CN104776633A - Hybrid power refrigeration system and control method thereof - Google Patents
Hybrid power refrigeration system and control method thereof Download PDFInfo
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- CN104776633A CN104776633A CN201510104865.7A CN201510104865A CN104776633A CN 104776633 A CN104776633 A CN 104776633A CN 201510104865 A CN201510104865 A CN 201510104865A CN 104776633 A CN104776633 A CN 104776633A
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- 238000005057 refrigeration Methods 0.000 title claims abstract description 76
- 238000000034 method Methods 0.000 title claims abstract description 28
- 239000007788 liquid Substances 0.000 claims description 5
- 238000004891 communication Methods 0.000 claims description 3
- 239000003507 refrigerant Substances 0.000 abstract description 9
- 239000002699 waste material Substances 0.000 abstract description 4
- 238000004134 energy conservation Methods 0.000 abstract description 2
- 230000001276 controlling effect Effects 0.000 description 9
- 230000000694 effects Effects 0.000 description 3
- 230000003190 augmentative effect Effects 0.000 description 1
- 238000006243 chemical reaction Methods 0.000 description 1
- 230000004087 circulation Effects 0.000 description 1
- 230000005494 condensation Effects 0.000 description 1
- 238000009833 condensation Methods 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000001704 evaporation Methods 0.000 description 1
- 230000008020 evaporation Effects 0.000 description 1
- 230000005484 gravity Effects 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 238000005086 pumping Methods 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
- 238000005070 sampling Methods 0.000 description 1
- 238000012163 sequencing technique Methods 0.000 description 1
- 230000001839 systemic circulation Effects 0.000 description 1
Classifications
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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
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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
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F11/00—Control or safety arrangements
- F24F11/30—Control or safety arrangements for purposes related to the operation of the system, e.g. for safety or monitoring
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F11/00—Control or safety arrangements
- F24F11/89—Arrangement or mounting of control or safety devices
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F2110/00—Control inputs relating to air properties
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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
- F25B49/022—Compressor control arrangements
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Life Sciences & Earth Sciences (AREA)
- Atmospheric Sciences (AREA)
- Air Conditioning Control Device (AREA)
- Devices That Are Associated With Refrigeration Equipment (AREA)
Abstract
The invention discloses a hybrid power refrigeration system and a control method thereof. The system comprises an indoor evaporator, a compressor, a flow control valve, an indoor fan, a first control part, an outdoor condenser, an outdoor fan, a refrigerant pump and a second control part, wherein the indoor evaporator is arranged indoors, the compressor is connected with an outlet of the indoor evaporator, the flow control valve is connected with an inlet of the indoor evaporator, the indoor fan is matched with the indoor evaporator, the outdoor condenser is arranged outdoors and is connected with an outlet of the compressor, the outdoor fan is matched with the outdoor condenser, the refrigerant pump is connected with the outdoor condenser, an outlet of the refrigerant pump is connected with the flow control valve, and the first control part is communicated with the second control part. According to the hybrid power refrigeration system and the control method of the hybrid power refrigeration system, energy waste can be effectively avoided in a refrigeration process, so as to realize the purpose of energy conservation.
Description
Technical field
The present invention relates to refrigeration system, particularly relate to a kind of hybrid power refrigeration system and control method thereof.
Background technology
Only relate to the hybrid power system of constant volume compressor and different refrigerated medium pump composition in present hybrid refrigeration system, wherein the start and stop of pump and capacity control method have following several:
The first is in constant volume compressor and fixed delivery pump system, and the start and stop of refrigerated medium pump determine according to the condition such as indoor load and outdoor temperature;
It two is in constant volume compressor and varying capacity pumping system, and the start and stop of refrigerated medium pump and capacity regulating regulate according to the evaporator outlet degree of superheat, or provide fixing lift by the volume output of PID method control pump.
Such scheme is all judge according to outdoor temperature; control the switching of different mode (as compressor mode, press pump pattern, pump pattern); a pattern all needs a minimum downtime to another pattern; generally can control at 3 minutes; this handoff procedure causes refrigerating capacity to have larger fluctuation, and computer room temperature fluctuation is also larger.And the start and stop of refrigerated medium pump are also decide according to outdoor environment temperature or indoor/outdoor temperature-difference, even if system does not need the operation of opening pump, as long as outdoor temperature reaches, system will open pump, and the aperture that sometimes even can there are system throttles parts is very little, and pump
needthere is provided very high lift to meet the circulation of system, there is larger energy waste, do not reach the effect of maximum energy-saving.Such as, in the installation site of outdoor unit than indoor location position height 15m, the power of more than 1.5bar just can be provided under the Action of Gravity Field of R22 refrigerant liquid itself, the needs of systemic circulation can be met, do not need to open refrigerated medium pump, but traditional hybrid power system is only according to the unlatching of outdoor temperature determination refrigerated medium pump, causes the very little increase SR of the aperture of system expansion valve, carry out balance sysmte, there is the significant wastage of the energy.
