CN104913459B - Refrigeration air-conditioner cold medium flux real-time control method and device - Google Patents
Refrigeration air-conditioner cold medium flux real-time control method and device Download PDFInfo
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- CN104913459B CN104913459B CN201510358203.2A CN201510358203A CN104913459B CN 104913459 B CN104913459 B CN 104913459B CN 201510358203 A CN201510358203 A CN 201510358203A CN 104913459 B CN104913459 B CN 104913459B
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- 238000000034 method Methods 0.000 title claims abstract description 22
- 238000005057 refrigeration Methods 0.000 title claims abstract description 18
- 230000004907 flux Effects 0.000 title abstract 4
- 239000007788 liquid Substances 0.000 claims abstract description 13
- 239000003507 refrigerant Substances 0.000 claims description 19
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims description 16
- 238000001514 detection method Methods 0.000 claims description 10
- 238000001704 evaporation Methods 0.000 claims description 8
- 230000008020 evaporation Effects 0.000 claims description 8
- 238000010438 heat treatment Methods 0.000 claims description 8
- 230000003993 interaction Effects 0.000 claims description 6
- 238000004364 calculation method Methods 0.000 claims description 5
- 238000004378 air conditioning Methods 0.000 claims description 4
- 238000001816 cooling Methods 0.000 claims 1
- 239000011552 falling film Substances 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000007547 defect Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
Classifications
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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
- F24F2110/00—Control inputs relating to air properties
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F2140/00—Control inputs relating to system states
- F24F2140/10—Pressure
- F24F2140/12—Heat-exchange fluid pressure
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Life Sciences & Earth Sciences (AREA)
- Atmospheric Sciences (AREA)
- Air Conditioning Control Device (AREA)
Abstract
The present invention, which provides a kind of refrigeration air-conditioner cold medium flux real-time control method and device, methods described, to be included：Calculate expansion valve first opens step number；If compressor actual motion is oepration at full load, step number control unit liquid supply rate is opened according to the first of the expansion valve；If compressor actual motion is operation at part load, according to the first of the expansion valve the second unlatching step number or its correction value for opening step number calculating expansion valve, according to the liquid supply rate for stating the second unlatching step number or its correction value control unit of the expansion valve.Refrigeration air-conditioner cold medium flux real-time control method and device of the present invention, by calculating unlatching step number of the expansion valve when compressor actual load is run, electronic expansion valve opening is adjusted in real time, to reach the purpose of accuracy-control system cold medium flux, its advantage is to control more accurately, ensures reliable, the stable operation of unit.
Description
Technical Field
The invention belongs to the technical field of central air conditioning unit control, and mainly relates to a method and a device for controlling the refrigerant flow of an air conditioning unit in real time.
Background
At present, the suction superheat degree of a compressor is generally adopted by a flooded or falling film type cold water/heat pump unit as a feedback signal of an electronic expansion valve for liquid supply control, the control method is more suitable for units with larger suction superheat degree (2-5 ℃) of the compressor such as a dry type cold water/heat pump, but the defects that the control precision and the stability are difficult to guarantee exist for the units with small or even zero suction superheat degree of the compressor such as the flooded or falling film type cold water/heat pump.
Disclosure of Invention
In view of the above-mentioned drawbacks of the prior art, an object of the present invention is to provide a method and an apparatus for controlling the flow rate of refrigerant in real time for a refrigeration and air-conditioning system.
In order to achieve the above and other related objects, the present invention provides a method for controlling refrigerant flow of a refrigeration air conditioner in real time, the method comprising:
calculating a first opening step number of the expansion valve;
if the compressor is actually operated at full load, controlling the liquid supply amount of the unit according to the first opening step number of the expansion valve;
and if the actual operation of the compressor is partial load operation, calculating a second opening step number of the expansion valve or a correction value thereof according to the first opening step number of the expansion valve, and controlling the liquid supply amount of the unit according to the second opening step number of the expansion valve or the correction value thereof.
According to the invention, the first number of opening steps of the expansion valve is the number of opening steps during full-load operation of the compressor; the second number of opening steps of the expansion valve is the number of opening steps when the compressor is in partial load operation.
