CN106705334A - Energy recovery double-cold-source high-enthalpy-difference energy storage fresh air handling unit and control method thereof - Google Patents

Energy recovery double-cold-source high-enthalpy-difference energy storage fresh air handling unit and control method thereof Download PDF

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Publication number
CN106705334A
CN106705334A CN201611015029.2A CN201611015029A CN106705334A CN 106705334 A CN106705334 A CN 106705334A CN 201611015029 A CN201611015029 A CN 201611015029A CN 106705334 A CN106705334 A CN 106705334A
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China
Prior art keywords
fresh air
energy
air
low
outlet
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CN201611015029.2A
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Chinese (zh)
Inventor
吕智
丁力行
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Guangdong Hot & Air Conditioning Co
Zhongkai University of Agriculture and Engineering
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Guangdong Hot & Air Conditioning Co
Zhongkai University of Agriculture and Engineering
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Priority to CN201611015029.2A priority Critical patent/CN106705334A/en
Publication of CN106705334A publication Critical patent/CN106705334A/en
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Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24HEATING; RANGES; VENTILATING
    • F24FAIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F7/00Ventilation
    • F24F7/04Ventilation with ducting systems also by double walls; with natural circulation
    • F24F7/06Ventilation with ducting systems also by double walls; with natural circulation with forced air circulation, e.g. by fan positioning of a ventilator in or against a conduit
    • F24F7/08Ventilation with ducting systems also 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
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24HEATING; RANGES; VENTILATING
    • F24FAIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F12/00Use of energy recovery systems in air conditioning, ventilation or screening
    • F24F12/001Use of energy recovery systems in air conditioning, ventilation or screening with heat-exchange between supplied and exhausted air
    • F24F12/006Use of energy recovery systems in air conditioning, ventilation or screening with heat-exchange between supplied and exhausted air using an air-to-air heat exchanger
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24HEATING; RANGES; VENTILATING
    • F24FAIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F13/00Details common to, or for air-conditioning, air-humidification, ventilation or use of air currents for screening
    • F24F13/30Arrangement or mounting of heat-exchangers
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00Fluid-circulation arrangements
    • F25B41/20Disposition of valves, e.g. of on-off valves or flow control valves
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00Fluid-circulation arrangements
    • F25B41/30Expansion means; Dispositions thereof
    • F25B41/31Expansion valves
    • YGENERAL 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
    • Y02TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02BCLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/56Heat recovery units

Abstract

The invention discloses an energy recovery double-cold-source high-enthalpy-difference energy storage fresh air handling unit. The unit comprises an air conditioning system, a heat pump system and an energy storage system; the air conditioning system includes a fresh air machine, an exhaust fan and an air total-heat recoverer; the heat pump system includes an annular close-connected compressor, a condensation heat recoverer, a condenser, an expansion valve, a direct expansion evaporator and an energy storage evaporator; the energy storage system includes an energy storage tank and a high-entralpy-difference surface cooler connected with each other; and the condensation heat recoverer, the direct expansion evaporator and the high-entralpy-difference surface cooler are respectively arranged on a fresh air channel. The unit largely reduces the operation cost by using the peak-valley price, provides low-temperature frozen water needed by deep dehumidification, increases the energy-efficiency ratio of the heat pump system through recovering the condensation heat, can improve the quality of indoor air through low-temperature cold sources and increment of the fresh air quantity, reduces the fresh air conditioning energy consumption by exhausting and heat recovery, and facilitates to save the energy and reduce the environmental pollution.

Description

The double big enthalpy difference accumulation of energy Fresh air handling units of low-temperature receiver of energy recovery type and its control method
Technical field
The present invention relates to a kind of accumulation of energy fresh air conditioner, more particularly to a kind of energy recovery type big enthalpy difference accumulation of energy fresh air of double low-temperature receivers Unit.
