CN104613615A - Air-conditioner and control method thereof - Google Patents
Air-conditioner and control method thereof Download PDFInfo
- Publication number
- CN104613615A CN104613615A CN201510057112.5A CN201510057112A CN104613615A CN 104613615 A CN104613615 A CN 104613615A CN 201510057112 A CN201510057112 A CN 201510057112A CN 104613615 A CN104613615 A CN 104613615A
- Authority
- CN
- China
- Prior art keywords
- control valve
- delivery temperature
- aperture
- compressor
- air
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Classifications
-
- 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
- F24F11/62—Control or safety arrangements characterised by the type of control or by internal processing, e.g. using fuzzy logic, adaptive control or estimation of values
-
- 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
- F24F11/70—Control systems characterised by their outputs; Constructional details thereof
- F24F11/80—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air
- F24F11/83—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers
-
- 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
-
- 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
- F24F11/62—Control or safety arrangements characterised by the type of control or by internal processing, e.g. using fuzzy logic, adaptive control or estimation of values
- F24F11/63—Electronic processing
- F24F11/64—Electronic processing using pre-stored data
-
- 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
- F24F11/70—Control systems characterised by their outputs; Constructional details thereof
- F24F11/80—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air
- F24F11/83—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers
- F24F11/84—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers using valves
Abstract
The invention provides an air-conditioner and a control method thereof. The air-conditioner comprises a first compressor and a second compressor which are arranged in parallel. The air-conditioner further comprises a first air suction pipe, a first air exhaust pipe, a second air suction pipe and a second air exhaust pipe, wherein the first air suction pipe and the first air exhaust pipe are connected to the first compressor, and the second air suction pipe and the second air exhaust pipe are connected to the second compressor. The air-conditioner further comprises a first temperature sensor, a second temperature sensor, a first regulating valve and a second regulating valve. The first temperature sensor is arranged on the first air exhaust pipe and used for acquiring the first air exhaust temperature of the first compressor, and the second temperature sensor is arranged on the second air exhaust pipe and used for acquiring the second air exhaust temperature of the second compressor. The first regulating valve is used for controlling the refrigerant suction volume of the first compressor, the second regulating valve is used for controlling the refrigerant suction volume of the second compressor, and the opening degree of the first regulating valve and/or the opening degree of the second regulating valve are/is determined through the difference value of the first air exhaust temperature and the second air exhaust temperature. According to the technical scheme, the problem that the refrigerant suction volumes of all the compressors in a parallel connection compressor set in an air-conditioner cannot be controlled easily in the prior art is effectively solved.
Description
Technical field
The present invention relates to air-conditioning technical field, in particular to a kind of air-conditioner and control method thereof.
Background technology
In light-duty business air conditioner unit, because the self character of screw compressor and the scope of application consider, the compressor of 10 and 12 is the most conventional, and cost performance is the highest.Therefore when the requirement refrigerating capacity of compressor bank reach 60,70 even larger time, in order to not make system quantity too much cause balancing boom number of devices huge, generally individual system all can adopt the compressor parallel of 2 10 or 12.But, adopt parallel compressor unit while raising cost performance, there will be that unit is too high in pressure ratio, too low or cooling medium charging is bigger than normal.Cooling medium charging is bigger than normal easily causes the unbalanced phenomena that between parallel connection compressor, inspiratory capacity deviation is excessive, thus the compressor oil temperature causing inspiratory capacity large is on the low side, and then there is the phenomenon of compressor oil insufficient lubrication and system instability, affect reliable use and the life-span of compressor.
For the problems referred to above, in prior art, impedance match operation is carried out to the pipeline runner of two compressors, balanced to ensure the inspiratory capacity of two parallel connection compressors.But when after parallel compressor unit work a period of time, the parameters of unit changes, be difficult to ensure that the pipe resistance of parallel connection compressor is consistent, therefore the refrigerant soakage of two compressors is difficult to control.
Summary of the invention
Main purpose of the present invention is to provide a kind of air-conditioner and control method thereof, with the unmanageable problem of each compressor refrigerant soakage in the parallel compressor unit solving air-conditioner in prior art.