According to the invention, the first opening step number of the expansion valve is calculated according to the opening step numbers of the heating working condition and the refrigerating working condition and the air suction and exhaust pressure difference.
Preferably, the pressure difference between the suction gas and the discharge gas is calculated according to a measured value of the discharge pressure and a nominal suction pressure, wherein the nominal suction pressure is equal to a refrigerant saturation pressure corresponding to a nominal evaporation temperature.
According to the invention, the second number of opening steps of the expansion valve is corrected when the theoretical load differs from the actual load at the 75% and 50% levels.
According to the invention, the liquid supply amount of the unit is controlled by controlling the opening step number of the expansion valve; firstly, setting the maximum value and the minimum value of the opening steps of the expansion valve; if the calculated first opening step number of the expansion valve or the second opening step number of the expansion valve or the corrected value of the second opening step number is larger than the maximum value of the opening step number of the expansion valve, controlling the actual opening step number of the expansion valve to be equal to the maximum value of the opening step number of the expansion valve; and if the calculated first opening step number of the expansion valve or the second opening step number of the expansion valve or the corrected value of the second opening step number of the expansion valve is smaller than the minimum value of the opening step numbers of the expansion valve, controlling the actual opening step number of the expansion valve to be equal to the minimum value of the opening step numbers of the expansion valve.
In order to realize the method, the invention also provides a device for controlling the refrigerant flow of the refrigeration air conditioner in real time, which comprises a control module, a pressure detection module and a temperature detection module; wherein,
the control module is used for processing the temperature and pressure data and controlling the starting of the compressor and the opening and closing of the expansion valve according to the processing result;
the pressure detection module is used for acquiring pressure data of the evaporator and the condenser;
and the temperature detection module is used for acquiring temperature data of the evaporator and the condenser.
Preferably, the device further comprises a human-computer interaction module for realizing human-computer interaction.
Preferably, the pressure detection module comprises a high-pressure sensor and a low-pressure sensor, which are respectively connected with the analog input port of the control module, and are used for collecting the pressure value of the evaporator and the pressure value of the condenser.
Preferably, the temperature detection module comprises an evaporator outlet water temperature sensor and a condenser outlet water temperature sensor, which are respectively connected with the temperature data input port of the control module, and are used for acquiring the outlet water temperature of the evaporator and the outlet water temperature of the condenser.
As described above, the method and the device for controlling the refrigerant flow of the refrigeration air conditioner in real time adjust the opening of the electronic expansion valve in real time by calculating the opening steps of the expansion valve during the actual load operation of the compressor, so as to achieve the purpose of accurately controlling the refrigerant flow of the system.
Drawings
In order to more clearly illustrate the technical solutions in the embodiments of the present invention, the drawings needed to be used in the description of the embodiments will be briefly introduced below, and it is obvious that the drawings in the following description are only some embodiments of the present invention, and it is obvious for those skilled in the art to obtain other drawings based on these drawings without creative efforts.
Fig. 1 is a flow chart of refrigerant flow of a unit when a compressor operates at full load according to embodiment 1 of the present invention.
Fig. 2 is a schematic structural diagram of a device for controlling refrigerant flow rate of a refrigeration air conditioner in real time according to embodiment 2 of the present invention.
Fig. 3 is a flow chart of the refrigerant flow rate of the unit when the compressor operates at partial load according to embodiment 2 of the present invention.
Detailed Description
The embodiments of the present invention are described below with reference to specific embodiments, and other advantages and effects of the present invention will be easily understood by those skilled in the art from the disclosure of the present specification. The invention is capable of other and different embodiments and of being practiced or of being carried out in various ways, and its several details are capable of modification in various respects, all without departing from the spirit and scope of the present invention.
Please refer to fig. 1 to 3. It should be understood that the drawings provided in this embodiment are only for illustrating the basic idea of the present invention, and the components related to the present invention are only shown in the drawings rather than drawn according to the number, shape and size of the components in actual implementation, and the type, number and proportion of the components in actual implementation may be changed freely, and the layout of the components may be more complicated.