Summary of the invention
The technical problem to be solved in the present invention is, for the defect of prior art, provides a kind of hybrid power refrigeration system and control method thereof.
The technical solution adopted for the present invention to solve the technical problems is: a kind of hybrid power refrigeration system, comprise be arranged at indoor indoor evaporator, export the compressor be connected with described indoor evaporator, the flow control valve be connected with described indoor evaporator entrance, and described indoor evaporator with the use of indoor fan and the first control part;
Also comprise be arranged at the outdoor outdoor condenser be connected with described compressor outlet, with described outdoor condenser with the use of outdoor fan, the refrigerated medium pump be connected with described outdoor condenser and the second control part, described refrigerated medium pump exports and is connected with described flow control valve; First control part and the second control part are connected by communication;
Described first control part is connected with described compressor, described flow control valve and described indoor fan, for controlling the volume output of described indoor fan according to indoor refrigeration demand, control the aperture of described flow control valve according to the outlet superheat degree of indoor evaporator, control start and stop and/or the volume output of described compressor according to the pressure difference before and after indoor refrigeration demand and described compressor;
Described second control part is connected with described refrigerated medium pump with described outdoor fan, for controlling the volume output of described outdoor fan according to the outlet pressure of described outdoor condenser; The volume output of described refrigerated medium pump is controlled according to the aperture of described flow control valve.
Preferably, the device for storing liquid be connected between described outdoor condenser and described refrigerated medium pump is also comprised.
Preferably, described compressor is constant volume compressor or variable conpacitance compressor, and described refrigerated medium pump is varying capacity refrigerated medium pump;
Described first control part controls the start and stop of described constant volume compressor according to the pressure difference before and after described indoor refrigeration demand and described compressor; Or
Described first control part controls start and stop and the volume output of described variable conpacitance compressor according to the pressure difference before and after described indoor refrigeration demand and described compressor.
Preferably, also comprise the first stop valve that described flow-control valve inlet is set, the second stop valve being arranged on described compressor outlet, be arranged on the 3rd stop valve of described refrigerated medium pump outlet and be arranged on the 4th stop valve of described outdoor condenser inlet.
Preferably, the one-way conduction valve be arranged in parallel with described compressor and/or described refrigerated medium pump is also comprised.
The present invention also provides a kind of control method of hybrid power refrigeration system, comprises the following steps that the first control part performs:
S11: determine the pressure difference before and after the outlet superheat degree of indoor refrigeration demand, indoor evaporator, compressor;
S12: the start and stop controlling the volume output of described indoor fan, the start and stop of described flow control valve and described compressor according to indoor refrigeration demand;
S13: the aperture controlling described flow control valve according to the outlet superheat degree of indoor evaporator;
S14: control the start and stop of described compressor or start and stop and volume output according to the pressure difference before and after described compressor;
Also comprise the following steps that the second control part performs:
S21: determine the outlet pressure of outdoor condenser and the aperture of flow control valve;
S22: the rotating speed controlling described outdoor fan according to the outlet pressure of described outdoor condenser;
S23: the volume output controlling described refrigerated medium pump according to the aperture of described flow control valve.
Preferably, described compressor is constant volume compressor or variable conpacitance compressor, and described refrigerated medium pump is varying capacity refrigerated medium pump;
Described first control part controls the start and stop of described constant volume compressor according to the pressure difference before and after described compressor; Or
Described first control part controls start and stop and the volume output of described variable conpacitance compressor according to the pressure difference before and after described compressor.
Preferably, described step S11 comprises: gather indoor environment temperature, and described indoor environment temperature and preset temperature value are compared, both calculating temperature gap is to determine described indoor refrigeration demand;
Gather the first outlet temperature and/or first outlet pressure of indoor evaporator outlet, calculate the outlet superheat degree determining described indoor evaporator;
Gather described compressor inlet pressure and compressor delivery pressure, calculate to determine the pressure difference before and after described compressor.
Preferably, described step S12 comprises: described indoor refrigeration demand compared with the refrigeration threshold value preset, if described indoor refrigeration demand is more than or equal to described refrigeration threshold value, then controls described flow control valve and described compressor start, and control the volume output of described indoor fan; If not, then control described flow control valve and described compressor quits work, and maintain the volume output of described indoor fan;
And/or
Described step S13 comprises: compared with the degree of superheat threshold range preset by the outlet superheat degree of described indoor evaporator, if the outlet superheat degree of described indoor evaporator is less than described degree of superheat threshold range, then reduce the aperture of described flow control valve; If the outlet superheat degree of described indoor evaporator is greater than described degree of superheat threshold range, then increase the aperture of described flow control valve; If the outlet superheat degree of described indoor evaporator within described degree of superheat threshold range, then maintains the aperture of described flow control valve;
And/or
Described step S14 comprises: compared with the threshold pressure differential scope preset by the pressure difference before and after described compressor; If described pressure difference is less than described threshold pressure differential scope, controls constant volume compressor and quit work or reduce the volume output of variable conpacitance compressor; If described pressure difference is greater than described threshold pressure differential scope, controls described constant volume compressor start or increase the volume output of described variable conpacitance compressor; If described pressure difference is within described threshold pressure differential scope, controls described constant volume compressor start or maintain the volume output of described variable conpacitance compressor.
