperature evaporator and the low-temperature evaporator in the double-evaporation-temperature refrigerating system module formed by components are used for cooling and dehumidifying fresh air, and a middle heat exchange medium can be omitted, so that lower coil surface temperature can be obtained through lower evaporation temperature, and higher dehumidification capacity and dehumidification capacity are achieved. In addition, the condensation heat recoverer can reheat the fresh air subjected to cooling and dehumidification by utilizing the condensation waste heat of the double-evaporation-temperature refrigerating system module, and the phenomenon that the electric heating is used for bringing out unreasonable energy for cold and heat offset is avoided.
Meanwhile, the invention is attached to the double evaporation temperature refrigerating system module, the dehumidification requirements under different working conditions can be met, when the dehumidification amount of fresh air is large, the frequency of the double suction compressors is increased, the opening of the corresponding electronic expansion valve is adjusted, the evaporation temperature is reduced, the surface temperature of the high-temperature evaporator coil is reduced, the high-temperature evaporator is in a wet working condition running state to assist the low-temperature evaporator in dehumidification, the purpose of deep dehumidification of fresh air is achieved, when the dehumidification amount of fresh air is not high, the frequency of the double suction compressors is reduced, the opening of the corresponding electronic expansion valve is adjusted, the evaporation temperature is increased, the surface temperature of the high-temperature evaporator coil is increased, the high-temperature evaporator is in a dry working condition running state, at the moment, the effect of the high-temperature evaporator is only to cool fresh air, the evaporation temperature of refrigerant in the high-temperature evaporator is higher than that in a wet working condition running state, and the energy efficiency of the double evaporation temperature refrigerating system module is higher than that of the high-temperature evaporator in a wet working condition running state.
In addition, the glycol exhaust heat recovery circulation module composed of the air inlet heat recovery heat exchange coil and the exhaust heat recovery heat exchange coil through the solution circulation loop can be used for precooling or preheating fresh air by recovering exhaust energy, so that the energy consumption and the running cost of the system are reduced.
In addition, the main controller can perform feedforward control on fresh air quantity, air supply moisture content and temperature under the change of air exhaust quantity and perform feedback control on the air supply moisture content and temperature under the influence of factors such as outdoor fresh air state change or deviation of feedforward control by a control method combining feedforward control and feedback control, so that the special ventilation requirement in a laboratory can be met, and the accurate control on the air supply state and the better control on the indoor temperature and humidity state can be realized.
Drawings
FIG. 1 is a schematic diagram of a laboratory fresh air handling unit based on a dual evaporating temperature refrigeration system in an embodiment of the present invention;
FIG. 2 is a flow chart of control by a master controller in an embodiment of the invention;
FIG. 3 is an enthalpy-humidity diagram of a treatment process under a dry working condition of a high-temperature evaporator under a condition that the requirements on fresh air dehumidification are not high in an embodiment of the invention.
Detailed Description
In order to make the technical means and effects of the present invention easy to understand, the present invention will be specifically described with reference to the following examples and the accompanying drawings.
< Example >
Fig. 1 is a schematic structural diagram of a laboratory fresh air handling unit based on a dual-evaporation temperature refrigeration system according to an embodiment of the present invention.
As shown in fig. 1, a laboratory fresh air handling unit 100 based on a dual-evaporation temperature refrigeration system of the present embodiment is used for controlling the temperature and humidity in a laboratory, and can simultaneously meet the higher temperature and humidity control requirements and the special ventilation requirements in the laboratory, and includes a fresh air duct 1, a fresh air filter 2, an intake heat recovery heat exchange coil 3, a high temperature evaporator 4, a low temperature evaporator 5, a moisture content transmitter 6, a condensation heat recovery unit 7, a temperature sensor 8, a fresh air blower 9, a condensation water tray 10, a condensation water drain pipe 11, a condenser 12, a dual-suction air compressor 13, an electric control valve 14, a first electromagnetic valve 15, a check valve 16, a high temperature electronic expansion valve 17, a low temperature electronic expansion valve 18, a low temperature side gas-liquid separator 19, a high temperature side gas-liquid separator 20, an exhaust duct 21, an exhaust filter 22, an exhaust heat recovery heat exchange coil 23, an air speed sensor 24, an exhaust fan 25, a solution circulation loop 26, an expansion valve 27, a liquid supplementing valve 28, a second electromagnetic valve 29, a solution circulation pump 30, a third electromagnetic valve 31, a fourth electromagnetic valve 32, a fifth electromagnetic valve 33, a sixth electromagnetic valve 33, a frequency converter 35, a liquid drain valve 37, a standby electromagnetic valve 39, and a main control valve 37.
The fresh air duct 1 is used for feeding fresh air into a room, and a fresh air filter 2, an air inlet heat recovery heat exchange coil 3, a high-temperature evaporator 4, a low-temperature evaporator 5, a moisture content transmitter 6, a condensation heat recovery device 7, a temperature sensor 8 and a fresh air fan 9 are sequentially arranged in the fresh air flowing direction.
In this embodiment, the treatment process of the fresh air in the fresh air duct 1 is as follows:
Fresh air enters the fresh air duct 1 and then flows through the fresh air filter 2, carried particles are removed through filtration of the fresh air filter 2, then flows through the air inlet heat recovery heat exchange coil 3 and performs sensible heat exchange with glycol solution in the fresh air, and the air inlet heat recovery heat exchange coil 3 transmits air exhaust cold energy recovered through glycol air exhaust heat recovery circulation to the fresh air, so that the purpose of pre-cooling the fresh air is achieved.