To achieve these goals, according to an aspect of the present invention, provide a kind of air-conditioner, comprise: the first compressor be arranged in parallel and the second compressor, air-conditioner also comprises and is connected to the first air intake duct on the first compressor and downtake pipe and the second air intake duct be connected on the second compressor and second exhaust pipe, air-conditioner also comprises: the first temperature sensor, to be arranged on downtake pipe and the first delivery temperature for obtaining the first compressor; Second temperature sensor, to be arranged on second exhaust pipe and the second delivery temperature for obtaining the second compressor; First control valve, is arranged on the first air intake duct, and the first control valve is for controlling the refrigerant soakage of the first compressor; Second control valve, is arranged on the second air intake duct, and the second control valve is for controlling the refrigerant soakage of the second compressor, and wherein, the aperture of the first control valve and/or the second control valve is determined by the difference of the first delivery temperature and the second delivery temperature.
Further, air-conditioner also comprises controller, and the first temperature sensor, the second temperature sensor, the first control valve and the second control valve are all connected with controller.
According to a further aspect in the invention, provide a kind of control method of air-conditioner, air-conditioner is above-mentioned air-conditioner, and control method comprises: the first delivery temperature obtaining downtake pipe, obtains the second delivery temperature of second exhaust pipe; The aperture of the first control valve and/or the second control valve is controlled by the difference of the first delivery temperature and the second delivery temperature.
Further, the step being controlled the aperture of the first control valve and/or the second control valve by the difference of the first delivery temperature and the second delivery temperature is comprised: when the first delivery temperature is greater than the second delivery temperature, and the difference of the first delivery temperature and the second delivery temperature is when being greater than the first preset value, the aperture maintaining the first control valve is constant, reduces the aperture of the second control valve; When the first delivery temperature is less than the second delivery temperature, and when the difference of the first delivery temperature and the second delivery temperature is less than the second preset value, the aperture maintaining the second control valve is constant, reduces the aperture of the first control valve; When the difference of the first delivery temperature and the second delivery temperature is between the first preset value and the second preset value, the aperture maintaining the first control valve and the second control valve is constant.
Further, the step being controlled the aperture of the first control valve and/or the second control valve by the difference of the first delivery temperature and the second delivery temperature is comprised: when the first delivery temperature is greater than the second delivery temperature, and the difference of the first delivery temperature and the second delivery temperature is when being greater than the first preset value, the aperture maintaining the second control valve is constant, increases the aperture of the first control valve; When the first delivery temperature is less than the second delivery temperature, and when the difference of the first delivery temperature and the second delivery temperature is less than the second preset value, the aperture maintaining the first control valve is constant, increases the aperture of the second control valve; When the difference of the first delivery temperature and the second delivery temperature is between the first preset value and the second preset value, the aperture maintaining the first control valve and the second control valve is constant.
Further, the step being controlled the aperture of the first control valve and/or the second control valve by the difference of the first delivery temperature and the second delivery temperature is comprised: when the first delivery temperature is greater than the second delivery temperature, and the difference of the first delivery temperature and the second delivery temperature is when being greater than the first preset value, while increasing the aperture of the first control valve, reduce the aperture of the second control valve; When the first delivery temperature is less than the second delivery temperature, and when the difference of the first delivery temperature and the second delivery temperature is less than the second preset value, while increasing the aperture of the second control valve, reduce the aperture of the first control valve; When the difference of the first delivery temperature and the second delivery temperature is between the first preset value and the second preset value, the aperture maintaining the first control valve and the second control valve is constant.
Further, the first preset value is 5 DEG C, and the second preset value is-5 DEG C.
Further, reduce in the step of the aperture of the second control valve, the percentage of the reduction of the aperture of the second control valve is obtained by following formula: A=((T
1-T
2)/5) %; Wherein, A is the percentage of the reduction of the aperture of the second control valve, and T1 is the first delivery temperature, and T2 is the second delivery temperature.
Further, reduce in the step of the aperture of the first control valve, the percentage of the reduction of the aperture of the first control valve is obtained by following formula: B=((T
2-T
1)/5) %; Wherein, B is the percentage of the reduction of the aperture of the first control valve, and T2 is the second delivery temperature, and T1 is the first delivery temperature.
Further, obtain the first delivery temperature of downtake pipe, further comprising the steps of before obtaining the second delivery temperature of second exhaust pipe: to close the first control valve and the second control valve; Open the first control valve and the second control valve, and make the first control valve and the second control valve have identical aperture; Open the first compressor and the second compressor simultaneously.
Further, the step making the first control valve and the second control valve have identical aperture comprises: make the first control valve and the second control valve all open to maximum opening.