Preferably, described step S22 comprises: compared with the pressure threshold scope preset by the outlet pressure of described outdoor condenser, if the outlet pressure of described outdoor condenser is less than described default pressure threshold scope, then reduce the rotating speed of described outdoor fan; If the outlet pressure of described outdoor condenser is greater than described default pressure threshold scope, then increase the rotating speed of described outdoor fan; If the outlet pressure of described outdoor condenser within described default pressure threshold scope, then maintains the rotating speed of described outdoor fan;
And/or
Described step S23 comprises: the aperture of described flow control valve compared with the aperture threshold range preset, if the aperture of described flow control valve is less than described aperture threshold range, then reduce the volume output of described refrigerated medium pump; If the aperture of described flow control valve is greater than described aperture threshold range, then increase the volume output of described refrigerated medium pump; If the aperture of described flow control valve within described aperture threshold range, then maintains the volume output of described refrigerated medium pump.
The present invention compared with prior art tool has the following advantages: implement the present invention, by the first control part, independent control is carried out to indoor fan, compressor and flow control valve, the second control part is adopted to carry out independent control to outdoor fan and refrigerated medium pump, when compressor and refrigerated medium pump provide power to refrigeration system according to its separately conditional sampling control, without the need to carrying out pattern switching, avoid occurring in mode handover procedure causing refrigerating capacity to occur fluctuation, realize effectively energy-conservation; The volume output of refrigerated medium pump controls according to the aperture of flow control valve, avoids energy waste.
Accompanying drawing explanation
Below in conjunction with drawings and Examples, the invention will be further described, in accompanying drawing:
Fig. 1 is a structural representation of hybrid power refrigeration system in the embodiment of the present invention 1.
Fig. 2 is another structural representation of hybrid power refrigeration system in the embodiment of the present invention 1.
Fig. 3 is another structural representation of hybrid power refrigeration system in the embodiment of the present invention 1.
Fig. 4 is another structural representation of hybrid power refrigeration system in the embodiment of the present invention 1.
Fig. 5 is another structural representation of hybrid power refrigeration system in the embodiment of the present invention 1.
Fig. 6 is another structural representation of hybrid power refrigeration system in the embodiment of the present invention 1.
Fig. 7 is the flow chart of the control method of hybrid power refrigeration system in the embodiment of the present invention 2.
Fig. 8 is the flow chart of step S12 in Fig. 7.
Fig. 9 is the flow chart of step S13 in Fig. 7.
Figure 10 is the flow chart of step S14 in Fig. 7.
Figure 11 is the flow chart of step S22 in Fig. 7.
Figure 12 is the flow chart of step S23 in Fig. 7.
In figure: 10, indoor evaporator; 11, compressor; 12, flow control valve; 13, indoor fan; 14, the first control part; 15, the second control part; 16, outdoor condenser; 17, outdoor fan; 18, refrigerated medium pump; 19, device for storing liquid; 20, one-way conduction valve; 21, the first stop valve; 22, the second stop valve; 23, the 3rd stop valve; 24, the 4th stop valve.
Detailed description of the invention
In order to there be understanding clearly to technical characteristic of the present invention, object and effect, now contrast accompanying drawing and describe the specific embodiment of the present invention in detail.
Embodiment 1
Fig. 1-Fig. 6 illustrates the hybrid power refrigeration system in the present embodiment.This hybrid power refrigeration system comprise be arranged at indoor indoor evaporator 10, export the compressor 11 be connected with indoor evaporator 10, the flow control valve 12 be connected with indoor evaporator 10 entrance, and indoor evaporator 10 with the use of indoor fan 13 and the first control part 14.Particularly, first control part 14 is connected with compressor 11, flow control valve 12 and indoor fan 13, for the volume output according to indoor refrigeration demand control room inner blower 13, according to the aperture of the outlet superheat degree control flow check control valve 12 of indoor evaporator 10, control start and stop and/or the volume output of compressor 11 according to the pressure difference before and after indoor refrigeration demand and compressor 11.Understandably, the first control part 14 adopts PID control method or P control method, to the volume output according to corresponding controlled condition independence control room inner blower 13, the aperture of flow control valve 12 and the start and stop of compressor 11 or start and stop and volume output.