The fresh air immediately flows through the high temperature evaporator 4 after being filtered and precooled. When the fresh air dehumidifying amount is not large, the frequency of the double air suction compressors 13 is regulated, the opening of the corresponding electronic expansion valve 17 is regulated, the evaporating temperature is increased, the surface temperature of the coil pipe of the high-temperature evaporator 4 is increased (higher than the dew point temperature of the fresh air contacted with the coil pipe), the coil pipe is in a dry working condition running state, and the high-temperature evaporator 4 plays a role in secondary pre-cooling of the fresh air. When the fresh air dehumidifying amount is large, the frequency of the double air suction compressors 13 is adjusted, the opening of the high-temperature electronic expansion valve 17 is adjusted, the evaporating temperature is reduced, the surface temperature of the coil pipe of the high-temperature evaporator 4 is reduced (lower than the dew point temperature of the fresh air contacted with the coil pipe), the coil pipe is in a wet working condition running state, and the high-temperature evaporator 4 plays roles of cooling the fresh air and assisting in dehumidifying.
After the fresh air flows through the high-temperature evaporator 4 and is subjected to secondary precooling (constant-humidity cooling) or cooling and dehumidifying, the fresh air immediately flows through the low-temperature evaporator 5 for heat-humidity exchange. Namely, the purposes of cooling fresh air and deeply dehumidifying are realized through the low-temperature evaporator 5.
After the fresh air passes through the low-temperature evaporator 5 to be cooled and deeply dehumidified, the fresh air immediately passes through the condensation heat recoverer 7 to perform sensible heat exchange. The fresh air is heated by the condensation heat recoverer 7, namely, the purpose of reheating (equal humidity heating) the fresh air is realized through the condensation heat recoverer 7.
After the fresh air flows through the condensation heat recoverer 7 and is reheated, the fresh air flows to the fresh air blower 9, and is sent into a room by the fresh air blower 9.
A condensate tray 10 for collecting condensate water on the surface of the coil is also arranged below the high-temperature evaporator 4 and the low-temperature evaporator 5, and a condensate water drain pipe 11 arranged outside the fresh air pipeline 1 is arranged at the bottom end of the condensate tray 10 to drain the condensate water.
In this embodiment, condensed water on the surface of the pipes in the process of treating fresh air by the high-temperature evaporator 4 and the low-temperature evaporator 5 falls into the condensed water tray 10 under the action of gravity, and finally is discharged from the condensed water drain pipe 11.
The dual evaporation temperature refrigeration system module includes a dual suction compressor 13, a high temperature electronic expansion valve 17, a low temperature electronic expansion valve 18, a high temperature side gas-liquid separator 20, a low temperature side gas-liquid separator 19, an electric control valve 14, a first solenoid valve 15, a check valve 16, a condenser 12, a condensation heat recovery device 7, a high temperature evaporator 4, and a low temperature evaporator 5.
The input flow direction of the double suction compressor 13 is connected with the high temperature evaporator 4 and the low temperature evaporator 5, the output flow direction is connected with the condensation heat recoverer 7 and the condenser 12,
The output flow direction of the double suction compressor 13 is split by an electric regulating valve 14 and a first electromagnetic valve 15, and is correspondingly connected with the condensation heat recoverer 7 and the condenser 12 after split, the input flow direction is correspondingly connected with the high temperature evaporator 4 and the low temperature evaporator 5 by a high temperature side gas-liquid separator 20 and a low temperature side gas-liquid separator 19,
The high temperature side gas-liquid separator 19 is provided in a pipe section flowing from the high temperature evaporator 4 to the double suction compressor 13, the low temperature side gas-liquid separator 19 is provided in a pipe section flowing from the low temperature evaporator 5 to the double suction compressor 13,
The output flow direction of the condenser 12 is connected with the high-temperature evaporator 4 and the low-temperature evaporator 5, the input flow direction is connected with a refrigerant public pipeline, the refrigerant public pipeline is connected with the condensation heat recoverer 7 and is simultaneously connected with the double-suction compressor 13 through a first electromagnetic valve 15 for converging and conveying the two branches after the double-suction compressor 13 is split,
A check valve 16 is provided between the condensation heat recoverer 7 and the refrigerant common line,
The high-temperature electronic expansion valve 17 is provided in a pipe section flowing from the condenser 12 to the high-temperature evaporator 4,
The low-temperature electronic expansion valve 18 is provided in a pipe section flowing from the condenser 12 to the low-temperature evaporator 5.
In the double evaporation temperature refrigerating system module, after refrigerant flows through the double suction compressors 13 and is isentropically compressed into high-temperature high-pressure refrigerant steam, the refrigerant steam is divided into two paths through the electric regulating valve 14 and the first electromagnetic valve 15, one path of superheated steam flows to the condensation heat recoverer 7 for reheating fresh air, the other path of superheated steam directly flows to the condenser 12, the superheated steam flowing to the condensation heat recoverer 7 performs sensible heat exchange with the cooled and dehumidified fresh air, the superheated steam is converged with the superheated steam directly flowing to the other path of condensation heat recoverer 12 through the check valve 16 and flows to the condensation heat recoverer 12 through a common refrigerant pipeline,
The mixed superheated steam is condensed and released heat in the condenser 12 and becomes liquid refrigerant, the liquid refrigerant output by the condenser is divided into two paths, one path of the liquid refrigerant is throttled and depressurized by the high-temperature electronic expansion valve 17 and flows to the high-temperature evaporator 4, the high-temperature vapor-liquid separator 20 is subjected to heat absorption and evaporation by the high-temperature evaporator 4, then the mixed superheated steam flows back to the double-suction compressor 13 through the high-temperature side vapor-liquid separator 20, the other path of the liquid refrigerant is throttled and depressurized by the low-temperature electronic expansion valve 18 and flows to the low-temperature evaporator 5, the liquid refrigerant is subjected to heat absorption and evaporation by the low-temperature evaporator 5 and flows to the low-temperature side vapor-liquid separator 19, and then the liquid refrigerant flows back to the double-suction compressor 13 through the low-temperature side vapor-liquid separator 19.
