CN106247652A - Air conditioning system and control method thereof - Google Patents
Air conditioning system and control method thereof Download PDFInfo
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- CN106247652A CN106247652A CN201610867664.7A CN201610867664A CN106247652A CN 106247652 A CN106247652 A CN 106247652A CN 201610867664 A CN201610867664 A CN 201610867664A CN 106247652 A CN106247652 A CN 106247652A
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- Prior art keywords
- expansion valve
- electronic expansion
- conditioning system
- air conditioning
- compressor
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B49/00—Arrangement or mounting of control or safety devices
- F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2600/00—Control issues
- F25B2600/25—Control of valves
- F25B2600/2513—Expansion valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2115—Temperatures of a compressor or the drive means therefor
- F25B2700/21151—Temperatures of a compressor or the drive means therefor at the suction side of the compressor
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2115—Temperatures of a compressor or the drive means therefor
- F25B2700/21152—Temperatures of a compressor or the drive means therefor at the discharge side of the compressor
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Air Conditioning Control Device (AREA)
Abstract
The open a kind of air conditioning system of the present invention, including being sequentially connected with and formed the compressor of twin-tub independent compression of refrigerant circulation circuit, reversing unit, outdoor heat exchanger, the first electric expansion valve, gas-liquid separator, the second electric expansion valve, indoor heat exchanger；Air conditioning system also includes controller, according to the operational factor of air conditioning system, determines aperture and the aperture of the second electric expansion valve of the first electric expansion valve；During air conditioning system is run, target exhaust temperature according to compressor or the return-air degree of superheat, regulate the aperture of the second electric expansion valve, and when the aperture of the second electric expansion valve reaches aperture maximum or the aperture minima of this electric expansion valve, when compressor target exhaust temperature or the return-air degree of superheat are still unable to reach, adjust the aperture of the first electric expansion valve.The invention also discloses the control method of a kind of air conditioning system.The present invention is not only so that this air conditioning system can quickly meet operation demand, but also ensures the operational energy efficiency of air conditioning system.
Description
Technical Field
The invention relates to the technical field of air conditioners, in particular to an air conditioning system and a control method thereof.
Background
The existing air conditioning system does not carry out optimal cycle design on the gas refrigerant after throttling and before entering the evaporator, so that the gas refrigerant influences the heat exchange performance of the evaporator, and the compression power consumption of the compressor is increased, thereby influencing the energy efficiency level of the air conditioner.
Although the enhanced vapor injection and double-cylinder compression technologies can improve the heating capacity level of the air-conditioning system at low temperature and ultralow temperature, in the control of the air-conditioning system, in order to ensure the normal operation and the operation energy efficiency of the air-conditioning system, the throttling regulation of the throttling device is extremely important, for example, when the air-conditioning system operates in a refrigeration mode, the refrigerant circulated out of the outdoor heat exchanger is subjected to primary throttling depressurization through the first throttling device, and the refrigerant circulated to the indoor heat exchanger is subjected to secondary throttling depressurization through the second throttling device. However, the existing throttling regulation is independently controlled and is regulated according to respective influence parameters, so that the operation energy efficiency of the air conditioning system cannot be ensured.
Disclosure of Invention
The invention mainly aims to provide an air conditioning system and a control method thereof, and aims to solve the technical problem that the operation energy efficiency of the air conditioning system cannot be ensured when independent control throttling is performed on the conventional air conditioning system.
In order to achieve the purpose, the air conditioning system provided by the invention comprises a double-cylinder independently-compressed compressor, a reversing unit, an outdoor heat exchanger, a first electronic expansion valve, a gas-liquid separator, a second electronic expansion valve and an indoor heat exchanger which are sequentially connected and form a refrigerant circulation loop; the air conditioning system also comprises a controller, wherein the controller determines the opening K11 of the first electronic expansion valve and the opening K21 of the second electronic expansion valve according to the operation parameters of the air conditioning system; during the operation of the air conditioning system, the opening K21 of the second electronic expansion valve is adjusted according to the target exhaust temperature or the return air superheat degree of the compressor, and when the opening K21 of the second electronic expansion valve reaches the maximum opening value or the minimum opening value of the electronic expansion valve and the target exhaust temperature or the return air superheat degree of the compressor cannot be reached yet, the opening K11 of the first electronic expansion valve is adjusted.
Preferably, the controller is configured to: and when the air conditioning system operates in a refrigeration mode, determining the opening K11 of the first electronic expansion valve according to the operating frequency of a compressor of the air conditioning system and the operating temperature of the air conditioner.
Preferably, the operating frequency of the compressor includes a current operating frequency or a frequency variation value of the compressor; the operating temperature includes a current temperature value or a temperature change value.
Preferably, the controller is configured to: and determining the opening K21 of the second electronic expansion valve according to the exhaust temperature or the return air superheat degree of the compressor.
