CN112050299B - Air conditioner - Google Patents

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Publication number
CN112050299B
CN112050299B CN202010942177.9A CN202010942177A CN112050299B CN 112050299 B CN112050299 B CN 112050299B CN 202010942177 A CN202010942177 A CN 202010942177A CN 112050299 B CN112050299 B CN 112050299B
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Prior art keywords
refrigerant
air conditioner
temperature
preset value
compressor
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CN202010942177.9A
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CN112050299A (en
Inventor
高岭
顾晓宇
林文涛
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Qingdao Hisense Hitachi Air Conditioning System Co Ltd
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Qingdao Hisense Hitachi Air Conditioning System Co Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/0007—Indoor units, e.g. fan coil units
    • F24F1/0068—Indoor units, e.g. fan coil units characterised by the arrangement of refrigerant piping outside the heat exchanger within the unit casing
    • 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
    • F24F11/62—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
    • F24F11/65—Electronic processing for selecting an operating mode
    • 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
    • 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
    • F24F2110/10—Temperature
    • 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
    • F24F2110/10—Temperature
    • F24F2110/12—Temperature of the outside air
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F2140/00—Control inputs relating to system states
    • F24F2140/10—Pressure
    • F24F2140/12—Heat-exchange fluid pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F2140/00—Control inputs relating to system states
    • F24F2140/20—Heat-exchange fluid temperature

Abstract

The invention discloses an air conditioner, comprising: a control unit configured to: when the air conditioner is in a refrigeration operation mode, the refrigerant quantity is determined by at least one of the following modes: a, determining the saturation temperature Tc, Te and Pd of refrigerant gas corresponding to the discharge pressure Pd of the compressor; b, determining k, Tc, Te and Td, wherein k is related to the opening of an electronic expansion valve of the indoor unit, the refrigerant gas saturation pressure corresponding to the temperature Tchg of a liquid side stop valve of the outdoor unit, the suction pressure of the compressor and the running frequency of the compressor; c: determined according to Tc, Tchg and k; and the low refrigerant quantity is determined by at least one of the following modes: a' is determined at least based on Td and Tc; b' is determined according to k, Tc and Tchg. The invention judges the refrigerant quantity in real time through the operation parameters of the air conditioner, and avoids the influence of too much or too little refrigerant on the reliability of the system.

Description

Air conditioner
Technical Field
The invention belongs to the technical field of air conditioners, and particularly relates to an air conditioner.
Background
The multi-split air conditioner is widely applied to various large-scale office buildings, hospitals, villas and the like, and particularly relates to a one-split large-scale multi-split air conditioner which comprises at least one indoor unit and at least one outdoor unit module connected with the indoor units through refrigerant connecting pipelines, and can provide refrigeration or heating for the indoor units simultaneously, so that the known refrigeration and heating requirements of various large-scale occasions are met.
In a multi-split system, particularly a large multi-split system, the number of indoor units is large, the pipeline connection is complex, the pipeline length is long, and the amount of refrigerant to be filled in the system is large. Due to the fact that the system pipelines are complex, the number of indoor units is large, and the number of refrigerant in the system is too large or too small due to the fact that human errors are calculated possibly, the number of welded junctions of the multi-split air conditioner system is generally large, and the difference of engineering installation quality is large. If the pressure maintaining time of the system is not long enough, refrigerant is filled, and the like, micro leakage can occur when the system is started, or the refrigerant leakage phenomenon occurs after the system is operated for a period of time and the refrigerant is insufficient.
When the amount of refrigerant in the system is large, the liquid return of the system can be caused seriously to cause liquid compression, or the system pressure is too high, and high-pressure protection shutdown occurs; when the amount of refrigerant in the system is small, the indoor unit may lack refrigerant, the capacity of the indoor unit is insufficient, and the requirement of a user for cooling and heating cannot be met, and the superheat degree may be large, which may lead to high-temperature exhaust protection or low-pressure over-low protection. Therefore, it is important in engineering practice to determine the amount of the system refrigerant.
In the related art, the amount of the system refrigerant is mainly determined by the discharge of the compressor, the discharge superheat degree of the compressor, the high pressure and low pressure of the system, the return superheat degree of the compressor, and the like, but in a complicated use environment, erroneous determination may occur.