Background technology
China's air conditioning in residential buildings system mostly uses new return air mixed mode, because most of air is circulated indoors, Prevent pollutant is from the outdoor that is discharged to quickly, human health is endangered.Resh air requirement (or using method of operation of all-fresh air) is increased, Indoor harmful substance can be diluted and discharge outdoor, hence it is evident that improve indoor air quality;But then, fresh air energy consumption is accounted for Whole air conditioning energy consumption ratio 30-40%, the increase of resh air requirement causes that Fresh air handing energy consumption is greatly increased;In addition to air Processing mode at present more uses common 7/12 DEG C of chilled water or the directly dehumidification mode of evaporation, and this air conditioning mode exists following several The drawbacks of individual aspect:First, using vortex and rotor-type compressor more than direct-evaporation-type fresh air conditioner, compressor performance coefficient is low; Simultaneously to obtain relatively low evaporating temperature, the efficiency of unit is also decreased;2nd, chiller unit is relatively low cold in order to provide Freeze coolant-temperature gage, need also exist for relatively low evaporating temperature, the efficiency of cooling-water machine is also decreased;3rd, it is difficult in adapt to heat moisture ratio Change, is only cooled down and is dehumidified by conventional evaporation mode to air, and its sensible heat for absorbing and latent heat are than can only be certain In the range of change, and the heat moisture ratio that building is actually needed changes in the larger context, usually sacrifices the control to humidity System, is compromised by only meeting the requirement of indoor temperature, causes the phenomenon that indoor relative humidity is too high or too low;4th, because of air-out Temperature is too low to cause the presence of condensed water, and the surface of indoor coil forms the hotbed for growing various moulds, is degrading Interior Space Gas quality, triggers various Cure of Sick Building Syndrome;5th, low temperature and low humidity air draft wastes substantial amounts of cold.
Additionally, it is necessary to Fresh air handing unit provides dry outdoor fresh air in humiture independence control air conditioner system, with full The demand of sufficient hydrofuge, row CO2, row's taste and offer fresh air.It is a kind of possible solution route using rotary wheel dehumidifying mode, The wheel surface that aglite makes is attached to hygroscopic materials such as silica gel, molecular sieves.But rotary dehumidifier heat energy utilization is imitated The low essence of rate is that to dehumidify and regenerate the two processes be all constant-enthalpy process and non-isothermal process, wet between wheel surface and air Degree difference and temperature difference are all very uneven, cause very big irreversible loss, and regenerative process is with greater need for a large amount of energy consumptions of consumption;Another Dehumidification mode is the solution air-conditioning that air is directly contacted with salting liquid, and through in a few years promoting, a large amount of problems start to manifest:Equipment is made Valency is high;Heat transmission equipment inefficiency, the corrosivity of salting liquid is strong, and fault rate is high, it is extremely difficult to promote.
Therefore, it is necessary to be further improved.
The content of the invention
The purpose of the present invention aim to provide it is a kind of it is simple and reasonable, operate steadily, the energy of low energy consumption and low operating cost The amount reclaiming type big enthalpy difference accumulation of energy Fresh air handling units of double low-temperature receivers, to overcome weak point of the prior art.
A kind of energy recovery type big enthalpy difference accumulation of energy Fresh air handling units of double low-temperature receivers designed by this purpose, including air-treatment system System, heat pump and energy-storage system;The air treatment system includes the new blower fan being arranged in fresh air channel, is arranged at air draft Exhaust blower in passage, and it is respectively communicated with the air total heat recovery device of fresh air channel and air exhaust passage;It is characterized in that:The heat Pumping system includes compressor, condensation heat recoverer, condenser, expansion valve, direct expansion evaporator and the storage of annular closure connection Energy evaporator, the energy-storage system includes the energy storage tank, big enthalpy difference surface cooler, water pump and the electronic proportional integral valve that are connected with each other, Wherein, condensation heat recoverer, direct expansion evaporator and big enthalpy difference surface cooler are respectively arranged in fresh air channel.
The air total heat recovery device is provided with fresh air inlet, fresh air outlet, air draft entrance and wind exhausting outlet, fresh air inlet Communicated with the air inlet of fresh air channel, fresh air outlet is communicated with the air outlet of fresh air channel, and air draft entrance enters with air exhaust passage Air port is communicated, and wind exhausting outlet is communicated with the air outlet of air exhaust passage;Direct expansion evaporator, big enthalpy difference surface cooler and condensation heat are returned Receive device to be set in turn between the outlet of the fresh air of air total heat recovery device and the air outlet of fresh air channel, fresh air is sequentially passed through directly Expansion evaporator, big enthalpy difference surface cooler and condensation heat recoverer.