Apply technical scheme of the present invention, first air intake duct and downtake pipe of the first compressor arrange the first control valve and the first temperature sensor, second air intake duct and second exhaust pipe of the second compressor arrange the second control valve and the second temperature sensor.When the first compressor and the second compressor operating, obtained the first delivery temperature of the first compressor by the first temperature sensor, obtained the second delivery temperature of the second compressor by the second temperature sensor.Judge that whether the first compressor is consistent with the refrigerant soakage of the second compressor by the first delivery temperature and the difference of the second delivery temperature, and then with the aperture of the second control valve, adjustment the first control valve guarantees that the first air intake duct is consistent with the resistance of the second air intake duct, ensure that the refrigerant soakage of the first compressor and the second compressor is balanced.Therefore technical scheme of the present invention can solve each compressor refrigerant soakage in the parallel compressor unit of air-conditioner in prior art and is difficult to control problem.
Accompanying drawing explanation
The Figure of description forming a application's part is used to provide a further understanding of the present invention, and schematic description and description of the present invention, for explaining the present invention, does not form inappropriate limitation of the present invention.In the accompanying drawings:
Fig. 1 shows the structural representation of the embodiment one according to air-conditioner of the present invention;
Fig. 2 shows the schematic flow sheet of the embodiment one according to the control method of air-conditioner of the present invention;
Fig. 3 shows the schematic flow sheet of the embodiment two according to the control method of air-conditioner of the present invention; And
Fig. 4 shows the schematic flow sheet of the embodiment three according to the control method of air-conditioner of the present invention.
Wherein, above-mentioned accompanying drawing comprises the following drawings mark:
10, the first compressor; 11, the first air intake duct; 12, downtake pipe; 13, the first temperature sensor; 14, the first control valve; 20, the second compressor; 21, the second air intake duct; 22, second exhaust pipe; 23, the second temperature sensor; 24, the second control valve; 30, controller.
Detailed description of the invention
It should be noted that, when not conflicting, the embodiment in the application and the feature in embodiment can combine mutually.Below with reference to the accompanying drawings and describe the present invention in detail in conjunction with the embodiments.
As shown in Figure 1, the air-conditioner of embodiment one comprises the first compressor 10 and the second compressor 20 be arranged in parallel.Air-conditioner also comprises and is connected to the first air intake duct 11 on the first compressor 10 and downtake pipe 12 and the second air intake duct 21 be connected on the second compressor 20 and second exhaust pipe 22.Air-conditioner also comprises the first temperature sensor 13, first control valve 14, second temperature sensor 23 and the second control valve 24.First temperature sensor 13 to be arranged on downtake pipe 12 and the first delivery temperature for obtaining the first compressor 10.Second temperature sensor 23 to be arranged on second exhaust pipe 22 and the second delivery temperature for obtaining the second compressor 20.First control valve 14 to be arranged on the first air intake duct 11 and refrigerant soakage for controlling the first compressor 10.Second control valve 24 to be arranged on the second air intake duct 21 and refrigerant soakage for controlling the second compressor 20.Wherein, the aperture of the first control valve 14 and/or the second control valve 24 is determined by the difference of the first delivery temperature and the second delivery temperature.
The technical scheme of application the present embodiment, first air intake duct 11 and downtake pipe 12 of the first compressor 10 arrange the first control valve 14 and the first temperature sensor 13, second air intake duct 21 and second exhaust pipe 22 of the second compressor 20 arrange the second control valve 24 and the second temperature sensor 23.When the first compressor 10 and the second compressor 20 work, obtained the first delivery temperature of the first compressor 10 by the first temperature sensor 13, obtained the second delivery temperature of the second compressor 20 by the second temperature sensor 23.Judge that whether the first compressor 10 is consistent with the refrigerant soakage of the second compressor 20 by the first delivery temperature and the difference of the second delivery temperature, and then with the aperture of the second control valve 24, adjustment the first control valve 14 guarantees that the first air intake duct 11 is consistent with the resistance of the second air intake duct 21, ensure that the refrigerant soakage of the first compressor 10 and the second compressor 20 is balanced.Therefore technical scheme of the present invention can solve each compressor refrigerant soakage in the parallel compressor unit of air-conditioner in prior art and is difficult to control problem.
As shown in Figure 1, in the technical scheme of the present embodiment, air-conditioner also comprises controller 30, and the first temperature sensor 13, second temperature sensor 23, first control valve 14 and the second control valve 24 are all connected with controller 30.Controller 30 obtains the first delivery temperature by the first temperature sensor 13, obtains the second delivery temperature by the second temperature sensor 23.Controller 30 can control the aperture of the first control valve 14 and the second control valve 24.