The exhaust air duct 21 is stacked above the fresh air duct 1 and used for indoor exhaust, and an exhaust filter 22, an exhaust heat recovery heat exchange coil 23, an air speed sensor 24 and an exhaust fan 25 are sequentially arranged in the exhaust air flowing direction.
The glycol exhaust heat recovery circulation module comprises an air intake heat recovery heat exchange coil 3, an exhaust heat recovery heat exchange coil 23 and a solution circulation loop 26 for connecting the air intake heat recovery heat exchange coil 3 and the exhaust heat recovery heat exchange coil 23, wherein the solution circulation loop 26 comprises an expansion valve 27, a liquid supplementing valve 28, a second electromagnetic valve 29, a solution circulation pump 30, a third electromagnetic valve 31, a fourth electromagnetic valve 32, a fifth electromagnetic valve 33, a standby solution circulation pump 34, a sixth electromagnetic valve 35 and a liquid draining valve 36.
In the solution circulation loop 26, an expansion valve 27, a fluid supplementing valve 28, a second electromagnetic valve 29, a solution circulation pump 30, a third electromagnetic valve 31 and a fourth electromagnetic valve 32 are sequentially arranged on a pipe section flowing from the exhaust heat recovery heat exchange coil 23 to the intake heat recovery heat exchange coil 3, a branch is further arranged behind the fluid supplementing valve 28, one end of the branch is arranged between the fluid supplementing valve 28 and the second electromagnetic valve 29, the other end of the branch is arranged between the third electromagnetic valve 31 and the fourth electromagnetic valve 32, a fifth electromagnetic valve 33, a standby solution circulation pump 34 and a sixth electromagnetic valve 35 are sequentially arranged in the branch along the flowing direction,
In the solution circulation loop 26, a drain valve 36 is provided on a pipe section from the intake heat recovery coil 3 to the exhaust heat recovery coil 23.
In the glycol exhaust heat recovery circulation module, glycol solution is arranged in an air inlet heat recovery heat exchange coil 3 and an exhaust heat recovery heat exchange coil 23 for heat exchange, the air inlet heat recovery heat exchange coil 3 and the exhaust heat recovery heat exchange coil 23 are connected through a solution circulation loop 26 for circulation of the glycol solution,
The glycol solution in the exhaust heat recovery heat exchange coil 23 absorbs the low-temperature low-humidity cold energy from the exhaust air, the solution circulating pump 30 conveys the glycol solution carrying the low-temperature low-humidity cold energy to the intake heat recovery heat exchange coil 3, then the glycol solution releases the low-temperature cold energy to fresh air in the intake heat recovery heat exchange coil 3 to pre-cool the fresh air, and the heated glycol solution flows back to the exhaust heat recovery heat exchange coil 23 again to be cooled by the low-temperature cold energy of the exhaust air, so that heat recovery circulation is formed.
The air supply quantity and air supply state control module comprises a fan frequency converter 37 connected with the fresh air fan 9 and arranged outside the fresh air duct 1, a compressor frequency converter 38 connected with the double-suction air compressor 13, and a main controller 39 connected with the moisture content transmitter 6, the temperature sensor 8, the air speed sensor 24, the fan frequency converter 37, the compressor frequency converter 38 and the electric regulating valve 14.
In the air supply quantity and air supply state control module, a fan frequency converter 37 is used for adjusting the frequency of the fresh air fan 9, a compressor frequency converter 38 is used for adjusting the frequency of the double-suction compressor 13, an electric adjusting valve 14 is used for adjusting the heating capacity of the condensation heat recoverer 7 on fresh air, a high-temperature electronic expansion valve 17 and a low-temperature electronic expansion valve 18 are used for correspondingly adjusting the processing capacity of the high-temperature evaporator 4 and the low-temperature evaporator 5 on fresh air,
After obtaining the sensing data of the moisture content transmitter 6, the temperature sensor 8 and the wind speed sensor 24 and calculating the fresh air quantity, the air supply moisture content and the air supply temperature actually required through a control algorithm, the main controller 39 correspondingly controls the fan frequency converter 37, the compressor frequency converter 38 and the electric regulating valve 14 through a control method combining feedforward control and feedback control, and simultaneously manually regulates the opening degrees of the high-temperature electronic expansion valve 17 and the low-temperature electronic expansion valve 18 so that the air supply quantity and the air supply state meet the actually required requirements.
Fig. 2 is a flow chart of control by the master controller in an embodiment of the invention.
As shown in fig. 2, the feedforward control is used to control the fresh air volume, the air supply moisture content and the temperature under the change of the exhaust air volume, and the feedback control is used to control the air supply moisture content and the temperature under the influence of factors such as the change of the outdoor fresh air state or the low feedforward control precision.
Under feedforward control, the main controller 39 calculates the air discharge volume according to the air speed in the air discharge duct 21 monitored by the air speed sensor 24 in real time, and adopts an air volume tracking method for controlling the fresh air supply volume and the air discharge volume difference to ensure the indoor negative pressure requirement (generally 80% -90% of the fresh air volume), the calculated fresh air volume required for ensuring the indoor and outdoor pressure difference is calculated through a control algorithm, the main controller 39 compares the calculated fresh air volume with the minimum fresh air volume meeting the indoor personnel hygiene requirement, if the calculated fresh air volume is larger than the minimum fresh air volume, the indoor actual required fresh air volume is determined according to the calculated fresh air volume, otherwise, the indoor actual required fresh air volume is determined according to the minimum fresh air volume, after the actual required fresh air volume is determined, the main controller 39 controls the fresh air volume fed into the room by controlling the frequency converter 37 to regulate the frequency of the fresh air fan 9, meanwhile, the main controller 39 calculates the moisture content and the temperature of the air supply state point located at the fresh air fan 9 after being regulated to the actual required fresh air volume through a control algorithm, and correspondingly controls the compressor frequency converter 38 and the electric regulating valve 14, and meanwhile, the opening degree of the high-temperature electronic expansion valve 17 and the low-temperature electronic expansion valve 18 are manually regulated, and the humidity state is correspondingly changed.