The outlet of the compressor connects the entrance of condenser and the entrance of condensation heat recoverer, condensation heat recoverer respectively Outlet connection condenser entrance, the entrance and energy storage evaporator of the outlet of condenser connection direct expansion evaporator respectively Entrance, the outlet of energy storage evaporator and the outlet of direct expansion evaporator connect the entrance of compressor respectively.
The second magnetic valve is provided between the outlet of the compressor and the entrance of condenser;The outlet of the compressor with The first magnetic valve is provided between the entrance of condensation heat recoverer;The outlet of the condensation heat recoverer and the entrance of condenser it Between be connected with the first check valve;The outlet connection expansion valve of condenser, sets between expansion valve and the entrance of direct expansion evaporator The 3rd magnetic valve is equipped with, the 4th magnetic valve is provided between expansion valve and the entrance of energy storage evaporator;Direct expansion evaporator The second check valve is connected between outlet and the entrance of compressor;Connected between the outlet of energy storage evaporator and the entrance of compressor There is the 3rd check valve.
The type of cooling of the condenser can be water cooling or air cooling.
The energy storage evaporator is arranged in energy storage tank, and the outlet of energy storage tank connects entering for big enthalpy difference surface cooler by water pump Mouthful, the outlet of big enthalpy difference surface cooler connects the entrance of energy storage tank by electronic proportional integral valve.
Energy storage phase change material is provided with the energy storage tank, the freezing point temperature of the setting temperature higher than water of the energy storage phase change material Degree, less than 5 DEG C.
The big enthalpy difference surface cooler pipe row is surface-type heat exchanger more than six rows.
Fresh air and air draft realize energy regenerating respectively through air total heat recovery device in air total heat recovery device;Newly Blower fan is arranged at the air outlet of fresh air channel, and exhaust blower is arranged at the air outlet of air exhaust passage.
A kind of control method for this energy recovery type big enthalpy difference accumulation of energy Fresh air handling units of double low-temperature receivers, it is characterised in that:Night Late electricity price low-valley interval, heat pump work, it is comprised the following steps:
The closing of a, new blower fan and exhaust blower, compressor start, the first magnetic valve and the 3rd closed electromagnetic valve, the second magnetic valve And the 4th solenoid valves open;
B, the exhaust of compressor HTHP turn into cryogenic high pressure liquid refrigerants after condenser is cooled down, then by expansion valve After expansion, as low-temp low-pressure vapour-liquid admixture refrigerant;
C, low-temp low-pressure vapour-liquid admixture refrigerant evaporate in energy storage evaporator, and the phase-change material in energy storage tank utilizes material The chemical energy of material carries out accumulation of energy, and total maximum treatment load proportion of fresh air shared by compressor accumulation of energy capacity should be by different regions peak-trough electricity Valency preferential policy determines, generally 2/3rds, insufficient section completes by heat pump cooperation.
A kind of control method for this energy recovery type big enthalpy difference accumulation of energy Fresh air handling units of double low-temperature receivers, it is characterised in that:In vain The control method of its electricity price par period is comprised the following steps:
A), air treatment system works first:Open new blower fan and exhaust blower, hot humid fresh air and low temperature and low humidity air draft After air total heat recovery device carries out energy regenerating, air draft is discharged to outdoor after releasing cold by exhaust blower, and fresh air absorbs cold After sequentially pass through direct expansion evaporator, big enthalpy difference surface cooler and condensation heat recoverer;
B), heat pump is started working:
1), compressor start, the first magnetic valve, the second magnetic valve and the 3rd solenoid valves are opened, and the 4th magnetic valve is closed Close;
2), by condensation heat recoverer and condenser to be cooled to cryogenic high pressure liquid simultaneously cold for the exhaust of compressor HTHP Matchmaker, cryogenic high pressure liquid refrigerants by expansion valve expansion after, as low-temp low-pressure vapour-liquid admixture refrigerant;
3), low-temp low-pressure vapour-liquid admixture refrigerant evaporates in direct expansion evaporator, to the fresh air after Total heat exchange Pre-processed, evaporate complete low temperature low pressure gas and return to compressor;
C), fresh air then passes through the big enthalpy difference surface cooler of cryogenic freezing water by direct expansion evaporator cool-down dehumidification, this When electronic proportional integral valve connect, water pump is opened, and the phase-change material in energy storage tank starts to release cold, and cryogenic freezing water is started the cycle over, Make fresh air water capacity less than requirement of the humiture independent process system to fresh air water capacity, low temperature and low humidity fresh air is again by condensation heat The reheating of recover, leaving air temp is controlled by the aperture for adjusting the first magnetic valve, fresh air leaving air temp is reached humiture only Vertical requirement of the processing system to fresh air leaving air temp.