Present invention also provides a kind of control method of air-conditioner, air-conditioner is above-mentioned air-conditioner.As shown in Figure 2, the control method of embodiment one comprises: the first delivery temperature obtaining downtake pipe 12, obtains the second delivery temperature of second exhaust pipe 22; The aperture of the first control valve 14 and/or the second control valve 24 is controlled by the difference of the first delivery temperature and the second delivery temperature.
The technical scheme of application the present embodiment, judge that whether the first compressor 10 is consistent with the refrigerant soakage of the second compressor 20 by the first delivery temperature and the difference of the second delivery temperature, and then with the aperture of the second control valve 24, adjustment the first control valve 14 guarantees that the first air intake duct 11 is consistent with the resistance of the second air intake duct 21, ensure that the refrigerant soakage of the first compressor 10 and the second compressor 20 is balanced.Therefore technical scheme of the present invention can solve each compressor refrigerant soakage in the parallel compressor unit of air-conditioner in prior art and is difficult to control problem.
As shown in Figure 2, in the technical scheme of the present embodiment, the step being controlled the aperture of the first control valve 14 and/or the second control valve 24 by the difference of the first delivery temperature and the second delivery temperature is comprised:
When the first delivery temperature is greater than the second delivery temperature, and when the difference of the first delivery temperature and the second delivery temperature is greater than the first preset value, the aperture maintaining the first control valve 14 is constant, reduces the aperture of the second control valve 24.Particularly, when the first delivery temperature is greater than the second delivery temperature, and when the first delivery temperature is greater than the second delivery temperature certain numerical value, illustrates that the second compressor 20 sucks coolant quantity too much, cause delivery temperature low.Second compressor 20 sucks coolant quantity and the second compressor 20 oil temperature too much can be caused too low, causes the second compressor 20 insufficient lubrication, affects job stability and the equipment life of the second compressor 20.Now need the aperture of reduction second control valve 24, and then increase the resistance of ducting of the second air intake duct 21, thus reduce the refrigerant soakage of the second compressor 20, ensure the normal work of the second compressor.
Preferably, the percentage of the reduction of the aperture of the second control valve 24 is obtained by following formula:
Formula one: A=((T1-T2)/5) %;
Wherein, A is the percentage of the reduction of the aperture of the second control valve 24, and T1 is the first delivery temperature, and T2 is the second delivery temperature.Certainly, the decreasing value of the aperture of the second control valve 24 is not limited to use formula one acquisition, and other modes can be adopted to obtain.
When the first delivery temperature is less than the second delivery temperature, and when the difference of the first delivery temperature and the second delivery temperature is less than the second preset value, the aperture maintaining the second control valve 24 is constant, reduces the aperture of the first control valve 14.Particularly, when the first delivery temperature is less than the second delivery temperature, and when the first delivery temperature is less than the second delivery temperature certain numerical value, illustrates that the first compressor 10 sucks coolant quantity too much, cause delivery temperature low.First compressor 10 sucks coolant quantity and the first compressor 10 oil temperature too much can be caused too low, causes the first compressor 10 insufficient lubrication, affects job stability and the equipment life of the first compressor 10.Now need the aperture of reduction first control valve 14, and then increase the resistance of ducting of the first air intake duct 11, thus reduce the refrigerant soakage of the first compressor 10, ensure the normal work of the first compressor.
Preferably, the percentage of the reduction of the aperture of the first control valve 14 is obtained by following formula:
Formula two: B=((T2-T1)/5) %;
Wherein, B is the percentage of the reduction of the aperture of the second control valve 24, and T2 is the second delivery temperature, and T1 is the first delivery temperature.Certainly, the decreasing value of the aperture of the second control valve 24 is not limited to use formula one acquisition, and other modes can be adopted to obtain.
When the difference of the first delivery temperature and the second delivery temperature is between the first preset value and the second preset value, the aperture maintaining the first control valve 14 and the second control valve 24 is constant.Particularly, the first preset value is 5 DEG C, and the second preset value is-5 DEG C.When the difference of the first delivery temperature and the second delivery temperature is in the scope of-5 to 5 DEG C, think the first compressor 10 and the second compressor 20 working properly, the aperture of the first control valve 14 and the second control valve 24 does not make any adjustments.The concrete numerical value of certain first preset value and the second preset value does not limit, and can adjust according to equipment situation and actual needs,
As shown in Figure 2, in the technical scheme of the present embodiment, in order to ensure that the first control valve 14 and the second control valve 24 can normally work, therefore, obtain the first delivery temperature of downtake pipe 12, further comprising the steps of before obtaining the second delivery temperature of second exhaust pipe 22:
First close the first control valve 14 and the second control valve 24, opening the first control valve 14 and the second control valve 24, and make the first control valve 14 and the second control valve 24 have identical aperture, aforesaid operations ensures not to be stuck at work front first control valve 14 and the second control valve 24 of the first compressor 10 and the second compressor 20.