Preferably, the controller is configured to: and determining the opening degree K21 of the second electronic expansion valve according to the opening degree K11 of the first electronic expansion valve and a preset difference value or a preset proportion value.
Preferably, the controller is configured to: and when the opening degree of the second electronic expansion valve reaches the maximum opening degree or the minimum opening degree of the electronic expansion valve and the target exhaust temperature or the return air superheat degree of the compressor cannot be reached, controlling the opening degree K11 of the first electronic expansion valve to be adjusted within the range of [ K11-delta K, K11+ delta K ].
Preferably, the value range of Δ K is [0,0.1K ], where K is the maximum opening degree of the electronic expansion valve.
In addition, in order to achieve the above object, the present invention further provides a control method of an air conditioning system, including the steps of:
acquiring operation parameters of an air conditioning system in the operation process of the air conditioner;
determining the opening degree K11 of the first electronic expansion valve and the opening degree K21 of the second electronic expansion valve according to the operation parameters of the air conditioning system;
during the operation of the air conditioning system, the opening K21 of the second electronic expansion valve is adjusted according to the target exhaust temperature or the return air superheat degree of the compressor;
when the opening degree K21 of the second electronic expansion valve reaches the maximum opening degree of the electronic expansion valve and the target exhaust temperature of the compressor or the superheat degree of return air cannot be reached, the opening degree K11 of the first electronic expansion valve is adjusted.
Preferably, the step of determining the opening degree K11 of the first electronic expansion valve according to the operation parameters of the air conditioning system comprises:
and when the air conditioning system operates in a refrigeration mode, determining the opening K11 of the first electronic expansion valve according to the operating frequency of a compressor of the air conditioning system and the operating temperature of the air conditioner.
Preferably, the step of determining the opening degree K21 of the second electronic expansion valve according to the operation parameters of the air conditioning system comprises:
determining the opening K21 of the second electronic expansion valve according to the exhaust temperature or the return air superheat degree of the compressor; or,
and determining the opening degree K21 of the second electronic expansion valve according to the opening degree K11 of the first electronic expansion valve and a preset difference value or a preset proportion value.
In the throttling control of the air conditioning system, the opening degree of a first electronic expansion valve and the opening degree of a second electronic expansion valve are determined according to air conditioning operation parameters, then the opening degree of the second electronic expansion valve is adjusted according to the target exhaust temperature or the return air superheat degree of a compressor, and the opening degree of the first electronic expansion valve is adjusted when the second electronic expansion valve is adjusted to the maximum opening degree or the minimum opening degree and still cannot reach the target exhaust temperature or the return air superheat degree of the compressor. Therefore, the air conditioning system controls the adjustment of the second electronic expansion valve through the exhaust or return air parameters of the compressor, so that the air conditioning system can quickly meet the operation requirement; in addition, when the operation requirement cannot be met after the second electronic expansion valve is adjusted, the first electronic expansion valve is adjusted again to ensure the operation energy efficiency of the air-conditioning system.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings used in the description of the embodiments or the prior art will be briefly described below, it is obvious that the drawings in the following description are only some embodiments of the present invention, and for those skilled in the art, other drawings can be obtained according to the structures shown in the drawings without creative efforts.
FIG. 1 is a schematic structural diagram of an embodiment of an air conditioning system according to the present invention;
fig. 2 is a flowchart illustrating a control method of an air conditioning system according to an embodiment of the present invention.
The reference numbers illustrate:
| reference numerals | Name (R) | Reference numerals | Name (R) |
| 1 | Compressor with a compressor housing having a plurality of compressor blades | 11 | First cylinder |
| 12 | The second cylinder | 13 | The first liquid storage tank |
| 14 | Second liquid storage tank | 2 | Reversing unit |
| 3 | Outdoor heat exchanger | 4 | First electronic expansion valve |
| 5 | Gas-liquid separator | 6 | Second electronic expansion valve |
| 7 | Indoor heat exchanger |
The implementation, functional features and advantages of the objects of the present invention will be further explained with reference to the accompanying drawings.
Detailed Description
The technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.
It should be noted that, if directional indications (such as up, down, left, right, front, and back … …) are referred to in the embodiments of the present invention, it is only used to explain the relative positional relationship between the components, the movement situation, and the like in a specific posture (as shown in the drawings), and if the specific posture is changed, the directional indication is changed accordingly.
In addition, if the description of "first", "second", etc. is referred to in the present invention, it is used for descriptive purposes only and is not to be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include at least one such feature. In addition, technical solutions between various embodiments may be combined with each other, but must be realized by a person skilled in the art, and when the technical solutions are contradictory or cannot be realized, such a combination should not be considered to exist, and is not within the protection scope of the present invention.