Example 1
Calculating a nominal evaporation temperature Te (Teo-2) according to the evaporator outlet water temperature Teo acquired by the system in real time, and calculating an air suction and exhaust pressure difference x (P) according to an exhaust pressure measured value and a nominal suction pressured-Ps，(PdIs an exhaust pressure measured value; psAt nominal suction pressure, which is equal to the refrigerant saturation pressure for Te).
According to the theoretical opening steps of the expansion valve and the pressure difference of suction and exhaust under the heating working condition and the refrigeration working condition, the opening step y of the expansion valve when the compressor runs at full load is calculated by the formula (1),
wherein d1 is the pressure difference of suction and discharge under refrigeration condition, n1 is the opening step number of the electronic expansion valve under refrigeration condition, d2 is the pressure difference of suction and discharge under heating condition, n2 is the opening step number of the electronic expansion valve under heating condition, and x is the actually measured pressure difference of suction and discharge.
And if the compressor is actually operated at full load, controlling the liquid supply amount of the unit by the opening step number y of the expansion valve in the full load operation of the compressor and the limit value of the opening step number of the expansion valve, which are calculated by the formula (1). Firstly, setting the maximum value and the minimum value of the opening steps of the expansion valve; if y is larger than the maximum value of the opening steps of the expansion valve, controlling the actual opening steps of the expansion valve to be equal to the maximum value of the opening steps of the expansion valve; and if y is smaller than the minimum value of the opening steps of the expansion valve, controlling the actual opening steps of the expansion valve to be equal to the minimum value of the opening steps of the expansion valve, so that the flow of the refrigerant can be controlled in real time.
Example 2
A controller adopting a novel refrigerant flow real-time control algorithm comprises a human-computer interaction unit, a program controller, a high-pressure sensor, a low-pressure sensor, an evaporator water outlet temperature sensor and a condenser water outlet temperature sensor, as shown in figure 2, wherein the human-computer interaction unit is connected with the program controller, and the high-pressure sensor, the low-pressure sensor, the evaporator water outlet temperature sensor and the condenser water outlet temperature sensor are respectively connected with the program controller through circuits.
When the air conditioner is used, the evaporator outlet water temperature sensor is connected to an evaporator of the air conditioner, the condenser outlet water temperature sensor is connected to a condenser, the high-pressure sensor is connected to the evaporator, and the low-pressure sensor is connected to the condenser. And the program controller controls the liquid supply amount of the unit by adopting the following method according to the acquired temperature and pressure values.
The method of example 1 was used to calculate the number of opening steps y of the expansion valve at full compressor operation and then the number of opening steps of the expansion valve at partial compressor operation. The percentage bx of the expansion valve cold volume in the expansion valve full-open cold volume can be obtained according to y-bx data (expansion valve performance curve data) built in a program controller; if the program controller has no built-in y-bx data, the y-bx data can be calculated according to the formula (2),
bx＝(A1y2-B1y+C1)/1000 (2)，
wherein, A1, B1 and C1 are the values of a group of corresponding bx calculated by comparing the cold quantity of the expansion valve performance curve at y point steps when y is equal to different opening steps with the cold quantity of the expansion valve when the expansion valve is fully opened, then filling the data into an excel table, fitting the curve to obtain A1, B1 and C1, then arranging the formula (2) in a program controller, and calculating bx according to different y values.
When the calculated bx value is less than 0, taking bx as 0; when the calculated bx is greater than 1, 1 is taken as bx. When bx is 0. ltoreq. bx.ltoreq.1, bx is a value calculated by the formula (2).
Assuming that the current energy level is u (1.00 is more than or equal to u and more than or equal to 0.00), the percentage k of the cold of the partial load expansion valve in the cold of the full open is bx.u,
calculating the opening step number yp of the electronic expansion valve when the compressor is in partial load operation according to the formula (3),
yp＝(A2k3+B2k2+C2k+D2)/1000 (3)
when yp is equal to different opening steps, A2, B2, C2 and D2 obtain a bx value according to an expansion valve performance curve, substituting the bx value into k-bx. u to obtain a k value corresponding to yp, filling a group of data obtained by the method into an excel table, fitting a curve to obtain A2, B2, C2 and D2, wherein yp is the opening step number of the expansion valve, and the calculation result is an integer; the formula (3) is built in a program controller, and yp is calculated according to different k values.
