CN106403427A - Control method for electronic expansion valve in starting stage of refrigeration system - Google Patents
Control method for electronic expansion valve in starting stage of refrigeration system Download PDFInfo
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- CN106403427A CN106403427A CN201610784038.1A CN201610784038A CN106403427A CN 106403427 A CN106403427 A CN 106403427A CN 201610784038 A CN201610784038 A CN 201610784038A CN 106403427 A CN106403427 A CN 106403427A
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- 238000005057 refrigeration Methods 0.000 title claims abstract description 20
- 238000000034 method Methods 0.000 title claims abstract description 19
- 238000009790 rate-determining step (RDS) Methods 0.000 claims description 3
- 230000009467 reduction Effects 0.000 claims description 3
- 238000001514 detection method Methods 0.000 claims description 2
- 230000005611 electricity Effects 0.000 claims description 2
- 240000002853 Nelumbo nucifera Species 0.000 claims 1
- 235000006508 Nelumbo nucifera Nutrition 0.000 claims 1
- 235000006510 Nelumbo pentapetala Nutrition 0.000 claims 1
- 239000007788 liquid Substances 0.000 abstract description 11
- 230000008569 process Effects 0.000 abstract description 2
- 230000003111 delayed effect Effects 0.000 abstract 1
- 230000006835 compression Effects 0.000 description 3
- 238000007906 compression Methods 0.000 description 3
- 230000006872 improvement Effects 0.000 description 3
- 238000004364 calculation method Methods 0.000 description 2
- 230000006378 damage Effects 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 239000006200 vaporizer Substances 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 230000007812 deficiency Effects 0.000 description 1
- 238000001704 evaporation Methods 0.000 description 1
- 239000010687 lubricating oil Substances 0.000 description 1
- 239000000203 mixture Substances 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 238000003359 percent control normalization Methods 0.000 description 1
- 239000010726 refrigerant oil Substances 0.000 description 1
- 238000006467 substitution reaction Methods 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 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
- F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/30—Expansion means; Dispositions thereof
- F25B41/31—Expansion valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/30—Expansion means; Dispositions thereof
- F25B41/31—Expansion valves
- F25B41/34—Expansion valves with the valve member being actuated by electric means, e.g. by piezoelectric actuators
-
- 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
- F25B2500/00—Problems to be solved
- F25B2500/26—Problems to be solved characterised by the startup of the refrigeration cycle
-
- 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
- F25B2500/00—Problems to be solved
- F25B2500/28—Means for preventing liquid refrigerant entering into the compressor
-
- 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
- F25B2600/2513—Expansion valves
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
- Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
- Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Air Conditioning Control Device (AREA)
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
Abstract
The invention relates to a control method for an electronic expansion valve in the starting stage of a refrigeration system. The electronic expansion valve and a controller are included. The control method is characterized in that the load rate of a compressor is divided into a plurality of load rate control points within the range of 0%-100%, and the current opening degree value Kn is calculated according to the set electronic expansion valve opening degree percentage P, the maximum step number A and the minimum step number B of the electronic expansion valve and the load rate control points Cn. The control method includes the steps that the compressor of the refrigeration system is started, the load rate of the compressor is detected continuously, when the load rate of the compressor reaches the nth control point value Cn, the opening degree Kn of the expansion valve at that time is worked out according to the nth control point value Cn and the formula of Kn=P*Cn*(A-B)+B; and after time is delayed for T1, a suction air overheat degree control program is started until the compressor goes into a normal work state. Through the electronic expansion valve opening degree control implemented according to the above specified process, the occurrence of a liquid impact phenomenon of the compressor is reduced, loss caused by liquid impact of the compressor is avoided, and the reliability and stability of the system are improved.
Description
Technical field
The present invention relates to technical field of refrigeration equipment, more particularly, to a kind of control of refrigeration system startup stage electric expansion valve
Method processed.
Background technology
Handpiece Water Chilling Units electronic expansion valve controls system is individually controlled by suction superheat, and whole control logic is only around air-breathing
The degree of superheat controls, and system refrigerant or lubricating oil are excessive, and expansion valve open degree is excessive, and vaporizer thermic load is unstable, quickly opens
Open electric expansion valve, or in compressor unloading, electric expansion valve closing velocity is excessively slow, is likely to cause the liquid of compressor
Hit phenomenon, frequent liquid hammer, gently then causes compressor stuck, section components damage, heavy then whole compressor is scrapped.