Particularly, compressor 11 can be constant volume compressor 11 or variable conpacitance compressor 11, if during constant volume compressor 11, controls the start and stop of constant volume compressor 11 according to the pressure difference before and after indoor refrigeration demand and compressor 11; If variable conpacitance compressor 11, control start and stop and the volume output of variable conpacitance compressor 11 according to the pressure difference before and after indoor refrigeration demand and compressor 11.Understandably, according to the start and stop of the pressure difference determination compressor 11 before and after compressor 11, pressure difference before and after compressor 11 be less than default threshold pressure differential scope or be 0 time, stop compressor 11 to run, and the size control constant volume compressor 11 controlling pressure difference starts or variable conpacitance compressor 11 starts and volume output.
As shown in figs 1 to 6, this hybrid power refrigeration system also comprise be arranged at outdoor export with compressor 11 be connected outdoor condenser 16, with outdoor condenser 16 with the use of outdoor fan 17, the refrigerated medium pump 18 be connected with outdoor condenser 16 and the second control part 15, refrigerated medium pump 18 exports and is connected with flow control valve 12; First control part 14 and the second control part 15 are connected by communication.Second control part 15 is connected with refrigerated medium pump 18 with outdoor fan 17, for controlling the volume output of outdoor fan 17 according to the outlet pressure of outdoor condenser 16; The volume output of refrigerated medium pump 18 is controlled according to the aperture of flow control valve 12.Understandably, refrigerated medium pump 18 exports to the power of indoor evaporator 10 entrance as outdoor condenser 16, coordinates flow control valve 12 with the flow of balanced system cooling system,
i.e. indoor refrigeration demand;when flow control valve 12 aperture is close or when reaching maximum, refrigeration system can not meet flow needed for refrigeration system, control the volume output of refrigerated medium pump 18 according to the aperture of flow control valve 12, to reach energy-saving effect.
As shown in figures 3 to 6, this hybrid power refrigeration system also comprises and being connected between outdoor condenser 16 and refrigerated medium pump 18 for storing the device for storing liquid 19 of refrigerant.Understandably, this refrigerant can be phase change refrigerant, utilizes phase change refrigerant evaporation endothermic, and condensation heat release principle is to realize energy exchange.
As shown in figs 1 to 6, this hybrid power refrigeration system also comprises the first stop valve 21 arranging flow control valve 12 entrance, the second stop valve 22 being arranged on compressor 11 outlet, is arranged on the 3rd stop valve 23 of refrigerated medium pump 18 outlet and the 4th stop valve 24 of condenser disposed in the outdoor 16 entrance.Understandably, by the setting of the first stop valve 21 and the second stop valve 22, the 3rd stop valve 23 and the 4th stop valve 24, can realize independently controlling the indoor and outdoors of refrigeration system, to meet the user demand of user.
As shown in Fig. 2, Fig. 3, Fig. 5 and Fig. 6, this hybrid power refrigeration system also comprises the one-way conduction valve 20 be arranged in parallel with compressor 11 and/or refrigerated medium pump 18.Understandably, the setting of one-way conduction valve 20 can the conducting when system is without the need to using compressor 11 and/or refrigerated medium pump 18, refrigerant is made directly to avoid, by compressor 11 and/or refrigerated medium pump 18, causing resistance to increase, and then cause energy waste by one-way conduction valve 20.
Embodiment 2
Fig. 7 illustrates the control method of the hybrid power refrigeration system in the present embodiment.This hybrid power refrigeration system comprises the following steps that the first control part 14 performs:
S11: determine the pressure difference Δ P before and after the outlet superheat degree SHr1 of indoor refrigeration demand CFr1, indoor evaporator 10, compressor 11.In the present embodiment, compressor 11 can be constant volume compressor 11 or variable conpacitance compressor 11, and described refrigerated medium pump 18 is varying capacity refrigerated medium pump 18.
Particularly, step S11 comprises the steps: that the first control part 14 gathers indoor environment temperature T1, and is compared by indoor environment temperature T1 and preset temperature value Tset1, and both calculating temperature gap is to determine indoor refrigeration demand CFr1.First control part 14 gathers the first outlet temperature T2 and/or the first outlet pressure P1 of indoor evaporator 10 outlet, calculates according to degree of superheat computing formula with the outlet superheat degree SHr1 determining indoor evaporator 10.Particularly, export the first outlet pressure P1 of 2 the first outlet temperature T1 or two by gathering indoor evaporator 10 or gather the first outlet temperature T2 and/or the first outlet pressure P1 of any point simultaneously, all can calculate the outlet superheat degree SHr1 of indoor evaporator 10.First control part 14 collect and process machine 11 inlet pressure P2 and compressor 11 outlet pressure P3, calculates the pressure difference Δ P determined before and after compressor 11.
S12: the first control part 14 is according to the volume output of indoor refrigeration demand CFr1 control room inner blower 13, the start and stop of flow control valve 12 and the start and stop of compressor 11.As shown in Figure 8, step S12 comprises the steps: indoor refrigeration demand CFr1 to compare with the refrigeration threshold value CFset1 preset, if described indoor refrigeration demand CFr1 is more than or equal to refrigeration threshold value CFset1, then control flow check control valve 12 and compressor 11 start, and the volume output of control room inner blower 13; If not, then control flow check control valve 12 and compressor 11 quit work, and maintain the volume output of indoor fan 13.
