CN105737419A - Active-type dynamic cooling control device and method - Google Patents
Active-type dynamic cooling control device and method Download PDFInfo
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- CN105737419A CN105737419A CN201610112983.7A CN201610112983A CN105737419A CN 105737419 A CN105737419 A CN 105737419A CN 201610112983 A CN201610112983 A CN 201610112983A CN 105737419 A CN105737419 A CN 105737419A
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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
- F25B1/00—Compression machines, plants or systems with non-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
- F25B49/00—Arrangement or mounting of control or safety devices
- F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
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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
- F25B2600/00—Control issues
- F25B2600/25—Control of 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
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
Abstract
The invention provides an active-type dynamic cooling control device and method. The device comprises a refrigerating basic unit, a control unit and a cooling space, wherein a compressor, a condenser and an evaporator are sequentially connected to form a closed ring, namely the refrigerating basic unit; a cooled object and the evaporator are both arranged in the cooling space; the control unit comprises a controller and a control valve, wherein the control valve is arranged between the condenser and the evaporator, and the output cooling capacity of the compressor is adjusted by changing the opening of the control valve; and the controller transmits an adjustment command to the control valve according to stored performance parameters and operation parameters which are acquired in real time, so that dynamic balance between the output cooling capacity of the compressor and the heat exchange amount of the cooled object in a cooling process is realized. According to the active-type dynamic cooling control device and method, active-type refrigerating is realized by keeping the output cooling capacity of the compressor and the heat exchange amount of the cooled object identical in real time.
Description
Technical field
The present invention relates to temperature preservation field, be specifically related to a kind of active dynamic cooling control device and method.
Background technology
Air-conditioning and refrigerating plant are widely used to the field that cooled object need to be lowered the temperature by quick-freezing fresh-keeping technique, beverage quickly cooling technology etc..Fast cooling is the main purpose of air-conditioning and refrigerating plant, and therefore the cooling rate of cooled object becomes key process technology index.Existing air-conditioning or refrigerating plant are generally and regulate the flow of refrigeration system cold-producing medium by the such as restricting element such as capillary tube, heating power expansion valve, using kind of refrigeration cycle parameters such as the cold degree that the evaporator outlet degree of superheat (inner equilibrium heating power expansion valve) or capillary tube refrigerant inlet are crossed as inputting parameter, cooled object thermic load change corresponding thereto is matched, it is achieved the cooling of cooled object in the way of passive type adjusting refrigerant flow rate and evaporating temperature.It can be seen that heat transfer (cold) process of cooled object cooling is: cold-producing medium evaporation endothermic makes evaporator wall surface temperature reduction → vaporizer, by heat convection, cold be passed to air → air, by heat convection, cold passed to cooled object.
After refrigeration system is determined, its convection transfer rate is substantially stationary.If heat output is limited (namely air side restriction) by convection transfer rate, the way that will improve heat exchange amount strengthens heat transfer temperature difference exactly.So, to reach the fastest cooling rate in temperature-fall period, the maximum heat transfer temperature difference (even if the evaporating temperature of kind of refrigeration cycle remains minimum) of cold-producing medium and cooled object need to be maintained.And the kind of refrigeration cycle being restricting element with heating power expansion valve is lowered the temperature in adjustment process at goods, the evaporating temperature of cold-producing medium can be gradually lowered along with the reduction of cooled object temperature, evaporating temperature causes that the heat transfer temperature difference between cold-producing medium and goods diminishes from high to low, thus have impact on the cooling rate of goods.
With capillary tube be restricting element air-conditioning or refrigerating plant in, under the occasion that particularly cooled object cooling extent is bigger, capillary tube is limited to the regulating power of kind of refrigeration cycle refrigerant flow and evaporating temperature；And the heat exchange amount of its temperature-fall period is not limited by heat transfer temperature difference by unit refrigerating capacity, now, if owing to the limited evaporating temperature that can not realize of throttling arrangement range of accommodation reduces along with the reduction of cooled object temperature, then the cold of the output of unit can not maximize, and causes that the cooling rate of cooled object is slack-off.
