CN108444127B - Trans-critical cycle CO2The control method of regenerator under heat pump system optimal performance - Google Patents
Trans-critical cycle CO2The control method of regenerator under heat pump system optimal performance Download PDFInfo
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- CN108444127B CN108444127B CN201810327375.7A CN201810327375A CN108444127B CN 108444127 B CN108444127 B CN 108444127B CN 201810327375 A CN201810327375 A CN 201810327375A CN 108444127 B CN108444127 B CN 108444127B
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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
- F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
- F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
- F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B13/00—Compression machines, plants or systems, with reversible cycle
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B40/00—Subcoolers, desuperheaters or superheaters
- F25B40/06—Superheaters
-
- 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
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/029—Control issues
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Abstract
The present invention discloses a kind of Trans-critical cycle CO2The control method of regenerator under heat pump system optimal performance, Trans-critical cycle CO2Heat pump system includes: the entrance of the outlet connection gas cooler of compressor, the entrance of the first by-passing valve of outlet connection of gas cooler, the first entrance of the first outlet connection regenerator of first by-passing valve, the second outlet of by-passing valve connects the entrance of throttle valve with the first outlet of regenerator, the entrance of the outlet connection evaporator of throttle valve, the entrance of the second by-passing valve of outlet connection of evaporator, the second entrance of the first outlet connection regenerator of second by-passing valve, the entrance of the second outlet connect compressor of the second outlet and regenerator of by-passing valve.The present invention is judged whether to need by the outlet temperature of gas cooler using regenerator, using the conversion and opening and closing of by-passing valve, in due course by regenerator access system, so that Trans-critical cycle CO2Heat pump system always works under optimal performance.
Description
Technical field
The invention belongs to technical field of air-conditioning heat pumps, in particular to a kind of Trans-critical cycle CO with regenerator2Heat pump system
Control method.
Background technique
It is well known that the artificial synthesized refrigeration working medium of CFCs and HCFCs class is to lead to one of principal element of global warming,
Therefore it finds and has become the problem of international community is paid close attention to jointly using efficient, environmentally protective refrigeration working medium, it is extremely urgent.
Natural refrigerant CO2As Substitute Working Medium not only environmental protection but also function admirable, high exhaust temperature possessed by trans critical cycle and
Temperature glide is very suitable to water temperature heating, it is allowed to have incomparable excellent of other known working medium in Teat pump boiler application field
Gesture, but conventional system restriction loss limits greatly the raising of system performance.In order to accelerate CO2As refrigeration working medium to functionization
The paces that product strides forward, scholars have studied cycle performance of the various modes to improve system, such as swollen in order to reduce throttling
Swollen loss, increases injector in systems；Regenerator etc. is added in systems in order to reduce hot-fluid loss.It adds back in systems
After hot device, in low-pressure side, regenerator increases the temperature into the refrigerant vapour of compressor, and makes to make due to pressure drop
Cryogen inlet pressure reduces, and the two both increases the specific capacity of refrigerant, to reduce mass flow.In high-pressure side, working medium
It is cooling so that refrigeration effect increases, while improving heating efficiency by the refrigerant from evaporator outlet after regenerator
A possibility that improving liquid refrigerant supercriticality occur before reaching expansion device.
Adding regenerator can be improved the cycle performance of system, to CO2Trans critical cycle heat pump system has very big benefit.
But it is whether to additionally depend on other many factors using regenerator, such as complexity, cost aspect of system etc..And even if
List is from the aspect of the improvement to system performance, and regenerator also can always not be significantly improved to system performance, this also takes
Which kind of certainly in specific working condition, but do not come to a conclusion so far under operating condition using regenerator.
Summary of the invention
The object of the present invention is to provide a kind of Trans-critical cycle CO2The controlling party of regenerator under heat pump system optimal performance
Method judges whether to need to utilize by-passing valve using regenerator under specific operating condition by the outlet temperature of gas cooler
Conversion and opening and closing, in due course by regenerator access system, so that Trans-critical cycle CO2Heat pump system always works under optimal performance.