Beneficial effects of the present invention:
Present invention utilizes time-of-use tariffs phase-changing energy-storing technology reduction operation of air conditioner expense while removed there is provided depth Cryogenic freezing water needed for wet, condensation heat recoverer improves the Energy Efficiency Ratio of heat pump;Can also be by included in fresh air channel Plus filtering and sterilizing unit can remove the dust and bacterium carried secretly in air, play a part of purify air, improve interior Air quality;System reclaims the energy of indoor exhaust wind, reduces Fresh air handing energy consumption, low taste thermal source is utilized, and helps In the environmental situation of energy-conservation and improvement caused by coal-fired, fuel oil.
The present invention not only solves the deficiencies in the prior art, also uses the cryogenic freezing water of time-of-use tariffs and energy accumulation air conditioner The characteristics of (5/13 DEG C of water temperature of turnover), reaches following beneficial effect:
1. power network peak load is balanced, is improved and is generated electricity and power transmission efficiency;
2. refrigeration host computer capacity reduces, and reduces air-conditioning system power capacity increasing tariff;
3. cold air distribution is realized, water wind induction system is reduced investment outlay and energy consumption;
4. the absolute humidity that fresh air can be processed is lower, improves air quality;
5. electricity price between peak and valley is make use of, operation of air conditioner expense is reduced;
6. there is emergent low-temperature receiver, reliability is improved;
7. humiture independent process system is suitable for, and room air process part can use high temperature chilled water (Inlet and outlet water 16/20 DEG C of temperature), system is more energy efficient.
By the low dew-point temperature of cryogenic freezing water, this structure can not only undertake whole fresh air sensible heats and latent heat load, also Assume responsibility for room air whole latent heat and part sensible heat load;Because unit reclaims exhaust cold pair using air total heat recovery device Pre-cooling of fresh air, and the condensation heat of heat pump has been reclaimed, the relative humidity of air-out is reduced, thus it is too low in the absence of leaving air temp The danger of condensation;Unit also undertakes removal interior CO2, peculiar smell simultaneously, to ensure the task of IAQ;And the present invention is adopted Air conditioner fresh air is processed with energy accumulating technique, cryogenic freezing water not only enhances effect on moisture extraction, is also greatly reduced microbial growth, changes It has been apt to indoor air quality;System reclaims the energy of indoor exhaust wind, reduces Fresh air handing energy consumption;It is defeated that the big temperature difference improves water wind Send efficiency Energy Efficiency Ratio;Project is greatly reduced while systematic energy efficiency ratio is improved once to invest.
Brief description of the drawings
Fig. 1 is the operation principle schematic diagram of one embodiment of the invention.
In figure:1 is new blower fan, and 2 is exhaust blower, and 3 is air total heat recovery device, and 4 is compressor, and 5 is condenser, and 6 is swollen Swollen valve, 7 is direct expansion evaporator, and 8 is energy storage evaporator, and 9 is energy storage tank, and 10 is big enthalpy difference surface cooler, and 11 return for condensation heat Device is received, 12 is the first magnetic valve, and 13 is the second magnetic valve, and 14 is the 3rd magnetic valve, and 15 is the 4th magnetic valve, and 16 is first unidirectional Valve, 17 is the second check valve, and 18 is the 3rd check valve, and 19 is water pump, and 20 is electronic proportional integral valve.
Specific embodiment
Below in conjunction with the accompanying drawings and embodiment the invention will be further described.
Referring to Fig. 1, this energy recovery type big enthalpy difference accumulation of energy Fresh air handling units of double low-temperature receivers, including air treatment system, heat pump system System and energy-storage system;The air treatment system includes the new blower fan 1 being arranged in fresh air channel A, is arranged in air exhaust passage B Exhaust blower 2 and be respectively communicated with the air total heat recovery device 3 of fresh air channel A and air exhaust passage B (dotted arrow represent row in figure The direction of wind passage B interior air-flows, solid arrow represents the direction of fresh air channel A interior air-flows);The heat pump is closed including annular Compressor 4, condensation heat recoverer 11, condenser 5, expansion valve 6, direct expansion evaporator 7 and the energy storage evaporator 8 of connection are closed, The energy-storage system includes the energy storage tank 9, water pump 19, electronic proportional integral valve 20 and the big enthalpy difference surface cooler 10 that are connected with each other, its In, condensation heat recoverer 11, direct expansion evaporator 7 and big enthalpy difference surface cooler 10 are respectively arranged on fresh air channel A, to fresh air Carry out heat and wet treatment.