Summary of the invention
In view of this, the present invention provides a kind of active dynamic cooling control device and method, it is intended to realize cooled object the soonest, reliably lower the temperature.
The technical solution used in the present invention particularly as follows:
A kind of active dynamic cooling control device, including refrigeration elementary cell, control unit and cooling space；Wherein:
Compressor, condenser and vaporizer are sequentially connected the closed loop of formation and are refrigeration elementary cell；
Cooled object and described vaporizer are placed in described cooling space；
Described control unit includes controller and controls valve；Wherein:
Described control valve is located between condenser and vaporizer, adjusts compressor output cold by changing its aperture；
Described control valve is sent adjustment instruction according to the performance parameter of storage and the operational factor of Real-time Collection by described controller, it is achieved the dynamic equilibrium of compressor output cold and cooled object heat exchange amount in process of refrigerastion.
In above-mentioned active dynamic cooling control device, the input of described controller and compressor, sets of temperature sensors, evaporator fan are respectively connected with, and are used for gathering operational factor；Outfan is then connected with described control valve, for adjusting, according to the operational factor gathered and the performance parameter prestored, the valve opening controlling valve.
In above-mentioned active dynamic cooling control device, described sets of temperature sensors includes the first temperature sensing and the second sensor, is respectively used to gather wind pushing temperature and the return air temperature of vaporizer.
In above-mentioned active dynamic cooling control device, the performance parameter prestored includes compressor performance parameter and evaporator fan performance parameter；Wherein:
Compressor performance parameter is compressor performance curves, and for the relation curve between compressor refrigerating capacity and operational factor, operational factor includes evaporating temperature, condensation temperature, Suck and exhaust pressure and input power and pressure of inspiration(Pi) relation curve；
Evaporator fan performance parameter is the relation of rotation speed of fan and mass flow.
A kind of active dynamic control method for lowering temp, specifically includes following steps:
Heat transfer step: the cold-producing medium evaporation endothermic in vaporizer makes the wall surface temperature of vaporizer reduce, passes to cooled object after the cold that temperature reduction obtains being passed to the air in cooling space by heat convection further；
Regulating step: in the process that heat transfer step carries out, the controller performance parameter according to the compressor stored and vaporizer, operational factor in conjunction with Real-time Collection, the dynamic equilibrium of compressor output cold and cooled object heat exchange amount in process of refrigerastion is realized, until the temperature of cooled object reaches setting level by adjusting the aperture controlling valve.
In above-mentioned active dynamic control method for lowering temp, described compressor output cold is namely from the cold-producing medium of vaporizer to the heat exchange amount Q of cooled objecta1=kA (To-Te)；
In above formula:
A is the heat exchange area of cooled object；
ToFor cooled object temperature；
TeFor refrigerant evaporating temperature；
K is the coefficient of heat transfer between cold-producing medium and cooled object；
In above formula:
h1For the convection transfer rate between cold-producing medium and wall；
δ is evaporator wall face thickness；
λ is vaporizer wall heat conductivity；
h2The coefficient of heat transfer for vaporizer wall Yu air；
h3The coefficient of heat transfer for air Yu cooled object；
The cooled object heat exchange amount Q that the cold wind of described cooled object heat exchange amount and vaporizer is sent outa2=cm (Tin-Tout)；
In above formula:
C is air specific heat；
M is MAF；
TinFor vaporizer return air temperature；
ToutFor evaporator blowing temperature.
Controller exports the relation between cold and cooled object heat exchange amount by monitoring compressor in real time, analyze and show that heat exchange limits cold transmission or compressor refrigerating capacity limits the conclusion that cold transmits, make compressor output cold dynamically equal with cooled object heat exchange amount by controller further, until cooled object reaches design temperature.
In above-mentioned active dynamic control method for lowering temp, when cold-producing medium and the heat output machine by compression output refrigerating capacity restriction of cooled object, control valve and keep maximum opening, make compressor output maximum cooling capacity, make cooled object cooling rate the fastest.