Disclosure of Invention
The embodiment of the invention provides an air conditioner, which judges the amount of a refrigerant in real time according to the operation parameters of the air conditioner, and avoids the influence of too much or too little refrigerant on the reliability of a system.
In order to realize the purpose of the invention, the invention is realized by adopting the following technical scheme:
the present application relates to an air conditioner, comprising: the outdoor unit and at least one indoor unit connected through a refrigerant pipeline; it is characterized in that the preparation method is characterized in that,
the air conditioner further includes:
a control unit configured to:
when the air conditioner is in a refrigeration operation mode, the refrigerant quantity is determined by at least one of the following modes:
a, determining the saturation temperature Tc of refrigerant gas, the temperature Te of the heat exchange liquid side of the outdoor unit and Pd according to the discharge pressure Pd of the compressor;
b, determining according to first parameters k, Tc and Te and the exhaust temperature Td of the compressor, wherein k is related to the opening Evi of an electronic expansion valve of the indoor unit in the starting state, the refrigerant gas saturation pressure P1 corresponding to the temperature Tchg of a liquid side stop valve of the outdoor unit, the suction pressure Ps of the compressor and the operation frequency Ft of the compressor;
c: determining according to Tc, Tchg and the first parameter;
when the air conditioner is in a refrigeration operation mode, the low refrigerant quantity is determined by at least one of the following modes:
a' is determined by at least Td and Tc;
b' is determined according to k, Tc and Tchg.
In some embodiments of the present application, the a mode is specifically configured to: calculating the difference Δ T1 between Tc and Te; if the delta T1 is not less than the first preset value and Pd is more than the second preset value, the refrigerant quantity is determined to be high.
In some embodiments of the present application, the first parameter k is calculated using the following formula:
Figure DEST_PATH_IMAGE001
and n is the number of the indoor units.
In some embodiments of the present application, the B mode is specifically configured to: calculating the difference Δ T1 between Tc and Te and the difference Δ T2 between Td and Tc; and if the delta T1 is not less than the third preset value, the delta T2 is less than the fourth preset value, and k is less than the fifth preset value, judging that the refrigerant quantity is high.
In some embodiments of the present application, the mode C is specifically configured to: calculating the difference Δ T3 between Tc and Tchg; and if the delta T3 is larger than the sixth preset value and k is smaller than the seventh preset value, judging that the refrigerant quantity is high.
In some embodiments of the present application, the a' mode is specifically configured to: and calculating the difference delta T4 between Td and Tc, and if delta T4 is larger than an eighth preset value, determining that the refrigerant quantity is low.
In some embodiments of the present application, the a' mode is specifically configured to: and the temperature is determined according to Td, Tc and Te and the temperature Tchg of the outdoor unit liquid side stop valve.
In some embodiments of the present application, the a' mode is further specifically configured to: calculating the difference Δ T4 between Td and Tc; calculating the difference Δ T1 between Tc and Te and the difference Δ T5 between Te and Tchg; and if the delta T4 is larger than the ninth preset value, the delta T1 is smaller than the tenth preset value, and the delta T5 is larger than the eleventh preset value, the refrigerant quantity is judged to be low.
In some embodiments of the present application, the B' mode is specifically configured to: the first parameter k is calculated using the following formula:
Figure 748451DEST_PATH_IMAGE002
wherein n is the number of the indoor units; calculating the difference Δ T6 between Tc and Tchg; if delta T6 is larger than the twelfth preset value and k is larger than the thirteenth preset value, the refrigerant quantity is judged to be low.
According to the air conditioner provided by the invention, when the air conditioner is in a refrigeration running mode, the running parameters of the air conditioner in the running process are collected, whether the refrigerant quantity in the air conditioner is in a proper range is accurately judged in real time according to the collected running parameters, and the influence of the high or low refrigerant quantity on the reliability of the air conditioner is avoided.
Other features and advantages of the present invention will become more apparent from the following detailed description of the invention when taken in conjunction with the accompanying drawings.
Drawings
In order to more clearly illustrate the technical solutions in the embodiments of the present invention, the drawings needed to be used in the embodiments are briefly introduced below, and it is obvious that the drawings in the following description are some embodiments of the present invention, and it is obvious for those skilled in the art to obtain other drawings based on these drawings without creative efforts.
Fig. 1 is a block diagram of an embodiment of an air conditioner proposed by the present invention;
FIG. 2 is a flow chart of determining the refrigerant quantity in the embodiment of the air conditioner according to the present invention;
fig. 3 is a flowchart illustrating a low refrigerant quantity determination process in an embodiment of an air conditioner according to the present invention.
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. In the description of the present invention, it is to be understood that the terms "center", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", and the like indicate orientations or positional relationships based on those shown in the drawings, and are only for convenience of description and simplicity of description, and do not indicate or imply that the referenced devices or elements must have a particular orientation, be constructed and operated in a particular orientation, and thus, are not to be construed as limiting the present invention.
In the description of the present invention, it should be noted that the terms "mounted," "connected," and "connected" are to be construed broadly and may be, for example, fixedly connected, detachably connected, or integrally connected unless otherwise explicitly stated or limited. The specific meanings of the above terms in the present invention can be understood in specific cases to those skilled in the art. In the foregoing description of embodiments, the particular features, structures, materials, or characteristics may be combined in any suitable manner in any one or more embodiments or examples.
The terms "first", "second" and "first" are used for descriptive purposes only and are 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 one or more of that feature. In the description of the present invention, "a plurality" means two or more unless otherwise specified.
[ basic operation principle of air conditioner ]
A refrigeration cycle of an air conditioner includes a compressor, a condenser, an expansion valve, and an evaporator. The refrigeration cycle includes a series of processes involving compression, condensation, expansion, and evaporation, and supplies refrigerant to the air that has been conditioned and heat-exchanged.
The compressor compresses a refrigerant gas in a high-temperature and high-pressure state and discharges the compressed refrigerant gas. The discharged refrigerant gas flows into the condenser. The condenser condenses the compressed refrigerant into a liquid phase, and heat is released to the surrounding environment through the condensation process.
The expansion valve expands the liquid-phase refrigerant in a high-temperature and high-pressure state condensed in the condenser into a low-pressure liquid-phase refrigerant. The evaporator evaporates the refrigerant expanded in the expansion valve and returns the refrigerant gas in a low-temperature and low-pressure state to the compressor. The evaporator can achieve a cooling effect by heat-exchanging with a material to be cooled using latent heat of evaporation of a refrigerant. The air conditioner can adjust the temperature of the indoor space throughout the cycle.
The outdoor unit of an air conditioner refers to a portion including a compressor of a refrigeration cycle and includes an outdoor heat exchanger, the indoor unit of an air conditioner includes an indoor heat exchanger, and an electronic expansion valve may be provided in the indoor unit or the outdoor unit of an air conditioner.
The indoor heat exchanger and the outdoor heat exchanger serve as a condenser or an evaporator. When the indoor heat exchanger is used as a condenser, the air conditioner is used as a heater in a heating mode, and when the indoor heat exchanger is used as an evaporator, the air conditioner is used as a cooler in a cooling operation mode.
[ air-conditioner ]
The application relates to an air conditioner.
The air conditioner comprises at least one outdoor unit and at least one indoor unit, wherein the outdoor units are arranged in parallel and connected with the indoor units through refrigerant pipelines, and the indoor units are also arranged in parallel.
Each indoor unit includes an indoor heat exchanger (i.e., an indoor heat exchanger as described above) and an indoor fan for blowing cold or hot air generated by the indoor heat exchanger toward an indoor space, respectively.
The outdoor unit comprises a compressor, a four-way valve, a gas side stop valve, a throttling element, a liquid side stop valve, an outdoor heat exchanger and an outdoor fan.
The four-way valve switches the flow path of the refrigerant discharged from the compressor and has four terminals C, D, S and E.
When the four-way valve is powered off, the default C is connected with the default D, and the default S is connected with the default E, so that the heat exchanger of the indoor unit is used as an evaporator, and the air conditioner refrigerates.
When the four-way valve is electrified and reversed, the C is connected with the S, and the D is connected with the E, so that the heat exchanger of the indoor unit is used as a condenser, and the air conditioner heats.
The determination of the amount of refrigerant in the present application is performed when the air conditioner is in the cooling operation mode, and therefore, only the cooling operation mode of the air conditioner of the present application will be described with reference to fig. 1, and the solid arrow indicates the flow direction of the refrigerant in the cooling operation mode.
In fig. 1, one indoor unit is shown by a solid line and two indoor units are shown by a dotted line, and a cooling operation mode of the air conditioner will be described by taking one outdoor unit and one indoor unit as examples.
The four-way valve 2 is powered off, D and C are communicated and E and S are communicated by default, the compressor 1 compresses low-temperature and low-pressure refrigerants into a high-temperature and high-pressure state, the refrigerants discharged by the compressor 1 are throttled by the air pipe throttling device 13 (in the application, an electronic expansion valve) through the D and C and then enter the outdoor heat exchanger 11 (an outdoor fan 12 is arranged at the position of the outdoor heat exchanger 11), the refrigerants are condensed and release heat after heat exchange of the outdoor heat exchanger 11 to become liquid refrigerants, then the refrigerants pass through the liquid pipe throttling device 10 (in the application, the electronic expansion valve), the liquid side stop valve 9 and the liquid side piping 8, enter the indoor machine side throttling element 7 (in the application, the electronic expansion valve) for throttling and then enter the indoor heat exchanger 5 (the indoor heat exchanger 5 is self-provided with the indoor fan 6) for evaporation and heat absorption to become gaseous state, and the refrigerants discharged by the indoor heat exchanger 5 pass through the air side piping 4, The gas side cut-off valve 3 and E and S of the four-way valve 2 enter the gas-liquid separator 14, and are finally sucked into the compressor 1 to be compressed, thereby completing the refrigeration cycle.
S1: the air conditioner performs the cooling operation mode and goes to S2 or S3.
Referring to fig. 1, in the present application, the control unit is configured to determine whether the refrigerant quantity in the refrigerant circulation system is high or low when the air conditioner is in the cooling operation mode.
When the air conditioner is in a cooling operation mode, the indoor heat exchanger is used as an evaporator, and the outdoor heat exchanger is used as a condenser, at the moment, the operation state of the air conditioner is relatively stable, and the air conditioner is suitable for judging the amount of refrigerant filled into an air conditioner system.
When the air conditioner is in a heating operation mode, the indoor heat exchanger is used as a condenser, the outdoor heat exchanger is used as an evaporator, and when the environment temperature is low, the surface of the evaporator is easy to frost, so that the judgment of the refrigerant quantity is inaccurate.
Therefore, during the installation and operation of the air conditioner, the refrigerant quantity is generally determined when the air conditioner is in the cooling operation mode.
In the present application, when each indoor unit is in cooling operation (and the indoor air volume is set to be in sharp-wind operation), the refrigerant after heat exchange from the outdoor heat exchanger sequentially passes through the liquid pipe throttling device and the liquid side stop valve, and reaches an appropriate amount of refrigerant when the refrigerant in the liquid side pipe between the liquid side throttling element and the indoor unit side throttling element reaches a saturated liquid state.
S2: whether the refrigerant amount is high is judged according to at least one of the following modes A/B/C.
A: and determining the pressure according to the refrigerant gas saturation temperature Tc, the outdoor heat-exchange liquid side temperature Te and the compressor discharge pressure Pd corresponding to the compressor discharge pressure Pd.
The compressor discharge pressure Pd can be obtained by the prior art means of additionally installing a pressure gauge or a pressure transmitter and the like at the air outlet of the compressor.
The refrigerant gas saturation temperature Tc is obtained by querying a refrigerant property table according to the compressor discharge pressure Pd, which belongs to the common technology and is not described herein.
The outdoor heat-exchange liquid side temperature Te is the outdoor heat-exchanger liquid side temperature, and can be detected by providing a temperature sensing bulb on a pipeline close to the outdoor heat-exchanger liquid side.
The air conditioner further includes a calculation unit for calculating a difference Δ T1 between the refrigerant gas saturation temperature Tc and the outdoor heat-exchange liquid side temperature Te.
The air conditioner also comprises a comparison unit which judges the refrigerant quantity is high when the delta T1 is more than or equal to a first preset value and Pd is more than a second preset value.
The first preset value is an experimental value obtained during experimental debugging according to the configuration of the current air conditioner, and can be selected to be between 5 and 30 ℃.
The second preset value is the sum of the correction value Pdc obtained from the outdoor ambient temperature and the preset value Tth.
The correction value Pdc is a correction amount determined according to the influence of the outdoor ambient temperature on the discharge pressure of the compressor at the time of experimental debugging, and the preset value Tth is selected to be 0.1MPa in the present application.
B: the temperature control method is characterized by comprising the following steps of determining a first parameter k, a refrigerant gas saturation temperature Tc, an outdoor heat-exchange liquid side temperature Te and a compressor exhaust temperature Td, wherein the first parameter k is related to the opening degree Evi of an electronic expansion valve of an indoor unit in the starting state, the refrigerant gas saturation pressure P1 corresponding to the outdoor unit liquid side stop valve temperature Tchg, the compressor suction pressure Ps and the compressor operation frequency Ft.
The temperature acquisition of the refrigerant gas saturation temperature Tc and the outdoor heat-exchange liquid side temperature Te can be referred to as described above.
The compressor discharge temperature Td, that is, the temperature of the refrigerant in the discharge pipe at the discharge port of the compressor, can be detected by providing a thermal bulb on the pipeline near the discharge port of the compressor.
The opening degree of the electronic expansion valve of the indoor unit, namely the opening degree of the electronic expansion valve of the indoor unit in the starting state in the plurality of indoor units.
The outdoor unit liquid side shutoff valve temperature Tchg is the temperature of the refrigerant entering the liquid side shutoff valve after the refrigerant having exchanged heat from the outdoor heat exchanger has been throttled by the liquid pipe throttling element, and can be detected by providing a temperature sensing bulb on the liquid side piping close to the liquid side shutoff valve.
The refrigerant gas saturation pressure P1 corresponding to the outdoor unit liquid side shutoff valve temperature Tchg can be obtained by looking up the refrigerant physical property table based on the outdoor unit liquid side shutoff valve temperature Tchg.
The suction pressure Ps of the compressor can be obtained by the means of the prior art such as additionally installing a pressure gauge or a pressure transmitter at the suction port of the compressor.
The air conditioner further comprises a calculating unit, and the calculating unit calculates a first parameter k according to the opening Evi of the electronic expansion valve of the indoor unit in the starting state, the refrigerant gas saturation pressure P1 corresponding to the temperature Tchg of the liquid side stop valve of the outdoor unit, the suction pressure Ps of the compressor and the running frequency Ft of the compressor by using the following formula.
Figure 324926DEST_PATH_IMAGE002
Wherein n is the number of the indoor units,
Figure 100002_DEST_PATH_IMAGE004
the sum of the opening degrees of the electronic expansion valves of all the indoor units, namely the sum of the opening degrees of the electronic expansion valves of the indoor units in the on state (the opening degree of the electronic expansion valve of the indoor unit in the off state is zero) in the plurality of indoor units, k1 is a correction coefficient of the capacity (namely the working efficiency in unit time) of the indoor unit, and the correction coefficient is a fixed value after experimental debugging.
The calculating unit is also used to calculate the difference Δ T1 (as described above) between the refrigerant gas saturation temperature Tc and the outdoor heat-exchange liquid side temperature Te, and the difference Δ T2 between the compressor discharge temperature Td and the refrigerant gas saturation temperature Tc.
The air conditioner also comprises a comparison unit which judges the refrigerant quantity is high when k is less than a third preset value, delta T1 is more than or equal to a fourth preset value, and delta T2 is less than a fifth preset value.
The third preset value is an experimental value obtained during experimental debugging according to the configuration of the current air conditioner, and can be selected to be between 5 and 30 ℃.
The fourth preset value is a correction value A obtained according to the outdoor ambient temperature.
The correction value A is a correction value determined according to the influence of outdoor loop temperature on the refrigerant gas saturation temperature Tc and the outdoor heat-exchange liquid side temperature T during experimental debugging, and can be selected to be between 5 and 30 ℃.
The fifth preset value is a correction value B obtained according to the outdoor ambient temperature.
The correction value B is a correction value determined according to the influence of the outdoor environment temperature on the discharge temperature Td of the compressor and the saturation temperature Tc of the refrigerant gas during the experimental debugging, and can be selected to be between 5 and 30 ℃.
C: the temperature of the outdoor unit liquid side stop valve is determined according to the refrigerant gas saturation temperature Tc, the outdoor unit liquid side stop valve temperature Tchg and a first parameter k under the condition that the compressor discharge pressure Pd corresponds to the refrigerant gas saturation temperature Tc, the outdoor unit liquid side stop valve temperature Tchg and the first parameter k.
The refrigerant gas saturation temperature Tc, the outdoor unit liquid side stop valve temperature Tchg and the first parameter k can be obtained as described above, and are not described herein again.
The air conditioner further comprises a calculating unit, and the calculating unit is further used for calculating the difference delta T3 between the refrigerant gas saturation temperature Tc and the outdoor unit liquid side stop valve temperature Tchg.
The air conditioner also comprises a comparison unit, and when the delta T3 is larger than a sixth preset value and k is smaller than a seventh preset value, the refrigerant quantity is judged to be high.
In this application, the sixth preset value is a half of a difference between a refrigerant gas saturation temperature Tc corresponding to the compressor discharge pressure Pd and a refrigerant gas saturation temperature Tcs corresponding to the compressor suction pressure Ps.
The refrigerant gas saturation temperature Tcs corresponding to the compressor suction pressure Ps can be obtained by querying the refrigerant property table according to the compressor suction pressure Ps obtained as described above.
The seventh preset value is a fixed value related to a value kEvijd determined according to the influence of the outdoor environment temperature on the first parameter k during experimental debugging, and is specifically k1 × kEvijd, wherein k1 is a correction coefficient and is a fixed value.
When any one of the mode A, the mode B and the mode C is met, the refrigerant quantity in the current refrigerant circulating system can be judged.
S3: whether the amount of refrigerant is low is judged according to at least one of the following modes A '/B'.
A': the temperature is determined at least according to the compressor discharge temperature Td and the refrigerant gas saturation temperature Tc corresponding to the compressor discharge pressure Pd.
The obtaining of the discharge temperature Td of the compressor and the saturation temperature Tc of the refrigerant gas can be referred to the above description, and is not described herein.
The air conditioner further includes a calculation unit for calculating a difference Δ T4 between the compressor discharge temperature Td and the refrigerant gas saturation temperature Tc.
The air conditioner also comprises a comparison unit used for judging that the refrigerant quantity is low when the delta T4 is larger than an eighth preset value.
The eighth preset value is a fixed value related to a value tmp1 determined according to the influence of the outdoor ring temperature on Δ T4 at the time of experimental commissioning, which is specifically k2+ tmp1, where k2 is a correction coefficient.
In some embodiments, the a 'mode may also be configured as the following detailed mode AA'.
AA': the temperature is determined according to the discharge temperature Td of the compressor, the saturation temperature Tc of the refrigerant gas, the outdoor heat-exchange liquid side temperature Te and the temperature Tchg of an outdoor unit liquid side stop valve.
The acquisition of Td, Tc, Te and Tchg is described above.
The air conditioner further includes a calculation unit for calculating a difference Δ T4 between the compressor discharge temperature Td and the refrigerant gas saturation temperature Tc, a difference Δ T1 between the refrigerant gas saturation temperature Tc and the outdoor heat-exchange liquid side temperature Te, and a difference Δ T5 between the outdoor heat-exchange liquid side temperature Te and the outdoor unit liquid side shutoff valve temperature Tchg.
The air conditioner also comprises a comparison unit used for judging that the refrigerant quantity is low when the delta T4 is larger than a ninth preset value, the delta T1 is smaller than a tenth preset value and the delta T5 is larger than an eleventh preset value.
The ninth preset value is a fixed value related to a value tmp2 determined according to the influence of the outdoor ring temperature on Δ T4 at the time of experimental commissioning, which is specifically k3+ tmp2, where k3 is a correction coefficient.
The tenth preset value is a fixed experimental value obtained during experimental debugging according to the configuration of the current air conditioner.
The eleventh preset value is a fixed value associated with a value tmp3 determined according to the influence of the outdoor ring temperature on Δ T5 at the time of experimental commissioning, and is specifically tmp3-k4, where k4 is a correction coefficient.
B': and determining according to the first parameter k, the refrigerant gas saturation temperature Tc and the outdoor unit liquid side stop valve temperature Tchg.
k. The Tc and Tchg acquisitions are as described above.
The air conditioner has a calculation unit for calculating a difference Δ T6 between Tc and Tchg.
The air conditioner also comprises a comparison unit which judges that the refrigerant quantity is low when k is larger than a twelfth preset value and delta T6 is larger than a thirteenth preset value.
The twelfth preset value is a value kEvijd determined according to the influence of the outdoor environment temperature on the first parameter k during experimental debugging.
The thirteenth preset value is a fixed value related to a value tmp4 determined according to the influence of the outdoor ring temperature on Δ T6 at the time of experimental commissioning, and is specifically tmp4-k5, where k5 is a correction coefficient.
When either of the A 'mode and the B' mode is satisfied, the refrigerant quantity in the current refrigerant circulating system can be judged to be low.
If neither of the A, B, C, A 'and B' modes is satisfied, that is, if the refrigerant quantity is determined to be within the appropriate range, it is considered to be normal.
The application provides an air conditioner, through gathering the operating parameter of air conditioner under the refrigeration mode of operation, when satisfying above-mentioned A mode, arbitrary kind of condition in B mode and the C mode, judge the refrigerant volume height, and when satisfying arbitrary kind of condition in A 'mode and the B' mode, judge that the refrigerant volume is low, these operating parameter all are the real-time parameter of air conditioner operation in-process, consequently, adopt this real-time parameter to judge the refrigerant volume, it is accurate and reliable, can in time avoid because of the influence that the refrigerant volume height or low caused air conditioner operational reliability.
The above examples are only intended to illustrate the technical solution of the present invention, but not to limit it; although the present invention has been described in detail with reference to the foregoing embodiments, it will be apparent to those skilled in the art that various changes may be made and equivalents may be substituted for elements thereof; and such modifications or substitutions do not depart from the spirit and scope of the corresponding technical solutions.

Claims (1)

1. An air conditioner comprising: the outdoor unit and at least one indoor unit connected through a refrigerant pipeline;
it is characterized in that the preparation method is characterized in that,
the air conditioner further includes:
a control unit configured to:
when the air conditioner is in a refrigeration operation mode, the refrigerant quantity is determined by at least one of the following modes:
b: calculating a difference delta T1 between a refrigerant gas saturation temperature Tc and an outdoor unit heat-exchange liquid side temperature Te and a difference delta T2 between a compressor discharge temperature Td and Tc corresponding to a compressor discharge pressure Pd;
if k is smaller than the third preset value, the delta T1 is larger than or equal to the fourth preset value, and the delta T2 is smaller than the fifth preset value, the refrigerant quantity is judged to be high;
c: calculating the difference delta T3 between Tc and the temperature Tchg of the liquid side stop valve of the outdoor unit;
if the delta T3 is larger than a sixth preset value and k is smaller than a seventh preset value, judging that the refrigerant quantity is high;
when the air conditioner is in a refrigeration operation mode, the low refrigerant quantity is determined by the following method:
b': calculating the difference Δ T6 between Tc and Tchg;
if k is larger than a twelfth preset value and delta T6 is larger than a thirteenth preset value, judging that the refrigerant quantity is low;
wherein the content of the first and second substances,
Figure DEST_PATH_IMAGE002
n is the number of the indoor units,
Figure DEST_PATH_IMAGE004
the sum of the opening degrees of the electronic expansion valves of the indoor units in the starting state in all the indoor units, wherein the opening degree of the electronic expansion valve of the indoor unit in the non-starting state is zero, P1 is the refrigerant gas saturation pressure corresponding to Tchg, Ps is the suction pressure of the compressor, Ft is the running frequency of the compressor, and k1 is the capacity correction coefficient of the indoor unit.
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