In this embodiment, after the main controller 39 calculates the moisture content and the temperature of the air supply status point located at the fresh air machine 9 after the air volume is adjusted to the actual required fresh air volume through the control algorithm, the main controller 39 correspondingly adjusts the frequency of the dual air suction compressor 13 and the opening of the electric adjusting valve 14 by controlling the compressor frequency converter 38 and the electric adjusting valve 14, and simultaneously manually adjusts the opening of the high-temperature electronic expansion valve 17 and the opening of the low-temperature electronic expansion valve 18 so as to correspondingly adjust the cooling and dehumidifying capacities of the high-temperature evaporator 4 and the low-temperature evaporator 5 (when the fresh air dehumidifying requirement is high, the high-temperature evaporator 4 can play a role of assisting in dehumidifying) and the reheating capacity of the condensation heat recoverer 7 at the same time), thereby realizing the corresponding adjustment of the parameters (moisture content and temperature) of the air supply status point after the fresh air volume is changed.
Under feedback control, the moisture content transmitter 6 and the temperature sensor 8 monitor the moisture content of fresh air flowing through the low-temperature evaporator 5 and the temperature flowing through the condensation heat recoverer 7 in real time, and transmit monitoring signals to the main controller 39 in real time, the main controller 39 receives the monitoring signals to obtain real-time monitoring values, the real-time monitoring values of the moisture content and the temperature are compared with calculated values obtained through a control algorithm under the actual required fresh air quantity, if the real-time monitoring values and the calculated values are different, the main controller 39 correspondingly adjusts the frequency of the double-suction compressor 13 and the opening of the electric regulating valve 14 by controlling the compressor frequency converter 38 and the electric regulating valve 14, and manually adjusts the opening of the high-temperature electronic expansion valve 17 and the opening of the low-temperature electronic expansion valve 18, so as to adjust the moisture content of air supply and the air supply temperature to the calculated values under the actual required fresh air quantity.
In this embodiment, when the real-time monitoring value is different from the calculated value under the actual required fresh air volume, the main controller 39 correspondingly adjusts the frequency of the dual suction compressors 13 and the opening of the electric adjusting valve 14 by controlling the compressor frequency converter 38 and the electric adjusting valve 14, and simultaneously manually adjusts the opening of the high-temperature electronic expansion valve 17 and the opening of the low-temperature electronic expansion valve 18 so as to correspondingly adjust the cooling and dehumidifying capacities of the high-temperature evaporator 4 and the low-temperature evaporator 5 (when the fresh air dehumidifying requirement is high, the high-temperature evaporator 4 can play a role of assisting in dehumidifying) and the reheating capacity of the condensation heat recoverer 7, thereby effectively ensuring that the air supply state point parameter can be timely adjusted to the calculated value under the corresponding fresh air volume under the influence of the state change of outdoor fresh air or the deviation of feedforward control.
In this embodiment, when the requirement on fresh air dehumidification is not high (the high temperature evaporator runs under dry working conditions), the working conditions of the indoor exhaust cabinet change (hereinafter, the indoor exhaust amount is suddenly increased for example), and the outdoor fresh air state parameter is stable, the steps to be adjusted of the laboratory fresh air unit based on the double-evaporation temperature refrigeration system are as follows:
When the indoor air discharge amount suddenly increases and the outdoor fresh air state parameter is stable, the air speed sensor 24 monitors the air speed of the air discharge duct and transmits the measured value to the main controller 39. After receiving the measured value of the wind speed sensor 24, the main controller 39 calculates the air output in the air exhaust duct 21 at this time, adopts an air output tracking method for controlling the fresh air output and the air output difference to ensure the indoor negative pressure requirement (generally 80% -90% of the fresh air output), and calculates the calculated fresh air output required for ensuring the indoor and outdoor pressure difference through a control algorithm. The main controller 39 needs to compare the calculated fresh air volume calculated at this time with the minimum fresh air volume satisfying the indoor personal hygiene requirement, and if the calculated fresh air volume is greater than the minimum fresh air volume, the indoor actual required fresh air volume is determined according to the calculated fresh air volume, whereas the indoor actual required fresh air volume is determined according to the minimum fresh air volume.
After the main controller 39 determines the corresponding actual required fresh air volume through calculation and comparison (assuming that the fresh air volume calculated by the control algorithm is larger than the minimum fresh air volume at this time), the main controller 39 transmits a control signal of the required air volume to the fan frequency converter 37, and after the fan frequency converter 37 receives the control signal, the rotation speed of the fresh air fan 9 is increased through frequency conversion, so that the fresh air volume is correspondingly increased.
Further, after the main controller 39 determines the corresponding required fresh air volume through corresponding calculation and comparison, the main controller 39 calculates and determines the moisture content and the temperature of the air supply state point after the fresh air volume is adjusted through a control algorithm according to the actual required fresh air volume, the indoor heat and humidity load and the designed indoor state point parameters, and at this time, the moisture content and the temperature of the calculated air supply state point should be increased. After the main controller 39 determines the humidity and temperature of the air supply state after the fresh air volume is adjusted by the control algorithm, the processing signals are correspondingly transmitted to the compressor inverter 38 and the electric control valve 14. After receiving the control signal of the main controller 39, the compressor frequency converter 38 and the electric control valve 14 correspondingly adjust the frequency of the double suction compressor 13 and the opening of the electric control valve 14, and simultaneously manually adjust the opening of the high-temperature electronic expansion valve 17 and the low-temperature electronic expansion valve 18, correspondingly change the cooling capacity of the high-temperature evaporator 4 and the cooling and dehumidifying capacity of the low-temperature evaporator 5 (by changing the surface temperature of the coil pipe of the high-temperature evaporator and the low-temperature evaporator), and adjust the reheating capacity of the condensation heat recoverer 7, thereby realizing the corresponding adjustment of the air supply state point parameters (moisture content and temperature) after the fresh air volume is increased.