Referring to fig. 1, an air conditioning system provided by the present invention includes: the double-cylinder independent compression type air conditioner comprises a double-cylinder independent compression compressor 1, a reversing unit 2, an outdoor heat exchanger 3, a first electronic expansion valve 4, a gas-liquid separator 5, a second electronic expansion valve 6 and an indoor heat exchanger 7 which are sequentially communicated and form a refrigerant loop. The compressor 1 comprises a shell, a first cylinder 11 and a second cylinder 12 are arranged in the shell, and a first liquid storage tank 13 and a second liquid storage tank 14 are arranged outside the shell. The shell of the compressor 1 is also provided with an exhaust port communicated with the reversing unit 2, a first return air port communicated with the suction port of the first cylinder 11, and a second return air port communicated with the suction port of the second cylinder 12. One end of the first liquid storage tank 13 is communicated with the reversing unit 2, and the other end of the first liquid storage tank is communicated with the first air return port; one end of the second liquid storage tank 14 is communicated with a gas outlet of the gas-liquid separator 5, and the other end is communicated with a second air return port. It will be appreciated that the second reservoir 14 may also be omitted. The second reservoir tank 14 is connected to the second return air port to further improve the stability of the air conditioning system.
In the air conditioner, compressed refrigerants discharged from the first cylinder 11 and compressed refrigerants discharged from the second cylinder 12 are respectively discharged into the shell 1 and then discharged from the exhaust port through independent compression of the first cylinder 11 and the second cylinder 12. In addition, the gas outlet of the gas-liquid separator 5 is directly communicated with the return air inlet of the compressor 1, after the refrigerant passing through the first electronic expansion valve 4 passes through the gas-liquid separator 5, the gaseous refrigerant passes through the gas outlet of the gas-liquid separator 5 and is circularly compressed in the second cylinder 12 of the compressor, so that the compression power consumption is reduced, and the energy efficiency is improved.
Specifically, the value of the ratio of the exhaust volumes of the second cylinder 12 to the first cylinder 11 ranges from 1% to 10%. Further, the range of the ratio of the exhaust volumes of the second cylinder 12 and the first cylinder 11 is 1% to 9%, and preferably, the range of the ratio of the exhaust volumes of the second cylinder 12 and the first cylinder 11 is 4% to 9%. For example, the ratio of the exhaust volumes of the second cylinder 12 and the first cylinder 11 may be 4%, 5%, 8%, or 8.5%.
The reversing unit 2 is preferably a four-way valve, and is communicated with the first return air port through the first liquid storage tank 13, the reversing unit 2 includes a first valve port D to a fourth valve port S, the first valve port D is communicated with one of the second valve port C and the third valve port E, the fourth valve port S is communicated with the other of the second valve port C and the third valve port E, the first valve port D is connected with an air outlet of the compressor 1, and the fourth valve port S is connected with the first liquid storage tank 13. The first end of the outdoor heat exchanger 3 is connected with the second valve port C, and the first end of the indoor heat exchanger 4 is connected with the third valve port E. Specifically, when the cooling and heating type air conditioner 100 cools, the first port D communicates with the second port C and the third port E communicates with the fourth port S, and when the air conditioning system heats, the first port D communicates with the third port E and the second port C communicates with the fourth port S.
The gas-liquid separator 5 comprises a gas outlet, a first interface and a second interface, the gas outlet is connected with the second return air port, the first interface is connected with the second end of the outdoor heat exchanger 3, the second interface is connected with the second end of the indoor heat exchanger 7, a first electronic expansion valve 4 is connected between the first interface and the outdoor heat exchanger 3 in series, and a second electronic expansion valve 6 is connected between the second interface and the indoor heat exchanger 7 in series.
The air conditioning system also comprises a controller, wherein the controller can be an independently arranged functional component or a control panel arranged together with the control functional components of other components in the air conditioning system. Specifically, the controller is configured to: determining the opening degree K11 of the first electronic expansion valve 4 and the opening degree K21 of the second electronic expansion valve 6 according to the operation parameters of the air conditioning system; during the operation of the air conditioning system, the opening K21 of the second electronic expansion valve is adjusted according to the target exhaust temperature or the return air superheat degree of the compressor, and when the opening K21 of the second electronic expansion valve reaches the maximum opening value or the minimum opening value of the electronic expansion valve and the target exhaust temperature or the return air superheat degree of the compressor cannot be reached yet, the opening K11 of the first electronic expansion valve is adjusted.
The first electronic expansion valve 4 and the second electronic expansion valve 6 are adjustable throttle valves, and the purpose of adjusting pressure and flow is achieved by changing the sectional area of a valve passage. For example, when the opening range of the electronic expansion valve is [0, 450], that is, the opening of the electronic expansion valve is 0, the throttle valve is completely closed, and the refrigerant is not allowed to pass through; when the opening degree of the electronic expansion valve is 450, the throttle valve is fully opened, and all the refrigerant passes through the throttle valve.
