CN107990584A - A kind of CO 2 trans-critical heat pump formula refrigeration system - Google Patents
A kind of CO 2 trans-critical heat pump formula refrigeration system Download PDFInfo
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- CN107990584A CN107990584A CN201711183848.2A CN201711183848A CN107990584A CN 107990584 A CN107990584 A CN 107990584A CN 201711183848 A CN201711183848 A CN 201711183848A CN 107990584 A CN107990584 A CN 107990584A
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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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- B—PERFORMING OPERATIONS; TRANSPORTING
- B01—PHYSICAL OR CHEMICAL PROCESSES OR APPARATUS IN GENERAL
- B01D—SEPARATION
- B01D3/00—Distillation or related exchange processes in which liquids are contacted with gaseous media, e.g. stripping
- B01D3/06—Flash distillation
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/30—Expansion means; Dispositions thereof
- F25B41/31—Expansion valves
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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
- F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
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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]
- Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating
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- Mechanical Engineering (AREA)
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- Power Engineering (AREA)
- Chemical Kinetics & Catalysis (AREA)
- Other Air-Conditioning Systems (AREA)
Abstract
The present invention discloses a kind of CO 2 trans-critical heat pump formula refrigeration system, and the exhaust outlet of first and second compressor is all connected with the first opening of the first electric three passes, and the second opening of the first electric three passes connects check valve by refrigerant water- to-water heat exchanger and combines；First opening of the 3rd opening connection refrigerant air heat exchanger of the first electric three passes；The vapor phase refrigerant outlet of the air entry connection flash tank of second compressor；The gas vent of the air entry connection gas-liquid separator of first compressor；The entrance of gas-liquid separator connects the first opening of the second electric three passes, the first opening of the second opening connection refrigerant air heat exchanger of the second electric three passes, the 3rd opening connection refrigerant water- to-water heat exchanger of the second electric three passes；The liquid phase refrigerant outlet of the two phase refrigerant entrance and flash tank of flash tank is all connected with check valve combination.After this attached a set of equipment of building, cooling in summer, heat supply in winter, the trilogy supply energy-saving system of annual domestic hot-water supply can be realized.
Description
Technical field
The invention belongs to HVAC refrigeration and technical field of heat pumps, be related to it is a kind of allow hand over refrigeration and heating mode across facing
Boundary CO2Refrigeration system.
Background technology
In recent years, as people have become government to the growing interest of environmental problem, use environment friendly refrigerant
And the target that various research institutions are of interest, wherein, it is most important part using natural refrigerant as refrigerant.CO2Tool
There is preferable environmental-protecting performance, any unfavorable result will not be produced to environment as refrigerant.CO2Belong to inert gas, it is nontoxic
It is non-stimulated；It is safe and non-toxic with good security and chemical stability, it is non-combustible, even if not decomposing generation at high temperature yet
Pernicious gas；It is 1, CO to global warming potential index GWP2Commercial synthesis is not required, it is only necessary to which extraction can in an atmosphere
With easy to use；Meanwhile it to atmospheric ozone layer without destruction, ODP 0.Also, CO2Superior thermophysical property itself and
Good migration characteristic also is adapted for it as refrigeration working medium, and thermal conductivity factor and specific heat at constant pressure are high, and vapour density is small, dynamic viscosity
Small, surface tension is small, these features provide premise for the miniaturization of unit and cost savings.Preceding International Institute or Refrigeration chairman
G.Lorentzen is advocated using natural refrigerant energetically, he proposes modern Trans-critical cycle CO2Refrigeration and heat pump circulating system, from this,
CO2The research of refrigerating plant using another with becoming valued hot spot in the world.
Continuous worsening due to China's environmental problem and energy crisis, field of heating in the winter time is using low-carbon environment-friendly stabilization again
Efficient heat pump techniques have become national heat supply energy sustainable development to substitute original distributed coal-fired, gas fired-boiler
Key project and instruction policy.The requirement for the field relevant criterion that heated according to us, the hot water supply of heat sink heating end
Temperature requirement is higher than 70 DEG C, this is a huge challenge for the heat pump system produced based on conventional refrigerant.So
And Trans-critical cycle CO2Heat pump is due to the operating mode of its trans critical cycle, its huge temperature glide in Trans-critical cycle area rather than fixed
The condensation process of temperature enables this system that hot water is heated to very high temperature, is very suitable in the reality in heating field
Demand, huge development potentiality is suffered from for the energy burden and environmental pollution for solving China's warm season.
Trans-critical cycle CO2The huge advantage of heat pump is that it is being badly in need of having incomparable property in the heating field of high-temperature water outlet
Can advantage.Due to CO2When huge temperature glide rather than conventional refrigerant when Trans-critical cycle goes operation are run in close-to-critical range
Fixed condensation temperature so that recirculated water can be once heated to high temperature and possess preferable efficiency at the same time by him.It is many
Well known, the thermal energy (can be considered as solar energy) in atmospheric environment can operationally be absorbed and be transferred to by heat pump system to be added
Heat sink side, is a kind of sustainable energy application mode of green clean environment firendly, and effectiveness of performance can generally reach more than 3.0.
Therefore, if Trans-critical cycle CO can be used2Heat pump come replace the circle's common coal-burning boiler of institute of China's heating at present and gas fired-boiler to
Family carries out heating hot water and the supply of domestic hot-water, and the environmental problem and energy crisis faced at present for solution China is all one
The very important behave of item.