To achieve the goals above, the technical solution adopted by the present invention is that:
Trans-critical cycle CO2The control method of regenerator under heat pump system optimal performance, the Trans-critical cycle CO2Heat pump system includes:
Compressor, gas cooler, the first by-passing valve, regenerator, throttle valve, evaporator and the second by-passing valve；The outlet of compressor connects
Connect the entrance of gas cooler, the entrance of the first by-passing valve of outlet connection of gas cooler, the first outlet of the first by-passing valve
The first entrance of regenerator is connected, the second outlet of by-passing valve connects the entrance of throttle valve with the first outlet of regenerator, throttles
The entrance of the outlet connection evaporator of valve, the entrance of the second by-passing valve of outlet connection of evaporator, the first of the second by-passing valve go out
The second entrance of mouth connection regenerator, the entrance of the second outlet connect compressor of the second outlet and regenerator of by-passing valve；
The control method includes: the opening and closing of the interface by the first by-passing valve of control and the second by-passing valve, controls backheat
Whether device accesses in the circulatory system；When the entrance and first outlet of the first by-passing valve are opened, second outlet is closed, the second by-passing valve
Entrance and first outlet open, when second outlet is closed, in regenerator access system；When the entrance and second outlet of by-passing valve
It opens, first outlet is closed, and the entrance and second outlet of by-passing valve are opened, and when first outlet is closed, refrigerant is without backheat
Device.
Further, the relationship of environment temperature and the critical value for the outlet temperature for needing the gas cooler using regenerator
Formula is as follows:
Tgas0=0.125*Tenv+32.5 (1)
Wherein: Tgas0--- the critical value using the outlet temperature of gas cooler when regenerator is needed, unit: DEG C；
Tenv--- ambient temperature value, value range are -30 DEG C≤Tenv≤ 30 DEG C, unit: DEG C.
Further, under summer operating mode:
As the outlet temperature T of gas coolergasLower than Tgas0When, do not use regenerator；
As the outlet temperature T of gas coolergasHigher than Tgas0When, using regenerator；
As the outlet temperature T of gas coolergasEqual to Tgas0When, if Compressor Discharge Pressure P is not higher than 8.5MPa
When, using regenerator；If Compressor Discharge Pressure P is higher than 8.5MPa, regenerator is not used.
Further, according to the outlet temperature T of air coolergasAnd Tgas0Size relation difference, by largely testing
With the processing to experimental data, the optimal pressure at expulsion of compressor and the outlet of gas cooler are obtained respectively under various operating conditions
Function correlation between temperature, in practical projects, according to the outlet temperature of gas cooler, control the row of compressor
Atmospheric pressure is optimal exhaust pressure value, to obtain the optimal COP of system；It is systemic to being improved in experimental study from now on
Can, there is directive significance that is very clear and using；
As the outlet temperature T of gas coolergasLower than Tgas0When, the optimal pressure at expulsion of compressor and gas cooling at this time
It is as follows that the outlet temperature of device obtains correlation:
P=0.0032*T*T+0.0702*T+7.1075 (2)
Wherein: P --- the optimal exhaust pressure value of system, unit KPa；
The Outlet Temperature value of the gas cooler of T --- system, unit are DEG C；
As the outlet temperature T of gas coolergasHigher than Tgas0When, the optimal pressure at expulsion of compressor and gas cooling at this time
It is as follows that the outlet temperature of device obtains correlation:
P=0.005*T*T+0.1541*T+2.5125 (3)
Wherein: P --- the optimal exhaust pressure value of system, unit KPa；
The Outlet Temperature value of the gas cooler of T --- system, unit are DEG C；
Further, in winter under operating condition:
As the outlet temperature T of gas coolergasLower than Tgas0When, do not use regenerator；
As the outlet temperature T of gas coolergasHigher than Tgas0When, using regenerator；
As the outlet temperature T of gas coolergasEqual to Tgas0When, if Compressor Discharge Pressure P is not higher than 10MPa,
Using regenerator；When Compressor Discharge Pressure P is higher than 10MPa, regenerator is not used.