When k is less than 0.1, let yp be 0; when k is greater than 0.97, let yp be the maximum opening step number of the expansion valve. When k is 0.1. ltoreq. k.ltoreq.0.97, the value of yp is a value calculated by the formula (3).
When the actual loads of the 75% and 50% energy levels are not 75% and 50%, in order to make the calculation result more accurate, yp should be corrected according to the actual situation under the following conditions, and the correction method is as follows:
when the measured evaporation temperature value S1_ temp is less than or equal to T1 ℃ (T1 is a set value, the value is an empirical value, the range can be set between 0-12 ℃), and the difference Teo-S1_ temp between the evaporator outlet water temperature and the measured evaporation temperature is more than or equal to T2 ℃ (T2 is a set value, the value is an empirical value, the range can be set between 1-10 ℃), the yp value calculated by the formula (3) is corrected by the formula (4), and the corrected opening step number yz of the electronic expansion valve is as follows:
yz＝yp*(1+S) (4)
whereinTblCorrecting a proportional band for small temperature difference; and M is an empirical value, and the correction limit values of the opening steps of the electronic expansion valve are all values.
In order to control the opening steps of the electronic expansion valve more accurately and thus control the liquid supply amount, it is necessary to set a limit on the opening steps of the expansion valve, where the maximum value is ymaxAnd minimum value of ymin。
As long as the compressor is turned on, y must be guaranteedminYz (or yp) is less than or equal to ymax. If yz (or yp) is less than or equal to yminLet yz (or yp) be yminIf yz (or yp) ≧ ymaxLet yz (or yp) be ymax。
The foregoing embodiments are merely illustrative of the principles and utilities of the present invention and are not intended to limit the invention. Any person skilled in the art can modify or change the above-mentioned embodiments without departing from the spirit and scope of the present invention. Accordingly, it is intended that all equivalent modifications or changes which can be made by those skilled in the art without departing from the spirit and technical spirit of the present invention be covered by the claims of the present invention.
Claims (9)
1. A method for controlling the flow of a refrigerant of a refrigeration air conditioner in real time is characterized by comprising the following steps:
calculating a first opening step number of the expansion valve;
if the compressor is actually operated at full load, controlling the liquid supply amount of the unit according to the first opening step number of the expansion valve;
if the actual operation of the compressor is partial load operation, calculating a second opening step number of the expansion valve or a correction value thereof according to the first opening step number of the expansion valve, and controlling the liquid supply amount of the unit according to the second opening step number of the expansion valve or the correction value thereof;
wherein, the first opening step number of the expansion valve is the opening step number when the compressor runs at full load; the second opening step number of the expansion valve is the opening step number of the compressor during partial load operation;
calculating the opening step number y of the expansion valve when the compressor runs at full load through an equation (1),
<mrow> <mi>y</mi> <mo>=</mo> <mfrac> <mrow> <msub> <mi>n</mi> <mn>1</mn> </msub> <mo>-</mo> <msub> <mi>n</mi> <mn>2</mn> </msub> </mrow> <mrow> <msub> <mi>d</mi> <mn>1</mn> </msub> <mo>-</mo> <msub> <mi>d</mi> <mn>2</mn> </msub> </mrow> </mfrac> <mi>x</mi> <mo>+</mo> <msub> <mi>n</mi> <mn>1</mn> </msub> <mo>-</mo> <mfrac> <mrow> <msub> <mi>n</mi> <mn>1</mn> </msub> <mo>-</mo> <msub> <mi>n</mi> <mn>2</mn> </msub> </mrow> <mrow> <msub> <mi>d</mi> <mn>1</mn> </msub> <mo>-</mo> <msub> <mi>d</mi> <mn>2</mn> </msub> </mrow> </mfrac> <msub> <mi>d</mi> <mn>1</mn> </msub> <mo>-</mo> <mo>-</mo> <mo>-</mo> <mrow> <mo>(</mo> <mn>1</mn> <mo>)</mo> </mrow> </mrow>