In above-mentioned active dynamic control method for lowering temp, when the heat output of cold-producing medium Yu cooled object is limited by convection transfer rate, control valve and keep minimum aperture, make evaporating temperature keep maximum heat transfer temperature difference with cooled object, make cooled object cooling rate the fastest.
The beneficial effect comprise that:
The active dynamic control method for lowering temp of the present invention is with the operational factor of refrigeration unit refrigeration compressor, evaporator fan operational factor, vaporizer air blow and return temperature for Main Basis, with adjusting control valve for Main Means, the refrigerating capacity of coupling compressor output and the heat exchange amount of cooled object, make to be cooled and between object and cold-producing medium, reach maximum heat exchange amount, cooled object is carried out fast cooling.
Accompanying drawing explanation
When considered in conjunction with the accompanying drawings, it is possible to be more completely more fully understood that the present invention.Accompanying drawing described herein is used for providing a further understanding of the present invention, embodiment and explanation thereof to be used for explaining the present invention, is not intended that inappropriate limitation of the present invention.
Fig. 1 is the structural representation of a kind of active dynamic cooling control device of the present invention；
Fig. 2 is the compressor refrigerating capacity graph of a relation one with cooled object heat exchange amount of a kind of active dynamic cooling control device of the present invention；
Fig. 3 is the compressor refrigerating capacity graph of a relation two (by under coefficient of heat transfer limited case) with cooled object heat exchange amount of a kind of active dynamic cooling control device of the present invention；
Fig. 4 is the compressor refrigerating capacity graph of a relation three (by compression under mechanism cold limited case) with cooled object heat exchange amount of a kind of active dynamic cooling control device of the present invention.
In figure:
1, compressor 2, condenser 3, control valve 4, vaporizer 5, controller 6, evaporator fan 7, cooling space 8, wind pushing temperature sensor 9, return air temperature sensor 10, cooled object.
Detailed description of the invention
Below in conjunction with drawings and Examples, technical scheme is described in further detail.
The active dynamic cooling control device of one as shown in Figure 1, mainly includes compressor 1, condenser 2, controls valve 3, vaporizer 4 and controller 5；Wherein:
Compressor 1, condenser 2 and vaporizer 4 are sequentially connected, and form a closed loop, as refrigeration elementary cell；
Vaporizer 4 and cooled object 10 are placed in cooling space 7；
The input of controller 5 is connected with compressor 1 and the collection wind pushing temperature sensor 8 of vaporizer 4 temperature parameter, return air temperature sensor 9 and evaporator fan 6 respectively, outfan is then connected with the control valve 3 being located between condenser 2 and vaporizer 4, ensures that in process of refrigerastion, compressor output cold is dynamically identical with cooled object heat exchange amount by regulating its aperture.
Said apparatus realize the temperature-fall period of cooled object 10 particularly as follows:
Controller 5 according to the operational factor of the compressor 1 gathered and evaporator fan 6 and and the compressor 1 of storage and the performance parameter of evaporator fan 6 in interior data, cooled object 10 is carried out cooling and passes cold.Wherein compressor performance parameter is contracting machine performance curve, i.e. the relation of compressor refrigerating capacity and each relevant operational factor；As: the relation curve of compressor refrigerating capacity and evaporating temperature/condensation temperature, Suck and exhaust pressure and input power etc.；Fan performance parameter then refers to the relation between rotation speed of fan and mass flow.Specifically:
Cold-producing medium evaporation endothermic in vaporizer 4 makes the wall surface temperature of vaporizer 4 reduce, by carrying out heat convection, temperature reducing the cold that obtains and passes to the air in cooling space 7, the cold of acquisition is passed to cooled object 10 (as fresh) by heat convection by air further.