And/or
S13: the first control part 14 is according to the aperture Xr1 of the outlet superheat degree SHr1 control flow check control valve 12 of indoor evaporator 10.As shown in Figure 9, step S13 comprises the steps: the outlet superheat degree SHr1 of indoor evaporator 10 to compare with the degree of superheat threshold range SHset1 preset, if the outlet superheat degree SHr1 of indoor evaporator 10 is less than degree of superheat threshold range SHset1, then reduce the aperture Xr1 of flow control valve 12; If the outlet superheat degree SHr1 of indoor evaporator 10 is greater than degree of superheat threshold range SHset1, then the aperture Xr1 of augmented flow control valve 12; If the outlet superheat degree SHr1 of indoor evaporator 10 is within degree of superheat threshold range SHset1, then maintain the aperture Xr1 of flow control valve 12.
And/or
S14: the first control part 14 controls the start and stop of compressor 11 or start and stop and volume output according to the pressure difference Δ P before and after compressor 11.Particularly, the first control part 14 controls the start and stop of constant volume compressor 11 according to the pressure difference Δ P before and after compressor 11; Or the first control part 14 controls start and stop and the volume output of variable conpacitance compressor 11 according to the pressure difference Δ P before and after compressor 11.As shown in Figure 10, step S14 comprises the steps: that the pressure difference Δ P before and after by compressor 11 compares with the threshold pressure differential Pset1 scope preset; If pressure difference Δ P is less than threshold pressure differential scope, controls constant volume compressor 11 and quit work or reduce the volume output of variable conpacitance compressor 11; If pressure difference Δ P is greater than threshold pressure differential scope Pset1, control the volume output that constant volume compressor 11 starts or increase variable conpacitance compressor 11; If pressure difference Δ P is within threshold pressure differential scope Pset1, controls constant volume compressor 11 and start the volume output maintaining variable conpacitance compressor 11.
The control method of this hybrid power refrigeration system also comprises the following steps of the second control part 15 execution:
S21: the second control part 15 determines the outlet pressure P4 of outdoor the condenser 16 and aperture Xr1 of flow control valve 12;
S22: the second control part 15 controls the rotating speed of outdoor fan 17 according to the outlet pressure P4 of outdoor condenser 16.As shown in figure 11, step S22 comprises the steps: the outlet pressure P4 of outdoor condenser 16 to compare with the pressure threshold scope Pset2 preset, if the outlet pressure P4 of described outdoor condenser 16 is less than default pressure threshold scope Pset2, then reduce the rotating speed of outdoor fan 17; If the outlet pressure P4 of outdoor condenser 16 is greater than default pressure threshold scope Pset2, then increase the rotating speed of outdoor fan 17; If the outlet pressure P4 of outdoor condenser 16 is within the pressure threshold scope Pset2 preset, then maintain the rotating speed of outdoor fan 17.
And/or
S23: the second control part 15 controls the volume output of refrigerated medium pump 18 according to the aperture Xr1 of flow control valve 12.As shown in figure 12, step S23 comprises the steps: the aperture Xr1 of flow control valve 12 to compare with the aperture threshold range Xset1 preset, if the aperture Xr1 of flow control valve 12 is less than aperture threshold range Xset1, then reduces the volume output of refrigerated medium pump 18; If the aperture Xr1 of flow control valve 12 is greater than aperture threshold range Xset1, then increase the volume output of refrigerated medium pump 18; If the aperture Xr1 of flow control valve 12 is within aperture threshold range Xset1, then maintain the volume output of refrigerated medium pump 18.
Understandably, first control part 14 adopts PID control method or P control method to adopt the control to outdoor fan 17 and refrigerated medium pump 18 of PID control method or P control method to be independent of each other power to the control of indoor fan 13, compressor 11 or flow control valve 12 and the second control part 15, namely each other without sequencing, independently control according to respective controlled condition, without the need to carrying out compressor mode, switching between press pump module and pump pattern, avoid in mode handover procedure, causing refrigerating capacity to fluctuate.
The present invention is described by a specific embodiment, it will be appreciated by those skilled in the art that, without departing from the present invention, can also carry out various conversion and be equal to substituting to the present invention.In addition, for particular condition or concrete condition, various amendment can be made to the present invention, and not depart from the scope of the present invention.Therefore, the present invention is not limited to disclosed specific embodiment, and should comprise the whole embodiments fallen within the scope of the claims in the present invention.