Further, the moisture content transducer 6 and the temperature sensor 8 monitor in real time the moisture content (i.e., the moisture content of the feed air) of the fresh air flowing through the low temperature evaporator 5 and the temperature (i.e., the temperature of the feed air) of the fresh air flowing through the condensation heat recoverer 7, and transmit respective monitoring signals to the main controller 39 in real time. The main controller 3 receives the detection signals of the moisture content transmitter 6 and the temperature sensor 8, compares the measured value with the calculated value of the moisture content and the temperature of the air supply obtained by a control algorithm under the corresponding fresh air quantity, if the measured value of the moisture content and the temperature are different from the calculated value under the corresponding fresh air quantity,
The main controller 39 transmits the processing signals to the compressor inverter 38 and the electric control valve 14, respectively. After receiving the control signal of the main controller 39, the compressor frequency converter 38 and the electric control valve 14 correspondingly adjust the frequency of the double suction compressor 13 and the opening of the electric control valve 14, and simultaneously manually adjust the opening of the high-temperature electronic expansion valve 17 and the low-temperature electronic expansion valve 18, correspondingly adjust the cooling capacity of the high-temperature evaporator 4 and the cooling and dehumidifying capacity of the low-temperature evaporator 5 (by changing the surface temperature of the coil pipe of the high-temperature evaporator and the low-temperature evaporator) and adjust the reheating capacity of the condensation heat recoverer 7, thereby effectively ensuring that the air supply parameter can be timely adjusted to the calculated value corresponding to the fresh air quantity through feedback control under the condition that the control precision of feedforward control has deviation.
FIG. 3 is an enthalpy-humidity diagram of a treatment process under a dry working condition of a high-temperature evaporator under a condition that the requirements on fresh air dehumidification are not high in an embodiment of the invention.
As shown in fig. 3, point W is an outdoor state point, point N is an indoor state point, point W 1 is a state point after fresh air flows through the intake heat recovery heat exchange coil 3, point W 2 is a state point after fresh air flows through the high temperature evaporator 4, point L is a state point after fresh air flows through the low temperature evaporator 5, point O is an air supply state point, point L 1 is a state point after fresh air flows through the low temperature evaporator 5 after fresh air volume is increased, and point O 1 is a new air supply state point after fresh air volume is increased; the point W 3 is the state point of the fresh air flowing through the air inlet heat recovery heat exchange coil 3 after the fresh air quantity is increased, the point W 4 is the state point of the fresh air flowing through the high temperature evaporator 4 after the fresh air quantity is increased,
Under the dry working condition of the high-temperature evaporator, the fresh air enters from the outdoor state point W and reaches the state point W 1 after sensible heat exchange of the air inlet heat recovery heat exchange coil 3, then reaches the state point W 2 after constant humidity cooling of the high-temperature evaporator 4, reaches the state point L after heat humidity exchange of the low-temperature evaporator 5, finally reaches the air supply state point O after the fresh air is reheated (heated with constant humidity) by the condensation heat recoverer 7, and the indoor state point N is reached by air supply of the fresh air blower 9,
When the indoor air discharge volume suddenly increases and the outdoor state point W is stable, the main controller 39 controls the fresh air volume to increase, calculates and determines the moisture content and the temperature of the air supply state point after the fresh air volume is adjusted through a control algorithm, and at this time, the calculated moisture content and temperature of the air supply state point should be increased, and the main controller 39 correspondingly changes the cooling capacity of the high-temperature evaporator 4 and the cooling and dehumidifying capacity of the low-temperature evaporator 5 (by changing the surface temperature of the coil of the high-temperature evaporator) and adjusts the reheating capacity of the condensation heat recoverer 7 by correspondingly adjusting the frequency of the double-suction compressor 13 and the opening of the electric control valve 14, and simultaneously manually adjusts the opening of the high-temperature electronic expansion valve 17 and the opening of the low-temperature electronic expansion valve 18, so as to adjust the parameters (moisture content and temperature) of the air supply state point after the fresh air volume is increased to reach the air supply state point O 1. At this time, the temperature of the fresh air flowing through the air inlet heat recovery heat exchange coil 3 is further reduced to reach a state point W 3, then the fresh air is subjected to equal humidity cooling through the high-temperature evaporator 4, then the fresh air is subjected to heat-humidity exchange through the low-temperature evaporator 5 to reach a state point L 1, finally the fresh air is reheated (equal humidity heating) through the condensation heat recovery device 7, then the fresh air is subjected to increased air supply state point O 1, the corresponding adjustment of the parameters (moisture content and temperature) of the air supply state point after the fresh air volume is increased is realized, and the stability of the indoor state point N can be maintained.
In this embodiment, when the dehumidification requirement on fresh air is higher, and the indoor total exhaust air amount is stable and the outdoor fresh air state parameter is changed (hereinafter, taking temperature reduction, absolute humidity increase and outdoor fresh air enthalpy increase as examples, the dehumidification requirement on fresh air is increased, and the high temperature evaporator 4 is required to operate under the wet working condition to assist the low temperature evaporator 5 to dehumidify the fresh air depth), the laboratory fresh air unit based on the dual-evaporation temperature refrigeration system of the invention will adjust the following steps:
Since the indoor air discharge amount is kept stable, the main controller 39 does not change the fresh air supply amount after calculation by real-time control, and therefore, the frequency of the double suction compressors 13 and the opening of the electric control valve 14 are not changed by feedforward control. Therefore, in the case where the total indoor exhaust air amount is stable and the outdoor fresh air state parameter is changed (the temperature is reduced, the absolute humidity is increased, and the outdoor fresh air enthalpy value is increased), the main controller 39 can adjust the air supply state parameter to the calculated value corresponding to the fresh air amount only by the feedback control.