Especially refrigeration system start-up course starts evaporator superheat is zero, and system change scope is big, speed fast it is impossible to
Electronic expansion valve opening is controlled according to the degree of superheat.For the compression having gas-liquid separator before totally-enclosed compressor or air-breathing
Machine, evaporator outlet carries the no much harm of liquid in short-term on a small quantity, but in start-up course, if the biphase refrigeration of evaporator outlet without
Other measures are directly entered compressor air suction chamber, then can cause compressor liquid hit phenomenon.Even result in system failure.
Content of the invention
The present invention is directed to above-mentioned the deficiencies in the prior art, provides a kind of refrigeration system that can prevent compressor liquid hammer to start rank
The control method of section electric expansion valve.
The technical scheme that the present invention solves above-mentioned technical problem is as follows：A kind of refrigeration system startup stage electric expansion valve
Control method, including electric expansion valve and controller, also includes detecting suction superheat, discharge superheat and compressor load
Rate it is characterised in that:
The rate of load condensate of compressor is divided into several rate of load condensate control point from 0%～100%, the electronics that controller sets
Expansion valve opening percentage ratio is P, and the maximum step number of electric expansion valve is A, and minimum step number is B, and the numerical value at rate of load condensate control point is
Cn, electric expansion valve calculating aperture at this moment is Kn；Wherein,
N is the sequence number at rate of load condensate control point；N=1,2,3 ...；
The span of P is：P=30%～100%
Kn computing formula such as formula (1), this opening value is electronic expansion valve opening controlling value.
Kn=P × Cn × (A-B)+B ... ... (1)
Rate-determining steps are as follows：
1), start refrigeration system compressor, detect compressor load rate, when compressor load rate reaches the first control points
During value C1, calculate according to the first of compressor load rate the control point value C1, by formula (1) electric expansion valve at this moment based on
Calculation aperture is K1：
(2), time delay, for a period of time after T1, proceeds to the control program adjusting electronic expansion valve opening according to suction superheat；
I.e. adjust automatically expansion valve opening reaches the second control point value C2 until the rate of load condensate of compressor, now proceeds to again by above-mentioned
It is K2 that formula (1) calculates electric expansion valve calculating aperture at this moment；
(3), time delay, for a period of time after T1, proceeds to the control program adjusting electronic expansion valve opening according to suction superheat；
(4), persistently detect compressor load rate, when compressor load rate reaches the n-th control point value Cn, according to compression
The n-th of machine rate of load condensate controls point value Cn, calculates electric expansion valve calculating aperture at this moment by formula (1) for Kn：
(5), time delay, for a period of time after T1, proceeds to the control program adjusting electronic expansion valve opening according to suction superheat；
(6), repeat (4th) and (5th) step until compressor load rate be Cn=100%；
(7), time delay, for a period of time after T1, proceeds to the control program adjusting electronic expansion valve opening according to suction superheat；
(8), when the compressor accumulative available machine time reaching T2, detect discharge superheat, if discharge superheat is higher than to set
Temperature W1, electric expansion valve continues executing with the control program adjusting electronic expansion valve opening according to suction superheat, if aerofluxuss
Temperature is less than W2；Then proceed to step (9)；
(9), time delay, for a period of time after T3, proceeds to the control journey adjusting electronic expansion valve opening according to discharge superheat again
Sequence, and set adjustment cycle T 4, often through cycle T 4, reduce electric expansion valve N step, until discharge superheat is higher than W1, then turn
Enter step (8) to run.
On the basis of technique scheme, the present invention can also do following improvement.
Further, the control program of described discharge superheat adjustment electronic expansion valve opening is：W1 described in step (8) is
20 DEG C, W2 is 18 DEG C.
Further, the rate of load condensate control point of described compressor selects 25%, 50%, 75% and 100% successively.
Further, described T1 is 5～10 seconds.
Further, described T2 is 150 seconds～200 seconds；Described T3 is 25 seconds～35 seconds.
Further, the described adjustment cycle T 4 that sets is 2 seconds；Described reduction electric expansion valve N step, wherein N is 3～5 steps.
The invention has the beneficial effects as follows：Controlled by specifying the electronic expansion valve opening of flow process, decrease compressor liquid hammer
The appearance of phenomenon, it is to avoid the loss that compressor causes because of liquid hammer, improves reliability and the stability of system.
Brief description
Fig. 1 is present configuration block diagram；
Specific embodiment
Below in conjunction with accompanying drawing, the principle of the present invention and feature are described, example is served only for explaining the present invention, and
Non- for limiting the scope of the present invention.