In the embodiment of the invention, the first-stage throttling depressurization and the second-stage throttling depressurization are realized by controlling the first electronic expansion valve and the second electronic expansion valve, and simultaneously, after the refrigerant subjected to the first-stage throttling depressurization is subjected to gas-liquid separation, the gas refrigerant is circulated to the second cylinder 12 of the compressor for cyclic compression, so that the gas content in the refrigerant flowing into the indoor heat exchanger 7 during refrigeration is reduced, the gas content in the refrigerant flowing into the outdoor heat exchanger 3 during heating is reduced, and the influence of the gas refrigerant on the heat exchange performance of the indoor heat exchanger 7 or the outdoor heat exchanger 3 serving as an evaporator is reduced, thereby improving the heat exchange efficiency and reducing the compression power consumption of the compressor.
It can be understood that, because the refrigerant circulation loop in the heating mode of the air-conditioning system is exactly opposite to the refrigerant circulation loop in the cooling mode of the air-conditioning system, namely, when the air-conditioning system operates in the cooling mode, the first electronic expansion valve 4 has a primary throttling and pressure reducing function, and the second electronic expansion valve 6 has a secondary throttling and pressure reducing function; when the air conditioning system operates in a heating mode, the second electronic expansion valve 6 has a first-stage throttling and pressure reducing effect, and the first electronic expansion valve 4 has a second-stage throttling and pressure reducing effect. Therefore, in the present invention, the control principle of the first electronic expansion valve 4 and the second electronic expansion valve 6 when the air conditioning system operates in the cooling mode is substantially the same as the control principle of the second electronic expansion valve 6 and the first electronic expansion valve 4 when the air conditioning system operates in the heating mode, so the following embodiment only describes the throttling control of the electronic expansion valves in the cooling mode of the air conditioning system.
In this embodiment, the opening degree K11 of the first electronic expansion valve 4 and the opening degree K21 of the second electronic expansion valve 6 will be determined separately according to the operating parameters of the air conditioning system. Specifically, the method comprises the following steps:
when the air-conditioning system operates in a refrigeration mode, the opening K11 of the first electronic expansion valve is determined according to the operating frequency of a compressor of the air-conditioning system and the operating temperature of the air-conditioning system, and in order to ensure that the refrigeration system enters an optimal intermediate pressure state of gas-liquid separation after being subjected to throttling regulation by the first electronic expansion valve.
In this embodiment, the air conditioner operating temperature may include a discharge temperature of the compressor, an outdoor ambient temperature, and a gas-liquid separator inlet temperature. The operation frequency of the compressor can be read from a main control panel of the air conditioning system, the exhaust temperature of the compressor can be obtained through a temperature sensor arranged at an exhaust port of the compressor, the outdoor environment temperature can be obtained through a temperature sensor arranged on an outdoor unit, and the inlet temperature of the gas-liquid separator can be obtained through a temperature sensor arranged on an inlet pipe of the gas-liquid separator. In addition, the operation frequency of the compressor may include a current operation frequency or a frequency variation value of the compressor. For example, the operation frequency of the compressor is periodically read from a main control board of the air conditioning system, and then the difference value of the operation frequencies of the two adjacent compressors is calculated to obtain the frequency variation value. The operating temperature may also include a current temperature value or a temperature change value.
In the embodiment of the invention, at least one group of weight coefficients are preset in the air conditioning system in advance, when the opening degree needs to be calculated, the weight coefficients are read from the pre-stored position of the air conditioning system, and then weighted summation is carried out according to the operating parameters of the air conditioning system, so as to obtain the opening degree K11 of the first electronic expansion valve. For example, the opening K11 of the first electronic expansion valve is a11 × frequency + B11 × ambient temperature + C11 × discharge temperature + D11 × gas-liquid separator inlet temperature. A11, B11, C11 and D11 are fixed weight coefficients prestored in the air conditioning system, and multiple groups of weight coefficients can be set to be correspondingly set according to different operating conditions. It will be understood that the parameters used for calculating the opening degree of the first electronic expansion valve may also be several of the four mentioned above, although the opening degree of the first electronic expansion valve calculated on the basis of the four mentioned parameters is more accurate.
In the air conditioning system operating in the heating mode, the determination process of the opening K21 of the second electronic expansion valve may refer to the determination process of the opening K11 of the first electronic expansion valve, and will not be described herein again.
Further, the controller is further configured to: and when the air conditioning system operates in a refrigeration mode, determining the opening K21 of the second electronic expansion valve according to the exhaust temperature or the return air superheat degree of the compressor, and entering an evaporator in an optimal dryness state after the refrigeration system is subjected to throttling regulation by the second electronic expansion valve to improve the evaporation heat exchange capacity.
Specifically, when the air conditioning system operates in the cooling mode, the opening degree K21 of the second electronic expansion valve 6 is determined according to the discharge temperature or the return air superheat degree of the compressor. The exhaust temperature of the compressor is obtained by detecting a temperature sensor arranged at an exhaust port of the compressor, the return air superheat degree of the compressor is the difference value between the return air temperature of the compressor and the evaporation temperature, and when the air conditioning system operates in a refrigeration mode, the return air superheat degree is the difference value between the return air temperature of the compressor and the evaporation temperature of the indoor heat exchanger. The return air temperature is obtained by detecting a temperature sensor arranged at an air return port of the compressor, and the evaporation temperature is obtained by detecting a temperature sensor arranged at the indoor heat exchanger. In this embodiment, a mapping relationship between the exhaust gas temperature and the degree of superheat of the returned gas, respectively, and the opening degree of the electronic expansion valve may be set in advance, and when the exhaust gas temperature or the degree of superheat of the returned gas is obtained, the opening degree K21 of the second electronic expansion valve may be obtained based on the mapping relationship.
In another example, the opening degree K21 of the second electronic expansion valve 6 may also be determined according to the opening degree K11 of the first electronic expansion valve 4 and a preset difference value or a preset proportional value, so as to determine the opening degree K21 of the second electronic expansion valve. For example, in the embodiment, the opening degree of one electronic expansion valve is determined according to the air conditioner operation parameters, and then the opening degree of the other electronic expansion valve is determined according to the preset difference value or the preset proportional value, so that the opening degrees of the two electronic expansion valves are not required to be calculated respectively, and therefore, the electronic expansion valves can be adjusted quickly, and the control operation is simple. Specifically, the preset difference value has a value range of [0,200], and the preset ratio value has a value range of [0.1,10 ]. The preset difference value and the preset proportion value are set to be values which ensure that the compressor does not return liquid when the air conditioning system is actually operated under different working conditions, and the system is ensured to operate stably and reliably.
In the air conditioning system operating in the heating mode, the determination process of the opening K11 of the first electronic expansion valve may refer to the determination process of the opening K21 of the second electronic expansion valve, and will not be described herein again.
Further, during the operation of the air conditioning system, the opening degree of the second electronic expansion valve 6 is also adjusted according to the target exhaust temperature or the return air superheat degree of the compressor, so that the current exhaust temperature of the compressor reaches the target exhaust temperature or the current compressor reaches the preset return air superheat degree through the adjustment of the opening degree of the second electronic expansion valve 6.
Specifically, the current discharge temperature of the compressor is compared with the target discharge temperature, and the opening degree of the second electronic expansion valve 6 is adjusted according to the comparison result. That is, when the current exhaust temperature is lower than the target exhaust temperature, the opening degree of the second electronic expansion valve 6 is decreased, and when the current exhaust temperature is higher than the target exhaust temperature, the opening degree of the second electronic expansion valve 6 is increased. Or comparing the current return air superheat degree of the compressor with a preset return air superheat degree, and adjusting the opening degree of the second electronic expansion valve 6 according to the comparison result. That is, when the current return air superheat degree is less than the preset return air superheat degree, the opening degree of the second electronic expansion valve 6 is reduced, and when the current return air superheat degree is greater than the preset return air superheat degree, the opening degree of the second electronic expansion valve 6 is increased, so that the air conditioning system is ensured to work in the optimal circulation state, and the energy efficiency is improved.
And when the opening degree of the second electronic expansion valve reaches the maximum opening degree or the minimum opening degree of the electronic expansion valve and the target exhaust temperature or the return air superheat degree of the compressor cannot be reached, controlling the opening degree K11 of the first electronic expansion valve to be adjusted within the range of [ K11-delta K, K11+ delta K ].
When the opening degree of the second electronic expansion valve 6 is adjusted, if the opening degree of the second electronic expansion valve has reached the maximum opening degree value or the minimum opening degree value of the electronic expansion valve and the target exhaust gas temperature or the return air superheat degree of the compressor still cannot be reached at this time, it means that the air conditioner operation requirement cannot be met through the adjustment of the second electronic expansion valve 6. Therefore, the opening degree K11 of the first electronic expansion valve 4 will be adjusted. Further, in order to ensure excessive adjustment of the opening degree of the first electronic expansion valve 4, in the present embodiment, an adjustment range, i.e., [ K11- Δ K, K11+ Δ K ] will be set. The value range of the delta K is [0,0.1K ], wherein K is the maximum opening value of the electronic expansion valve.
In the throttling control of the air conditioning system, the opening degree of a first electronic expansion valve and the opening degree of a second electronic expansion valve are determined according to air conditioning operation parameters, then the opening degree of the second electronic expansion valve is adjusted according to the target exhaust temperature or the return air superheat degree of a compressor, and the opening degree of the first electronic expansion valve is adjusted when the second electronic expansion valve is adjusted to the maximum opening degree or the minimum opening degree and still cannot reach the target exhaust temperature or the return air superheat degree of the compressor. Therefore, the air conditioning system controls the adjustment of the second electronic expansion valve through the exhaust or return air parameters of the compressor, so that the air conditioning system can quickly meet the operation requirement; in addition, when the operation requirement cannot be met after the second electronic expansion valve is adjusted, the first electronic expansion valve is adjusted again to ensure the operation energy efficiency of the air-conditioning system.
Correspondingly, the invention further provides a control method of the air conditioning system. As shown in fig. 2, the control method of the air conditioning system includes the steps of:
step S110, acquiring operation parameters of an air conditioning system in the air conditioning operation process;
the operating parameters of the air conditioning system may include an operating frequency of the compressor, an operating temperature of the air conditioning system, wherein the operating temperature may include a discharge temperature of the compressor, an outdoor ambient temperature, and a gas-liquid separator inlet temperature. The operation frequency of the compressor can be read from a main control panel of the air conditioning system, the exhaust temperature of the compressor can be obtained through a temperature sensor arranged at an exhaust port of the compressor, the outdoor environment temperature can be obtained through a temperature sensor arranged on an outdoor unit, and the inlet temperature of the gas-liquid separator can be obtained through a temperature sensor arranged on an inlet pipe of the gas-liquid separator. In addition, the operation frequency of the compressor may include a current operation frequency or a frequency variation value of the compressor. For example, the operation frequency of the compressor is periodically read from a main control board of the air conditioning system, and then the difference value of the operation frequencies of the two adjacent compressors is calculated to obtain the frequency variation value. The operating temperature may also include a current temperature value or a temperature change value.
Step S120, determining the opening K11 of the first electronic expansion valve and the opening K21 of the second electronic expansion valve according to the operation parameters of the air conditioning system;
according to the operating parameters of the air conditioning system and the preset operation rules, the opening degree K11 of the first electronic expansion valve 4 and the opening degree K21 of the second electronic expansion valve 6 can be determined.
Step S130, during the operation of the air conditioning system, adjusting the opening K21 of the second electronic expansion valve according to the target exhaust temperature or the return air superheat degree of the compressor;
specifically, the current discharge temperature of the compressor is compared with the target discharge temperature, and the opening degree of the second electronic expansion valve 6 is adjusted according to the comparison result. That is, when the current exhaust temperature is lower than the target exhaust temperature, the opening degree of the second electronic expansion valve 6 is decreased, and when the current exhaust temperature is higher than the target exhaust temperature, the opening degree of the second electronic expansion valve 6 is increased. Or comparing the current return air superheat degree of the compressor with a preset return air superheat degree, and adjusting the opening degree of the second electronic expansion valve 6 according to the comparison result. That is, when the current return air superheat degree is less than the preset return air superheat degree, the opening degree of the second electronic expansion valve 6 is reduced, and when the current return air superheat degree is greater than the preset return air superheat degree, the opening degree of the second electronic expansion valve 6 is increased, so that the air conditioning system is ensured to work in the optimal circulation state, and the energy efficiency is improved.
And step S140, when the opening K21 of the second electronic expansion valve reaches the maximum opening of the electronic expansion valve and the target exhaust temperature of the compressor or the superheat degree of return air cannot be reached, adjusting the opening K11 of the first electronic expansion valve.
And when the opening degree of the second electronic expansion valve reaches the maximum opening degree or the minimum opening degree of the electronic expansion valve and the target exhaust temperature or the return air superheat degree of the compressor cannot be reached, controlling the opening degree K11 of the first electronic expansion valve to be adjusted within the range of [ K11-delta K, K11+ delta K ].
When the opening degree of the second electronic expansion valve 6 is adjusted, if the opening degree of the second electronic expansion valve has reached the maximum opening degree value or the minimum opening degree value of the electronic expansion valve and the target exhaust gas temperature or the return air superheat degree of the compressor still cannot be reached at this time, it means that the air conditioner operation requirement cannot be met through the adjustment of the second electronic expansion valve 6. Therefore, the opening degree K11 of the first electronic expansion valve 4 will be adjusted. Further, in order to ensure excessive adjustment of the opening degree of the first electronic expansion valve 4, in the present embodiment, an adjustment range, i.e., [ K11- Δ K, K11+ Δ K ] will be set. The value range of the delta K is [0,0.1K ], wherein K is the maximum opening value of the electronic expansion valve.