Claims (10)
1. a hybrid power refrigeration system, it is characterized in that, comprise be arranged at indoor indoor evaporator (10), export the compressor (11) be connected with described indoor evaporator (10), the flow control valve (12) be connected with described indoor evaporator (10) entrance, and described indoor evaporator (10) with the use of indoor fan (13) and the first control part (14);
Also comprise be arranged at outdoor export with described compressor (11) be connected outdoor condenser (16), with described outdoor condenser (16) with the use of outdoor fan (17), the refrigerated medium pump (18) be connected with described outdoor condenser (16) and the second control part (15), described refrigerated medium pump (18) exports and is connected with described flow control valve (12); First control part (14) and the second control part (15) are connected by communication;
Described first control part (14) is connected with described compressor (11), described flow control valve (12) and described indoor fan (13), for controlling the volume output of described indoor fan (13) according to indoor refrigeration demand, control the aperture of described flow control valve (12) according to the outlet superheat degree of indoor evaporator (10), control start and stop and/or the volume output of described compressor (11) according to the pressure difference before and after indoor refrigeration demand and described compressor (11);
Described second control part (15) is connected with described refrigerated medium pump (18) with described outdoor fan (17), for controlling the volume output of described outdoor fan (17) according to the outlet pressure of described outdoor condenser (16); The volume output of described refrigerated medium pump (18) is controlled according to the aperture of described flow control valve (12).
2. hybrid power refrigeration system according to claim 1, is characterized in that, also comprises the device for storing liquid (19) be connected between described outdoor condenser (16) and described refrigerated medium pump (18).
3. hybrid power refrigeration system according to claim 1 and 2, is characterized in that, described compressor (11) is constant volume compressor (11) or variable conpacitance compressor (11), and described refrigerated medium pump (18) is varying capacity refrigerated medium pump (18);
Described first control part (14) controls the start and stop of described constant volume compressor (11) according to the pressure difference before and after described indoor refrigeration demand and described compressor (11); Or
Described first control part (14) controls start and stop and the volume output of described variable conpacitance compressor (11) according to the pressure difference before and after described indoor refrigeration demand and described compressor (11).
4. hybrid power refrigeration system according to claim 3, it is characterized in that, also comprise described flow control valve (12) entrance is set the first stop valve (21), be arranged on the second stop valve (22) that described compressor (11) exports, be arranged on the 3rd stop valve (23) that described refrigerated medium pump (18) exports and the 4th stop valve (24) being arranged on described outdoor condenser (16) entrance.
5. hybrid power refrigeration system according to claim 3, is characterized in that, also comprises the one-way conduction valve (20) be arranged in parallel with described compressor (11) and/or described refrigerated medium pump (18).
6. the control method of the hybrid power refrigeration system described in any one of claim 1-5, is characterized in that, comprises the following steps that the first control part (14) performs:
S11: determine the pressure difference before and after the outlet superheat degree of indoor refrigeration demand, indoor evaporator (10), compressor (11);
S12: control the volume output of described indoor fan (13), the start and stop of described flow control valve (12) and the start and stop of described compressor (11) according to indoor refrigeration demand;
S13: the aperture controlling described flow control valve (12) according to the outlet superheat degree of indoor evaporator (10);
S14: control the start and stop of described compressor (11) or start and stop and volume output according to the pressure difference before and after described compressor (11);
Also comprise the following steps that the second control part (15) performs:
S21: determine the outlet pressure of outdoor condenser (16) and the aperture of flow control valve (12);
S22: the rotating speed controlling described outdoor fan (17) according to the outlet pressure of described outdoor condenser (16);
S23: the volume output controlling described refrigerated medium pump (18) according to the aperture of described flow control valve (12).
7. the control method of hybrid power refrigeration system according to claim 6, is characterized in that, described compressor (11) is constant volume compressor (11) or variable conpacitance compressor (11), and described refrigerated medium pump (18) is varying capacity refrigerated medium pump (18);
Described first control part (14) controls the start and stop of described constant volume compressor (11) according to the pressure difference before and after described compressor (11); Or
Described first control part (14) controls start and stop and the volume output of described variable conpacitance compressor (11) according to the pressure difference before and after described compressor (11).
8. the control method of hybrid power refrigeration system according to claim 7, is characterized in that,
Described step S11 comprises: gather indoor environment temperature, and described indoor environment temperature and preset temperature value are compared, both calculating temperature gap is to determine described indoor refrigeration demand;
The first outlet temperature that collection indoor evaporator (10) exports and/or the first outlet pressure, calculate the outlet superheat degree determining described indoor evaporator (10);
Gather described compressor (11) inlet pressure and compressor (11) outlet pressure, calculate to determine the pressure difference before and after described compressor (11).