Furtherly, the air total heat recovery device 3 is provided with fresh air inlet, fresh air outlet, air draft entrance and air draft and goes out Mouthful, fresh air inlet communicated with the air inlet of fresh air channel A, and fresh air outlet is communicated with the air outlet of fresh air channel A, air draft entrance and The air inlet of air exhaust passage B is communicated, and wind exhausting outlet is communicated with the air outlet of air exhaust passage B;Direct expansion evaporator 7, big enthalpy difference Surface cooler 10 and condensation heat recoverer 11 are set in turn between fresh air outlet and the air outlet of fresh air channel A, and fresh air is passed through successively Cross direct expansion evaporator 7, big enthalpy difference surface cooler 10 and condensation heat recoverer 11.
Furtherly, the outlet of the compressor 4 connects the entrance of condenser 5 and entering for condensation heat recoverer 11 respectively Mouthful;Condensation heat recoverer 11 outlet connection condenser 5 entrance, and for avoid adverse current, the outlet of condensation heat recoverer 11 with The first check valve 16 is connected between the entrance of condenser 5, to ensure condensation heat recoverer 11 and the unilaterally connected of condenser 5;It is cold The outlet of condenser 5 connects the entrance of direct expansion evaporator 7 and the entrance of energy storage evaporator 8 respectively;The outlet of energy storage evaporator 8 Outlet with direct expansion evaporator 7 connects the entrance of compressor 4, and the outlet of energy storage evaporator 8 and entering for compressor 4 respectively The 3rd check valve 18 is provided between mouthful, to ensure energy storage evaporator 8 and the unilaterally connected of compressor 4, direct expansion evaporator 7 The second check valve 17 is provided between outlet and the entrance of compressor 4, it is unidirectional with compressor 4 to ensure direct expansion evaporator 7 Connection.
Furtherly, the second magnetic valve 13 is provided between the entrance of the outlet of the compressor 4 and condenser 5;It is described The first magnetic valve 12 is provided between the outlet of compressor 4 and the entrance of condensation heat recoverer 11;The outlet connection of condenser 5 is swollen The 3rd magnetic valve 14, expansion valve 6 and energy-storage evaporation are provided between the entrance of swollen valve 6, expansion valve 6 and direct expansion evaporator 7 The 4th magnetic valve 15 is provided between the entrance of device 8.
Furtherly, the type of cooling of the condenser 5 can be water cooling or air cooling, viewing system size or live feelings Condition is determined.
Furtherly, the energy storage evaporator 8 is arranged in energy storage tank 9, and the outlet of energy storage tank 9 is connected greatly by water pump 19 The entrance of enthalpy difference surface cooler 10, the outlet of big enthalpy difference surface cooler 10 connects the entrance of energy storage tank 9 by electronic proportional integral valve 20. Pass in and out 5/13 DEG C of water temperature cryogenic freezing water provided by energy storage tank 9, electronic proportional integral valve 20 can with precise control water-carrying capacity with Adjust the big treatment of enthalpy difference surface cooler 10 air condition point.
Furtherly, energy storage phase change material is provided with the energy storage tank 9, the energy storage phase change material is solid-liquid phase change material Material, its setting temperature, less than 5 DEG C, is conducive to improving heat pump evaporating temperature, while using phase transformation higher than the freezing point temperature of water The chemical energy of material carries out accumulation of energy, helps to increase cold storage capacity, reduces cold-storage space.Due to 5/13 DEG C of cryogenic freezing water of water temperature Directly provided by energy storage evaporator 8, eliminate pump energy consumption during conventional ice-storage system ice-reserving, and heat pump evaporating temperature Between 0-3 DEG C, for -5 DEG C to -3 DEG C of more current Xu Yuanzhong evaporating temperature, compressor Energy Efficiency Ratio is improve.