Further,
As the outlet temperature T of gas coolergasLower than Tgas0When, the optimal pressure at expulsion of compressor and gas cooling at this time
It is as follows that the outlet temperature of device obtains correlation:
P=0.0151*T*T-0.9405*T+23.215 (4)
Wherein: P --- the optimal exhaust pressure value of system, unit KPa；
The Outlet Temperature value of the gas cooler of T --- system, unit are DEG C；
As the outlet temperature T of gas coolergasHigher than Tgas0When, the optimal pressure at expulsion of compressor and gas cooling at this time
It is as follows that the outlet temperature of device obtains correlation:
P=-0.007*T*T+0.7325*T-8.2168 (5)
Wherein: P --- the optimal exhaust pressure value of system, unit KPa；
The Outlet Temperature value of the gas cooler of T --- system, unit are DEG C.
Compared with the existing technology, the present invention according to have it is following the utility model has the advantages that
In the prior art, for conventional refrigerant subcritical cycle.The cycle performance of system can be improved in regenerator, substantially
Have become the field conventional technology.For CO2Trans-critical cycle heat pump cycle also has and improves system circulation using regenerator
The relevant technologies of energy, but these technologies all do not account for, and under certain specific operating conditions, in transcritical CO_2 circulation, return
Hot device can not improve system circulation performance, or even play the role of negative.Whether using regenerator additionally depend on other it is numerous because
Element, such as complexity, the cost aspect of system etc..And even if single from the aspect of the improvement to system performance, regenerator
Also it can always not be significantly improved to system performance, this additionally depends on specific working condition, but under which kind of operating condition
It is not come to a conclusion so far using regenerator.
The present invention has been pointed out with precision by the fitting of lot of experimental data using regenerator under which kind of operating condition, at what
Do not need that there is very specific directive function to later research experiment using regenerator under kind operating condition.Also, how is the present invention
When using the guidance of regenerator on the basis of, according to the simulation of experimental data, give under different operating conditions, gas cooler go out
The correlation of the optimum pressure of mouth temperature value and system can be cold by gas according to specific actual condition by the correlation
But the Outlet Temperature value of device, the pressure at expulsion for controlling compressor are optimal exhaust pressure value, so that system obtains maximum
COP, the experimental study for being similarly later provide extremely use direction guidance.
Detailed description of the invention
Fig. 1 is a kind of Trans-critical cycle CO of the present invention2The structural schematic diagram of heat pump system.
Specific embodiment
The present invention is described in further detail below in conjunction with the accompanying drawings.
Please refer to Fig. 1, a kind of Trans-critical cycle CO2Heat pump system, comprising: compressor 1, gas cooler 2, by-passing valve 3, backheat
Device 4, throttle valve 5, evaporator 6 and by-passing valve 7.The entrance of the outlet connection gas cooler 2 of compressor 1, gas cooler 2
Export connecting bypass valve 3 the port a, by-passing valve 3 the port c connection regenerator 4 first entrance, the port b of by-passing valve 3 and
The entrance of the first outlet connection throttle valve 5 of regenerator 4, the entrance of the outlet connection evaporator 6 of throttle valve 5, evaporator 6 go out
The port d of mouthful connecting bypass valve 7, the second entrance of the port the f connection regenerator 4 of by-passing valve 7 and are returned the port e of by-passing valve 7
The entrance of the second outlet connect compressor 1 of hot device 4.
A kind of Trans-critical cycle CO2The control method of regenerator under heat pump system optimal performance, comprising: by controlling by-passing valve 3
With the opening and closing of the interface of by-passing valve 7, control whether regenerator 4 accesses in the circulatory system.When the end a of by-passing valve 3 and the end c opening, b
End is closed, and the end d of by-passing valve 7 and the end f are opened, when the end e is closed, in 4 access system of regenerator；When the end a and the end b of by-passing valve 3
It opens, the end c is closed, and the end d of by-passing valve 7 and the end e are opened, and when the end f is closed, refrigerant is without regenerator 4.