wherein d1 is the pressure difference of suction and exhaust under refrigeration condition, n1 is the opening step number of the electronic expansion valve under refrigeration condition, d2 is the pressure difference of suction and exhaust under heating condition, n2 is the opening step number of the electronic expansion valve under heating condition, and x is the actually measured pressure difference of suction and exhaust;
the percentage bx of the expansion valve cold volume in the expansion valve full-open cold volume can be obtained according to y-bx data (expansion valve performance curve data) built in a program controller; if the program controller has no built-in y-bx data, the y-bx data can be calculated according to the formula (2),
bx＝(A1y2-B1y+C1)/1000 (2)
wherein, A1, B1 and C1 are that when y is equal to different opening steps, the cold quantity of the expansion valve performance curve at y point steps is compared with the cold quantity of the expansion valve when the expansion valve is fully opened, a group of corresponding bx values are obtained by calculation, the data are filled in an excel table, curves are fitted to obtain A1, B1 and C1, then the formula (2) is arranged in a program controller, and the bx is calculated according to different y values;
when the calculated bx value is less than 0, taking bx as 0; when the calculated bx value is larger than 1, taking bx as 1; bx is the value calculated by the formula (2) when bx is more than or equal to 0 and less than or equal to 1; assuming that the current energy level is u (1.00 is more than or equal to u and more than or equal to 0.00), the cold quantity percentage k of the partial load expansion valve in the full-open state is bx.u;
calculating the opening step number yp of the electronic expansion valve when the compressor is in partial load operation according to the formula (3),
yP＝(A2k3+B2k2+C2k+D2)/1000 (3)
when yp is equal to different opening steps, A2, B2, C2 and D2 obtain a bx value according to an expansion valve performance curve, substituting the bx value into k-bx. u to obtain a k value corresponding to yp, filling a group of data obtained by the method into an excel table, fitting a curve to obtain A2, B2, C2 and D2, wherein yp is the opening step number of the expansion valve, and the calculation result is an integer; the formula (3) is built in a program controller, and yp is calculated according to different k values.
2. The method as claimed in claim 1, wherein the first number of opening steps of the expansion valve is calculated according to the number of opening steps of the heating and cooling operation and the pressure difference between the suction and the exhaust.
3. The method as claimed in claim 2, wherein the pressure difference between the suction and discharge pressures is calculated according to a measured discharge pressure and a nominal suction pressure, wherein the nominal suction pressure is equal to a refrigerant saturation pressure corresponding to a nominal evaporation temperature, and the nominal evaporation temperature is an evaporation temperature under a nominal working condition design.
4. The method as claimed in claim 1, wherein the second number of opening steps of the expansion valve is corrected when the theoretical load is different from the actual load at the 75% and 50% levels.
5. The method as claimed in claim 4, wherein the liquid supply amount of the unit is controlled by controlling the number of opening steps of the expansion valve; firstly, setting the maximum value and the minimum value of the opening steps of the expansion valve; if the calculated first opening step number of the expansion valve or the second opening step number of the expansion valve or the corrected value of the second opening step number is larger than the maximum value of the opening step number of the expansion valve, controlling the actual opening step number of the expansion valve to be equal to the maximum value of the opening step number of the expansion valve; and if the calculated first opening step number of the expansion valve or the second opening step number of the expansion valve or the corrected value of the second opening step number of the expansion valve is smaller than the minimum value of the opening step numbers of the expansion valve, controlling the actual opening step number of the expansion valve to be equal to the minimum value of the opening step numbers of the expansion valve.
6. The device for controlling the refrigerant flow of the refrigeration air conditioner in real time is characterized by comprising a control module, a pressure detection module and a temperature detection module; wherein,
the control module is used for processing the temperature and pressure data and controlling the opening and closing of the expansion valve according to the processing result;
the pressure detection module is used for acquiring pressure data of the evaporator and the condenser;
the temperature detection module is used for acquiring temperature data of the evaporator and the condenser;
the processing mode of the control module for processing the temperature and pressure data is as follows:
firstly, calculating a nominal evaporation temperature Te (Teo-2) according to an evaporator outlet water temperature Teo acquired by a system in real time, calculating a suction-discharge pressure difference x (Pd-Ps) (Pd is an exhaust pressure measured value; Ps is a nominal suction pressure which is equal to a refrigerant saturation pressure corresponding to Te) according to an exhaust pressure measured value and a nominal suction pressure, and calculating a starting step number y when a compressor is in full load operation and a starting step number yp when a compressor is in partial load operation by the calculation method according to the theoretical starting step number and the suction-discharge pressure difference of an expansion valve under heating working conditions and refrigeration working conditions;
in order to control the opening steps of the electronic expansion valve more accurately and thus control the liquid supply amount, it is necessary to set a limit on the opening steps of the expansion valve, where the maximum value is ymaxAnd minimum value of yminAs long as the compressor is turned on, it is necessary to ensure yminYz (or yp) is less than or equal to ymax(ii) a If yz (or yp) is less than or equal to yminLet yz (or yp) be yminIf yz (or yp) ≧ ymaxLet yz (or yp) be ymax(ii) a Wherein yz is the opening step number of the corrected electronic expansion valve, and yz is yp (1+ S);
wherein,Tblcorrecting a proportional band for small temperature difference; and M is an empirical value, and the correction limit values of the opening steps of the electronic expansion valve are all values.
7. The refrigerant flow rate real-time control device for a refrigeration and air-conditioning as claimed in claim 6, further comprising a human-computer interaction module for implementing human-computer interaction.
8. The device as claimed in claim 6, wherein the pressure detecting module comprises a high pressure sensor and a low pressure sensor, which are respectively connected to the analog input port of the control module for collecting the pressure values of the evaporator and the condenser.
9. The device as claimed in claim 6, wherein the temperature detecting module comprises an evaporator outlet temperature sensor and a condenser outlet temperature sensor, which are respectively connected to the temperature data input port of the control module for collecting the evaporator outlet temperature and the condenser outlet temperature.
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| WO2017107111A1 (en) * | 2015-12-23 | 2017-06-29 | 詹坤田 | Method and device for controlling flow rate of flooded screw compressor on the basis of opening size |
| CN106055882B (en) * | 2016-05-24 | 2019-04-02 | 珠海格力电器股份有限公司 | Water-cooling screw heat pump unit type selection calculation method and device |
| CN106568165B (en) * | 2016-11-02 | 2019-05-17 | 广东美的暖通设备有限公司 | A kind of adjusting method of air conditioner electronic expansion valve, system and air conditioner |
| CN106595141B (en) * | 2016-12-12 | 2019-12-27 | 重庆美的通用制冷设备有限公司 | Control method and device of electronic expansion valve and refrigerating system |
| CN109579191B (en) * | 2018-12-25 | 2021-07-13 | 荏原冷热***（中国）有限公司 | Double-compressor air conditioning system and control method and control device for refrigerant circulation amount thereof |
| CN111609590B (en) * | 2020-04-24 | 2021-06-29 | 珠海格力电器股份有限公司 | Double-temperature air conditioning system, control method and air conditioner |
| CN112050299B (en) * | 2020-09-09 | 2022-03-18 | 青岛海信日立空调***有限公司 | Air conditioner |
| CN112303856A (en) * | 2020-11-10 | 2021-02-02 | 深圳市柏涛蓝森国际建筑设计有限公司 | Method and system for realizing air conditioner cold load calculation |
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| JP3043770B2 (en) * | 1990-01-12 | 2000-05-22 | 株式会社日立製作所 | Air conditioner |
| KR100868344B1 (en) * | 2002-08-02 | 2008-11-13 | 엘지전자 주식회사 | A driving control method of inverter air- conditioner |
| CN1553111A (en) * | 2003-05-30 | 2004-12-08 | 乐金电子(天津)电器有限公司 | Starting controlling method for frequency-variable air conditioner |
| CN200986353Y (en) * | 2006-11-08 | 2007-12-05 | 江***亚空调工程有限公司 | Device for controlling amount of feeding liquid of full liquid type water-cooling screw rod water chilling unit |
| CN101603751B (en) * | 2009-07-15 | 2013-07-10 | 北京科技大学 | Variable frequency energy-saving control method for refrigeration system |
| CN204787045U (en) * | 2015-06-25 | 2015-11-18 | 山东格瑞德集团有限公司 | Refrigeration air conditioner varied refrigerant volume real time control device |
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