Furtherly, the pipe row of the big enthalpy difference surface cooler is more than 6 rows, to be conducive to by cryogenic freezing water to fresh air Lowered the temperature and more thoroughly dehumidified.
Furtherly, fresh air and air draft are respectively through air total heat recovery device 3, and are realized in air total heat recovery device 3 Energy regenerating;New blower fan 1 is arranged at the air outlet of fresh air channel A, and exhaust blower 2 is arranged at the air outlet of air exhaust passage B.
Specific control method:
Night electricity price low-valley interval, new blower fan 1 and exhaust blower 2 are closed, and compressor 4 starts, the first magnetic valve 12 and the 3rd Magnetic valve 14 is closed, and the second magnetic valve 13 and the 4th magnetic valve 15 are powered and open, and the HTHP of compressor 4 is vented by condenser Turn into cryogenic high pressure liquid refrigerants after 5 coolings, then by after the expansion of expansion valve 6, as low-temp low-pressure vapour-liquid admixture refrigerant, Then evaporation in energy storage evaporator 8 again in energy storage tank 9, the phase-change material in energy storage tank 9 is carried out using the chemical energy of material Accumulation of energy, phase-change material is changed into solid-liquid admixture from liquid;Capacity in view of compressor 4 and energy storage tank 9 should be adapted to electricity on daytime The cold of valency par period Fresh air handing, total maximum treatment load proportion of fresh air shared by the accumulation of energy capacity of compressor 4 should be by differently Area time-of-use tariffs preferential policy determines, preferably 2/3rds, insufficient section is completed by heat pump cooperation;Condenser 5 Radiated by air-cooled or water-cooling pattern.
The electricity price par period on daytime, when outdoor fresh air is hot humid air, air treatment system is:Open new blower fan 1 and exhaust blower 2, hot humid fresh air with low temperature and low humidity air draft after air total heat recovery device 3 carries out energy regenerating, put by air draft Outdoor is discharged to by exhaust blower 2 after going out cold, by the direct expansion evaporator 7 of heat pump after fresh air absorption cold, at this time Because fresh air humiture is still higher, the evaporating temperature of direct expansion evaporator 7 is higher than return air state air, heat pump system System Energy Efficiency Ratio is high;Humiture independent process system is also not reaching to new by the fresh air of the cool-down dehumidification of direct expansion evaporator 7 The requirement of wind-warm syndrome humidity, at this time fresh air is again by the big enthalpy difference surface cooler 10 of cryogenic freezing water, now big enthalpy difference surface cooler 10 On electronic proportional integral valve 20 connect, open water pump 19, the phase-change material in energy storage tank 9 starts to release cold, and cryogenic freezing water is opened Begin to circulate, electronic proportional integral valve 20 is step-less adjustment, and the absolute humidity of precise control fresh air is water capacity;Fresh air at this time Water capacity reaches requirement of the humiture independent process system to fresh air water capacity, and temperature is significantly less than humiture independent process Requirement of the system to fresh air leaving air temp (18-20 DEG C), through the low temperature and low humidity fresh air of excessive enthalpy difference surface cooler 10 again by condensation The intensification of heat regenerator 11, by adjusting the aperture size of the first magnetic valve 12, control leaving air temp is in rational temperature range In (18-20 DEG C), while cooling of the low temperature to condensation heat recoverer 11 also contributes to reduce the condensation temperature of heat pump, improve The Energy Efficiency Ratio of heat pump.Heat pump ruuning situation is:Compressor 4 starts, the first magnetic valve 12, the second magnetic valve 13 and Three magnetic valve 14 is powered and opens, and the 4th magnetic valve 15 is closed, and the exhaust of the HTHP of compressor 4 is simultaneously by condensation heat recoverer 11 And condenser 5 is cooled to cryogenic high pressure liquid refrigerants, unit leaving air temp height is by the entrance of heat pump condensation heat recoverer 11 The aperture size control of the first magnetic valve 12, the relatively low aperture of temperature is increased, and temperature drift aperture reduces, cryogenic high pressure liquid refrigerants By after the expansion of expansion valve 6, as low-temp low-pressure vapour-liquid admixture refrigerant, then being evaporated in direct expansion evaporator 7 again, Cool-down dehumidification pretreatment is carried out to the fresh air after Total heat exchange, complete low-temp low-pressure saturation cold media gas is evaporated and is returned to compressor 4 mufflers.