As shown in figure 1, a kind of control method of refrigeration system startup stage electric expansion valve, including electric expansion valve and control
Device processed, also include detecting suction superheat, discharge superheat and compressor load rate it is characterised in that:
The rate of load condensate of compressor is divided into several rate of load condensate control point from 0%～100%, the electronics that controller sets
Expansion valve opening percentage ratio is P, and the maximum step number of electric expansion valve is A, and minimum step number is B, and the numerical value at rate of load condensate control point is
Cn, electric expansion valve calculating aperture at this moment is Kn；Wherein,
N is the sequence number at rate of load condensate control point；N=1,2,3 ...；
The span of P is：P=30%～100%；Preferably by 50%.
Kn computing formula such as formula (1), this opening value is electronic expansion valve opening controlling value, and this controlling value is conveyed to electricity
The motor of sub- expansion valve, to adjust the aperture of electric expansion valve.
Kn=P × Cn × (A-B)+B ... ... (1)
Rate-determining steps are as follows：
1), start refrigeration system compressor, detect compressor load rate, when compressor load rate reaches the first control points
During value C1, calculate according to the first of compressor load rate the control point value C1, by formula (1) electric expansion valve at this moment based on
Calculation aperture is K1：
(2), time delay, for a period of time after T1, proceeds to the control program adjusting electronic expansion valve opening according to suction superheat；
I.e. adjust automatically expansion valve opening reaches the second control point value C2 until the rate of load condensate of compressor, now proceeds to again by above-mentioned
It is K2 that formula (1) calculates electric expansion valve calculating aperture at this moment；
(3), time delay, for a period of time after T1, proceeds to the control program adjusting electronic expansion valve opening according to suction superheat；
(4), persistently detect compressor load rate, when compressor load rate reaches the n-th control point value Cn, according to compression
The n-th of machine rate of load condensate controls point value Cn, calculates electric expansion valve calculating aperture at this moment by formula (1) for Kn：
(5), time delay, for a period of time after T1, proceeds to the control program adjusting electronic expansion valve opening according to suction superheat；
(6), repeat (4th) and (5th) step until compressor load rate be Cn=100%；
(7), time delay, for a period of time after T1, proceeds to the control program adjusting electronic expansion valve opening according to suction superheat；
(8), when the compressor accumulative available machine time reaching T2, detect discharge superheat, if discharge superheat is higher than to set
Temperature W1, electric expansion valve continues executing with the control program adjusting electronic expansion valve opening according to suction superheat, if aerofluxuss
Temperature is less than W2；Then proceed to step (9)；
(9), time delay, for a period of time after T3, proceeds to the control journey adjusting electronic expansion valve opening according to discharge superheat again
Sequence, and set adjustment cycle T 4, often through cycle T 4, reduce electric expansion valve N step, until discharge superheat is higher than W1, then turn
Enter step (8) to run.
On the basis of technique scheme, the present invention can also do following improvement.
Further, the control program of described discharge superheat adjustment electronic expansion valve opening is：W1 described in step (8) is
20 DEG C, W2 is 18 DEG C.
Further, the rate of load condensate control point of described compressor selects 25%, 50%, 75% and 100% successively.
Further, described T1 is 5～10 seconds.
Further, described T2 is 150 seconds～200 seconds；Described T3 is 25 seconds～35 seconds.
Further, the described adjustment cycle T 4 that sets is 2 seconds；Described reduction electric expansion valve N step, wherein N is 3～5 steps.
Fig. 1 illustrate described compressor rate of load condensate control point select successively 25%, 50%, 75% and 100% control
Block diagram.Wherein the control program adjusting electronic expansion valve opening according to suction superheat is referred to as suction superheat and controls journey
Sequence.Corresponding Cn value is followed successively by 0.25,0.50,0.75 and 1.00.In this example, T1 is 10 seconds；T2 is 180 seconds；T3 is 30
Second；T4 is 2 seconds, and corresponding electric expansion valve step number N is 5 steps.Described W1 is 20 DEG C, and W2 is 18 DEG C.
Above-mentioned suction superheat and discharge superheat control system generally comprise electric expansion valve, pressure transducer, temperature
Sensor, controller composition, during work, controller detects suction temperature and the discharge duct of aspirating air pipe by temperature sensor
Delivery temperature, the pressure transducer detection saturation evaporating pressure of suction end of the compressor and saturation condensing pressure of exhaust end,
Controller acts on electric expansion valve by after signal processing, calculating suction superheat and discharge superheat, subsequent output order
Motor, valve is reached the position of needs.With the liquid supply rate keeping vaporizer to need.