9. the control method of hybrid power refrigeration system according to claim 8, is characterized in that,
Described step S12 comprises: described indoor refrigeration demand compared with the refrigeration threshold value preset, if described indoor refrigeration demand is more than or equal to described refrigeration threshold value, then control described flow control valve (12) and described compressor (11) startup, and control the volume output of described indoor fan (13); If not, then control described flow control valve (12) and described compressor (11) quits work, and maintain the volume output of described indoor fan (13);
And/or
Described step S13 comprises: compared with the degree of superheat threshold range preset by the outlet superheat degree of described indoor evaporator (10), if the outlet superheat degree of described indoor evaporator (10) is less than described degree of superheat threshold range, then reduce the aperture of described flow control valve (12); If the outlet superheat degree of described indoor evaporator (10) is greater than described degree of superheat threshold range, then increase the aperture of described flow control valve (12); If the outlet superheat degree of described indoor evaporator (10) within described degree of superheat threshold range, then maintains the aperture of described flow control valve (12);
And/or
Described step S14 comprises: compared with the threshold pressure differential scope preset by the pressure difference before and after described compressor (11); If described pressure difference is less than described threshold pressure differential scope, controls constant volume compressor (11) and quit work or reduce the volume output of variable conpacitance compressor (11); If described pressure difference is greater than described threshold pressure differential scope, control the volume output that described constant volume compressor (11) starts or increase described variable conpacitance compressor (11); If described pressure difference is within described threshold pressure differential scope, controls described constant volume compressor (11) and start or maintain the volume output of described variable conpacitance compressor (11).
10. the control method of the hybrid power refrigeration system according to any one of claim 6-9, is characterized in that,
Described step S22 comprises: compared with the pressure threshold scope preset by the outlet pressure of described outdoor condenser (16), if the outlet pressure of described outdoor condenser (16) is less than described default pressure threshold scope, then reduce the rotating speed of described outdoor fan (17); If the outlet pressure of described outdoor condenser (16) is greater than described default pressure threshold scope, then increase the rotating speed of described outdoor fan (17); If the outlet pressure of described outdoor condenser (16) within described default pressure threshold scope, then maintains the rotating speed of described outdoor fan (17);
And/or
Described step S23 comprises: the aperture of described flow control valve (12) compared with the aperture threshold range preset, if the aperture of described flow control valve (12) is less than described aperture threshold range, then reduce the volume output of described refrigerated medium pump (18); If the aperture of described flow control valve (12) is greater than described aperture threshold range, then increase the volume output of described refrigerated medium pump (18); If the aperture of described flow control valve (12) within described aperture threshold range, then maintains the volume output of described refrigerated medium pump (18).
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| CN201510104865.7A CN104776633B (en) | 2015-03-10 | 2015-03-10 | Hybrid power refrigeration system and control method thereof |
| PCT/CN2016/073229 WO2016141791A1 (en) | 2015-03-10 | 2016-02-02 | Hybrid-power refrigerating system and control method thereof |
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Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105783328A (en) * | 2016-04-28 | 2016-07-20 | 深圳市艾特网能技术有限公司 | Mixed cold source hybrid power refrigerating system and control method thereof |
| CN105910313A (en) * | 2016-04-15 | 2016-08-31 | 深圳市艾特网能技术有限公司 | Liquid cooling hybrid power cooling system and control method thereof |
| WO2016141791A1 (en) * | 2015-03-10 | 2016-09-15 | 深圳市艾特网能有限公司 | Hybrid-power refrigerating system and control method thereof |
| CN107024013A (en) * | 2016-02-01 | 2017-08-08 | 珠海格力电器股份有限公司 | Air conditioner and control method thereof |
| WO2017177457A1 (en) * | 2016-04-15 | 2017-10-19 | 深圳市艾特网能技术有限公司 | Liquid cooling hybrid power refrigerating system and control method thereof |
| WO2017185298A1 (en) * | 2016-04-28 | 2017-11-02 | 深圳市艾特网能技术有限公司 | Hybrid power refrigerating system of mixed cold source and control method therefor |
| CN108758920A (en) * | 2018-07-03 | 2018-11-06 | 依米康科技集团股份有限公司 | A kind of air conditioner coolant flow quantity control system and its control method |