Above-mentioned is preferred scheme of the invention, and general principle of the invention, principal character and the present invention has been shown and described Advantage.Those skilled in the art should be recognized that the present invention is not limited to the above embodiments, above-described embodiment and specification Described in merely illustrate the principles of the invention, without departing from the spirit and scope of the present invention the present invention also have it is various Changes and improvements, these changes and improvements all fall within the protetion scope of the claimed invention.The claimed scope of the invention is by institute Attached claims and its equivalent are defined.

Claims (10)

1. double big enthalpy difference accumulation of energy Fresh air handling units of low-temperature receiver of a kind of energy recovery type, including air treatment system, heat pump and accumulation of energy System;The air treatment system includes the new blower fan (1) being arranged in fresh air channel (A), is arranged in air exhaust passage (B) Exhaust blower (2), and it is respectively communicated with air total heat recovery device (3) of fresh air channel (A) and air exhaust passage (B);It is characterized in that:Institute Stating heat pump includes the compressor (4) of annular closure connection, condensation heat recoverer (11), condenser (5), expansion valve (6), straight Expansion evaporator (7) and energy storage evaporator (8) are connect, the energy-storage system includes that the energy storage tank (9) of interconnection, big enthalpy difference table are cold Device (10), water pump (19) and electronic proportional integral valve (20), wherein, condensation heat recoverer (11), direct expansion evaporator (7) and Big enthalpy difference surface cooler (10) is respectively arranged in fresh air channel (A).
2. double big enthalpy difference accumulation of energy Fresh air handling units of low-temperature receiver of energy recovery type according to claim 1, it is characterised in that:The air Total heat recovery device (3) is provided with fresh air inlet, fresh air outlet, air draft entrance and wind exhausting outlet, fresh air inlet and fresh air channel (A) Air inlet communicate, fresh air outlet is communicated with the air outlet of fresh air channel (A), the air inlet of air draft entrance and air exhaust passage (B) Communicate, wind exhausting outlet is communicated with the air outlet of air exhaust passage (B);Direct expansion evaporator (7), big enthalpy difference surface cooler (10) and cold Solidifying heat regenerator (11) is set in turn between the outlet of the fresh air of air total heat recovery device (3) and the air outlet of fresh air channel (A), Fresh air sequentially passes through direct expansion evaporator (7), big enthalpy difference surface cooler (10) and condensation heat recoverer (11).
3. double big enthalpy difference accumulation of energy Fresh air handling units of low-temperature receiver of energy recovery type according to claim 2, it is characterised in that:The compression The outlet of machine (4) connects the entrance of condenser (5) and the entrance of condensation heat recoverer (11) respectively, condensation heat recoverer (11) The entrance of outlet connection condenser (5), the outlet of condenser (5) connects entrance and the accumulation of energy of direct expansion evaporator (7) respectively The entrance of evaporator (8), the outlet of energy storage evaporator (8) and the outlet of direct expansion evaporator (7) connect compressor (4) respectively Entrance.
4. double big enthalpy difference accumulation of energy Fresh air handling units of low-temperature receiver of energy recovery type according to claim 3, it is characterised in that:The compression The second magnetic valve (13) is provided between the outlet of machine (4) and the entrance of condenser (5);The outlet of the compressor (4) with it is cold The first magnetic valve (12) is provided between the entrance of solidifying heat regenerator (11);The outlet of the condensation heat recoverer (11) and condensation The first check valve (16) is connected between the entrance of device (5);The outlet of condenser (5) connects expansion valve (6), expansion valve (6) with The 3rd magnetic valve (14) is provided between the entrance of direct expansion evaporator (7), expansion valve (6) enters with energy storage evaporator (8) The 4th magnetic valve (15) is provided between mouthful;It is connected between the outlet of direct expansion evaporator (7) and the entrance of compressor (4) Second check valve (17);The 3rd check valve (18) is connected between the outlet of energy storage evaporator (8) and the entrance of compressor (4).
5. double big enthalpy difference accumulation of energy Fresh air handling units of low-temperature receiver of energy recovery type according to claim 4, it is characterised in that:The condensation The type of cooling of device (5) is water cooling or air cooling.