The foregoing is only presently preferred embodiments of the present invention, not in order to limit the present invention, all spirit in the present invention and
Within principle, any modification, equivalent substitution and improvement made etc., should be included within the scope of the present invention.
Claims (6)
1. a kind of control method of refrigeration system startup stage electric expansion valve, including electric expansion valve and controller, also includes
Detection suction superheat, discharge superheat and compressor load rate it is characterised in that:
The rate of load condensate of compressor is divided into several rate of load condensate control point from 0%～100%, the electronic expansion that controller sets
Valve opening percentage is P, and the maximum step number of electric expansion valve is A, and minimum step number is B, and the numerical value at rate of load condensate control point is Cn, electricity
Sub- expansion valve calculating aperture at this moment is Kn；Wherein,
N is the sequence number at rate of load condensate control point；N=1,2,3 ...；
The span of P is：P=30%～100%
Kn computing formula such as formula (1)
Kn=P × Cn × (A-B)+B ... ... (1)
Rate-determining steps are as follows：
1), start refrigeration system compressor, detect compressor load rate, when compressor load rate reaches the first control point value C1
When, according to the first of compressor load rate the control point value C1, calculate electric expansion valve calculating at this moment by formula (1) and open
Spend for K1：
(2), time delay, for a period of time after T1, proceeds to the control program adjusting electronic expansion valve opening according to suction superheat；I.e. certainly
Dynamic adjustment expansion valve opening reaches the second control point value C2 until the rate of load condensate of compressor, now proceeds to again by above-mentioned formula
(1) calculating electric expansion valve calculating aperture at this moment is K2；
(3), time delay, for a period of time after T1, proceeds to the control program adjusting electronic expansion valve opening according to suction superheat；
(4), persistently detect compressor load rate, when compressor load rate reaches the n-th control point value Cn, born according to compressor
The n-th of lotus rate controls point value Cn, calculates electric expansion valve calculating aperture at this moment by formula (1) for Kn：
(5), time delay, for a period of time after T1, proceeds to the control program adjusting electronic expansion valve opening according to suction superheat；
(6), repeat (4th) and (5th) step until compressor load rate be Cn=100%；
(7), time delay, for a period of time after T1, proceeds to the control program adjusting electronic expansion valve opening according to suction superheat；
(8), when the compressor accumulative available machine time reaching T2, detect discharge superheat, if discharge superheat is higher than design temperature
W1, electric expansion valve continues executing with the control program adjusting electronic expansion valve opening according to suction superheat, if discharge superheat
Less than W2；Then proceed to step (9)；
(9), time delay, for a period of time after T3, proceeds to the control program adjusting electronic expansion valve opening according to discharge superheat again, and
Set adjustment cycle T 4, often through cycle T 4, reduce electric expansion valve N step, until discharge superheat is higher than W1, then proceed to step
(8) run.
2. the control method of refrigeration system startup stage electric expansion valve according to claim 1 is it is characterised in that described
Discharge superheat adjust electronic expansion valve opening control program be：W1 described in step (8) is 20 DEG C, and W2 is 18 DEG C.
3. the control method of refrigeration system startup stage electric expansion valve according to claim 1 is it is characterised in that described
The rate of load condensate control point of compressor selects 25%, 50%, 75% and 100% successively.
4. the control method of refrigeration system startup stage electric expansion valve according to claim 1 is it is characterised in that described
T1 is 5～10 seconds.
5. the control method of refrigeration system startup stage electric expansion valve according to claim 1 is it is characterised in that described
T2 is 150 seconds～200 seconds；Described T3 is 25 seconds～35 seconds.
6. the control method of refrigeration system startup stage electric expansion valve according to claim 1 is it is characterised in that described
Setting adjustment cycle T 4 is 2 seconds；Described reduction electric expansion valve N step, wherein N is 3～5 steps.