| CN111609497A (en) * | 2020-05-26 | 2020-09-01 | 深圳市艾特网能技术有限公司 | Control method and control device for natural cooling machine room air conditioner and natural cooling machine room air conditioner |
| CN111981649A (en) * | 2019-05-22 | 2020-11-24 | 广东美的制冷设备有限公司 | Air conditioner, air conditioner control method and device and readable storage medium |
Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20080115515A1 (en) * | 2006-11-22 | 2008-05-22 | Bailey Peter F | Cooling system and method |
| CN101611275A (en) * | 2006-12-22 | 2009-12-23 | 开利公司 | Be used to control the method and system of air-conditioning system |
| CN101688713A (en) * | 2006-12-22 | 2010-03-31 | 开利公司 | Air conditioning systems and methods having free-cooling pump starting sequences |
| WO2010094227A1 (en) * | 2009-02-19 | 2010-08-26 | 艾默生网络能源有限公司 | Air conditioner |
| US20100326105A1 (en) * | 2009-05-29 | 2010-12-30 | Wilson Willy Casas Noriega | Refrigerating device, in particular for aircraft |
| CN203464396U (en) * | 2013-08-12 | 2014-03-05 | 北京雅驿欣科技有限公司 | Multi-refrigerating-cycle energy-saving air conditioning unit with compact indoor unit structure |
| CN203478687U (en) * | 2013-07-30 | 2014-03-12 | 新奥科技发展有限公司 | Refrigeration system |
| CN204574599U (en) * | 2015-03-10 | 2015-08-19 | 深圳市艾特网能有限公司 | Hybrid power refrigeration system |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1776328A (en) * | 2005-12-06 | 2006-05-24 | 东南大学 | Mixed power gas heat pump air conditioner and its operating method |
| CN102242984B (en) * | 2010-11-25 | 2013-01-16 | 中原工学院 | Solar auxiliary heat engine drive type refrigerating device |
| US20120227429A1 (en) * | 2011-03-10 | 2012-09-13 | Timothy Louvar | Cooling system |
| CN203286826U (en) * | 2013-05-13 | 2013-11-13 | 艾默生网络能源有限公司 | Refrigeration control system of machine room |
| CN104776633B (en) * | 2015-03-10 | 2017-05-10 | 深圳市艾特网能有限公司 | Hybrid power refrigeration system and control method thereof |
-
2015
- 2015-03-10 CN CN201510104865.7A patent/CN104776633B/en active Active
-
2016
- 2016-02-02 WO PCT/CN2016/073229 patent/WO2016141791A1/en active Application Filing
Patent Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20080115515A1 (en) * | 2006-11-22 | 2008-05-22 | Bailey Peter F | Cooling system and method |
| CN101611275A (en) * | 2006-12-22 | 2009-12-23 | 开利公司 | Be used to control the method and system of air-conditioning system |
| CN101688713A (en) * | 2006-12-22 | 2010-03-31 | 开利公司 | Air conditioning systems and methods having free-cooling pump starting sequences |
| WO2010094227A1 (en) * | 2009-02-19 | 2010-08-26 | 艾默生网络能源有限公司 | Air conditioner |
| US20100326105A1 (en) * | 2009-05-29 | 2010-12-30 | Wilson Willy Casas Noriega | Refrigerating device, in particular for aircraft |
| CN203478687U (en) * | 2013-07-30 | 2014-03-12 | 新奥科技发展有限公司 | Refrigeration system |
| CN203464396U (en) * | 2013-08-12 | 2014-03-05 | 北京雅驿欣科技有限公司 | Multi-refrigerating-cycle energy-saving air conditioning unit with compact indoor unit structure |
| CN204574599U (en) * | 2015-03-10 | 2015-08-19 | 深圳市艾特网能有限公司 | Hybrid power refrigeration system |
Cited By (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2016141791A1 (en) * | 2015-03-10 | 2016-09-15 | 深圳市艾特网能有限公司 | Hybrid-power refrigerating system and control method thereof |
| CN107024013A (en) * | 2016-02-01 | 2017-08-08 | 珠海格力电器股份有限公司 | Air conditioner and control method thereof |
| CN107024013B (en) * | 2016-02-01 | 2019-07-23 | 珠海格力电器股份有限公司 | Air conditioner and control method thereof |
| CN105910313A (en) * | 2016-04-15 | 2016-08-31 | 深圳市艾特网能技术有限公司 | Liquid cooling hybrid power cooling system and control method thereof |
| WO2017177457A1 (en) * | 2016-04-15 | 2017-10-19 | 深圳市艾特网能技术有限公司 | Liquid cooling hybrid power refrigerating system and control method thereof |
| CN105783328A (en) * | 2016-04-28 | 2016-07-20 | 深圳市艾特网能技术有限公司 | Mixed cold source hybrid power refrigerating system and control method thereof |
| WO2017185298A1 (en) * | 2016-04-28 | 2017-11-02 | 深圳市艾特网能技术有限公司 | Hybrid power refrigerating system of mixed cold source and control method therefor |
| CN108758920A (en) * | 2018-07-03 | 2018-11-06 | 依米康科技集团股份有限公司 | A kind of air conditioner coolant flow quantity control system and its control method |
| CN111981649A (en) * | 2019-05-22 | 2020-11-24 | 广东美的制冷设备有限公司 | Air conditioner, air conditioner control method and device and readable storage medium |
| CN111981649B (en) * | 2019-05-22 | 2024-05-28 | 广东美的制冷设备有限公司 | Air conditioner, air conditioner control method, control device and readable storage medium |
| CN111609497A (en) * | 2020-05-26 | 2020-09-01 | 深圳市艾特网能技术有限公司 | Control method and control device for natural cooling machine room air conditioner and natural cooling machine room air conditioner |
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| Publication number | Publication date |
|---|---|
| CN104776633B (en) | 2017-05-10 |
| WO2016141791A1 (en) | 2016-09-15 |
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