In the throttling control of the air conditioning system, the opening degree of a first electronic expansion valve and the opening degree of a second electronic expansion valve are determined according to air conditioning operation parameters, then the opening degree of the second electronic expansion valve is adjusted according to the target exhaust temperature or the return air superheat degree of a compressor, and the opening degree of the first electronic expansion valve is adjusted when the second electronic expansion valve is adjusted to the maximum opening degree or the minimum opening degree and still cannot reach the target exhaust temperature or the return air superheat degree of the compressor. Therefore, the air conditioning system controls the adjustment of the second electronic expansion valve through the exhaust or return air parameters of the compressor, so that the air conditioning system can quickly meet the operation requirement; in addition, when the operation requirement cannot be met after the second electronic expansion valve is adjusted, the first electronic expansion valve is adjusted again to ensure the operation energy efficiency of the air-conditioning system.
Further, the determining the opening K11 of the first electronic expansion valve in step S120 may specifically include: and when the air conditioning system operates in a refrigeration mode, determining the opening K11 of the first electronic expansion valve according to the operating frequency of a compressor of the air conditioning system and the operating temperature of the air conditioner.
In the embodiment of the invention, at least one group of weight coefficients are preset in the air conditioning system in advance, when the opening degree needs to be calculated, the weight coefficients are read from the pre-stored position of the air conditioning system, and then weighted summation is carried out according to the operating parameters of the air conditioning system, so as to obtain the opening degree K11 of the first electronic expansion valve. For example, the opening K11 of the first electronic expansion valve is a11 × frequency + B11 × ambient temperature + C11 × discharge temperature + D11 × gas-liquid separator inlet temperature. A11, B11, C11 and D11 are fixed weight coefficients prestored in the air conditioning system, and multiple groups of weight coefficients can be set to be correspondingly set according to different operating conditions. It is understood that if the parameters used for calculating the opening degree of the first electronic expansion valve are also several of the four parameters, the opening degree of the first electronic expansion valve calculated according to the 4 parameters is more accurate.
Further, the determining the opening K21 of the second electronic expansion valve in step S120 may specifically include: and determining the opening K21 of the second electronic expansion valve according to the exhaust temperature or the return air superheat degree of the compressor, and entering an evaporator in an optimal dryness state to improve the evaporation heat exchange capacity after the refrigeration system enters the second electronic expansion valve for throttling regulation.
In the present embodiment, the opening degree K21 of the second electronic expansion valve 6 is determined based on the discharge temperature of the compressor or the degree of superheat of the return air. The exhaust temperature of the compressor is obtained by detecting a temperature sensor arranged at an exhaust port of the compressor, the return air superheat degree of the compressor is the difference value between the return air temperature of the compressor and the evaporation temperature, and when the air conditioning system operates in a refrigeration mode, the return air superheat degree is the difference value between the return air temperature of the compressor and the evaporation temperature of the indoor heat exchanger. The return air temperature is obtained by detecting a temperature sensor arranged at an air return port of the compressor, and the evaporation temperature is obtained by detecting a temperature sensor arranged at the indoor heat exchanger. In this embodiment, a mapping relationship between the exhaust gas temperature and the degree of superheat of the returned gas, respectively, and the opening degree of the electronic expansion valve may be set in advance, and when the exhaust gas temperature or the degree of superheat of the returned gas is obtained, the opening degree K21 of the second electronic expansion valve 6 may be obtained from the mapping relationship.
In another example, the opening degree K21 of the second electronic expansion valve may be determined according to the opening degree K11 of the first electronic expansion valve and a preset difference value or a preset proportional value. Specifically, the value range of the preset difference is [0,200], and the value range of the preset proportional value is [0.1,10 ]. In the embodiment, the opening degree of one electronic expansion valve is determined according to the air conditioner operation parameters, and then the opening degree of the other electronic expansion valve is determined according to the preset difference value, so that the opening degrees of the two electronic expansion valves are not required to be calculated respectively, the electronic expansion valves can be quickly adjusted, and the control operation is simple.
Further, the adjusting the opening K11 of the first electronic expansion valve in step S140 may specifically be: the opening degree K11 of the first electronic expansion valve is controlled to be adjusted within the range of [ K11-delta K, K11+ delta K ].
When the opening degree of the second electronic expansion valve 6 is adjusted, the maximum opening degree or the minimum opening degree of the electronic expansion valve is reached, and at this time, the target exhaust temperature or the return air superheat degree of the compressor cannot be reached, that is, the adjustment of the second electronic expansion valve 6 cannot meet the air conditioner operation requirement. Therefore, the opening degree K11 of the first electronic expansion valve 4 will be adjusted. Further, in order to ensure excessive adjustment of the opening degree of the first electronic expansion valve 4, in the present embodiment, an adjustment range, i.e., [ K11- Δ K, K11+ Δ K ] will be set. The value range of the delta K is [0,0.1K ], wherein K is the maximum opening value of the electronic expansion valve.