If however, by Trans-critical cycle CO2The effect of system is limited only within the heating application in cold time in winter, every year
The conventional operation time is only 100 days or so, not only increases the initial cost of daily use chemicals, and it also requires a set of refrigeration system of optional equipment
Unite to solve the refrigeration demand of building and user's summer.In fact, Trans-critical cycle CO2System is the same with conventional refrigerant system,
On the premise of it can efficiently heat and be placed in domestic hot-water and heating hot water, cold and hot pattern switching effect can be equally realized in summer
Fruit carries out cooling.Why Trans-critical cycle CO is had not yet to see2Heat pump and the double switching systems processed of refrigeration, completely for no other reason than that CO2
The conventional operating pressures of working medium are excessive, can not be directed to such hyperpressure on the market and the four-way reversing valve that manufacture and
.
Simultaneously as CO 2 trans-critical heat pump formula refrigeration system has the switching condition of double-mode, and it is each
The excursion of operating condition is also extremely extensive under pattern, thus the optimal pressure at expulsion of system also has greatly change accordingly
Dynamic scope, is badly in need of complete set and accurately calculates correlation to predict optimal exhaust pressure value and the optimal centre under different operating modes
Pressure value.
The content of the invention
In order to solve the above-mentioned problems of the prior art, it is an object of the invention to provide one kind can realize refrigeration with
The CO 2 trans-critical heat pump formula refrigeration system of two-way mode switching is heated, and in refrigeration and heating super large scope variable working condition
Under the conditions of can stable operation, and ensure all to operate in optimal pressure at expulsion and optimal under heating mode or refrigeration mode
Under the conditions of intermediate pressure.So that after this attached a set of equipment of building, cooling in summer, heat supply in winter, annual confession can be realized
The trilogy supply energy-saving system of domestic hot-water.
In order to achieve the above object, the present invention adopts the following technical scheme that：
A kind of CO 2 trans-critical heat pump formula refrigeration system, including the first compressor, the second compressor, first electronic three
Logical, the second electric three passes, refrigerant-water- to-water heat exchanger, check valve combination, flash tank, refrigerant-air heat exchanger and gas-liquid separation
Device；
The exhaust outlet of first compressor, the exhaust outlet of the second compressor are all connected with the first opening of the first electric three passes, the
First opening of second opening connection refrigerant-water- to-water heat exchanger of one electric three passes, the 3rd opening connection of the first electric three passes
First opening of refrigerant-air heat exchanger；Second opening connection check valve combination of refrigerant-water- to-water heat exchanger；
The vapor phase refrigerant outlet of the air entry connection flash tank of second compressor；The air entry connection gas of first compressor
The gas vent of liquid/gas separator；The entrance of gas-liquid separator connects the first opening of the second electric three passes, the second electric three passes
First opening of the second opening connection refrigerant-air heat exchanger, the 3rd opening connection refrigerant-water of the second electric three passes change
First opening of hot device；
The second opening, the liquid phase of the two phase refrigerant entrance of the flash tank and flash tank refrigeration of refrigerant-air heat exchanger
Agent outlet is all connected with check valve combination.
Further, check valve combination includes the first check valve, the second check valve, the 3rd check valve and the 4th check valve；
The outlet of the entrance and the 4th check valve of second opening the 3rd check valve of connection of refrigerant-water- to-water heat exchanger；Refrigerant-air changes
The outlet of the entrance and the second check valve of second opening the first check valve of connection of hot device；The outlet connection the 3rd of first check valve
The outlet of check valve and the two phase refrigerant entrance of flash tank；The entrance of second check valve connects entrance and the sudden strain of a muscle of the 4th check valve
The liquid phase refrigerant outlet of steaming pot.
Further, the outlet of the first check valve is entered by the two phase refrigerant of the first electric expansion valve connection flash tank
Mouthful；The liquid phase refrigerant that the entrance of second check valve connects flash tank by the second electric expansion valve exports.
Further, first filter is equipped between the outlet of the first check valve and the first electric expansion valve.
Further, it is equipped with the second filter between the outlet of the liquid phase refrigerant of the second electric expansion valve and flash tank.
Further, during heating operation, the paths of the first electric three passes switches to the first opening and the second open communication
Pass-through state, connects the discharge chamber and refrigerant-water heat exchanger of the first compressor and the second compressor, blocks compressor air-discharging
The connection of chamber and refrigerant-air heat exchanger；The path of second electric three passes switches to the first opening and the second open communication
Pass-through state, connect refrigerant-air heat exchanger and gas-liquid separator, block compressor air suction chamber and refrigerant-hydro-thermal
The connection of exchanger；First compressor is electronic by first with the high-temperature high-pressure refrigerant gas that the second compressor discharge chamber is discharged
Three-way flow is into refrigerant-water heat exchanger, during the cryogenic high pressure refrigerant gas after the completion of exchanging heat with water is combined into check valve；
Due to the unidirectional on-off action of check valve, the refrigerant gas flowed out in refrigerant-water- to-water heat exchanger can only pass through the 3rd check valve
Into in the first electric expansion valve, the middle compression refrigerant fluid to throttle by first order electric expansion valve enters flash tank, flashes
The vapor phase refrigerant gone out is passed directly into the second compressor and is compressed, and the refrigerant of liquid phase throttles via the second electric expansion valve
Enter refrigerant-air heat exchanger to low-pressure state, and by the second check valve, finally return to first via gas-liquid separator
The air entry of compressor, completes a circulation.