The present invention constantly summarizes achievement, constantly pays huge creation on the basis of a large amount of experiment and analogue data
Property labour improve, obtain environment temperature and need the critical value of the outlet temperature of gas cooler 2 using regenerator 4
Relational expression is as follows:
Tgas0=0.125*Tenv+32.5 (1)
Wherein: Tgas0--- the critical value using the outlet temperature of gas cooler 2 when regenerator 4 is needed, unit: DEG C；
Tenv--- ambient temperature value, value range are -30 DEG C≤Tenv≤ 30 DEG C, unit: DEG C；
Under summer operating mode, as the outlet temperature T of gas cooler 2gasLower than Tgas0When, since evaporating temperature is by environment
It determines, be held essentially constant, the temperature difference between the outlet temperature of gas cooler 2 and the outlet temperature of evaporator 6 is smaller at this time,
The specific enthalpy difference that regenerator 4 imports and exports refrigerant reduces, and using after regenerator 4,1 suction temperature of compressor is increased, and air-breathing is close
Degree decline, the mass flow of refrigerant reduce, and refrigerating capacity also declines, and do not use regenerator 4, i.e., at this time the port a of by-passing valve 3 and
The port b is opened, c port shutdown, and the port d of by-passing valve 7 and the port e are opened, f port shutdown.Refrigerant is in compressor 1 at this time
It after pressurized heating, is cooled into gas cooler 2, is then saved by being directly entered in expansion valve 5 after by-passing valve 3
Stream, subsequently enters the heat of vaporization that other working medium are absorbed in evaporator 6, finally by being returned directly in compressor after by-passing valve 7.
As the outlet temperature T of gas cooler 2gasHigher than Tgas0When, after regenerator 4, the inlet and outlet of regenerator are freezed
The ratio enthalpy difference of agent increases, and backheat effect is obvious, effectively reduces refrigerant and enters the temperature before expansion valve, therefore to system
Performance improves significantly, and using regenerator 4, i.e., the port a and the port c of by-passing valve 3 are opened at this time, b port shutdown, by-passing valve 7
The port d and the port f are opened, e port shutdown.After refrigerant is pressurized heating in compressor 1 at this time, into gas cooler 2
In be cooled, it is cold again into the refrigerant for being carried out flash-pot 6 in regenerator 4 then by going out after by-passing valve 3 from the port c
But, then enter in expansion valve 5 and be throttled, subsequently enter the heat of vaporization for absorbing other working medium in evaporator 6, then pass through side
Go out after port valve 7 from the port f, is heated, eventually pass back to again by the high temperature refrigerant from gas cooler 2 into regenerator 4
In compressor 1.
As the outlet temperature T of gas cooler 2gasEqual to Tgas0When, if the exhaust of compressor 1 is regarded using regenerator 4
Depending on pressure P, when pressure at expulsion P is not higher than 8.5MPa, pressure at expulsion is lower, and delivery temperature is also lower, is made using regenerator
The inlet and outlet enthalpy difference of refrigerant is larger after its progress heat exchange, and effect is more significant, and the air-breathing density of compressor is bigger, refrigerant
Mass flow it is bigger, therefore refrigerating capacity is also bigger, more preferable using the effect of regenerator, at this time the port a and the end c of by-passing valve 3
Mouth is opened, b port shutdown, and the port d of by-passing valve 7 and the port f are opened, e port shutdown.Refrigerant quilt in compressor 1 at this time
After pressurization heating, it is cooled into gas cooler 2, then by going out after by-passing valve 3 from the port c, into regenerator 4
The refrigerant for being carried out flash-pot 6 cools down again, then enters in expansion valve 5 and is throttled, subsequently enters in evaporator 6 and absorb it
The heat of vaporization of his working medium, then by going out after by-passing valve 7 from the port f, into regenerator 4 by from gas cooler 2
High temperature refrigerant heats again, eventually passes back in compressor 1.When pressure at expulsion P is higher than 8.5MPa, because pressure at expulsion is got over
The intake air temperature of height, compressor 1 is higher, and pressure at expulsion increases, although can reduce refrigerant using regenerator 4 reaches expansion valve
Preceding temperature also further improves delivery temperature to reduce regenerative losses, the effect ten finally promoted to system performance
It is point limited, it even results in performance and is declined, therefore do not use regenerator 4 at this time, is i.e. the port a and the port b of by-passing valve 3 at this time
It opens, c port shutdown, the port d of by-passing valve 7 and the port e are opened, f port shutdown.Refrigerant is added in compressor 1 at this time
It after pressure heating, is cooled into gas cooler 2, is then throttled, is connect by being directly entered in expansion valve 5 after by-passing valve 3
Enter in evaporator 6 and absorb the heat of vaporization of other working medium, finally by being returned directly in compressor after by-passing valve 7.
