CN114353234B - Heat recovery device and heat recovery method for fresh air system - Google Patents
Heat recovery device and heat recovery method for fresh air system Download PDFInfo
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- CN114353234B CN114353234B CN202210029833.5A CN202210029833A CN114353234B CN 114353234 B CN114353234 B CN 114353234B CN 202210029833 A CN202210029833 A CN 202210029833A CN 114353234 B CN114353234 B CN 114353234B
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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
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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
- F24F12/00—Use of energy recovery systems in air conditioning, ventilation or screening
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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
- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B13/00—Compression machines, plants or systems, with reversible cycle
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B29/00—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously
- F25B29/003—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously of the compression type system
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
- Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
- Y02B30/56—Heat recovery units
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- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
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Abstract
The invention provides a heat recovery device of a fresh air system and a heat recovery method thereof, wherein a compression circulation system comprises an evaporator, a condenser and a compressor; the evaporator is arranged in the fresh air unit, the condenser is arranged in the exhaust unit; one end of the evaporator is connected with one end of the condenser through an expansion valve; the other end is connected with the other end of the condenser through a four-way reversing valve; the four-way reversing valve is also connected with the compressor; the outdoor fresh air inlet of the fresh air unit is provided with an air valve MI, and the first surface cooler and the second surface cooler in the fresh air unit are in circulating connection through a circulating pump; the first surface cooler is provided with an air valve MII, and the second surface cooler is provided with an air valve MIII; the exhaust unit is provided with an air valve MIV. The evaporator cools and dehumidifies fresh air through refrigeration cycle, and the condenser recovers the cold energy of the exhaust unit so as to improve the efficiency of the whole refrigeration cycle; when the air-cooling capacity is insufficient, the air valve MIV is opened to supplement the cooling capacity; in the heating working condition, the evaporator is changed into a condenser to heat fresh air through the four-way reversing valve.
Description
Technical Field
The invention belongs to the technical field of heat recovery, and particularly relates to a heat recovery device and a heat recovery method of a fresh air system.
Background
With the development of technology and economy, various types of scientific research and experimental sites are increasing. The construction of each scientific research unit and laboratory in higher institutions clearly plays a significant role in technological innovation and scientific research development. In recent years, governments in countries and places, universities and colleges build various types of important laboratories and ordinary laboratories, and the investment in laboratory construction is increasing. With the construction of various laboratories, most laboratories are provided with air conditioning facilities to meet the comfort level of laboratory staff in the experiment, wherein the air conditioning standard of part of the laboratories is quite high. The specifications of the scientific research building design standard JGJ91-2019, the clinical laboratory design rule (GB/T20469-2006) and the laboratory biosafety general requirement (GB 19489-2008) have strict requirements on laboratory air conditioner design parameters.
Because a plurality of volatile medicines, in particular organic medicines, can be used in the experimental process, the waste gas generated in the experimental process has a plurality of types and high concentration and has certain hazard. Therefore, in order to remove the exhaust gas, laboratory ventilation is generally required to be high, and the exhaust air volume and the fresh air volume are very large.
In some common laboratories, outdoor fresh air introduced into the laboratory is not subjected to temperature and humidity treatment, and in this case, extremely cold and extremely hot outdoor air directly introduced in severe winter and in midsummer has a great influence on the comfort of indoor laboratory staff.
The fresh air introduced into a plurality of laboratories is simply cooled (for example, the fresh air is cooled to the indoor temperature in summer) so as to effectively improve the comfort of the indoor environment. In this way, most fresh air units only process a small part of wet load, and most of fresh air units also need to be loaded by fan coils in rooms, and humidity exceeds standard due to the fact that the fresh air quantity is large in a laboratory and the dehumidification capacity of the fan coils is insufficient. For example: in the actual use process, in laboratories in coastal humid areas of the south of the earth and the south of the China, the phenomenon of large-area condensation of laboratory equipment and an enclosure structure caused by insufficient dehumidification treatment of the introduced fresh air often occurs in some seasons, and great trouble is brought to maintenance and use of the laboratories, so that the normal use of the laboratories is influenced.
Therefore, the simple cold and hot treatment cannot meet the use requirement and the standard requirement, and the fresh air wet load of a laboratory must be borne by a fresh air unit; in order to make the room meet the temperature and humidity requirements, the fresh air is usually cooled and dehumidified to the indoor dew point, and then heated to the indoor temperature or close to the indoor temperature. At this time, the fresh air system needs to be heated as well as cooled. On the one hand, because the cold and the heat are balanced, the cold quantity required by cooling and dehumidification (w-l) is increased; on the other hand, a heat source is also required to be arranged in summer for reheating (L-O); in addition, the laboratory has huge fresh air volume, so that the energy consumption of the fresh air system is huge, and the energy-saving requirement of the fresh air system is particularly outstanding.
According to engineering design cases, the ventilation (fresh air-containing) load of the laboratory is high in proportion, and according to the using quantity and distribution conditions of the exhaust cabinets of the laboratory, the proportion of the fresh air load of the air conditioner caused by the ventilation system to the total air conditioner load of the laboratory is different from 40% to 90%, so that the fresh air load of the air conditioner is the largest component of the air conditioner load of the laboratory.
For the arrangement of an auxiliary heat source (reheating source), due to the use characteristics of a laboratory (various waste gases generated in the experimental process, high concentration and certain hazard), the problem can not be solved by a secondary return air mode. Therefore, it is generally considered to provide a four-pipe air conditioning system, to add a reheat source (such as a boiler) in summer, or to use electric heating. In order to reduce the reheat source, some heat recovery type water chilling units are adopted, and the condensation waste heat of the water chilling units is used as the reheat source of the system. The scheme is free, but the heat source does not reduce the balance of cold and heat, increases the cold quantity required by cooling and dehumidification (w-l), and does not utilize the cold quantity in exhaust air.
The most common practice at present is: the heat recovery device is arranged between the exhaust air and the fresh air to recover part of energy, so that the fresh air cooling load is reduced to a certain extent. The laboratory exhaust air comprises various volatile medicines and organic medicaments, and has certain hazard and corrosiveness. In order to avoid cross contamination, only sensible heat in the exhaust air can be recovered by using a temperature difference between media, but latent heat in the exhaust air cannot be recovered, so that heat recovery efficiency is relatively low. In general, a group of heat exchange coils are added on an exhaust pipeline, so that the exhaust air exchanges heat with a heating medium (usually ethylene glycol) in the coils, part of cold energy (or heat) in the exhaust air is transferred to the heating medium, and then the heating medium is utilized to pre-cool or preheat outdoor fresh air, thereby improving the air inlet working condition of a surface cooler of a fresh air handling unit and reducing the fresh air load. The system belongs to a passive heat recovery system, the amount of recovered cold (heat) is completely dependent on the indoor and outdoor air temperature difference, and when the outdoor temperature changes, the amount of recovered cold (heat) changes accordingly. And a reheat source is required.
Document (Zhou Jin) use of a novel heat recovery device in laboratory air conditioning systems [ J]119 122, 63) provides a novel heat recovery method, which adds a group of reheating coils in a traditional liquid circulation type heat recovery system, directly utilizes the heat recovery system to reheat fresh air which is in a low-temperature saturated state after dehumidification, further recovers cold energy in air supply with reduced temperature due to dehumidification, further reduces the temperature of a secondary refrigerant in circulation (from t' w1 to tw 1), and usesThe outdoor fresh air is precooled by the refrigerating medium with lower temperature, so that the precooling amount is increased, the cooling load of the surface cooler of the fresh air unit is reduced, and the aim of further energy conservation is fulfilled. According to the scheme, the fresh air preheating coil, the exhaust heat recovery coil and the reheating coil are connected in series, and fresh air exchanges sensible heat with exhaust air through liquid circulation and then exchanges heat with fresh air after cooling and dehumidification. By establishing a heat exchange model and calculating the heat of the heat recovery coil in practice under the design working condition by using matlab (tx 1=32 ℃, tx 1=14 ℃, tp 1=24 ℃, the heat exchanger adopts U-6-12-54, and water flow GW=5328 kg/h), the heat recovery quantity of the heat recovery coil under the design working condition can be found to be almost 0, namely the exhaust energy is not utilized and recovered. And secondly, because of the heat recovery, resistance (heat recovery coil, reheating coil and preheating coil) is increased on the fresh air and exhaust air passages, and the running energy consumption of the fresh air and exhaust air fans is increased. For example, estimated at 200Pa per coil resistance, 100000m 3 The fan of the fresh air energy recovery system increases the power by about 25KW, and the cooling capacity is 100KW (the energy consumption of the air conditioning system is 4.0). When the temperature difference of the system is lower and the recovery energy is smaller than the value, the system not only saves energy but also consumes energy.
Disclosure of Invention
The invention aims to solve the technical problems that:
1. the energy consumption of exhaust is utilized to the maximum extent while the cancellation of cold and hot is solved;
2. the problem that the energy recovery is uneconomical in part of time period is solved.
3. Solves the problem of freezing of the freezing heating coil.
The invention adopts the following technical scheme:
the fresh air system heat recovery device comprises an exhaust unit, a fresh air unit and a compression circulation system;
the compression circulation system comprises an evaporator, a condenser and a compressor;
the evaporator is arranged in the fresh air unit;
the condenser is arranged in the exhaust unit;
one end of the evaporator is connected with one end of the condenser through an expansion valve; the other end is connected with the other end of the condenser through a four-way reversing valve;
the four-way reversing valve is also connected with the compressor;
the outdoor fresh air inlet of the fresh air unit is provided with an air valve MI, and the first surface cooler and the second surface cooler in the fresh air unit are in circulating connection through a circulating pump; the first surface cooler is provided with an air valve MII, and the second surface cooler is provided with an air valve MIII;
the exhaust unit is provided with an air valve MIV.
The heat recovery method of the fresh air system heat recovery device comprises the following steps:
the refrigerating working condition of the compression circulation system is that the evaporator cools and dehumidifies fresh air, and the condenser recovers the cold energy of the exhaust unit so as to improve the whole refrigerating circulation efficiency; when the air-cooling capacity is insufficient, the air valve MIV is opened to supplement the cooling capacity; in the heating working condition, the evaporator is changed into a condenser to heat fresh air through the four-way reversing valve;
the cooling working condition of the fresh air handling unit in summer forms a liquid heat recovery system through the circulating pump, the first surface cooler and the second surface cooler, and the recovery evaporator is cooled and dehumidified and then is in low temperature and full air, so that the fresh air is precooled, and the cooling capacity of the evaporator is reduced.
Drawings
FIG. 1 is a schematic diagram of the structure of the present invention;
fig. 2 is a flow chart of the summer air treatment of the present invention.
Detailed Description
The specific technical scheme of the invention is described with reference to the accompanying drawings.
As shown in fig. 1, the compression cycle system includes an evaporator 1, a condenser 5, and a compressor 2;
the evaporator 1 is arranged in a fresh air unit 8;
the condenser 5, the condenser 5 is set up in the exhaust unit 10;
one end of the evaporator 1 is connected with one end of the condenser 5 through the expansion valve 3; the other end is connected with the other end of the condenser 5 through a four-way reversing valve 4;
the four-way reversing valve 4 is also connected with the compressor 2;
an outdoor fresh air inlet of the fresh air unit 8 is provided with an air valve MI11, and the first surface cooler 6 and the second surface cooler 7 in the fresh air unit 8 are connected in a circulating way through a circulating pump 9; the first surface cooler 6 is provided with an air valve MII12, and the second surface cooler 7 is provided with an air valve MIII13;
the exhaust unit 10 is provided with an air valve MIV14;
the refrigerating working condition of the compression circulation system is that the evaporator 1 cools and dehumidifies fresh air, and the condenser 5 recovers the cold energy of the exhaust unit 10 so as to improve the whole refrigerating cycle efficiency. When the exhaust air cooling capacity is insufficient, the air valve MIV14 is opened to supplement the cooling capacity.
In the heating working condition, the evaporator 1 becomes a condenser 5 to heat fresh air through the four-way reversing valve 4.
The fresh air processing unit forms a liquid heat recovery system through a circulating pump 9, a first surface cooler 6 and a second surface cooler 7 under the refrigerating working condition in summer, and the recovery evaporator 1 is cooled and dehumidified and then is in low temperature and full air, so that fresh air is precooled, and the cooling capacity of the evaporator 1 is reduced; meanwhile, reheating is avoided, and a double energy-saving effect is achieved. A summer air treatment flow chart is shown in fig. 2.
The system is provided with three air valves of an air valve MI11, an air valve MII12 and an air valve MIII13, and is used in summer: when the heat recovery is uneconomical in part of time, the air valves MII12 and MIII13 are opened, the temperature is reduced simply, and the system resistance is reduced. When the outdoor fresh air parameter is close to indoor, the air valve MI11 is opened, and the refrigeration and air valves MII12 and MIII13 are closed, so that the system operates with minimum resistance. Only heating is needed in winter, and the MII12MII12 is started, so that the MII12MIII13 saves the energy consumption of the fan.
Anti-freezing in winter: when the outdoor temperature is lower than 0 ℃, the MII12MII12 and the MII12MIII13 are closed, the circulating pump 9 is started, and the heated air is utilized to preheat the fresh air, so that the intermediate heating coil is prevented from being frozen.
Claims (2)
1. The heat recovery device of the fresh air system is characterized by comprising an exhaust unit (10), a fresh air unit (8) and a compression circulation system;
the compression circulation system comprises an evaporator (1), a condenser (5) and a compressor (2);
the evaporator (1) is arranged in the fresh air unit (8);
the condenser (5), the condenser (5) is set up in the exhaust unit (10);
one end of the evaporator (1) is connected with one end of the condenser (5) through the expansion valve (3); the other end is connected with the other end of the condenser (5) through a four-way reversing valve (4);
the four-way reversing valve (4) is also connected with the compressor (2);
an outdoor fresh air inlet of the fresh air unit (8) is provided with an air valve MI (11), and a first surface cooler (6) and a second surface cooler (7) in the fresh air unit (8) are in circulating connection through a circulating pump (9); a liquid heat recovery system is formed by a circulating pump (9), a first surface cooler (6) and a second surface cooler (7); the first surface cooler (6) is provided with an air valve MII (12), and the second surface cooler (7) is provided with an air valve MIII (13);
the exhaust unit (10) is provided with an air valve MIV (14).
2. The heat recovery method of a fresh air system heat recovery device according to claim 1, comprising the steps of:
the refrigerating working condition of the compression circulation system is that the evaporator (1) cools and dehumidifies fresh air through refrigerating circulation, and the condenser (5) recovers the cold energy of the exhaust unit (10) so as to improve the efficiency of the whole refrigerating circulation; when the air-cooling capacity is insufficient, the air valve MIV (14) is opened to supplement the cooling capacity; in the heating working condition, the evaporator (1) is changed into a condenser (5) to heat fresh air through the four-way reversing valve (4);
the cooling working condition of the fresh air handling unit in summer forms a liquid heat recovery system through a circulating pump (9), a first surface cooler (6) and a second surface cooler (7), low-temperature air after cooling and dehumidifying of the evaporator (1) is recovered, fresh air is precooled, and the cooling capacity of the evaporator (1) is reduced.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202210029833.5A CN114353234B (en) | 2022-01-12 | 2022-01-12 | Heat recovery device and heat recovery method for fresh air system |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202210029833.5A CN114353234B (en) | 2022-01-12 | 2022-01-12 | Heat recovery device and heat recovery method for fresh air system |
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| Publication Number | Publication Date |
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| CN114353234A CN114353234A (en) | 2022-04-15 |
| CN114353234B true CN114353234B (en) | 2023-05-05 |
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Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN114877424A (en) * | 2022-05-31 | 2022-08-09 | 广州迪森劳力特空气净化技术有限公司 | Fresh air dehumidifier with heat recovery effect and system thereof |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN202501585U (en) * | 2012-02-01 | 2012-10-24 | 国电科学技术研究院 | Fresh air and exhaust air heat/moisture recovery heat pump set with bypass adjustment |
| CN102705920B (en) * | 2012-05-24 | 2015-02-04 | 吕智 | Double-cold-source heat pump total heat recovery humidity regulating and temperature controlling fresh air unit and control method thereof |
| CN106931551A (en) * | 2017-04-10 | 2017-07-07 | 上海云懋空气处理设备有限公司 | A kind of energy-saving dehumidification system |
| CN111473502A (en) * | 2020-04-28 | 2020-07-31 | 多乐空气处理设备（苏州）有限公司 | Fresh air energy-saving system with efficient heat recovery |
| CN112161367A (en) * | 2020-07-30 | 2021-01-01 | 中国建筑股份有限公司 | Air dehumidification fresh air system in underground space |
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