Concrete diabatic process equation is:
The heat exchange amount Q of cold-producing medium and cooled objecta1=kA (To-Te)
In above formula:
A is heat exchange area (cooled object 10)；
ToFor cooled object temperature；
TeFor refrigerant evaporating temperature；
K is the coefficient of heat transfer between cold-producing medium and cooled object；
In above formula:
h1For the convection transfer rate between cold-producing medium and wall；
δ is evaporator wall face thickness；
λ is vaporizer wall heat conductivity；
h2The coefficient of heat transfer for vaporizer wall Yu air；
h3The coefficient of heat transfer for air Yu cooled object.
After refrigeration system is determined, the A in above-mentioned parameter, (δ, λ, h1、h2、h3) and its k determined all be regarded as constant, say, that the heat exchange amount Q of cold-producing medium and cooled object 10aWith temperature for Main change amount, i.e. Qa=f (Te,To).As illustrated in fig. 2, it is assumed that cooling object temperature T1=To> T2> T3> T4> T5, it can be seen that when cooled object temperature gives timing, QaAlong with refrigerant evaporating temperature TeIncrease and reduce, and be linear relationship.Under different cooled object temperature, QaWith TeRelation curve be slope be negative straight line.
Simultaneously as the heat exchange amount of cooled object 10 is to send via the cold wind of vaporizer 4, therefore:
Qa2=cm (Tin-Tout)
In above formula:
C is air specific heat；
M is MAF；
TinFor vaporizer return air temperature；
ToutFor evaporator blowing temperature.
Compressor refrigerating capacity QcWith refrigerant evaporating temperature TeWith refrigerant condensing temperature TcRelevant, and after a refrigeration system is determined, TcIt is basically unchanged, say, that compressor refrigerating capacity QcWith refrigerant evaporating temperature TeFor Main change amount, i.e. Qc=f (Te), curve is also referring to Fig. 2, it can be seen that compressor refrigerating capacity QcAlong with refrigerant evaporating temperature TeIncrease and increase.
Qa1=kA (To-Te) for the classical formulas of thermal conduction study, it is the heat exchange amount that obtains cold-producing medium and cooled object of the angle from heat exchange, and Qa2=cm (Tin-Tout) it is the cold that show that air obtains from vaporizer of the angle from air.If system reaches stable state, the two numerical value is equal.But owing to cooled object temperature-fall period is dynamic process, the two is unequal.The present invention utilizes the two value unequal to analyze heat exchange just and limits cold transmission or compressor refrigerating capacity limits cold transmission, thus realizing the control of the fastest cooling rate.
When refrigeration system is started shooting, refrigerant evaporating temperature TeHigher, it is set to TE, 1, and set compressor refrigerating capacity now as QC, 1, the heat exchange amount of cold-producing medium and cooled object is。
Controller 5 detects evaporator blowing temperature T respectively by wind pushing temperature sensor 8 and return air temperature sensor 9inWith vaporizer return air temperature Tout, and combine the service data of evaporator fan 6 sent back in real time and calculate cooled object heat exchange amount；Concrete formula isWherein m is the mass flow of air, the rotary speed parameter of evaporator fan 6 transfers back to controller 5 in real time, the controller 5 relation according to the rotation speed of fan stored in it Yu mass flow, then can obtain the mass flow of blowing machine air-supply, namely can be drawn after the performance parameter comparison of storage with in controller 5 by the operational factor of evaporator fan 6；
Meanwhile, compressor real-time running data also passes controller 5 back, and controller 5, by it being compared with the compressor performance data prestored, calculates compressor refrigerating capacity QC, 1；Real-time operational factor is returned to controller 5 by compressor 1, by comparing with the corresponding compressor performance curves of storage in controller 5, can draw the refrigerating capacity of compressor 1.
Due to Q nowC, 1More than, namely controller 5 sends turns the instruction controlling valve 3 aperture down, and refrigerant evaporating temperature is reduced to TE, 2, make compressor output cold identical with cooled object heat exchange amount；
Cooled object may proceed to cooling afterwards, when temperature is reduced to T2Time, if refrigeration unit is still according to TE, 2Run, then compressor output cold is more than cooled object heat exchange amount, similar with above-mentioned adjustment process, it is necessary to reduces valve opening, makes evaporating temperature be reduced to TE, 3, make compressor output cold identical with cooled object heat exchange amount.