Further, during refrigerating operaton, the paths of the first electric three passes switches to the first opening and the 3rd open communication
Non- pass-through state, connects the discharge chamber and refrigerant-air heat exchanger of the first compressor and the second compressor, blocks compressor
The connection of discharge chamber and refrigerant-water heat exchanger；The path of second electric three passes switches to the first opening and the 3rd opening connects
The non-pass-through state passed through, connection refrigerant-water heat exchanger and gas-liquid separator, blocking compressor air suction chamber and refrigerant-
The connection of air heat exchanger；The high-temperature high-pressure refrigerant gas of compressor discharge chamber discharge flows into system by the first electric three passes
Cryogen-air heat exchanger, in being combined with the cryogenic high pressure refrigerant gas after the completion of air heat-exchange into check valve；Due to list
To the unidirectional on-off action of valve, the refrigerant gas flowed out in refrigerant-air heat exchanger can only pass through the entrance of the first check valve
In first electric expansion valve, the middle compression refrigerant fluid to throttle by first order electric expansion valve enters flash tank, flashes off
Vapor phase refrigerant is passed directly into the second compressor and is compressed, and the refrigerant of liquid phase throttles to low via the second electric expansion valve
After pressure condition, and enter refrigerant-water- to-water heat exchanger by the 4th check valve, finally return to the first compressor via gas-liquid separator
Air entry, complete one circulation.
Further, when system is run with heating mode, since the power condition changing situation residing for system operation is extremely multiple
It is miscellaneous, the inflow temperature T of recirculated waterw,f, recirculated water leaving water temperature Tw,sAnd the environment temperature T of system operationairCan be to across facing
The heating performance of boundary's carbon dioxide heat pump system produces strong influence.Under heating mode the optimal pressure at expulsion of system operation with
The situation of change of operating condition as shown in figure 3, according to the analogue data embodied in Fig. 3, the present invention proposes Trans-critical cycle dioxy
Change optimal pressure at expulsion (P of the carbon heat pump type refrigerating system when heating mode is rund) correlation is calculated, it is as follows：
Pd=14.5+1.135*Tw,f+1.1*(Tw,s-Tw,f)+0.7*Tair
Wherein optimal pressure at expulsion (Pd) unit be bar, recirculated water inflow temperature Tw,f, recirculated water leaving water temperature Tw,sWith
And environment temperature TairUnit for DEG C.
Further, when system is run in a chiller mode, since the cold water in national standard for handpiece Water Chilling Units imports and exports temperature
Degree, which has, to be distinctly claimed (inflow temperature of handpiece Water Chilling Units is 12 DEG C in national standard, and leaving water temperature is 7 DEG C), therefore Trans-critical cycle titanium dioxide
The major influence factors of carbon heat pump type refrigerating system performance are the environment temperature T of system operationair.System operation under refrigeration mode
Optimal pressure at expulsion as the situation of change of operating condition is as shown in figure 4, according to the analogue data embodied in Fig. 4, the present invention
Propose optimal pressure at expulsion (P of the CO 2 trans-critical heat pump formula refrigeration system when refrigeration mode is rund) calculating close
Connection formula, it is as follows：
Pd=2.6*Tair+7.5
Wherein optimal pressure at expulsion (Pd) unit be bar, environment temperature TairUnit for DEG C.
Further, when system is run with heating mode, to exist since invention introduces intermediate flash tank, system
Optimal intermediate pressure value P is certainly existed in operational processm.The optimal intermediate pressure of system operation is with operation under heating mode
The situation of change of operating mode is as shown in figure 3, according to the analogue data embodied in Fig. 3, and The present invention gives optimal intermediate pressure value
Computational methods, it is as follows：
Pm=0.92* (Pd*Pe)1/2
Wherein pressure at expulsion (Pd), evaporating pressure PeAnd intermediate pressure PmUnit be bar.
Further, when system is run in a chiller mode, to exist since invention introduces intermediate flash tank, system
Optimal intermediate pressure value P is certainly existed in operational processm.The optimal intermediate pressure of system operation is with operation under refrigeration mode
The situation of change of operating mode is as shown in figure 4, according to the analogue data embodied in Fig. 4, and The present invention gives optimal intermediate pressure value
Computational methods, it is as follows：
Pm=5.52* (Pd)1/2
Wherein pressure at expulsion (Pd) and intermediate pressure PmUnit be bar.
Compared to the prior art compared with the present invention has the following advantages：
1. the present invention by the reasonable disposition and synergistic effect of two electric three passes and four check valves, fully achieve across
Critical carbon dioxide system only allows in the four-way reversing valve and electric expansion valve for lacking safety and stability under conditions of one-way flow
Commutation problem, enable the refrigerant to the changing flow direction between two heat exchangers, solve existing Trans-critical cycle CO2System can only be used
The actuality problem of cooling in summer cannot be switched in heat supply in winter, realizes cooling in summer, heat supply in winter, whole year supply life
The application demand of hot water.
2. employing a flash tank and gas-liquid separator in the present invention, they are also aobvious on the basis of respective own job effect
Play the role of storing refrigerant with writing, system (can correspond to the maximum of the system according to the highest temperature operating mode of refrigeration mode
Circulating mass of refrigerant) fill refrigerant, and when system operation (corresponds to the system most in the lowest temperature operating mode of heating mode
Small circulating mass of refrigerant) under when, a large amount of refrigerants can be stored in two pressure vessels, and the circulating mass of refrigerant in system is still
It can so meet service requirement, the appropriate design of two heat exchangers, can realize that the present invention is huge with heating mode in refrigeration in addition
Good stability in big variable working condition scope and refrigerant flow mobility scale.