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| CN201610784038.1A CN106403427B (en) | 2016-08-31 | 2016-08-31 | A kind of control method of refrigeration system startup stage electric expansion valve |
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Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107676922A (en) * | 2017-10-31 | 2018-02-09 | 广东美的暖通设备有限公司 | The control method and air conditioner of air conditioner |
| CN110006138A (en) * | 2019-03-01 | 2019-07-12 | 青岛海尔空调电子有限公司 | Prevent the control method and control system of the compressor liquid hammer of air conditioner |
| CN110926064A (en) * | 2019-12-10 | 2020-03-27 | 北京京仪自动化装备技术有限公司 | Control method and device of electronic expansion valve, electronic equipment and storage medium |
| CN112283868A (en) * | 2020-10-28 | 2021-01-29 | 广东Tcl智能暖通设备有限公司 | Air conditioner expansion valve control method, air conditioner and storage medium |
| CN112361633A (en) * | 2020-11-09 | 2021-02-12 | 珠海格力电器股份有限公司 | Refrigeration system and control method thereof |
Citations (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1553110A (en) * | 2003-05-30 | 2004-12-08 | 乐金电子(天津)电器有限公司 | Running controlling method for frequency variable air-conditioner |
| CN101338948A (en) * | 2008-05-09 | 2009-01-07 | 浙江盾安人工环境设备股份有限公司 | Refrigeration system provided with electronic expansion valve opening control device |
| CN102374714A (en) * | 2011-11-09 | 2012-03-14 | 江苏天舒电器有限公司 | Control method for electronic expansion valve of heat-pump water heater and control device thereof |
| CN102419041A (en) * | 2011-12-13 | 2012-04-18 | Tcl空调器(中山)有限公司 | Throttle opening degree control method for varied-frequency air-conditioner |
| CN103868290A (en) * | 2014-02-26 | 2014-06-18 | 大连冰山嘉德自动化有限公司 | Method for controlling electronic expansion valve on basis of refrigerating energy-efficiency ratio and superheat degree |
| CN104110768A (en) * | 2013-05-30 | 2014-10-22 | 广东美的制冷设备有限公司 | Control method and circuit for electronic expansion valve of air conditioner |
| CN104457072A (en) * | 2014-11-20 | 2015-03-25 | 珠海格力电器股份有限公司 | Electronic expansion valve control method and device and refrigeration/heating system |
| CN104567165A (en) * | 2015-02-06 | 2015-04-29 | 珠海格力电器股份有限公司 | Method and device for controlling opening of electronic expansion valve |
| CN104990294A (en) * | 2015-05-29 | 2015-10-21 | 重庆美的通用制冷设备有限公司 | Air conditioner, and control method and control device thereof |
| CN105091440A (en) * | 2014-05-20 | 2015-11-25 | Tcl空调器(中山)有限公司 | Control method and device of electronic expansion valve |
| CN105423498A (en) * | 2015-12-21 | 2016-03-23 | 珠海格力电器股份有限公司 | Control method of air conditioning system and air conditioning system |
-
2016
- 2016-08-31 CN CN201610784038.1A patent/CN106403427B/en active Active
Patent Citations (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1553110A (en) * | 2003-05-30 | 2004-12-08 | 乐金电子(天津)电器有限公司 | Running controlling method for frequency variable air-conditioner |
| CN101338948A (en) * | 2008-05-09 | 2009-01-07 | 浙江盾安人工环境设备股份有限公司 | Refrigeration system provided with electronic expansion valve opening control device |
| CN102374714A (en) * | 2011-11-09 | 2012-03-14 | 江苏天舒电器有限公司 | Control method for electronic expansion valve of heat-pump water heater and control device thereof |
| CN102419041A (en) * | 2011-12-13 | 2012-04-18 | Tcl空调器(中山)有限公司 | Throttle opening degree control method for varied-frequency air-conditioner |
| CN104110768A (en) * | 2013-05-30 | 2014-10-22 | 广东美的制冷设备有限公司 | Control method and circuit for electronic expansion valve of air conditioner |
| CN103868290A (en) * | 2014-02-26 | 2014-06-18 | 大连冰山嘉德自动化有限公司 | Method for controlling electronic expansion valve on basis of refrigerating energy-efficiency ratio and superheat degree |
| CN105091440A (en) * | 2014-05-20 | 2015-11-25 | Tcl空调器(中山)有限公司 | Control method and device of electronic expansion valve |
| CN104457072A (en) * | 2014-11-20 | 2015-03-25 | 珠海格力电器股份有限公司 | Electronic expansion valve control method and device and refrigeration/heating system |
| CN104567165A (en) * | 2015-02-06 | 2015-04-29 | 珠海格力电器股份有限公司 | Method and device for controlling opening of electronic expansion valve |
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| CN110926064B (en) * | 2019-12-10 | 2020-08-07 | 北京京仪自动化装备技术有限公司 | Control method and device of electronic expansion valve, electronic equipment and storage medium |
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