Namely to monitor the relation of cooled object heat exchange amount and compressor output cold in real time, make compressor output cold equal to cooled object heat exchange amount by the control of controller 5, until cooled object 10 reaches design temperature T5, corresponding refrigerant evaporating temperature Te,5。
When period adds new cooled object 10, the mean temperature of cooled object 10 rises to T4, now, refrigerator 5 controls the valve opening of valve 3 by adjusting so that it is be still in that to make refrigerant evaporating temperature be Te,5Aperture, refrigeration system output cold is less than the possible heat exchange amount of cooled object；
Controller 5, by calculating and compare cooled object heat exchange amount and the relation of compressor output cold, tunes up the aperture controlling valve 3, makes evaporating temperature increase, to Te,6, make compressor output cold QC, 4(in Fig. 29 point) is equal to cooled object heat exchange amount(in Fig. 29 point).Then according to cooled object temperature change, continue to regulate temperature-fall period.
Further, it is also possible to realized the operating mode of two kinds of special handlings of the fastest cooling rate and raising heat exchange amount by the cooling control device of the present invention:
One, after refrigeration system is determined, owing to convection transfer rate is substantially stationary and heat output is by convection transfer rate (air side) restriction, the way therefore improving heat exchange amount only strengthens heat transfer temperature difference.Therefore, in temperature-fall period, the fastest cooling rate to be reached, it is possible to make the evaporating temperature of kind of refrigeration cycle keep minimum, namely maintain cold-producing medium and the maximum heat transfer temperature difference of cooled object.Specific implementation process is with reference to Fig. 3:
When refrigeration system is started shooting, evaporating temperature is set to TE, 1, now compressor refrigerating capacity is QC, 1, under this evaporating temperature, the heat exchange amount of cold-producing medium and cooled object is.Controller 5 detects evaporator blowing temperature T by wind pushing temperature sensor 8 and return air temperature sensor 9inWith vaporizer return air temperature Tout, and calculate cooled object heat exchange amount by the service data of evaporator fan 6 passed back in real time.The real-time running data of compressor also passes controller back, and controller passes through the real-time running data of comparison compressor and the performance data of storage, calculates compressor refrigerating capacity QC, 1.Refrigerating capacity Q due to now compressorC, 1More than the maximum heat exchange amount with cooled object it isNamely controller 5 sends turns the control instruction controlling valve 3 aperture down.When valve opening is adjusted to minimum, evaporating temperature Te,2Lower compressor output cold is likely to heat exchange amount more than cooled object, and unit maintains minimum evaporating temperature Te,2.Cooled object temperature is reduced to die plate temperature T2, now, compressor output cold QC, 2Still above cooled object heat exchange amount.In this temperature-fall period, control valve opening and remain minimum aperture, to keep the maximum temperature difference of evaporating temperature and cooled object, thus realizing the fast cooling to cooled object 10.
With compressor operation parameters, evaporator blowing and return air temperature and evaporator fan operational factor for Main Basis, carry out refrigerating capacity adjustment based on this.Take full advantage of existing compressor performance data and evaporator fan performance data, it is not necessary to by complicated means of testing, the dynamic operation to cooling condition can be realized and regulate；
By the refrigerating capacity exported by compressor 1 and the heat exchange amount Dynamic Matching of cooled object 10, farthest improve the cooling rate of cooled object 10；Under extreme operating condition, by simple adjustment the heat exchange amount of cold-producing medium and cooled object 10 can being made to reach maximum unit, cooling object 10 realizes the fastest by cooling rate.
That is: when the heat output of cold-producing medium Yu cooled object is limited by convection transfer rate, control valve and keep minimum aperture, make evaporating temperature keep maximum heat transfer temperature difference with cooled object, make cooled object cooling rate the fastest.