Further, at this time, the moisture content and the temperature of the fresh air supply monitored in real time by the moisture content transmitter 6 and the temperature sensor 8 are higher than the calculated values corresponding to the fresh air quantity. The main controller 39 transmits a control signal to the compressor frequency converter 38 after calculation by a control algorithm, and the compressor frequency converter 38 immediately commands the double suction compressors 13 to correspondingly increase the frequency after receiving the control signal, and simultaneously, the opening degrees of the high-temperature electronic expansion valve 17 and the low-temperature electronic expansion valve 18 are manually adjusted. The frequency of the double air suction compressors 13 is regulated to be high, the opening of the corresponding electronic expansion valve is regulated to change the surface temperature of the high-low temperature evaporator coil, so that the high-temperature evaporator 4 is in a wet working condition running state to assist the low-temperature evaporator 5 in cooling and dehumidifying fresh air, the purpose of deep dehumidifying the fresh air is realized, meanwhile, the opening of the electronic regulating valve 14 is kept unchanged, and the main controller 39 is used for regulating the air supply state parameter to a calculated value corresponding to the fresh air quantity under the condition that the indoor total air exhaust quantity is stable and the outdoor fresh air state parameter is changed (the temperature is reduced, the absolute humidity is increased, and the outdoor fresh air enthalpy value is increased to cause higher dehumidification requirement on the fresh air).
Effects and effects of the examples
According to the laboratory fresh air handling unit based on the double-evaporation-temperature refrigerating system, the high-temperature evaporator and the low-temperature evaporator in the double-evaporation-temperature refrigerating system module formed by the components cool and dehumidify fresh air, and the middle heat exchange medium can be omitted, so that the lower coil surface temperature can be obtained through the lower evaporation temperature, and the higher dehumidification capacity and dehumidification capacity can be achieved. In addition, the condensation heat recoverer of the embodiment can reheat fresh air subjected to cooling and dehumidification by utilizing condensation waste heat of the double-evaporation-temperature refrigerating system module, and the phenomenon that the use of electric heating brings unreasonable energy for cold and hot offset is avoided.
Meanwhile, the embodiment depends on the dehumidification requirements under different working conditions of the double-evaporation-temperature refrigerating system module, when the dehumidification amount of fresh air is large, the frequency of the double-suction compressor is increased, the opening of the corresponding electronic expansion valve is adjusted, the evaporation temperature is reduced, the surface temperature of the high-temperature evaporator coil is reduced, the high-temperature evaporator is enabled to be in a wet working condition running state to assist the low-temperature evaporator in dehumidification, the purpose of deep dehumidification of the fresh air is achieved, when the dehumidification amount of the fresh air is not high, the opening of the corresponding electronic expansion valve is adjusted, the evaporation temperature is increased, the surface temperature of the high-temperature evaporator coil is increased, the high-temperature evaporator is enabled to be in a dry working condition running state, at the moment, the effect of the high-temperature evaporator is only to cool the fresh air, the evaporation temperature of refrigerant in the high-temperature evaporator is higher than that in the wet working condition running, and the energy efficiency of the double-evaporation-temperature refrigerating system module is higher than that of the high-temperature evaporator in the wet working condition running.
In addition, the glycol exhaust heat recovery circulation module composed of the air inlet heat recovery heat exchange coil and the exhaust heat recovery heat exchange coil through the solution circulation loop can be used for precooling or preheating fresh air by recovering exhaust energy, so that the energy consumption and the running cost of the system are reduced.
In addition, the main controller of the embodiment can perform feedforward control on fresh air quantity, air supply moisture content and temperature under the change of exhaust air quantity and perform feedback control on the air supply moisture content and temperature under the influence of factors such as outdoor fresh air state change or deviation of feedforward control through a control method combining feedforward control and feedback control, so that the special ventilation requirement in a laboratory can be met, and the accurate control on the air supply state and the better control on the indoor temperature and humidity state can be realized.
The above embodiments are preferred examples of the present invention, and are not intended to limit the scope of the present invention.

Claims (5)

1. Laboratory fresh air handling unit based on two evaporating temperature refrigerating system for temperature and humidity control in the laboratory, its characterized in that includes:
the fresh air duct is used for feeding fresh air into the room, and a fresh air filter, an air inlet heat recovery heat exchange coil, a high-temperature evaporator, a low-temperature evaporator, a moisture content transmitter, a condensation heat recoverer, a temperature sensor and a fresh air fan are sequentially arranged in the fresh air duct along the flow direction of the fresh air;
the air exhaust air duct is stacked above the fresh air duct and is used for indoor air exhaust, and an air exhaust filter, an air exhaust heat recovery heat exchange coil, an air speed sensor and an exhaust fan are sequentially arranged in the air exhaust air duct along the air exhaust flowing direction;
The double-evaporation temperature refrigerating system module comprises a double-suction compressor, a high-temperature electronic expansion valve, a low-temperature electronic expansion valve, a high-temperature side gas-liquid separator, a low-temperature side gas-liquid separator, an electric regulating valve, a first electromagnetic valve, a check valve, a condenser, the condensation heat recoverer, the high-temperature evaporator and the low-temperature evaporator;
The glycol exhaust heat recovery circulation module comprises an air inlet heat recovery heat exchange coil, an exhaust heat recovery heat exchange coil and a solution circulation loop for connecting the air inlet heat recovery heat exchange coil and the exhaust heat recovery heat exchange coil, wherein the solution circulation loop comprises an expansion valve, a liquid supplementing valve, a second electromagnetic valve, a solution circulation pump, a third electromagnetic valve, a fourth electromagnetic valve, a fifth electromagnetic valve, a standby solution circulation pump, a sixth electromagnetic valve and a liquid draining valve;
The air supply quantity and air supply state control module comprises a fan frequency converter which is connected with the fresh air fan and arranged outside the fresh air fan channel, a compressor frequency converter which is connected with the double-suction air compressor, and a main controller which is connected with the moisture content transmitter, the temperature sensor, the air speed sensor, the fan frequency converter, the compressor frequency converter and the electric regulating valve,
Wherein the input flow direction of the double-suction compressor is connected with the high-temperature evaporator and the low-temperature evaporator, the output flow direction is connected with the condensation heat recoverer and the condenser, the output flow direction of the double-suction compressor is split by the electric regulating valve and the first electromagnetic valve, the split flow direction is correspondingly connected with the condensation heat recoverer and the condenser, the input flow direction is correspondingly connected with the high-temperature evaporator and the low-temperature evaporator by the high-temperature side gas-liquid separator and the low-temperature side gas-liquid separator, the high-temperature side gas-liquid separator is arranged in a pipe section flowing from the high-temperature evaporator to the double-suction compressor, the low-temperature side gas-liquid separator is arranged in a pipe section flowing from the low-temperature evaporator to the double-suction compressor, the output flow direction of the condenser is connected with the high-temperature evaporator and the low-temperature evaporator, the input flow direction is correspondingly connected with a refrigerant common pipeline, the refrigerant common pipeline is connected with the condensation heat recoverer, the first electromagnetic valve is simultaneously arranged in an electronic expansion pipe section flowing from the high-temperature evaporator to the low-temperature evaporator and the double-suction heat recoverer, the two-suction heat recoverer is arranged in an electronic expansion pipe section flowing from the low-temperature evaporator to the double-suction heat recoverer,
In the air supply quantity and air supply state control module, the fan frequency converter is used for adjusting the frequency of the fresh air fan, the compressor frequency converter is used for adjusting the frequency of the double-suction air compressor, the electric adjusting valve is used for adjusting the heating capacity of the condensation heat recoverer to fresh air, the high-temperature electronic expansion valve and the low-temperature electronic expansion valve are used for correspondingly adjusting the processing capacity of the high-temperature evaporator and the low-temperature evaporator to the fresh air,
The main controller obtains the sensing data of the moisture content transmitter, the temperature sensor and the wind speed sensor and calculates the fresh air quantity, the air supply moisture content and the air supply temperature actually required through a control algorithm by a control method combining feedforward control and feedback control, correspondingly controls the fan frequency converter, the compressor frequency converter and the electric regulating valve, simultaneously manually regulates the opening degrees of the high-temperature electronic expansion valve and the low-temperature electronic expansion valve to ensure that the air supply quantity and the air supply state meet the actual requirement,
The feedforward control is used for controlling fresh air quantity, air supply moisture content and temperature under the change of the air exhaust quantity, under the feedforward control, the main controller calculates the air exhaust quantity according to the air speed in the air exhaust duct monitored by the air speed sensor in real time, and adopts an air quantity tracking method for controlling the fresh air quantity and the air exhaust quantity difference to ensure the indoor negative pressure requirement, the main controller calculates the calculated fresh air quantity required for ensuring the indoor and outdoor pressure difference through a control algorithm, the main controller compares the calculated fresh air quantity with the minimum fresh air quantity meeting the indoor personnel sanitary requirement, if the calculated fresh air quantity is larger than the minimum fresh air quantity, the indoor actual required fresh air quantity is determined according to the calculated fresh air quantity, otherwise, after the actual required fresh air quantity is determined, the main controller controls the indoor fresh air quantity by controlling the frequency of the fan frequency converter, simultaneously, the main controller calculates the state of the air supply at the position of the fan frequency converter after being adjusted to the actual required fresh air quantity, the air quantity corresponds to the temperature control point, the electric variable frequency converter and the electronic expansion valve after the temperature is adjusted, and the electronic expansion valve is correspondingly changed, the electronic expansion valve is correspondingly controlled by the electronic expansion valve,
The feedback control is used for controlling the moisture content and the temperature of the air supply under the condition that the outdoor fresh air state changes or the feedforward control precision is not high, under the feedback control, the moisture content transmitter and the temperature sensor monitor the moisture content of the fresh air after flowing through the low-temperature evaporator and the temperature after flowing through the condensation heat recoverer in real time and transmit monitoring signals to the main controller in real time, the main controller receives the monitoring signals to obtain real-time monitoring values, the real-time monitoring values of the moisture content and the temperature are compared with calculated values obtained through a control algorithm under the actual required fresh air quantity, and if the real-time monitoring values and the calculated values are different, the main controller correspondingly adjusts the frequency of the double-suction air compressor and the opening degree of the electric regulating valve through controlling the compressor frequency converter and the electric regulating valve, manually adjusts the opening degrees of the high-temperature electronic expansion valve and the low-temperature electronic expansion valve, and adjusts the moisture content of the air supply and the air supply temperature to the actual calculated values under the required fresh air quantity.