After confirmation first control valve 14 and the second control valve 24 do not have fault, open the first compressor 10 and the second compressor 20 simultaneously.
Preferably, little as much as possible in order to ensure the first compressor 10 and the second compressor 20 resistance when starting working in the first air intake duct 11 and the second air intake duct 21, make the first control valve 14 and the second control valve 24 have in the step of identical aperture, the first control valve 14 and the second control valve 24 all open to maximum opening.
Embodiment two is with the difference of embodiment one, and when the difference of the first delivery temperature and the second delivery temperature is not in the scope of the first preset value and the second preset value, the first control valve 14 is different with the control mode of the second control valve 24, as shown in Figure 3:
When the first delivery temperature is greater than the second delivery temperature, and when the difference of the first delivery temperature and the second delivery temperature is greater than the first preset value, the aperture maintaining the second control valve 24 is constant, increases the aperture of the first control valve 14.Particularly, the aperture increasing by the first control valve 14 can reduce the resistance in the first air intake duct 11.Because the first compressor 10 and the second compressor 20 are for being arranged in parallel, the resistance therefore in the second air intake duct 21 is constant, refrigerant can more flow in the less air intake duct of resistance.Therefore, the aperture maintaining the second control valve 24 is constant, and the aperture increasing by the first control valve 14 can reach the effect of the refrigerant soakage of minimizing second compressor.
When the first delivery temperature is less than the second delivery temperature, and when the difference of the first delivery temperature and the second delivery temperature is less than the second preset value, the aperture maintaining the first control valve 14 is constant, increases the aperture of the second control valve 24.Particularly, the aperture increasing by the second control valve 24 can reduce the resistance in the second air intake duct 21.Because the first compressor 10 and the second compressor 20 are for being arranged in parallel, the resistance therefore in the first air intake duct 11 is constant, refrigerant can more flow in the less air intake duct of resistance.Therefore, the aperture maintaining the first control valve 14 is constant, and the aperture increasing by the second control valve 24 can reach the effect of the refrigerant soakage of minimizing first compressor.
In embodiment two, when the difference of the first delivery temperature and the second delivery temperature is greater than the first preset value, or and identical with embodiment one with the impact of the second compressor 20 on the first compressor 10 when the first delivery temperature and the difference of the second delivery temperature are less than the second preset value, do not repeat them here.
Embodiment three is with the difference of other embodiments, and when the difference of the first delivery temperature and the second delivery temperature is not in the scope of the first preset value and the second preset value, the first control valve 14 is different with the control mode of the second control valve 24, as shown in Figure 4:
When the first delivery temperature is greater than the second delivery temperature, and the difference of the first delivery temperature and the second delivery temperature is when being greater than the first preset value, the aperture of the second control valve 24 is reduced while increasing the aperture of the first control valve 14, particularly, aforesaid operations increases the resistance in the second air intake duct 21 while making the resistance in reduction first air intake duct 11.Because the first compressor 10 and the second compressor 20 are for being arranged in parallel, resistance therefore in the first air intake duct 11 reduces and resistance in the second air intake duct 21 increases, refrigerant can more flow in the less air intake duct of resistance.Therefore, the aperture reducing the second control valve 24 while increasing the aperture of the first control valve 14 can reach the effect of the refrigerant soakage of minimizing first compressor.
When the first delivery temperature is less than the second delivery temperature, and when the difference of the first delivery temperature and the second delivery temperature is less than the second preset value, while increasing the aperture of the second control valve 24, reduce the aperture of the first control valve 14.Particularly, aforesaid operations reduces the resistance in the second air intake duct 21 while making the resistance in increase first air intake duct 11.Because the first compressor 10 and the second compressor 20 are for being arranged in parallel, resistance therefore in the first air intake duct 11 increases and resistance in the second air intake duct 21 reduces, refrigerant can more flow in the less air intake duct of resistance.Therefore, the aperture reducing the first control valve 14 while increasing the aperture of the second control valve 24 can reach the effect of the refrigerant soakage of minimizing first compressor.