The above description is only a preferred embodiment of the present invention, and is not intended to limit the scope of the present invention, and all modifications and equivalents of the present invention, which are made by the contents of the present specification and the accompanying drawings, or directly/indirectly applied to other related technical fields, are included in the scope of the present invention.
Claims (10)
1. An air conditioning system comprises a double-cylinder independently-compressed compressor, a reversing unit, an outdoor heat exchanger, a first electronic expansion valve, a gas-liquid separator, a second electronic expansion valve and an indoor heat exchanger which are sequentially connected and form a refrigerant circulation loop; the air conditioning system is characterized by further comprising a controller, wherein the controller determines the opening K11 of the first electronic expansion valve and the opening K21 of the second electronic expansion valve according to the operation parameters of the air conditioning system; during the operation of the air conditioning system, the opening K21 of the second electronic expansion valve is adjusted according to the target exhaust temperature or the return air superheat degree of the compressor, and when the opening K21 of the second electronic expansion valve reaches the maximum opening value or the minimum opening value of the electronic expansion valve and the target exhaust temperature or the return air superheat degree of the compressor cannot be reached yet, the opening K11 of the first electronic expansion valve is adjusted.
2. The air conditioning system of claim 1, wherein the controller is to: and when the air conditioning system operates in a refrigeration mode, determining the opening K11 of the first electronic expansion valve according to the operating frequency of a compressor of the air conditioning system and the operating temperature of the air conditioner.
3. The air conditioning system as claimed in claim 2, wherein the operation frequency of the compressor includes a current operation frequency or a frequency variation value of the compressor; the operating temperature includes a current temperature value or a temperature change value.
4. The air conditioning system of claim 2, wherein the controller is to: and determining the opening K21 of the second electronic expansion valve according to the exhaust temperature or the return air superheat degree of the compressor.
5. The air conditioning system of claim 2, wherein the controller is to: and determining the opening degree K21 of the second electronic expansion valve according to the opening degree K11 of the first electronic expansion valve and a preset difference value or a preset proportion value.
6. The air conditioning system of claim 5, wherein the controller is to: and when the opening degree of the second electronic expansion valve reaches the maximum opening degree or the minimum opening degree of the electronic expansion valve and the target exhaust temperature or the return air superheat degree of the compressor cannot be reached, controlling the opening degree K11 of the first electronic expansion valve to be adjusted within the range of [ K11-delta K, K11+ delta K ].
7. The air conditioning system of claim 1, wherein Δ K is in the range of [0,0.1K ], where K is the electronic expansion valve maximum opening value.
8. A control method of an air conditioning system is characterized by comprising the following steps:
acquiring operation parameters of an air conditioning system in the operation process of the air conditioner;
determining the opening degree K11 of the first electronic expansion valve and the opening degree K21 of the second electronic expansion valve according to the operation parameters of the air conditioning system;
during the operation of the air conditioning system, the opening K21 of the second electronic expansion valve is adjusted according to the target exhaust temperature or the return air superheat degree of the compressor;
when the opening degree K21 of the second electronic expansion valve reaches the maximum opening degree of the electronic expansion valve and the target exhaust temperature of the compressor or the superheat degree of return air cannot be reached, the opening degree K11 of the first electronic expansion valve is adjusted.
9. The control method of an air conditioning system as claimed in claim 8, wherein the step of determining the opening degree K11 of the first electronic expansion valve according to the operation parameters of the air conditioning system comprises:
and when the air conditioning system operates in a refrigeration mode, determining the opening K11 of the first electronic expansion valve according to the operating frequency of a compressor of the air conditioning system and the operating temperature of the air conditioner.
10. The control method of an air conditioning system as claimed in claim 9, wherein the step of determining the opening degree K21 of the second electronic expansion valve according to the operation parameters of the air conditioning system comprises:
determining the opening K21 of the second electronic expansion valve according to the exhaust temperature or the return air superheat degree of the compressor; or,
and determining the opening degree K21 of the second electronic expansion valve according to the opening degree K11 of the first electronic expansion valve and a preset difference value or a preset proportion value.
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| CN111208766A (en) * | 2020-02-18 | 2020-05-29 | 广东智科电子股份有限公司 | Control device of heat pump dryer |
| CN111397104A (en) * | 2020-03-24 | 2020-07-10 | 珠海格力电器股份有限公司 | Control method and device of air conditioning system, control equipment, medium and air conditioning system |
| CN111829173A (en) * | 2019-04-23 | 2020-10-27 | 杭州先途电子有限公司 | Control method and system and air source heat pump air heater |
| CN113108439A (en) * | 2021-05-20 | 2021-07-13 | 广东美的制冷设备有限公司 | Control method and device of air conditioner, air conditioner and storage medium |
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