Two, after refrigeration system is determined, convection transfer rate is substantially stationary and sufficiently large, and heat output is by compressor output power limit.The way improving heat exchange amount is to make compressor output maximum.Therefore, in temperature-fall period, the fastest cooling rate to be reached, though the evaporating temperature of kind of refrigeration cycle keep reaching the highest, maintain cold-producing medium and the minimum heat transfer temperature difference of cooled object.Specific implementation process is with reference to Fig. 4:
When refrigeration system is started shooting, evaporating temperature is set to Te,1, now compressor refrigerating capacity is QC, 1, under this evaporating temperature, the heat exchange amount of cold-producing medium and cooled object is.Controller (5) detects evaporator blowing temperature T by wind pushing temperature sensor 8 and return air temperature sensor 9inWith vaporizer return air temperature Tout, and calculate cooled object heat exchange amount by the service data of evaporator fan 6 sent back in real time.Compressor real-time running data also passes controller, controller and the compressor performance comparing of input back, calculates compressor refrigerating capacity QC, 1.Now, the refrigerating capacity Q of compressorC, 1Less than the maximum heat exchange amount with cooled object it is.Controller 5 sends and tunes up the control instruction controlling valve 3 aperture.But when valve opening is adjusted to maximum, evaporating temperature is Te,2, under this evaporating temperature, compressor output cold is likely to heat exchange amount still less than cooled object, and unit maintains the highest evaporating temperature Te,2.Cooled object temperature is reduced to target temperature T2, now, compressor output cold QC, 2Still less than cooled object heat exchange amount.In this temperature-fall period, control valve opening and remain maximum opening, to keep compressor to export maximum cold.
That is: when cold-producing medium and the heat output machine by compression output refrigerating capacity restriction of cooled object, control valve and keep maximum opening, make compressor output maximum cooling capacity, make cooled object cooling rate the fastest.
The present invention achieves refrigeration system by controller and lowers the temperature for the active of cooled object, with evaporator blowing and return air temperature, evaporator fan operational factor and compressor operation parameters for Main Basis, by controlling valve, refrigerating capacity is adjusted, dynamically realizes mating of compressor refrigerating capacity and cooled object heat exchange amount.
Above in association with accompanying drawing, embodiments of the invention having been explained, accompanying drawing herein is used to provide a further understanding of the present invention.Obviously; the foregoing is only the present invention preferably detailed description of the invention; but protection scope of the present invention is not limited thereto, any be to one skilled in the art can readily occur in, essentially without departing from the change of the present invention or replacement, be also all contained within protection scope of the present invention.
Claims (8)
1. an active dynamic cooling control device, it is characterised in that include refrigeration elementary cell, control unit and cooling space；Wherein:
Compressor, condenser and vaporizer are sequentially connected the closed loop of formation and are refrigeration elementary cell；
Cooled object and described vaporizer are placed in described cooling space；
Described control unit includes controller and controls valve；Wherein:
Described control valve is located between condenser and vaporizer, adjusts compressor output cold by changing its aperture；
Described control valve is sent adjustment instruction according to the performance parameter of storage and the operational factor of Real-time Collection by described controller, it is achieved the dynamic equilibrium of compressor output cold and cooled object heat exchange amount in process of refrigerastion.
2. active dynamic cooling control device according to claim 1, it is characterised in that the input of described controller and compressor, sets of temperature sensors, evaporator fan are respectively connected with, and are used for gathering operational factor；Outfan is then connected with described control valve, for adjusting, according to the operational factor gathered and the performance parameter prestored, the valve opening controlling valve.
3. active dynamic cooling control device according to claim 2, it is characterised in that described sets of temperature sensors includes the first temperature sensing and the second sensor, is respectively used to gather wind pushing temperature and the return air temperature of vaporizer.
4. active dynamic cooling control device according to claim 2, it is characterised in that the performance parameter prestored includes compressor performance parameter and evaporator fan performance parameter；Wherein:
Compressor performance parameter is compressor performance curves, and for the relation curve between compressor refrigerating capacity and operational factor, operational factor includes evaporating temperature, condensation temperature, Suck and exhaust pressure and input power and pressure of inspiration(Pi) relation curve；
Evaporator fan performance parameter is the relation of rotation speed of fan and mass flow.