In embodiment three, when the difference of the first delivery temperature and the second delivery temperature is greater than the first preset value, or and identical with embodiment two with embodiment one with the impact of the second compressor 20 on the first compressor 10 when the first delivery temperature and the difference of the second delivery temperature are less than the second preset value, do not repeat them here.
The foregoing is only the preferred embodiments of the present invention, be not limited to the present invention, for a person skilled in the art, the present invention can have various modifications and variations.Within the spirit and principles in the present invention all, any amendment done, equivalent replacement, improvement etc., all should be included within protection scope of the present invention.
Claims (11)
1. an air-conditioner, comprising:
The first compressor (10) be arranged in parallel and the second compressor (20), described air-conditioner also comprises and is connected to the first air intake duct (11) on described first compressor (10) and downtake pipe (12) and the second air intake duct (21) be connected on described second compressor (20) and second exhaust pipe (22)
It is characterized in that, described air-conditioner also comprises:
First temperature sensor (13), is arranged on upper and the first delivery temperature for obtaining described first compressor (10) of described downtake pipe (12);
Second temperature sensor (23), is arranged on upper and the second delivery temperature for obtaining described second compressor (20) of described second exhaust pipe (22);
First control valve (14), is arranged on described first air intake duct (11), and described first control valve (14) is for controlling the refrigerant soakage of described first compressor (10);
Second control valve (24), is arranged on described second air intake duct (21), described second control valve for controlling the refrigerant soakage of described second compressor (20),
Wherein, the aperture of described first control valve (14) and/or the second control valve (24) is determined by the difference of described first delivery temperature and described second delivery temperature.
2. air-conditioner according to claim 1, it is characterized in that, described air-conditioner also comprises controller (30), and described first temperature sensor (13), described second temperature sensor (23), described first control valve (14) and described second control valve (24) are all connected with described controller (30).
3. a control method for air-conditioner, is characterized in that, described air-conditioner comprises for the air-conditioner described in claim 1 or 2, described control method:
Obtain the first delivery temperature of downtake pipe (12), obtain the second delivery temperature of second exhaust pipe (22);
The aperture of described first control valve (14) and/or described second control valve (24) is controlled by the difference of described first delivery temperature and described second delivery temperature.
4. control method according to claim 3, it is characterized in that, being comprised by the step of described first delivery temperature and difference described first control valve (14) of control of described second delivery temperature and/or the aperture of described second control valve (24):
When described first delivery temperature is greater than described second delivery temperature, and the difference of described first delivery temperature and described second delivery temperature is when being greater than the first preset value, the aperture maintaining described first control valve (14) is constant, reduces the aperture of described second control valve (24);
When described first delivery temperature is less than described second delivery temperature, and the difference of described first delivery temperature and described second delivery temperature is when being less than the second preset value, the aperture maintaining described second control valve (24) is constant, reduces the aperture of described first control valve (14);
When the difference of described first delivery temperature and described second delivery temperature is between described first preset value and described second preset value, the aperture maintaining described first control valve (14) and described second control valve (24) is constant.
5. control method according to claim 3, it is characterized in that, being comprised by the step of described first delivery temperature and difference described first control valve (14) of control of described second delivery temperature and/or the aperture of described second control valve (24):
When described first delivery temperature is greater than described second delivery temperature, and the difference of described first delivery temperature and described second delivery temperature is when being greater than the first preset value, the aperture maintaining described second control valve (24) is constant, increases the aperture of described first control valve (14);
When described first delivery temperature is less than described second delivery temperature, and the difference of described first delivery temperature and described second delivery temperature is when being less than the second preset value, the aperture maintaining described first control valve (14) is constant, increases the aperture of described second control valve (24);
When the difference of described first delivery temperature and described second delivery temperature is between described first preset value and described second preset value, the aperture maintaining described first control valve (14) and described second control valve (24) is constant.
6. control method according to claim 3, it is characterized in that, being comprised by the step of described first delivery temperature and difference described first control valve (14) of control of described second delivery temperature and/or the aperture of described second control valve (24):
When described first delivery temperature is greater than described second delivery temperature, and the difference of described first delivery temperature and described second delivery temperature is when being greater than the first preset value, while increasing the aperture of described first control valve (14), reduce the aperture of the second control valve (24);
When described first delivery temperature is less than described second delivery temperature, and the difference of described first delivery temperature and described second delivery temperature is when being less than the second preset value, while increasing the aperture of described second control valve (24), reduce the aperture of the first control valve (14);
When the difference of described first delivery temperature and described second delivery temperature is between described first preset value and described second preset value, the aperture maintaining described first control valve (14) and described second control valve (24) is constant.