6. double big enthalpy difference accumulation of energy Fresh air handling units of low-temperature receiver of energy recovery type according to claim 5, it is characterised in that:The accumulation of energy Evaporator (8) is arranged in energy storage tank (9), and the outlet of energy storage tank (9) connects big enthalpy difference surface cooler (10) by water pump (19) Entrance, the outlet of big enthalpy difference surface cooler (10) connects the entrance of energy storage tank (9) by electronic proportional integral valve (20);The big enthalpy Difference surface cooler (10) pipe row is surface-type heat exchanger more than six rows.
7. double big enthalpy difference accumulation of energy Fresh air handling units of low-temperature receiver of energy recovery type according to claim 6, it is characterised in that:The accumulation of energy Energy storage phase change material is provided with tank (9), the freezing point temperature of the setting temperature higher than water of the energy storage phase change material, less than 5 DEG C.
8. double big enthalpy difference accumulation of energy Fresh air handling units of low-temperature receiver of the energy recovery type according to claim any one of 1-7, it is characterised in that: New blower fan (1) is arranged at the air outlet of fresh air channel (A), and exhaust blower (2) is arranged at the air outlet of air exhaust passage (B).
9. a kind of control method of the double big enthalpy difference accumulation of energy Fresh air handling units of low-temperature receiver of energy recovery type as claimed in claim 7, its feature It is:Night electricity price low-valley interval, heat pump work, it is comprised the following steps:
A, new blower fan (1) and exhaust blower (2) are closed, and compressor (4) starts, and the first magnetic valve (12) and the 3rd magnetic valve (14) are closed Close, the second magnetic valve (13) and the 4th magnetic valve (15) are powered and open;
B, the exhaust of compressor (4) HTHP turn into cryogenic high pressure liquid refrigerants after condenser (5) is cooled down, then by expansion After valve (6) expansion, as low-temp low-pressure vapour-liquid admixture refrigerant;
C, low-temp low-pressure vapour-liquid admixture the refrigerant evaporation in energy storage evaporator (8), the phase-change material in energy storage tank (9) are utilized The chemical energy of material carries out accumulation of energy.
10. a kind of control method of the double big enthalpy difference accumulation of energy Fresh air handling units of low-temperature receiver of energy recovery type as claimed in claim 7, its feature It is:The control method of electricity price par period on daytime is comprised the following steps:
A), air treatment system works first:New blower fan (1) and exhaust blower (2) are opened, hot humid fresh air is arranged with low temperature and low humidity After air total heat recovery device (3) carries out energy regenerating, air draft is discharged to outdoor, fresh air to wind after releasing cold by exhaust blower (2) Direct expansion evaporator (7), big enthalpy difference surface cooler (10) and condensing units (11) are sequentially passed through after absorbing cold;
B), heat pump is started working:
1), compressor (4) starts, and the first magnetic valve (12), the second magnetic valve (13) and the 3rd magnetic valve (14) are powered and open, the Four magnetic valves (15) are closed;
2), compressor (4) HTHP exhaust is cooled to cryogenic high pressure by condensation heat recoverer (11) and condenser (5) simultaneously Liquid refrigerants, cryogenic high pressure liquid refrigerants by expansion valve (6) expansion after, as low-temp low-pressure vapour-liquid admixture refrigerant;
3), the evaporation in direct expansion evaporator (7) of low-temp low-pressure vapour-liquid admixture refrigerant, enters to the fresh air after Total heat exchange Row pretreatment, evaporates complete low temperature low pressure gas and returns to compressor (4);
C), fresh air then passes through the big enthalpy difference surface cooler of cryogenic freezing water by direct expansion evaporator (7) cool-down dehumidification (10), now electronic proportional integral valve (20) is connected, and water pump (19) is opened, and the phase-change material in energy storage tank (9) starts to release cold, low Warm chilled water is started the cycle over, and makes fresh air water capacity less than requirement of the humiture independent process system to fresh air water capacity, and low temperature is low Wet fresh air by the reheating of condensation heat recoverer (11), leaving air temp is controlled by the aperture for adjusting the first magnetic valve (12) again, Fresh air leaving air temp is set to reach requirement of the humiture independent process system to fresh air leaving air temp.
CN201611015029.2A 2016-11-18 2016-11-18 Energy recovery double-cold-source high-enthalpy-difference energy storage fresh air handling unit and control method thereof Pending CN106705334A (en)

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