5. an active dynamic control method for lowering temp, specifically includes following steps:
Heat transfer step: the cold-producing medium evaporation endothermic in vaporizer makes the wall surface temperature of vaporizer reduce, passes to cooled object after the cold that temperature reduction obtains being passed to the air in cooling space by heat convection further；
Regulating step: in the process that heat transfer step carries out, the controller performance parameter according to the compressor stored and vaporizer, operational factor in conjunction with Real-time Collection, the dynamic equilibrium of compressor output cold and cooled object heat exchange amount in process of refrigerastion is realized, until the temperature of cooled object reaches setting level by adjusting the aperture controlling valve.
6. active dynamic control method for lowering temp according to claim 5, it is characterised in that described compressor output cold is namely from the cold-producing medium of vaporizer to the heat exchange amount Q of cooled objecta1=kA (To-Te)；In above formula:
A is the heat exchange area of cooled object；
ToFor cooled object temperature；
TeFor refrigerant evaporating temperature；
K is the coefficient of heat transfer between cold-producing medium and cooled object；
In above formula:
h1For the convection transfer rate between cold-producing medium and wall；
δ is evaporator wall face thickness；
λ is vaporizer wall heat conductivity；
h2The coefficient of heat transfer for vaporizer wall Yu air；
h3The coefficient of heat transfer for air Yu cooled object；
The cooled object heat exchange amount Q that the cold wind of described cooled object heat exchange amount and vaporizer is sent outa2=cm (Tin-Tout)；In above formula:
C is air specific heat；
M is MAF；
TinFor vaporizer return air temperature；
ToutFor evaporator blowing temperature；
Controller exports the relation between cold and cooled object heat exchange amount by monitoring compressor in real time, analyze and show that heat exchange limits cold transmission or compressor refrigerating capacity limits the conclusion that cold transmits, make compressor output cold dynamically equal with cooled object heat exchange amount by controller further, until cooled object reaches design temperature.
7. active dynamic control method for lowering temp according to claim 5, it is characterized in that, when cold-producing medium and the heat output machine by compression output refrigerating capacity restriction of cooled object, control valve and keep maximum opening, make compressor output maximum cooling capacity, make cooled object cooling rate the fastest.
8. active dynamic control method for lowering temp according to claim 5, it is characterized in that, in above-mentioned active dynamic control method for lowering temp, when the heat output of cold-producing medium Yu cooled object is limited by convection transfer rate, control valve and keep minimum aperture, make evaporating temperature keep maximum heat transfer temperature difference with cooled object, make cooled object cooling rate the fastest.
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| CN107255355A (en) * | 2017-05-05 | 2017-10-17 | 珠海格力电器股份有限公司 | Air-conditioning system control device and method |
| CN108397853A (en) * | 2018-02-11 | 2018-08-14 | 珠海格力电器股份有限公司 | Air-conditioner set control method and device |
| CN114963683A (en) * | 2022-06-01 | 2022-08-30 | 深圳市汉盛制冷科技有限公司 | Accurate temperature control refrigerating system |
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| CN1363805A (en) * | 2002-02-06 | 2002-08-14 | 黄明 | Energy-saving control method and controller for air conditioner for changing working condition with load variation |
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| CN108397853A (en) * | 2018-02-11 | 2018-08-14 | 珠海格力电器股份有限公司 | Air-conditioner set control method and device |
| CN108397853B (en) * | 2018-02-11 | 2019-11-01 | 珠海格力电器股份有限公司 | Air-conditioner set control method and device |
| CN114963683A (en) * | 2022-06-01 | 2022-08-30 | 深圳市汉盛制冷科技有限公司 | Accurate temperature control refrigerating system |
| CN114963683B (en) * | 2022-06-01 | 2023-09-15 | 深圳市汉盛制冷科技有限公司 | Accurate temperature control refrigerating system |
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