3. employ medium pressure flash tank in the present invention, change and gases at high pressure are once throttled directly to evaporating pressure weigh again
The present situation being newly compressed, but the most of gas that will first be flashed off using a primary electron expansion valve and medium pressure flash tank
Phase refrigerant introduces 2 air entry of compressor, and the endless form of parallel compression of beginning therefrom is pressed off so by some refrigerant, both can be with
A part of work done during compression is saved, and the refrigerant mass dryness fraction of evaporator can be made to be lower, coefficient of heat transfer enhancing, evaporator size subtracts
It is small.
4. the present invention proposes the CO 2 trans-critical heat pump formula refrigeration system under refrigeration mode and heating mode respectively
Optimal pressure at expulsion and optimal intermediate pressure control and calculate correlation, can ensure system normal work when, no matter
It is operated under refrigeration mode or heating mode, can be according to the optimal exhaust pressure of the change Automatic-searching of running environment operating mode
Power and intermediate pressure, ensure the coefficient of performance highest of system operation instantly, further improve the energy-saving effect of the system.
In view of the problems of the existing technology the present invention, has transformed system flow, between cleverly being combined using check valve
Runner switching fitting instead of the work of four-way reversing valve, solve common Trans-critical cycle CO2Heat pump system can only be used to winter
The application problem of heating, realizes Trans-critical cycle CO2The two-way mode switching that system heats between cooling in summer in the winter time, and add
The domestic hot-water supply that can accomplish of Trans-critical cycle system whole year, and the introducing of parallel compressors saved Partial shrinkage
Work(, and keep running under the conditions of optimal pressure at expulsion and optimal intermediate pressure throughout the year, greatly save the configuration of building HVAC
Initial cost and use cost, environment friendly reform for the cold and hot energy of country and play direction compared to having very big lifting at present
The effect of property.
Brief description of the drawings
Fig. 1 is a kind of CO 2 trans-critical heat pump formula refrigeration system that can realize refrigeration and the two-way switching of heating mode
Heating operation schematic diagram；
Fig. 2 is a kind of CO 2 trans-critical heat pump formula refrigeration system that can realize refrigeration and the two-way switching of heating mode
Refrigerating operaton schematic diagram；
Fig. 3 is the optimal pressure at expulsion of heating mode and optimal intermediate pressure curve；
Fig. 4 is the optimal pressure at expulsion of refrigeration mode and optimal intermediate pressure curve.
Embodiment
Refering to Figure 1, a kind of CO 2 trans-critical heat pump formula refrigeration system of the present invention, including the first compressor 1,
Second compressor 2, the first electric three passes E1, the second electric three passes E2, refrigerant-water- to-water heat exchanger 3, the first check valve SV1, second
Check valve SV2, the 3rd check valve SV3, the 4th check valve SV4, first filter F1, the second filter F 2, the first electronic expansion
Valve EV1, the second electric expansion valve EV2, flash tank 4, refrigerant-air heat exchanger 5 and gas-liquid separator 6.
The exhaust outlet of first compressor 1, the exhaust outlet of the second compressor 2 are all connected with the first of the first electric three passes E1 and open
Mouthful, the first opening of second opening connection refrigerant-water- to-water heat exchanger 3 of the first electric three passes E1, refrigerant-water- to-water heat exchanger 3
The outlet of the entrance and the 4th check valve SV4 of second the 3rd check valve SV3 of opening connection；The 3rd opening of first electric three passes E1
Connect the first opening of refrigerant-air heat exchanger 5；
The vapor phase refrigerant outlet of the air entry connection flash tank 4 of second compressor 2；The air entry of first compressor 1 connects
Connect the gas vent of gas-liquid separator 6；The entrance of gas-liquid separator 6 connects the first opening of the second electric three passes E2, the second electricity
First opening of the second opening connection refrigerant-air heat exchanger 5 of dynamic threeway E2, the 3rd opening of the second electric three passes E2 connect
Connect the first opening of refrigerant-water- to-water heat exchanger 3；
The entrance and the second check valve SV2 of second the first check valve SV1 of opening connection of refrigerant-air heat exchanger 5
Outlet；The outlet of the 3rd check valve SV3 of outlet connection and one end of first filter F1 of first check valve SV1, the first filtering
The device F1 other ends connect first electric expansion valve EV1 one end, and the first electric expansion valve EV1 other ends connect the two-phase of flash tank 4
Refrigerant inlet；The entrance of the 4th check valve SV4 of entrance connection of second check valve SV2 and the one of the second electric expansion valve EV2
End, the other end of the second electric expansion valve EV2 connect 2 one end of the second filter F, 2 other end of the second filter F connection flash tank
4 liquid phase refrigerant outlet.
On subassembly selection, since a kind of CO 2 trans-critical heat pump formula refrigeration system proposed by the present invention can be realized
Switched between freezing and heating both of which, therefore in compressor possessed by conventional transcritical carbon dioxide heat-pump,
Existing flash distillation under gas cooler, evaporator, gas-liquid separator, filter and electric expansion valve and parallel compress mode
On the basis of tank, and two electric three passes E1 are with the addition of, E2 and four set of check valve SV1, SV2, SV3, SV4, pass through electric three passes
With the mutual synergistic effect of check valve, acted on instead of commutation of the four-way reversing valve in conventional refrigerant system, ensure that system can be with
Switch between refrigeration and heating mode.Two electric three passes E1, E2 are respectively placed in the exhaust outlet and air entry of compressor, energy
Enough coordinated by the switching on valve road and realize that the gases at high pressure of exhaust outlet of compressor can be passed through different heat exchangers, afterwards via another
One heat exchanger returns to compressor.Further, since the electric expansion valve provisioned in critical-cross carbon dioxide system is path type
Expansion valve, that is to say, that fluid can only be allowed to flow through valve body from same direction, if fluid flow direction with defined direction on the contrary,
It cannot realize good throttling expansion effect.Therefore, in order to realize no matter under heating mode or refrigeration mode fluid from
Same direction flows through expansion valve, and the present invention is configured with a set of (four) check valve SV1, SV2, SV3, SV4 before expansion valve, passes through
The synergic adjustment effect of check valve, can realize no matter fluid from which heat exchanger outflow, can be flowed through by same direction
The process of expansion valve.
Further, since the present invention proposes the circulation pattern of middle pressure flash distillation plus parallel compression, it is possible to achieve two-stage throttling
Left and right, the refrigerant gas that the first order flashes off after throttling can be directly entered in parallel compressors therefrom pressure condition pressure
Be reduced to pressure at expulsion, and without rule circulation as usual like that by all refrigerants all throttling to low pressure recompression to high pressure conditions,
Therefore a part of work done during compression can be saved.On the other hand, since the middle compression refrigerant of gas phase state has been introduced into parallel compressors,
Therefore the import of second level throttling is the refrigerant of saturation liquid phase state, it is possible thereby to significantly reduce the refrigerant of evaporator
Mass dryness fraction, increase evaporator in the coefficient of heat transfer, reduce evaporator needed for heat exchange area thus reduce volume, be suitable for industry and commerce
And the limitation in civil applications occasion space.
In addition, the present invention proposes CO 2 trans-critical heat pump formula refrigeration system under refrigeration mode and heating mode respectively
No matter optimal pressure at expulsion and the optimal intermediate pressure control of system and calculating correlation, can ensure system in normal work
It is operated under refrigeration mode or heating mode, can be according to the optimal exhaust pressure of the change Automatic-searching of running environment operating mode
Power and intermediate pressure, ensure the coefficient of performance highest of system operation instantly, further improve the energy-saving effect of the system.
In above-mentioned, a kind of critical-cross carbon dioxide that can realize refrigeration and the two-way switching of heating mode proposed by the present invention
The operational process of heat pump type refrigerating system is as follows：
Refering to Figure 1, when CO 2 trans-critical heat pump formula refrigeration system proposed by the present invention needs heating operation
When, the path of the first electric three passes E1 switches to the pass-through state of the first opening and the second open communication, connects the first compressor 1
Discharge chamber outlet and refrigerant-water heat exchanger 3 with the second compressor 2, block compressor discharge chamber and refrigerant-air heat
The connection of exchanger 5；The path of second electric three passes E2 switches to the pass-through state of the first opening and the second open communication, connection
Refrigerant-air heat exchanger 5 and gas-liquid separator 6 (compressor air suction chamber), block compressor air suction chamber and refrigerant-hydro-thermal
The connection of exchanger 3.After electric three passes are provided with, the high-temperature high-pressure refrigerant gas of compressor discharge chamber discharge passes through first
Electric three passes E1 flows into refrigerant-water heat exchanger 3, and the cryogenic high pressure refrigerant gas after the completion of exchanging heat with water enters check valve
In combination.Due to the unidirectional on-off action of check valve, the refrigerant gas that is flowed out in refrigerant-water- to-water heat exchanger 3 can only pass through the
Three check valve SV3 enter in the combination of first filter F1 and the first electric expansion valve EV1, by first order electric expansion valve
The middle compression refrigerant fluid of EV1 throttlings enters flash tank 4, and the vapor phase refrigerant flashed off is passed directly into the second compressor 2 of auxiliary
It is compressed, and the refrigerant of liquid phase throttles to low-pressure state via the second filter F 2 and the second electric expansion valve EV2, again
Enter refrigerant-air heat exchanger 5 by the second check valve SV2, finally return to the first compressor 1 via gas-liquid separator 6
Air entry, completes a circulation.
Refer to shown in Fig. 2, when CO 2 trans-critical heat pump formula refrigeration system proposed by the present invention needs refrigerating operaton
When, the path of the first electric three passes E1 switches to the non-pass-through state of the first opening and the 3rd open communication, the compression of connection first
The discharge chamber and refrigerant-air heat exchanger 5 of 1 and second compressor 2 of machine, block compressor discharge chamber and refrigerant-hydro-thermal
The connection of exchanger 3；The path of second electric three passes E2 switches to the non-pass-through state that the first opening and the 3rd open communication are crossed,
Refrigerant-water heat exchanger 3 and gas-liquid separator 6 (compressor air suction chamber) are connected, blocks compressor air suction chamber and refrigerant-sky
The connection of gas-heat exchanger 5.After electric three passes are provided with, the high-temperature high-pressure refrigerant gas of compressor discharge chamber discharge passes through
First electric three passes E1 flows into refrigerant-air heat exchanger 5, with the cryogenic high pressure refrigerant gas after the completion of air heat-exchange into
Enter in check valve combination.Due to the unidirectional on-off action of check valve, the refrigerant gas that is flowed out in refrigerant-air heat exchanger 5
The first check valve SV1 can only be passed through to enter in the combination of first filter F1 and the first electric expansion valve EV1, by first order electricity
The middle compression refrigerant fluid of sub- expansion valve EV1 throttlings enters flash tank 4, and the vapor phase refrigerant flashed off is passed directly into auxiliary second
Compressor 2 is compressed, and the refrigerant of liquid phase throttles to low pressure shape via the second filter F 2 and the second electric expansion valve EV2
After state, and enter refrigerant-water- to-water heat exchanger 3 by the 4th check valve SV4, finally return to the first compressor via gas-liquid separator
1 air entry, completes a circulation.
The present invention proposes a kind of CO 2 trans-critical heat pump formula that can realize refrigeration and the two-way switching of heating mode
In addition refrigeration system, the system addition of two electric three passes on the basic components of conventional transcritical carbon dioxide heat pump system
And four check valves, by the reasonable disposition and synergistic effect of these valve bodies, play the role of the commutation in refrigeration system, realize
Conversion of the critical-cross carbon dioxide system between heating mode and refrigeration mode, to realize modern architecture cooling and warming life heat
Water combined supply system provides guiding scheme.In addition, medium pressure flash tank is employed in the system and is equipped with medium pressure gas
Parallel compression, presses the gas flashed off to be directly compressed to pressure at expulsion rather than be all throttled to all refrigerants low by middle
It is compressed again after pressure, on the one hand reduces compression general power, the refrigerant on the other hand greatly reduced into evaporator is done
Degree, therefore heat exchange property can be strengthened, reduce evaporator volume.
When system is run with heating mode, since the power condition changing situation residing for system operation is extremely complex, recirculated water
Inflow temperature Tw,f, recirculated water leaving water temperature Tw,sAnd the environment temperature T of system operationairCan be to Trans-critical cycle titanium dioxide
The heating performance of carbon heat pump system produces strong influence.The optimal pressure at expulsion of system operation is with operation work under heating mode
The situation of change of condition is as shown in figure 3, according to the analogue data embodied in Fig. 3, the present invention proposes CO 2 trans-critical heat pump
Optimal pressure at expulsion P of the formula refrigeration system when heating mode is rund(connect together during the exhaust outlet of two compressors, and
There is no the isolation such as any other valve member, therefore the pressure at expulsion of two compressors is exhaust that is consistent, being referred in the present invention
Pressure is all the common pressure at expulsion of two compressors) correlation is calculated, it is as follows：
Pd=14.5+1.135*Tw,f+1.1*(Tw,s-Tw,f)+0.7*Tair
Wherein optimal pressure at expulsion PdUnit be bar, recirculated water inflow temperature Tw,f, recirculated water leaving water temperature Tw,sAnd
Environment temperature TairUnit for DEG C.
When system is run in a chiller mode, since the cold water out temperature in national standard for handpiece Water Chilling Units has clearly
It is required that (inflow temperature of handpiece Water Chilling Units is 12 DEG C in national standard, and leaving water temperature is 7 DEG C), therefore CO 2 trans-critical heat pump formula system
The major influence factors of cooling system performance are the environment temperature T of system operationair.The optimal exhaust of system operation under refrigeration mode
As the situation of change of operating condition is as shown in figure 4, according to the analogue data embodied in Fig. 4, the present invention is proposed across facing pressure
Optimal pressure at expulsion P of boundary's carbon dioxide heat-pump formula refrigeration system when refrigeration mode is rundCalculating correlation, following institute
Show：
Pd=2.6*Tair+7.5
Wherein optimal pressure at expulsion PdUnit be bar, environment temperature TairUnit for DEG C.
When system is run with heating mode, since invention introduces intermediate flash tank, system is in operational process
In certainly exist optimal intermediate pressure value Pm.The optimal intermediate pressure of system operation is with the change of operating condition under heating mode
Change situation is as shown in figure 3, according to the analogue data embodied in Fig. 3, The present invention gives the computational methods of optimal intermediate pressure value,
It is as follows：
Pm=0.92* (Pd*Pe)1/2
Wherein pressure at expulsion Pd, evaporating pressure Pe(evaporating pressure herein refers to the refrigerant pressure in evaporator；Cause
To be heating operation mode, therefore refer to the pressure in refrigerant-air heat exchanger 5) and intermediate pressure Pm(intermediate pressure
Refer to the outlet pressure of flash tank 4, be also equal to the pressure of inspiration(Pi) of the second compressor 2) unit be bar.
When system is run in a chiller mode, since invention introduces intermediate flash tank, system is in operational process
In certainly exist optimal intermediate pressure value Pm.The optimal intermediate pressure of system operation is with the change of operating condition under refrigeration mode
Change situation is as shown in figure 4, according to the analogue data embodied in Fig. 4, The present invention gives the computational methods of optimal intermediate pressure value,
It is as follows：
Pm=5.52* (Pd)1/2
Wherein pressure at expulsion (Pd) and intermediate pressure PmUnit be bar.
The present invention proposes the CO 2 trans-critical heat pump formula refrigeration system under refrigeration mode and heating mode respectively
Optimal pressure at expulsion and optimal intermediate pressure control and calculating correlation, can ensure no matter system in normal work, works
Under refrigeration mode or heating mode, can according to the optimal pressure at expulsion of change Automatic-searching of running environment operating mode and
Intermediate pressure, ensures the coefficient of performance highest of system operation instantly, further improves the energy-saving effect of the system.
Claims (9)
1. a kind of CO 2 trans-critical heat pump formula refrigeration system, it is characterised in that including the first compressor (1), the second compression
Machine (2), the first electric three passes (E1), the second electric three passes (E2), refrigerant-water- to-water heat exchanger (3), check valve combination, flash tank
(4), refrigerant-air heat exchanger (5) and gas-liquid separator (6)；
Exhaust outlet, the exhaust outlet of the second compressor (2) of first compressor (1) are all connected with the first of the first electric three passes (E1) and open
Mouthful, the first opening of second opening connection refrigerant-water- to-water heat exchanger (3) of the first electric three passes (E1), the first electric three passes
(E1) the first opening of the 3rd opening connection refrigerant-air heat exchanger (5)；Second opening of refrigerant-water- to-water heat exchanger (3)
Connect check valve combination；
The vapor phase refrigerant outlet of the air entry connection flash tank (4) of second compressor (2)；The air entry of first compressor (1)
Connect the gas vent of gas-liquid separator (6)；The first of entrance the second electric three passes of connection (E2) of gas-liquid separator (6) opens
Mouthful, the first opening of the second opening connection refrigerant-air heat exchanger (5) of the second electric three passes (E2), the second electric three passes
(E2) the first opening of the 3rd opening connection refrigerant-water- to-water heat exchanger (3)；
The second opening, the liquid phase of the two phase refrigerant entrance of flash tank (4) and flash tank (4) of refrigerant-air heat exchanger (5)
Refrigerant outlet is all connected with check valve combination.
A kind of 2. CO 2 trans-critical heat pump formula refrigeration system according to claim 1, it is characterised in that unidirectional valve group
Conjunction includes the first check valve (SV1), the second check valve (SV2), the 3rd check valve (SV3) and the 4th check valve (SV4)；
The entrance and the 4th check valve (SV4) of second opening the 3rd check valve (SV3) of connection of refrigerant-water- to-water heat exchanger (3)
Outlet；The entrance and the second check valve (SV2) of second opening the first check valve of connection (SV1) of refrigerant-air heat exchanger (5)
Outlet；The outlet of first check valve (SV1) connects the outlet of the 3rd check valve (SV3) and the two phase refrigerant of flash tank (4)
Entrance；The liquid phase refrigerant of entrance and flash tank (4) that the entrance of second check valve (SV2) connects the 4th check valve (SV4) goes out
Mouthful.
3. a kind of CO 2 trans-critical heat pump formula refrigeration system according to claim 2, it is characterised in that first is unidirectional
The two-phase that the outlet of valve (SV1) and the 3rd check valve (SV3) connects flash tank (4) by the first electric expansion valve (EV1) is freezed
Agent entrance；The entrance of second check valve (SV2) and the 4th check valve (SV4) is connected by the second electric expansion valve (EV2) and flashed
The liquid phase refrigerant outlet of tank (4).
4. a kind of CO 2 trans-critical heat pump formula refrigeration system according to claim 3, it is characterised in that first is unidirectional
First filter (F1) is equipped between the outlet of valve (SV1) and the 3rd check valve (SV3) and the first electric expansion valve (EV1).
A kind of 5. CO 2 trans-critical heat pump formula refrigeration system according to claim 3, it is characterised in that the second electronics
The liquid phase refrigerant of expansion valve (EV2) and flash tank (4) is equipped with the second filter (F2) between outlet.
A kind of 6. CO 2 trans-critical heat pump formula refrigeration system according to claim 3, it is characterised in that heating operation
When, the path of the first electric three passes (E1) switches to the pass-through state of the first opening and the second open communication, the compression of connection first
The discharge chamber and refrigerant-water heat exchanger (3) of machine (1) and the second compressor (2), blocking compressor discharge chamber and refrigerant-
The connection of air heat exchanger (5)；The path of second electric three passes (E2) switches to the straight of the first opening and the second open communication
Logical state, connection refrigerant-air heat exchanger (5) and gas-liquid separator (6), block compressor air suction chamber and refrigerant-water
The connection of heat exchanger (3)；First compressor (1) and the high-temperature high-pressure refrigerant gas of the second compressor (2) discharge chamber discharge
Refrigerant-water heat exchanger (3) is flowed into by the first electric three passes (E1), the cryogenic high pressure refrigerant gas after the completion of exchanging heat with water
Body enters in check valve combination；Due to the unidirectional on-off action of check valve, the refrigerant of the middle outflow of refrigerant-water- to-water heat exchanger (3)
Gas can only pass through the 3rd check valve (SV3) and enter in the first electric expansion valve (EV1), by first order electric expansion valve
(EV1) the middle compression refrigerant fluid of throttling enters flash tank (4), and the vapor phase refrigerant flashed off is passed directly into the second compressor
(2) it is compressed, and the refrigerant of liquid phase throttles to low-pressure state via the second electric expansion valve (EV2), and by second
Check valve (SV2) enters refrigerant-air heat exchanger (5), finally returns to the first compressor (1) via gas-liquid separator (6)
Air entry, completes a circulation.
A kind of 7. CO 2 trans-critical heat pump formula refrigeration system according to claim 3, it is characterised in that refrigerating operaton
When, the path of the first electric three passes (E1) switches to the non-pass-through state of the first opening and the 3rd open communication, the pressure of connection first
The discharge chamber and refrigerant-air heat exchanger (5) of contracting machine (1) and the second compressor (2), block compressor discharge chamber and refrigeration
The connection of agent-water heat exchanger (3)；The path of second electric three passes (E2) switches to the first opening and the 3rd open communication crosses
Non- pass-through state, connection refrigerant-water heat exchanger (3) and gas-liquid separator (6), blocking compressor air suction chamber and refrigerant-
The connection of air heat exchanger (5)；The high-temperature high-pressure refrigerant gas of compressor discharge chamber discharge passes through the first electric three passes
(E1) refrigerant-air heat exchanger (5) is flowed into, enters check valve with the cryogenic high pressure refrigerant gas after the completion of air heat-exchange
In combination；Due to the unidirectional on-off action of check valve, the refrigerant gas of outflow can only be through in refrigerant-air heat exchanger (5)
Cross the first check valve (SV1) to enter in the first electric expansion valve (EV1), in throttling by first order electric expansion valve (EV1)
Compression refrigerant fluid enters flash tank (4), and the vapor phase refrigerant flashed off is passed directly into the second compressor (2) and is compressed, and
The refrigerant of liquid phase throttles to low-pressure state via the second electric expansion valve (EV2), and passes through the 4th check valve (SV4) and enter
Refrigerant-water- to-water heat exchanger (3), finally returns to the air entry of the first compressor (1) via gas-liquid separator, completes a circulation.
A kind of 8. CO 2 trans-critical heat pump formula refrigeration system according to claim 1, it is characterised in that when system with
When heating mode is run, optimal pressure at expulsion P is controlleddFor：
Pd=14.5+1.135*Tw,f+1.1*(Tw,s-Tw,f)+0.7*Tair
Wherein optimal pressure at expulsion PdUnit be bar, recirculated water inflow temperature Tw,f, recirculated water leaving water temperature Tw,sAnd environment
Temperature TairUnit for DEG C；
Alternatively, when system is run in a chiller mode, optimal pressure at expulsion P is controlleddFor：
Pd=2.6*Tair+7.5
Wherein optimal pressure at expulsion PdUnit be bar, environment temperature TairUnit for DEG C.
A kind of 9. CO 2 trans-critical heat pump formula refrigeration system according to claim 1, it is characterised in that when system with
When heating mode is run, the intermediate pressure value is controlled to be：
Pm=0.92* (Pd*Pe)1/2
Wherein pressure at expulsion Pd, evaporating pressure PeAnd intermediate pressure PmUnit be bar；
Alternatively, when system is run in a chiller mode, the intermediate pressure value is controlled to be：
Pm=5.52* (Pd)1/2
Wherein pressure at expulsion PdAnd intermediate pressure PmUnit be bar.
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Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111623553A (en) * | 2020-05-25 | 2020-09-04 | 青岛海尔空调电子有限公司 | Heat pump system |
| CN112303697A (en) * | 2020-10-28 | 2021-02-02 | 青岛海尔空调电子有限公司 | Heat pump system and control method thereof |
| WO2021228018A1 (en) * | 2020-08-27 | 2021-11-18 | 青岛海尔空调电子有限公司 | Air conditioning unit and control method therefor |
Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101319827A (en) * | 2008-05-26 | 2008-12-10 | 刘雄 | Multifunctional CO2 air conditioner heat pump device |
| CN101583834A (en) * | 2006-10-26 | 2009-11-18 | 江森自控科技公司 | Economized refrigeration system |
| CN102003833A (en) * | 2010-10-27 | 2011-04-06 | 华北电力大学（保定） | Transcritical carbon dioxide heat pump type air conditioning water heater using condensation residual heat |
| CN102232167A (en) * | 2008-10-01 | 2011-11-02 | 开利公司 | Liquid vapor separation in transcritical refrigerant cycle |
| CN205261964U (en) * | 2015-12-21 | 2016-05-25 | 珠海格力电器股份有限公司 | Critical heat pump device strides |
| EP3139110A1 (en) * | 2015-08-20 | 2017-03-08 | Lennox Industries Inc. | Carbon dioxide cooling system with subcooling |
| CN206037466U (en) * | 2016-08-31 | 2017-03-22 | 广东美芝制冷设备有限公司 | Cooling systems |
| CN206055993U (en) * | 2016-08-31 | 2017-03-29 | 广东美芝制冷设备有限公司 | Compressor and the refrigeration system with which |
-
2017
- 2017-11-23 CN CN201711183848.2A patent/CN107990584B/en active Active
Patent Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101583834A (en) * | 2006-10-26 | 2009-11-18 | 江森自控科技公司 | Economized refrigeration system |
| CN101319827A (en) * | 2008-05-26 | 2008-12-10 | 刘雄 | Multifunctional CO2 air conditioner heat pump device |
| CN102232167A (en) * | 2008-10-01 | 2011-11-02 | 开利公司 | Liquid vapor separation in transcritical refrigerant cycle |
| CN102003833A (en) * | 2010-10-27 | 2011-04-06 | 华北电力大学（保定） | Transcritical carbon dioxide heat pump type air conditioning water heater using condensation residual heat |
| EP3139110A1 (en) * | 2015-08-20 | 2017-03-08 | Lennox Industries Inc. | Carbon dioxide cooling system with subcooling |
| CN205261964U (en) * | 2015-12-21 | 2016-05-25 | 珠海格力电器股份有限公司 | Critical heat pump device strides |
| CN206037466U (en) * | 2016-08-31 | 2017-03-22 | 广东美芝制冷设备有限公司 | Cooling systems |
| CN206055993U (en) * | 2016-08-31 | 2017-03-29 | 广东美芝制冷设备有限公司 | Compressor and the refrigeration system with which |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111623553A (en) * | 2020-05-25 | 2020-09-04 | 青岛海尔空调电子有限公司 | Heat pump system |
| WO2021228018A1 (en) * | 2020-08-27 | 2021-11-18 | 青岛海尔空调电子有限公司 | Air conditioning unit and control method therefor |
| CN114110833A (en) * | 2020-08-27 | 2022-03-01 | 青岛海尔空调电子有限公司 | Air conditioning unit and control method thereof |
| CN114110833B (en) * | 2020-08-27 | 2023-02-28 | 青岛海尔空调电子有限公司 | Air conditioning unit and control method thereof |
| CN112303697A (en) * | 2020-10-28 | 2021-02-02 | 青岛海尔空调电子有限公司 | Heat pump system and control method thereof |
| CN112303697B (en) * | 2020-10-28 | 2023-12-22 | 青岛海尔空调电子有限公司 | Heat pump system and control method thereof |
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