2. The laboratory fresh air handling unit based on a dual evaporating temperature refrigeration system of claim 1, wherein:
In the dual-evaporation temperature refrigerating system module, after refrigerant flows through the dual-suction air compressor and is isentropically compressed into high-temperature high-pressure refrigerant steam, the refrigerant is divided into two paths through the electric regulating valve and the first electromagnetic valve, one path of superheated steam flows to the condensation heat recovery device for reheating fresh air, the other path of superheated steam directly flows to the condenser, after sensible heat exchange is carried out on the superheated steam flowing to the condenser heat recovery device with cooled and dehumidified fresh air, the superheated steam is converged with the superheated steam directly flowing to the other path of the condenser through the check valve and flows to the condenser through the refrigerant public pipeline, the mixed superheated steam is changed into liquid refrigerant after heat release by condensation of the condenser, the liquid refrigerant output by the condenser is divided into two paths, one path of the liquid refrigerant flows to the high-temperature evaporator after throttle pressure reduction of the high-temperature electronic expansion valve, the other path of superheated steam flows to the high-temperature side air-liquid separator after heat absorption evaporation of the high-temperature evaporator, the superheated steam flows to the dual-suction air-pressure side air-liquid separator after heat absorption evaporation of the high-temperature electronic expansion valve, the mixed superheated steam flows to the dual-suction air-pressure heat recovery device after heat absorption of the low-pressure expansion device, and the mixed superheated steam flows to the dual-suction air-pressure air-absorption device after heat absorption of the low-pressure expansion device.
3. The laboratory fresh air handling unit based on a dual evaporating temperature refrigeration system of claim 1, wherein:
The high-temperature evaporator and the low-temperature evaporator are also provided with a condensate water tray used for collecting condensate water on the surface of the coil, and the bottom end of the condensate water tray is provided with a condensate water drain pipe arranged outside the fresh air pipeline to drain the condensate water.
4. The laboratory fresh air handling unit based on a dual evaporating temperature refrigeration system of claim 1, wherein:
In the solution circulation loop, the expansion valve, the fluid supplementing valve, the second electromagnetic valve, the solution circulation pump, the third electromagnetic valve and the fourth electromagnetic valve are sequentially arranged on a pipe section flowing from the exhaust heat recovery heat exchange coil to the intake heat recovery heat exchange coil, a branch is further arranged behind the fluid supplementing valve, one end of the branch is arranged between the fluid supplementing valve and the second electromagnetic valve, the other end of the branch is arranged between the third electromagnetic valve and the fourth electromagnetic valve, a fifth electromagnetic valve, a standby solution circulation pump and a sixth electromagnetic valve are sequentially arranged in the branch along the flowing direction, and in the solution circulation loop, the liquid draining valve is arranged on the pipe section flowing from the intake heat recovery coil to the exhaust heat recovery coil.
5. The laboratory fresh air handling unit based on a dual evaporating temperature refrigeration system of claim 1, wherein:
in the glycol exhaust heat recovery circulation module, glycol solution is arranged in an air inlet heat recovery heat exchange coil and an air exhaust heat recovery heat exchange coil for heat exchange, circulation of the glycol solution is carried out between the air inlet heat recovery heat exchange coil and the air exhaust heat exchange coil through the solution circulation loop, the glycol solution in the air exhaust heat recovery heat exchange coil absorbs low-temperature low-humidity cold energy from air exhaust, the solution circulation pump distributes the glycol solution carrying the low-temperature low-humidity cold energy to the air inlet heat recovery heat exchange coil, then the glycol solution releases the low-temperature cold energy to fresh air in the air inlet heat recovery heat exchange coil for precooling the fresh air, and the heated glycol solution flows back to the air exhaust heat recovery heat exchange coil again for cooling by the low-temperature cold energy of air exhaust to form heat recovery circulation.
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Families Citing this family (2)

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CN116025964B (en) * 2022-12-29 2024-05-03 珠海格力电器股份有限公司 Heat pump unit and cooling control method for variable frequency module of heat pump unit
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Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106679003A (en) * 2017-03-23 2017-05-17 福州鹏飞制冷设备有限公司 Energy-saving fresh air device
CN109209812A (en) * 2018-09-12 2019-01-15 珠海格力电器股份有限公司 A kind of compressor and air-conditioning system and fresh air system
CN109237618A (en) * 2018-10-08 2019-01-18 福州鹏飞制冷设备有限公司 A kind of energy-saving purifier
CN109882939A (en) * 2019-02-01 2019-06-14 上海理工大学 A kind of double evaporation Fresh air handling units
CN111023497A (en) * 2019-12-17 2020-04-17 福建瑞博恩环境科技有限公司 Split type ethylene glycol heat recovery fresh air conditioning unit
CN113834161A (en) * 2020-06-23 2021-12-24 中国石油化工股份有限公司 Variable air volume laboratory temperature control system and method
WO2022022642A1 (en) * 2020-07-29 2022-02-03 山东朗进科技股份有限公司 Air conditioner and dehumidification method

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10690358B2 (en) * 2016-06-08 2020-06-23 Semco Llc Air conditioning with recovery wheel, passive dehumidification wheel, cooling coil, and secondary direct-expansion circuit

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106679003A (en) * 2017-03-23 2017-05-17 福州鹏飞制冷设备有限公司 Energy-saving fresh air device
CN109209812A (en) * 2018-09-12 2019-01-15 珠海格力电器股份有限公司 A kind of compressor and air-conditioning system and fresh air system
CN109237618A (en) * 2018-10-08 2019-01-18 福州鹏飞制冷设备有限公司 A kind of energy-saving purifier
CN109882939A (en) * 2019-02-01 2019-06-14 上海理工大学 A kind of double evaporation Fresh air handling units
CN111023497A (en) * 2019-12-17 2020-04-17 福建瑞博恩环境科技有限公司 Split type ethylene glycol heat recovery fresh air conditioning unit
CN113834161A (en) * 2020-06-23 2021-12-24 中国石油化工股份有限公司 Variable air volume laboratory temperature control system and method
WO2022022642A1 (en) * 2020-07-29 2022-02-03 山东朗进科技股份有限公司 Air conditioner and dehumidification method

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