7. the control method according to any one of claim 4 to 6, is characterized in that, described first preset value is 5 DEG C, and described second preset value is-5 DEG C.
8. control method according to claim 4, is characterized in that, reduce in the step of the aperture of described second control valve (24), the percentage of the reduction of the aperture of described second control valve (24) is obtained by following formula:
A＝((T
1-T
2)/5)％；
Wherein, described A is the percentage of the reduction of the aperture of described second control valve (24), described T
1for described first delivery temperature, described T
2for described second delivery temperature.
9. control method according to claim 4, is characterized in that, reduce in the step of the aperture of described first control valve (14), the percentage of the reduction of the aperture of described first control valve (14) is obtained by following formula:
B＝((T
2-T
1)/5)％；
Wherein, described B is the percentage of the reduction of the aperture of described first control valve (14), described T
2for described second delivery temperature, described T
1for described first delivery temperature.
10. control method according to claim 3, is characterized in that, obtains the first delivery temperature of described downtake pipe (12), further comprising the steps of before obtaining the second delivery temperature of described second exhaust pipe (22):
Close described first control valve (14) and described second control valve (24);
Open described first control valve (14) and described second control valve (24), and make described first control valve (14) and described second control valve (24) have identical aperture;
Open described first compressor (10) and described second compressor (20) simultaneously.
11. control methods according to claim 10, is characterized in that, the step making described first control valve (14) and described second control valve (24) have identical aperture comprises:
Described first control valve (14) and described second control valve (24) is made all to open to maximum opening.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510057112.5A CN104613615B (en) | 2015-02-03 | 2015-02-03 | Air-conditioner and its control method |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510057112.5A CN104613615B (en) | 2015-02-03 | 2015-02-03 | Air-conditioner and its control method |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN104613615A true CN104613615A (en) | 2015-05-13 |
| CN104613615B CN104613615B (en) | 2017-06-06 |
Family
ID=53148189
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201510057112.5A Active CN104613615B (en) | 2015-02-03 | 2015-02-03 | Air-conditioner and its control method |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN104613615B (en) |
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106338118A (en) * | 2016-09-29 | 2017-01-18 | 广东美的制冷设备有限公司 | Air conditioning system and control method thereof |
| CN106440273A (en) * | 2016-09-29 | 2017-02-22 | 广东美的制冷设备有限公司 | Air conditioner system and control method thereof |
| CN106705519A (en) * | 2015-11-12 | 2017-05-24 | 新特能源股份有限公司 | Multistage refrigerating device and control method thereof |
| CN106871372A (en) * | 2017-03-16 | 2017-06-20 | 广东美的暖通设备有限公司 | The recognition methods of air-conditioning system and its exhaust gas temperature sensor |
| CN107621047A (en) * | 2017-08-15 | 2018-01-23 | 珠海格力电器股份有限公司 | The control method and device of air-conditioner set |
| US11547243B2 (en) | 2017-08-09 | 2023-01-10 | Sharkninja Operating Llc | Cooking device and components thereof |
| WO2023124723A1 (en) * | 2021-12-29 | 2023-07-06 | 广东美的白色家电技术创新中心有限公司 | Compressor exhaust temperature control method and apparatus, device and medium |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH09243139A (en) * | 1996-03-05 | 1997-09-16 | Kajima Corp | Air conditioner system |
| CN2628969Y (en) * | 2003-04-02 | 2004-07-28 | 海尔集团公司 | Multi compressor variable capacity fixed frequency one with several air conditioner |
| EP1524475B1 (en) * | 2003-10-17 | 2008-02-20 | LG Electronics, Inc. | Apparatus and method for controlling the super-heating degree in a heat pump system |
| JP2014031916A (en) * | 2012-08-02 | 2014-02-20 | Panasonic Corp | Refrigeration device |
| CN103629791A (en) * | 2013-12-03 | 2014-03-12 | 孙厚永 | Air conditioning unit for machine room |
| CN203642549U (en) * | 2013-11-14 | 2014-06-11 | 广东美的暖通设备有限公司 | Compressor unit system and heat pump system |
-
2015