In winter under operating condition, as the outlet temperature T of gas cooler 2gasLower than Tgas0When, since evaporating temperature is by environment
It determines, be held essentially constant, the temperature difference between the outlet temperature of gas cooler 2 and the outlet temperature of evaporator 6 is smaller at this time,
The specific enthalpy difference that regenerator imports and exports refrigerant reduces, and using after regenerator, compressor air suction temperature is increased, under air-breathing density
Drop, the mass flow of refrigerant reduce, and refrigerating capacity also declines, and do not use regenerator, i.e. the port a and the port b of by-passing valve 3 at this time
It opens, c port shutdown, the port d of by-passing valve 7 and the port e are opened, f port shutdown.Refrigerant is added in compressor 1 at this time
It after pressure heating, is cooled into gas cooler 2, is then throttled, is connect by being directly entered in expansion valve 5 after by-passing valve 3
Enter in evaporator 6 and absorb the heat of vaporization of other working medium, finally by being returned directly in compressor after by-passing valve 7.
As the outlet temperature T of gas coolergasHigher than Tgas0When, after regenerator, the inlet and outlet refrigerant of regenerator
Ratio enthalpy difference increase, backheat effect is obvious, effectively reduces refrigerant and enters the temperature before expansion valve, therefore to the property of system
It can improve significantly, using regenerator, i.e., the port a and the port c of by-passing valve 3 are opened at this time, b port shutdown, the end d of by-passing valve 7
Mouth and the port f are opened, e port shutdown.After refrigerant is pressurized heating in compressor 1 at this time, into quilt in gas cooler 2
It is cooling, then by going out after by-passing valve 3 from the port c, cooled down again into the refrigerant for being carried out flash-pot 6 in regenerator 4, and
Enter in expansion valve 5 afterwards and be throttled, subsequently enter the heat of vaporization for absorbing other working medium in evaporator 6, then passes through by-passing valve 7
Go out afterwards from the port f, is heated again into regenerator 4 by the high temperature refrigerant from gas cooler 2, eventually pass back to compressor
In 1.
As the outlet temperature T of gas coolergasEqual to Tgas0When, if the exhaust pressure of compressor 1 is regarded using regenerator
Depending on power P, when pressure at expulsion P is not higher than 10MPa, pressure at expulsion is lower, and delivery temperature is also lower, makes it using regenerator
The inlet and outlet enthalpy difference of refrigerant is larger after progress heat exchange, and effect is more significant, and the air-breathing density of compressor is bigger, refrigerant
Mass flow is bigger, therefore refrigerating capacity is also bigger, more preferable using the effect of regenerator, at this time the port a and the port c of by-passing valve 3
It opens, b port shutdown, the port d of by-passing valve 7 and the port f are opened, e port shutdown.Refrigerant is added in compressor 1 at this time
It after pressure heating, is cooled into gas cooler 2, then by going out after by-passing valve 3 from the port c, into being come in regenerator 4
The refrigerant of flash-pot 6 cools down again, then enters in expansion valve 5 and is throttled, subsequently enters and absorb other works in evaporator 6
The heat of vaporization of matter, then by going out after by-passing valve 7 from the port f, into regenerator 4 by the high temperature from gas cooler 2
Refrigerant heats again, eventually passes back in compressor 1.When pressure at expulsion P is higher than 10MPa, regenerator is not used, because of exhaust
Pressure is higher, and the intake air temperature of compressor is higher, and pressure at expulsion increases, although it is swollen to reduce refrigerant arrival using regenerator
Temperature before swollen valve also further improves delivery temperature to reduce regenerative losses, the effect finally promoted to system performance
Fruit is extremely limited, even results in performance and is declined, therefore does not use regenerator at this time, i.e. the port a of by-passing valve 3 and b at this time
Port is opened, c port shutdown, and the port d of by-passing valve 7 and the port e are opened, f port shutdown.Refrigerant is in compressor 1 at this time
It after pressurized heating, is cooled into gas cooler 2, is then saved by being directly entered in expansion valve 5 after by-passing valve 3
Stream, subsequently enters the heat of vaporization that other working medium are absorbed in evaporator 6, finally by being returned directly in compressor after by-passing valve 7.
According to whether being fitted using the optimal pressure at expulsion of the outlet temperature and system of gas cooler 2 when regenerator
One is determined the correlation of optimal pressure at expulsion by 2 outlet temperature of gas cooler, therefore under summer operating mode, works as gas cooling
The outlet temperature T of device 2gasLower than Tgas0When, it since evaporating temperature is determined by environment, is held essentially constant, at this time gas cooler
The temperature difference between 2 outlet temperature and the outlet temperature of evaporator 6 is smaller, and the specific enthalpy difference that regenerator imports and exports refrigerant reduces,
And using after regenerator, compressor air suction temperature is increased, and the mass flow of the decline of air-breathing density, refrigerant reduces, refrigerating capacity
Also decline, when system does not use regenerator, the optimal pressure at expulsion of compressor 1 and the outlet temperature of gas cooler 2 are obtained at this time
Correlation is as follows:
P=0.0032*T*T-0.0702*T+7.1075 (2)
Wherein: P --- the optimal exhaust pressure value of system, unit KPa；
The Outlet Temperature value of the gas cooler of T --- system, unit are DEG C；
Under summer operating mode, as the outlet temperature T of gas coolergasHigher than Tgas0When, after regenerator, regenerator
The ratio enthalpy difference for importing and exporting refrigerant increases, and backheat effect is obvious, effectively reduces refrigerant and enters the temperature before expansion valve, because
This improves significantly the performance of system, and system uses regenerator, at this time the outlet temperature of optimal pressure at expulsion and gas cooler
It is as follows to obtain correlation:
P=0.005*T*T+0.1541*T+2.5125 (3)
Wherein: P --- the optimal exhaust pressure value of system, unit KPa；
The Outlet Temperature value of the gas cooler of T --- system, unit are DEG C；
Under winter condition, as the outlet temperature T of gas coolergasLower than Tgas0When, since evaporating temperature is determined by environment
It is fixed, it is held essentially constant, the temperature difference between the outlet temperature of air cooler and the outlet temperature of evaporator is smaller at this time, regenerator
The specific enthalpy difference for importing and exporting refrigerant reduces, and using after regenerator, compressor air suction temperature is increased, the decline of air-breathing density, system
The mass flow of cryogen reduces, and refrigerating capacity also declines, and system does not use regenerator, at this time optimal pressure at expulsion and gas cooler
Outlet temperature to obtain correlation as follows:
P=0.0151*T*T-0.9405*T+23.215 (4)
Wherein: P --- the optimal exhaust pressure value of system, unit KPa；
The Outlet Temperature value of the gas cooler of T --- system, unit are DEG C；
Under winter condition, as the outlet temperature T of gas coolergasHigher than Tgas0When, after regenerator, regenerator
The ratio enthalpy difference for importing and exporting refrigerant increases, and backheat effect is obvious, effectively reduces refrigerant and enters the temperature before expansion valve, because
This improves significantly the performance of system, and system uses regenerator, at this time the outlet temperature of optimal pressure at expulsion and gas cooler
It is as follows to obtain correlation:
P=-0.007*T*T+0.7325*T-8.2168 (5)
Wherein: P --- the optimal exhaust pressure value of system, unit KPa；
The Outlet Temperature value of the gas cooler of T --- system, unit are DEG C.
Claims (4)
1. Trans-critical cycle CO2The control method of regenerator under heat pump system optimal performance, which is characterized in that the Trans-critical cycle CO2Heat pump
System includes: compressor (1), gas cooler (2), the first by-passing valve (3), regenerator (4), throttle valve (5), evaporator (6)
With the second by-passing valve (7)；The outlet of the entrance of outlet connection gas cooler (2) of compressor (1), gas cooler (2) connects
The entrance of the first by-passing valve (3) is connect, the first outlet of the first by-passing valve connects the first entrance of regenerator (4), by-passing valve (3)
Second outlet connects the entrance of throttle valve (5) with the first outlet of regenerator (4), and the outlet of throttle valve (5) connects evaporator (6)
Entrance, the entrance of the outlet connection the second by-passing valve (7) of evaporator (6), the first outlet of the second by-passing valve connects regenerator
(4) second entrance, the entrance of the second outlet connect compressor of the second outlet and regenerator (4) of the second by-passing valve (7)；
The control method includes: the opening and closing of the interface by control the first by-passing valve (3) and the second by-passing valve (7), is controlled back
Whether hot device accesses in the circulatory system；When the entrance and first outlet of the first by-passing valve (3) are opened, second outlet is closed, and second
The entrance and first outlet of by-passing valve (7) are opened, when second outlet is closed, in regenerator access system；When entering for by-passing valve (3)
Mouth and second outlet are opened, and first outlet is closed, and the entrance and second outlet of the second by-passing valve (7) are opened, first outlet closing
When, refrigerant is without regenerator；
Environment temperature and the relational expression using the critical value of the outlet temperature of gas cooler when regenerator is needed, as follows:
Tgas0=0.125*Tenv+32.5 (1)
Wherein: Tgas0--- the critical value using the outlet temperature of gas cooler when regenerator is needed, unit: DEG C；
Tenv--- ambient temperature value, value range are -30 DEG C≤Tenv≤ 30 DEG C, unit: DEG C；
Under summer operating mode:
As the outlet temperature T of gas coolergasLower than Tgas0When, do not use regenerator；
As the outlet temperature T of gas coolergasHigher than Tgas0When, using regenerator；
As the outlet temperature T of gas coolergasEqual to Tgas0When, if Compressor Discharge Pressure P is not higher than 8.5MPa, use
Regenerator；If Compressor Discharge Pressure P is higher than 8.5MPa, regenerator is not used.
2. Trans-critical cycle CO according to claim 12The control method of regenerator, feature exist under heat pump system optimal performance
In:
As the outlet temperature T of gas coolergasLower than Tgas0When, the optimal pressure at expulsion of compressor and gas cooler go out at this time
It is as follows that mouth temperature obtains correlation:
P=0.0032*T*T-0.0702*T+7.1075 (2)
Wherein: P --- the optimal exhaust pressure value of system, unit KPa；
The Outlet Temperature value of the gas cooler of T --- system, unit are DEG C；
As the outlet temperature T of gas coolergasHigher than Tgas0When, the optimal pressure at expulsion of compressor and gas cooler go out at this time
It is as follows that mouth temperature obtains correlation:
P=0.005*T*T+0.1541*T+2.5125 (3)
Wherein: P --- the optimal exhaust pressure value of system, unit KPa；
The Outlet Temperature value of the gas cooler of T --- system, unit are DEG C.
3. Trans-critical cycle CO according to claim 12The control method of regenerator, feature exist under heat pump system optimal performance
In: in winter under operating condition:
As the outlet temperature T of gas coolergasLower than Tgas0When, do not use regenerator；
As the outlet temperature T of gas coolergasHigher than Tgas0When, using regenerator；
As the outlet temperature T of gas coolergasEqual to Tgas0When, if Compressor Discharge Pressure P is not higher than 10MPa, use
Regenerator；When Compressor Discharge Pressure P is higher than 10MPa, regenerator is not used.
4. Trans-critical cycle CO according to claim 32The control method of regenerator, feature exist under heat pump system optimal performance
In:
As the outlet temperature T of gas coolergasLower than Tgas0When, the optimal pressure at expulsion of compressor and gas cooler go out at this time
It is as follows that mouth temperature obtains correlation:
P=0.0151*T*T-0.9405*T+23.215 (4)
Wherein: P --- the optimal exhaust pressure value of system, unit KPa；
The Outlet Temperature value of the gas cooler of T --- system, unit are DEG C；
As the outlet temperature T of gas coolergasHigher than Tgas0When, the optimal pressure at expulsion of compressor and gas cooler go out at this time
It is as follows that mouth temperature obtains correlation:
P=-0.007*T*T+0.7325*T-8.2168 (5)
Wherein: P --- the optimal exhaust pressure value of system, unit KPa；
The Outlet Temperature value of the gas cooler of T --- system, unit are DEG C.
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