- 2015-02-03 CN CN201510057112.5A patent/CN104613615B/en active Active
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH09243139A (en) * | 1996-03-05 | 1997-09-16 | Kajima Corp | Air conditioner system |
| CN2628969Y (en) * | 2003-04-02 | 2004-07-28 | 海尔集团公司 | Multi compressor variable capacity fixed frequency one with several air conditioner |
| EP1524475B1 (en) * | 2003-10-17 | 2008-02-20 | LG Electronics, Inc. | Apparatus and method for controlling the super-heating degree in a heat pump system |
| JP2014031916A (en) * | 2012-08-02 | 2014-02-20 | Panasonic Corp | Refrigeration device |
| CN203642549U (en) * | 2013-11-14 | 2014-06-11 | 广东美的暖通设备有限公司 | Compressor unit system and heat pump system |
| CN103629791A (en) * | 2013-12-03 | 2014-03-12 | 孙厚永 | Air conditioning unit for machine room |
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106705519A (en) * | 2015-11-12 | 2017-05-24 | 新特能源股份有限公司 | Multistage refrigerating device and control method thereof |
| CN106705519B (en) * | 2015-11-12 | 2019-04-19 | 新特能源股份有限公司 | Multistage refrigerating plant and its control method |
| CN106338118A (en) * | 2016-09-29 | 2017-01-18 | 广东美的制冷设备有限公司 | Air conditioning system and control method thereof |
| CN106440273A (en) * | 2016-09-29 | 2017-02-22 | 广东美的制冷设备有限公司 | Air conditioner system and control method thereof |
| CN106871372A (en) * | 2017-03-16 | 2017-06-20 | 广东美的暖通设备有限公司 | The recognition methods of air-conditioning system and its exhaust gas temperature sensor |
| US11547243B2 (en) | 2017-08-09 | 2023-01-10 | Sharkninja Operating Llc | Cooking device and components thereof |
| CN107621047A (en) * | 2017-08-15 | 2018-01-23 | 珠海格力电器股份有限公司 | The control method and device of air-conditioner set |
| WO2023124723A1 (en) * | 2021-12-29 | 2023-07-06 | 广东美的白色家电技术创新中心有限公司 | Compressor exhaust temperature control method and apparatus, device and medium |
Also Published As
| Publication number | Publication date |
|---|---|
| CN104613615B (en) | 2017-06-06 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN104613615A (en) | Air-conditioner and control method thereof | |
| US10775069B2 (en) | HVAC system and corresponding methods of controlling HVAC fan and coil capacity | |
| CN105509387B (en) | Air-Cooled Heat Pump Unit and electronic expansion valve opening control method therein, air-conditioning | |
| CN102767887B (en) | VRF (varied refrigerant volume) air conditioning system and control method of VRF air conditioning system | |
| WO2020000922A1 (en) | Air conditioning system control method and device and air conditioning system | |
| WO2018223759A1 (en) | Method for controlling air-conditioner air cooling unit and air-conditioner | |
| WO2018223758A1 (en) | Method for controlling air-conditioner air cooling unit and air-conditioner | |
| CN105423500B (en) | The control method of air conditioner, the control system of air conditioner and air conditioner | |
| EP3153797A1 (en) | Multi-split air conditioning system and medium pressure control method thereof | |
| CN104913445B (en) | Control method, the control system of blower fan gear and the air conditioner of blower fan gear | |
| EP3040651B1 (en) | Variable refrigerant flow system operation in low ambient conditions | |
| CN106196786A (en) | The method of regulation outdoor machine of air-conditioner electronic expansion valve | |
| CN104833056A (en) | Control method and control system for outdoor fans of air conditioner | |
| CN107143973A (en) | A kind of control method of multi-connected machine underload refrigerating operaton | |
| JP2014190554A (en) | Air conditioner | |
| CN112361538B (en) | Oil return control method and device and multi-split system | |
| CN106895623A (en) | Air-conditioner and its delivery temperature control method | |
| CN105003996A (en) | Total heat exchange fresh air fan | |
| CN106052215A (en) | Control method of electronic expansion valve of outdoor unit of air conditioner | |
| CN106403349B (en) | Double-cylinder variable-capacity air conditioning system and control method | |
| CN104791912A (en) | Multi-compressor air conditioning system and control method thereof | |
| CN105588286A (en) | Control method and device for multi-split air conditioner | |
| WO2016045171A1 (en) | Oil-return control method, device and outdoor unit of variable-frequency air conditioner | |
| CN103375937B (en) | Multi-gang air conditioner and control method thereof | |
| CN110906514B (en) | Multi-split capacity control method and air conditioning system |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |