WO2022194218A1 - 一拖多空调器的压缩机频率的控制方法及一拖多空调器 - Google Patents
一拖多空调器的压缩机频率的控制方法及一拖多空调器 Download PDFInfo
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- WO2022194218A1 WO2022194218A1 PCT/CN2022/081225 CN2022081225W WO2022194218A1 WO 2022194218 A1 WO2022194218 A1 WO 2022194218A1 CN 2022081225 W CN2022081225 W CN 2022081225W WO 2022194218 A1 WO2022194218 A1 WO 2022194218A1
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- exhaust temperature
- temperature threshold
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- 238000000034 method Methods 0.000 title claims abstract description 105
- 230000003247 decreasing effect Effects 0.000 abstract description 2
- 239000007788 liquid Substances 0.000 description 36
- 239000003507 refrigerant Substances 0.000 description 31
- 238000001816 cooling Methods 0.000 description 9
- 238000010438 heat treatment Methods 0.000 description 9
- 238000005057 refrigeration Methods 0.000 description 9
- 238000004378 air conditioning Methods 0.000 description 5
- 238000010586 diagram Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 238000002474 experimental method Methods 0.000 description 2
- 230000001681 protective effect Effects 0.000 description 2
- 238000011946 reduction process Methods 0.000 description 2
- 238000006467 substitution reaction Methods 0.000 description 2
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 238000000926 separation method Methods 0.000 description 1
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F11/00—Control or safety arrangements
- F24F11/30—Control or safety arrangements for purposes related to the operation of the system, e.g. for safety or monitoring
- F24F11/49—Control or safety arrangements for purposes related to the operation of the system, e.g. for safety or monitoring ensuring correct operation, e.g. by trial operation or configuration checks
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F11/00—Control or safety arrangements
- F24F11/30—Control or safety arrangements for purposes related to the operation of the system, e.g. for safety or monitoring
- F24F11/32—Responding to malfunctions or emergencies
- F24F11/38—Failure diagnosis
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F11/00—Control or safety arrangements
- F24F11/50—Control or safety arrangements characterised by user interfaces or communication
- F24F11/52—Indication arrangements, e.g. displays
-
- 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
- F24F11/50—Control or safety arrangements characterised by user interfaces or communication
- F24F11/61—Control or safety arrangements characterised by user interfaces or communication using timers
-
- 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
-
- 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
- F24F2140/50—Load
Definitions
- the invention relates to an air conditioning system, in particular to a method for controlling the compressor frequency of a one-drive-multiple air conditioner and a one-drive-multiple air conditioner.
- One-to-many air conditioners usually refer to air conditioners with N indoor units (N is an integer greater than 1). During the use of this type of air conditioner, according to actual needs, the user will randomly turn on one, two, three, or N indoor units.
- Chinese invention patent CN106352611B discloses such a one-drive-multiple air conditioner.
- the one-to-many air conditioner includes an outdoor unit and at least two indoor heat exchangers (equivalent to two indoor units) that can form a refrigeration circuit with the outdoor unit.
- the outdoor unit includes a compressor, four-way valve, outdoor heat exchanger, and electronic expansion valve arranged in the same refrigeration circuit.
- the outdoor unit may also include more than one compressor in order to meet greater load demands.
- the compressor of the air conditioner When the exhaust air temperature of the air conditioner is too high and reaches a certain temperature, the compressor of the air conditioner will be shut down protectively. In order to avoid protective shutdown, in order to cooperate with the protection of the compressor's high discharge temperature, it is necessary to control the frequency of the compressor according to the frequency limit value of the discharge temperature, so as to effectively control the discharge temperature of the compressor, so as to ensure the normal operation of the air-conditioning system. run.
- the limit frequency value of the exhaust gas temperature also referred to as the "exhaust temperature threshold value”
- exhaust temperature threshold value is a preset temperature value in the air conditioning system. These preset temperature values remain the same regardless of the actual load on the air conditioning system. Turning on different numbers of indoor units means different starting loads.
- the present invention provides a compressor frequency control method of a one-drive-multiple air conditioner.
- Control Method The one-to-many air conditioner includes a variable frequency compressor, and the control method includes:
- the compressor When the real-time exhaust temperature T d is greater than the first dynamic exhaust temperature threshold, the compressor is shut down for a first predetermined period of time; and when the real-time exhaust temperature T d is less than or equal to the first dynamic when the exhaust gas temperature threshold is greater than the second dynamic exhaust temperature threshold, reducing the frequency of the compressor,
- the change direction of the first dynamic exhaust temperature threshold value and the second dynamic exhaust temperature threshold value is consistent with the change direction of the real-time start-up load KF.
- the first dynamic exhaust temperature threshold for controlling compressor shutdown and the first dynamic exhaust temperature threshold for controlling compressor frequency reduction are determined based on the real-time power-on load and change with the real-time power-on load, so they can be regarded as "dynamic". Further, the changing direction of the first dynamic exhaust temperature threshold and the second dynamic exhaust temperature threshold is consistent with the changing direction of the real-time start-up load.
- control method of the compressor frequency of the one-to-many air conditioner further includes:
- the change direction of the third dynamic exhaust gas temperature threshold is consistent with the change direction of the real-time start-up load KF.
- the third dynamic discharge temperature threshold determined based on the real-time start-up load KF, is used to determine under what conditions the compressor frequency can be kept constant. Specifically, under the condition that the real-time exhaust temperature T d is greater than the third dynamic exhaust temperature threshold and less than or equal to the second dynamic exhaust temperature threshold, the compressor frequency may remain unchanged.
- control method of the compressor frequency of the one-to-many air conditioner further includes:
- the one-to-many air conditioner When the real-time exhaust temperature T d is greater than the fourth dynamic exhaust temperature threshold and less than or equal to the third dynamic exhaust temperature threshold, the one-to-many air conditioner enters the compressor frequency automatic control mode; and when the When the real-time exhaust temperature T d is less than or equal to the fourth dynamic exhaust temperature threshold, the frequency of the compressor is increased,
- the change direction of the fourth dynamic exhaust temperature threshold value is consistent with the change direction of the real-time start-up load KF.
- the fourth dynamic discharge temperature threshold determined based on the real-time start-up load KF is used to determine under which conditions the compressor needs to be up-converted, and under which conditions the compressor (and thus the one-to-many air conditioner) can enter the normal control mode, That is, the automatic control mode based on indoor cooling/heating demand.
- the real-time exhaust temperature T d is greater than the fourth dynamic exhaust temperature threshold and less than or equal to the third dynamic exhaust temperature threshold, it means that the current exhaust temperature is more suitable, so the one-drive-multiple air conditioner can The cooling/heating demand enters the compressor frequency automatic control mode.
- the real-time exhaust temperature T d is less than or equal to the fourth dynamic exhaust temperature threshold, it is determined whether the frequency of the compressor needs to be increased according to the indoor cooling/heating demand.
- control method of the compressor frequency of the one-to-many air conditioner further includes:
- the second additional dynamic exhaust temperature threshold being less than or equal to the first dynamic exhaust temperature threshold and greater than the second dynamic exhaust temperature threshold
- the change direction of the second additional dynamic exhaust temperature threshold value is consistent with the change direction of the real-time start-up load KF.
- a second additional dynamic discharge temperature threshold determined based on the real-time start-up load KF, is used to control the speed of frequency reduction of the compressor.
- the frequency reduction speed of the compressor is relatively fast.
- the frequency reduction speed of the compressor is relatively slow. This allows for a more precise adjustment of the compressor frequency reduction process.
- control method for the compressor frequency of the one-to-many air conditioner when the compressor is stopped for a second predetermined period of time, the control method further includes:
- the second predetermined time period is greater than the first predetermined time period and less than the third predetermined time period.
- the real-time exhaust temperature T d is re-measured after the fifth predetermined time period has elapsed, And compare the current real-time exhaust temperature T d with the second dynamic exhaust temperature threshold, and if the real-time exhaust temperature T d is greater than the second dynamic exhaust temperature threshold, repeatedly reduce the compression machine frequency steps.
- the real-time discharge temperature T d of the compressor is re-measured, and the current real-time discharge temperature T d is compared with the second dynamic discharge temperature threshold. If the real-time exhaust temperature T d is still greater than the second dynamic exhaust temperature threshold and less than or equal to the first dynamic exhaust temperature threshold, it means that the previous frequency reduction process did not achieve the expected cooling effect, so the frequency of the compressor needs to be reduced again .
- the real-time exhaust temperature T d is re-measured after the sixth predetermined period of time has elapsed. , and compare the current real-time exhaust temperature T d with the fourth dynamic exhaust temperature threshold, if the real-time exhaust temperature T d is less than or equal to the fourth dynamic exhaust temperature threshold, repeat the increase the frequency of the compressor steps.
- the compressor frequency is increased, if the measured real-time exhaust temperature T d is still lower than the fourth dynamic exhaust temperature threshold, it means that the compressor frequency can be further increased to increase the exhaust temperature of the compressor.
- the first dynamic exhaust temperature threshold, the second additional dynamic exhaust temperature threshold, the second dynamic exhaust temperature threshold, the third dynamic exhaust temperature are respectively calculated based on the following formulas:
- the first dynamic exhaust temperature threshold first reference temperature+10KF(1),
- the second dynamic exhaust temperature threshold the second reference temperature+10KF(2),
- the third dynamic exhaust temperature threshold the third reference temperature+10KF(3),
- Fourth dynamic exhaust temperature threshold fourth reference temperature+10KF(4)
- the second additional dynamic exhaust temperature threshold the second additional reference temperature+10KF(5)
- KF is the real-time start-up load of one-to-many air conditioners, the unit is %,
- each dynamic exhaust temperature threshold is related to the real-time start-up load KF, and is consistent with the change direction of the real-time start-up load KF.
- the present invention also provides a A one-drive-multiple air conditioner includes a variable-frequency compressor, and the one-drive-multiple air conditioner uses the control method according to any one of the above to control the frequency of the compressor.
- the one-drive-multiple air conditioner of the present invention can overcome the technical problem of the failure of the exhaust temperature frequency limiting program under low load.
- Fig. 1 is the system schematic diagram of the embodiment of the one-drive-multiple air conditioner of the present invention
- Fig. 2 is the flow chart of the control method of the compressor frequency of the one-to-many air conditioner of the present invention
- Fig. 3 is the flow chart of the first embodiment of the control method of the compressor frequency of the one-drive-multiple air conditioner of the present invention
- FIG. 4 is a flow chart of the second embodiment of the method for controlling the compressor frequency of the one-drive-multiple air conditioner of the present invention
- Fig. 5 is the first part of the flow chart of the third embodiment of the control method of the compressor frequency of the one-to-many air conditioner of the present invention.
- FIG 6 is the second part of the flowchart of the third embodiment of the method for controlling the compressor frequency of the one-drive-multiple air conditioner of the present invention.
- One-to-many air conditioner 11. Outdoor unit; 111, Compressor; 112, Gas-liquid separator; 113, Outdoor heat exchanger; 114, Outdoor heat exchanger fan; 115, Distributor; 116, Four-way valve 117, liquid shut-off valve; 118, gas shut-off valve; 119, gaseous refrigerant header; 120, liquid refrigerant header; 121a, first filter; 121b, second filter; 121c, third filter; 121d, The fourth filter; 122a, the first electronic expansion valve; 122b, the second electronic expansion valve; 122c, the third electronic expansion valve; 122d, the fourth electronic expansion valve; 123a, the first gas pipe connection branch; 123b, the second gas pipe Connection branch; 123c, the third gas pipe connection branch; 123d, the fourth gas pipe connection branch; 124a, the first liquid pipe connection branch; 124b, the second liquid pipe connection branch; 124c, the third liquid pipe connection branch; 124d, the fourth Liquid pipe
- the present invention provides a method for controlling the compressor frequency of the one-drive-multiple air conditioners.
- the one-to-many air conditioner 1 includes a variable frequency compressor, and the control method includes:
- step S1 Detecting the real-time start-up load KF of the one-to-many air conditioner
- step S2 Determine at least a first dynamic exhaust temperature threshold and a second dynamic exhaust temperature threshold smaller than the first dynamic exhaust temperature threshold based on the real-time start-up load KF (step S2 );
- step S4 comparing the real-time exhaust temperature T d with the first dynamic exhaust temperature threshold and the second dynamic exhaust temperature threshold respectively.
- the compressor When the real-time exhaust temperature T d is greater than the first dynamic exhaust temperature threshold, the compressor is shut down for a first predetermined period of time; and when the real-time exhaust temperature T d is less than or equal to the first dynamic exhaust temperature threshold and greater than the second dynamic exhaust temperature When the air temperature threshold is reached, reduce the frequency of the compressor (step S5),
- the change direction of the first dynamic exhaust temperature threshold and the second dynamic exhaust temperature threshold is consistent with the change direction of the real-time start-up load KF.
- FIG. 1 is a system schematic diagram of an embodiment of the one-drive-multiple air conditioner of the present invention.
- the one-to-many air conditioner 1 includes an outdoor unit 11 (which is generally arranged in an outdoor environment) and a plurality of parallel-connected indoor units 21 (which are generally connected to a refrigeration circuit) that can be interconnected into a refrigeration circuit allowing refrigerant to flow therein. arranged indoors or in a room).
- the one-to-many air conditioner 1 has four indoor units connected in parallel: indoor unit A, indoor unit B, indoor unit C, and indoor unit D.
- FIG. 1 shows only the indoor unit A, that is, the indoor unit 21, and the remaining three indoor units are omitted. According to actual needs, the configurations of the four indoor units can be the same or different.
- the one-for-many air conditioner 1 may have two indoor units, three indoor units, or more than four indoor units.
- the outdoor unit 11 mainly includes a compressor 111, a gas-liquid separator 112, an outdoor heat exchanger 113, an outdoor heat exchanger fan 114, a four-way valve 116, and Electronic expansion valve. Due to the existence of the four-way valve 116, the one-drive-multiple air conditioner 1 of the present invention has at least cooling and heating functions. Alternatively, the outdoor unit 11 may not include the four-way valve 116, which means that the one-to-many air conditioner does not have a heating function.
- the compressor 111 is an inverter compressor. Alternatively, compressor 111 may include two or more compressors in parallel.
- the compressor 111 has an intake port and an exhaust port (not shown in the drawings).
- the discharge port of the compressor 111 is connected to the compressor connection port on the four-way valve 116 through a refrigerant pipe (ie, a pipe that allows refrigerant to flow therein).
- a discharge temperature sensor 125 for measuring the discharge temperature of the compressor 111 is arranged on the refrigerant pipe close to the discharge port of the compressor 111 .
- the suction port of the compressor 111 is connected to the air outlet on the gas-liquid separator 112 through a refrigerant pipe, and the air inlet of the gas-liquid separator 112 is connected to the gas-liquid separator connection port on the four-way valve 116 through a refrigerant pipe.
- the four-way valve 116 is also provided with an outdoor heat exchanger connection port and an indoor heat exchanger connection port.
- One end of the outdoor heat exchanger 113 is connected to the outdoor heat exchanger connection port of the four-way valve 116 through a refrigerant pipe.
- the outdoor heat exchanger 113 can be, but is not limited to, a fin coil heat exchanger and a plate heat exchanger, and is equipped with an outdoor heat exchanger fan 114 .
- the other end of the outdoor heat exchanger 113 is connected to the distributor 115 .
- the outdoor heat exchanger 113 is also provided with an outdoor heat exchanger temperature sensor 126 and a defrost sensor 127, respectively.
- connection port of the indoor heat exchanger of the four-way valve 116 is connected to the gaseous refrigerant header 119 through a refrigerant pipe, and a gas shut-off valve 118 is provided in the refrigerant pipe.
- the gaseous refrigerant header 119 is provided with four gas pipe connection branches: a first gas pipe connection branch 123a, which is configured to be connected to the indoor unit A; a second gas pipe connection branch 123b, which is configured to be connected to the indoor unit B; a third gas pipe
- the connection branch 123c is configured to be connectable to the indoor unit C; the fourth air pipe connection branch 123d is configured to be connectable to the indoor unit D.
- the distributor 115 is connected to the liquid refrigerant header 120 through a refrigerant pipe, and a liquid shut-off valve 117 is provided on the refrigerant pipe.
- the liquid refrigerant header 120 is provided with four liquid pipe connection branches: the first liquid pipe connection branch 124a, which is configured to be connected to the indoor unit A; the second liquid pipe connection branch 124b, which is configured to be connected to the indoor unit B; The third liquid pipe connection branch 124c is configured to be connectable to the indoor unit C; the fourth liquid pipe connection branch 124d is configured to be connectable to the indoor unit D.
- a first filter 121a and a first electronic expansion valve 122a are arranged on the first liquid pipe connection branch 124a, wherein the first filter 121a is located between the indoor unit A and the first electronic expansion valve 122a.
- a second filter 121b and a second electronic expansion valve 122b are arranged on the second liquid pipe connection branch 124b, wherein the second filter 121b is located between the indoor unit B and the second electronic expansion valve 122b.
- a third filter 121c and a third electronic expansion valve 122c are arranged on the third liquid pipe connection branch 124c, wherein the third filter 121c is located between the indoor unit C and the third electronic expansion valve 122c.
- a fourth filter 121d and a fourth electronic expansion valve 122d are arranged on the fourth liquid pipe connection branch 124d, wherein the fourth filter 121d is located between the indoor unit D and the fourth electronic expansion valve 122d.
- the indoor unit A21 includes an indoor heat exchanger 211 , an indoor heat exchanger fan 212 , and an indoor heat exchanger temperature sensor 213 that measures the temperature of the indoor heat exchanger 211 .
- the indoor heat exchanger 211 includes, but is not limited to, a fin-and-tube heat exchanger. Both ends of the indoor heat exchanger 211 may be connected to the first gas pipe connection branch 123a and the first liquid pipe connection branch 124a, respectively.
- the one-to-many air conditioner 1 can perform cooling and heating cycles.
- the outdoor heat exchanger 113 acts as a condenser
- the indoor heat exchanger 211 acts as an evaporator.
- the compressor 111 starts to start, and the refrigerant (for example, R410a) is compressed by the compressor 111 and enters the outdoor heat exchanger in the form of high-temperature and high-pressure gas through the interconnected ports of the four-way valve 116 113 (which acts as a condenser).
- the high-temperature and high-pressure gaseous refrigerant is condensed into a high-temperature and high-pressure liquid refrigerant by transferring heat to the air flow caused by the outdoor heat exchanger fan 114 .
- the high-temperature and high-pressure liquid refrigerant flows through the distributor 115 and the liquid shut-off valve 117 in sequence and enters the liquid refrigerant header 120 .
- the high-temperature and high-pressure liquid refrigerant is distributed to one or more of the first, second, third, and fourth liquid pipe connecting branches 124a, 124b, 124c, and 124d connected to the powered-on indoor unit, and is sent to the one or more
- the corresponding electronic expansion valves on the connecting branches of or multiple liquid pipes are expanded into liquid refrigerant with low temperature and low pressure.
- the low-temperature and low-pressure liquid refrigerant then flows into the indoor heat exchangers of the turned-on indoor units, such as the indoor heat exchangers 211, respectively.
- the low-temperature and low-pressure liquid refrigerant is evaporated into a low-temperature and low-pressure gaseous refrigerant by absorbing the heat of the indoor air, so that the indoor air is cooled down.
- the low-temperature and low-pressure gaseous refrigerant leaves the indoor heat exchanger 211 and then flows through the corresponding gas pipe connection branch, gas pipe header 119 , gas shut-off valve 118 , and four-way valve 116 in sequence, and then enters the gas-liquid separator 112 .
- the gaseous refrigerant after gas-liquid separation is sucked into it by the compressor 111 through the suction port. A complete refrigeration cycle is completed and such a refrigeration cycle can be performed without interruption in order to achieve the target refrigeration temperature.
- the flow direction of the refrigerant in the outdoor unit 11 and the indoor unit 21 is exactly opposite to that in the refrigeration cycle, and the outdoor heat exchanger 113 acts as an evaporator, while the indoor heat exchange
- the condenser 211 acts as a condenser.
- the compressor 111 When the compressor 111 is working, its exhaust temperature needs to be controlled within an appropriate range, otherwise, when the exhaust temperature exceeds a certain temperature value, the compressor is prone to protective shutdown. Therefore, one-to-many air conditioners are equipped with a frequency limiting control program for exhaust temperature. In order to avoid the technical problem of the failure of the exhaust temperature frequency limiting program under low load, the compressor frequency of the one-drive-multiple air conditioner of the present invention adopts the following control method.
- FIG. 2 is a flow chart of the control method of the compressor frequency of the one-drive-multiple air conditioner of the present invention.
- the real-time start-up load KF of the one-pull-multiple air conditioner is detected in step S1 .
- the one-to-many air conditioner has four indoor units, and the load powers of the four indoor units are 2.5KW, 2.5KW, 3.5KW, and 5.0KW, respectively.
- step S2 a first dynamic exhaust temperature threshold and a second exhaust temperature threshold are determined based on the detected real-time startup load KF, wherein the second dynamic exhaust temperature threshold is smaller than the first dynamic exhaust temperature threshold.
- the first dynamic exhaust temperature threshold and the second dynamic exhaust temperature threshold are calculated using the following equations (1) and (2), respectively:
- the first dynamic exhaust temperature threshold the first reference temperature + 10KF, (1)
- the second dynamic exhaust temperature threshold the second reference temperature+10KF, (2)
- KF is the real-time start-up load of the one-to-many air conditioner
- the unit is %
- the first reference temperature is greater than the second reference temperature and both are constants.
- the first reference temperature is 95°C
- the second reference temperature is 85°C.
- both the first reference temperature and the second reference temperature constants in this formula may vary, and therefore may be other suitable temperature values, and each constant can be determined through experiments.
- the real-time exhaust temperature T d of the one-to-many air conditioner is measured.
- the real-time discharge temperature T d is usually measured close to the compressor discharge port.
- step S4 the control method proceeds to step S4, where the real-time exhaust temperature T d and the first dynamic exhaust temperature are respectively The threshold is compared to a second dynamic exhaust temperature threshold.
- step S5 when the real-time exhaust temperature T d is greater than the first dynamic exhaust temperature threshold, the compressor is shut down for a first predetermined period of time; and when the real-time exhaust temperature T d is less than or equal to the first dynamic exhaust temperature threshold and Above the second dynamic discharge temperature threshold, the frequency of the compressor is reduced.
- the first predetermined time period is, for example, 1 minute, 2 minutes, or other suitable time period.
- the first predetermined period of time may be determined experimentally.
- the control method can be carried out repeatedly at certain time intervals.
- step S1 the control method detects the real-time start-up load KF of the one-to-many air conditioner after starting (step S1 ). Then, the control method proceeds to step S2a to determine a first dynamic exhaust temperature threshold, a second dynamic exhaust temperature threshold, and a third dynamic exhaust temperature threshold based on the real-time start-up load KF.
- the second dynamic exhaust temperature threshold is less than the first dynamic exhaust temperature threshold and greater than the third dynamic exhaust temperature threshold, and the first dynamic exhaust temperature threshold, the second dynamic exhaust temperature threshold, and the third dynamic exhaust temperature threshold The direction of change is consistent with that of the real-time start-up load.
- the first dynamic exhaust temperature threshold and the second exhaust temperature threshold may be determined according to equations (1) and (2) above, respectively.
- the third dynamic exhaust temperature threshold is calculated according to the following formula:
- the third dynamic exhaust temperature threshold the third reference temperature+10KF, (3)
- KF is the real-time start-up load of the one-to-many air conditioner
- the unit is %
- the third reference temperature is lower than the above-mentioned first and second reference temperatures and is also constant.
- the third reference temperature is 80°C or other suitable temperature value.
- the third reference temperature in this formula may vary and can be determined experimentally.
- the control method measures the real-time exhaust temperature T d of the one-to-many air conditioner in step S3. Then, the control method proceeds to step S4a. In step S4a, the real-time exhaust temperature T d is compared with the first dynamic exhaust temperature threshold, the second dynamic exhaust temperature threshold, and the third dynamic exhaust temperature threshold, respectively. Different control measures are performed on the compressor frequency according to the result of the comparison, so the control method proceeds to step S5a.
- step S5a the following control measures are implemented with respect to the compressor frequency.
- the compressor is shut down for a first predetermined period of time.
- the first predetermined time period is, for example, 1 minute, 2 minutes, or other suitable time period.
- reduce the frequency of the compressor for example, by 0.8 Hz/s, 1 Hz/s, 2 Hz/s, or other Appropriate speed reduces compressor frequency.
- the frequency of the compressor is kept unchanged.
- FIG. 4 is a flow chart of the second embodiment of the method for controlling the compressor frequency of the one-drive-multiple air conditioner of the present invention.
- the control method similarly detects the real-time start-up load KF of the one-to-many air conditioner after the start (step S1 ). Then, the control method proceeds to step S2b to determine the first dynamic exhaust temperature threshold, the second dynamic exhaust temperature threshold, the third dynamic exhaust temperature threshold, and the fourth dynamic exhaust temperature threshold based on the real-time startup load KF.
- the second dynamic exhaust temperature threshold is less than the first dynamic exhaust temperature threshold and greater than the third dynamic exhaust temperature threshold, which in turn is greater than the fourth dynamic exhaust temperature threshold.
- the changing direction of each of the first dynamic exhaust temperature threshold, the second dynamic exhaust temperature threshold, the third dynamic exhaust temperature threshold, and the fourth dynamic exhaust temperature threshold is consistent with the changing direction of the real-time startup load KF.
- the first dynamic exhaust temperature threshold, the second dynamic exhaust temperature threshold, and the third dynamic exhaust temperature threshold may be determined according to the above equations (1), (2), and (3), respectively.
- the fourth dynamic exhaust temperature threshold is calculated according to the following formula:
- Fourth dynamic exhaust temperature threshold fourth reference temperature+10KF, (4)
- KF is the real-time start-up load of the one-to-many air conditioner
- the unit is %
- the fourth reference temperature is lower than the above-mentioned fourth reference temperature and is also a constant.
- the fourth reference temperature is 75°C or other suitable temperature value.
- the fourth reference temperature in this formula may vary and can be determined through experiments.
- the control method then proceeds to step S3.
- step S3 the real-time exhaust temperature T d of the one-to-many air conditioner is measured. Then, the control method proceeds to step S4b.
- step S4b the real-time exhaust temperature T d is compared with the first dynamic exhaust temperature threshold, the second dynamic exhaust temperature threshold, the third dynamic exhaust temperature threshold, and the fourth dynamic exhaust temperature threshold, respectively. Different control measures are performed on the compressor frequency according to the result of the comparison, so the control method proceeds to step S5b.
- step S5b the following control measures are implemented with respect to the compressor frequency.
- the compressor is shut down for a first predetermined period of time.
- the first predetermined time period is, for example, 1 minute, 2 minutes, or other suitable time period.
- reduce the frequency of the compressor for example, by 0.8 Hz/s, 1 Hz/s, 2 Hz/s, or other Appropriate speed reduces compressor frequency.
- the frequency of the compressor is kept unchanged.
- the one-to-many air conditioner When the real-time exhaust temperature T d is less than or equal to the third dynamic exhaust temperature threshold and greater than the fourth dynamic exhaust temperature threshold, the one-to-many air conditioner enters the compressor frequency automatic control mode, that is, the one-to-many air conditioner is based on indoor cooling/ The heating demand goes into the compressor frequency automatic control.
- step S1 the control method similarly firstly detects the real-time start-up load KF of the one-to-many air conditioner after starting (step S1 ). Then, the control method proceeds to step S2c.
- step S2c the first dynamic exhaust temperature threshold T t1 , the second additional dynamic exhaust temperature threshold T t2 , the second dynamic exhaust temperature threshold T t3 , and the third dynamic exhaust temperature threshold T are determined based on the real-time start-up load KF t4 , and the fourth dynamic exhaust temperature threshold T t5 .
- first dynamic exhaust temperature threshold T t1 , second additional dynamic exhaust temperature threshold T t2 , second dynamic exhaust temperature threshold T t3 , third dynamic exhaust temperature threshold T t4 , and fourth dynamic exhaust temperature threshold T The size order of t5 is:
- the direction of change of each of the first dynamic exhaust temperature threshold, the second additional dynamic exhaust temperature threshold, the second dynamic exhaust temperature threshold, the third dynamic exhaust temperature threshold, and the fourth dynamic exhaust temperature threshold is related to the real-time power-on
- the load KF changes in the same direction.
- the first dynamic exhaust temperature threshold, the second dynamic exhaust temperature threshold, the third dynamic exhaust temperature threshold, and the fourth dynamic exhaust temperature threshold may be based on equations (1), (2), (3), and (4) Make sure.
- the second additional dynamic exhaust temperature threshold is calculated according to the following formula:
- the second additional dynamic exhaust temperature threshold the second additional reference temperature + 10KF, (5)
- KF is the real-time start-up load of the one-to-many air conditioner
- the unit is %
- the second additional reference temperature is a constant smaller than the first reference temperature and larger than the second reference temperature.
- the second additional reference temperature is 90°C or other suitable temperature value.
- the second additional reference temperature in this formula may vary and can be determined experimentally.
- step S41 the real-time exhaust gas temperature T d is compared with the first dynamic exhaust gas temperature threshold value T t1 . If the real-time exhaust temperature T d is less than or equal to the first dynamic exhaust temperature threshold T t1 , the control method proceeds to step S42. If the real-time discharge temperature T d is greater than the first dynamic discharge temperature threshold T t1 , the control method proceeds to step S51 to stop the compressor. After the compressor is shut down for a first predetermined time period, eg 2 minutes or other suitable time period, the control method proceeds to step 61, restarts the compressor, and re-measures the real-time discharge temperature T d .
- a first predetermined time period eg 2 minutes or other suitable time period
- step S71 the control method proceeds to step S71 to compare the currently obtained T d with the first dynamic exhaust gas temperature threshold value T t1 . If the currently obtained T d is less than or equal to the first dynamic exhaust gas temperature threshold value T t1 , the control method proceeds to step S42. If the currently obtained T d is still greater than the first dynamic exhaust temperature threshold T t1 , the control method proceeds to step S81 , and the compressor is shut down again for a second predetermined time period longer than the first predetermined time period, for example, 3 minutes or other suitable time period.
- step S91 determines whether the number of restarts of the compressor in the third predetermined time period (eg 1 hour or other suitable time) is less than a predetermined number of times, eg 3 times.
- the third predetermined time period is longer than the second predetermined time period. If the number of restarts of the compressor has reached the predetermined number of times, the control method proceeds to step S121, and a fault alarm is issued, indicating that the one-drive-multiple air conditioner has a high-frequency exhaust fault.
- step S101 If the number of restarts of the compressor is less than the predetermined number of times, the control method proceeds to step S101, restarts the compressor, and then operates the compressor at a preset low frequency for a fourth predetermined time period, such as 3 minutes or other suitable time period (step S101). S111). After the compressor operates at low frequency for a fourth predetermined period of time, the control method returns to step S1.
- step S42 the real-time exhaust temperature T d is compared with a second additional dynamic exhaust temperature threshold T t2 . If the real-time exhaust temperature T d is less than or equal to the second additional dynamic exhaust temperature threshold T t2 , the control method proceeds to step S43. If the real-time discharge temperature T d is greater than the second additional dynamic discharge temperature threshold T t2 , the control method proceeds to step S52 to reduce the frequency of the compressor at a higher speed, for example at a speed of 2 Hz/s .
- step S62 After the compressor is down-converted for a fifth predetermined time period, eg, 10 seconds, 20 seconds, or other suitable time periods, the control method proceeds to step S62 to re-measure the real-time exhaust gas temperature T d . Then, the control method proceeds to step S72 to compare the currently obtained T d with the second additional dynamic exhaust gas temperature threshold value T t2 . If the currently obtained T d is less than or equal to the second additional dynamic exhaust gas temperature threshold value T t2 , the control method proceeds to step S43. If the currently obtained T d is still greater than the second additional dynamic exhaust gas temperature threshold value T t2 , the control method returns to step S52 to implement the frequency reduction measure again.
- a fifth predetermined time period eg, 10 seconds, 20 seconds, or other suitable time periods
- step S43 the real-time exhaust gas temperature T d is compared with the second dynamic exhaust gas temperature threshold value T t3 . If the real-time exhaust temperature T d is less than or equal to the second dynamic exhaust temperature threshold T t3 , the control method proceeds to step S44. If the real-time exhaust temperature T d is greater than the second dynamic exhaust temperature threshold T t3 , the control method proceeds to step S53. In step S53, reduce the frequency of the compressor at a lower speed, for example, reduce the frequency of the compressor at a speed of 1 Hz/s.
- step S63 the control method proceeds to step S63 to re-measure the real-time exhaust gas temperature T d .
- the control method proceeds to step S73 to compare the currently obtained T d with the second dynamic exhaust gas temperature threshold value T t3 . If the currently obtained T d is less than or equal to the second additional dynamic exhaust gas temperature threshold value T t2 , the control method proceeds to step S44. If the currently obtained T d is still greater than the second dynamic exhaust gas temperature threshold value T t3 , the control method returns to step S53 to implement the frequency reduction measure again.
- step S44 the real-time exhaust gas temperature T d is compared with the third dynamic exhaust gas temperature threshold value T t4 . If the real-time exhaust temperature T d is less than or equal to the third dynamic exhaust temperature threshold T t4 , the control method proceeds to step S45. If the real-time exhaust temperature T d is greater than the third dynamic exhaust temperature threshold T t4 , the control method proceeds to step S54 to keep the frequency of the compressor unchanged.
- step S45 the real-time exhaust temperature T d is compared with the fourth dynamic exhaust temperature threshold T t5 . If the real-time exhaust temperature T d is greater than the fourth dynamic exhaust temperature threshold T t5 , the control method proceeds to step S56 , and the one-to-many air conditioner enters the normal control mode, that is, the compressor frequency automatic control based on the indoor cooling/heating demand . If the real-time exhaust temperature T d is less than or equal to the fourth dynamic exhaust temperature threshold T t5 , the control method proceeds to step S55.
- step S55 the frequency of the compressor is increased at a predetermined speed, eg, the frequency of the compressor is decreased at 1 Hz/s or other suitable speed.
- the control method proceeds to step S65 to re-measure the real-time exhaust gas temperature T d .
- the control method proceeds to step S75 to compare the currently obtained T d with the fourth dynamic exhaust gas temperature threshold value T t5 . If the currently obtained T d is greater than the fourth dynamic exhaust temperature threshold value T t5 , the control method proceeds to step S56 , and the multi-air conditioner enters the normal control mode. If the currently obtained T d is still less than or equal to the fourth dynamic exhaust gas temperature threshold value T t3 , the control method returns to step S55 to re-implement the frequency boosting measure.
Abstract
本发明涉及一种一拖多空调器的压缩机频率的控制方法及使用该控制方法的一拖多空调器。该控制方法包括：检测一拖多空调器的实时开机负荷KF；基于实时开机负荷KF至少确定第一动态排气温度阈值和比其小的第二动态排气温度阈值；测量压缩机的实时排气温度T d；将实时排气温度T d分别与第一和第二动态排气温度阈值进行比较；当实时排气温度T d大于第一动态排气温度阈值时，压缩机停机持续第一预定时间段；并且当实时排气温度T d小于等于第一动态排气温度阈值并大于第二动态排气温度阈值时，降低压缩机的频率，其中，第一动态排气温度阈值和第二动态排气温度阈值的变化方向与实时开机负荷KF的变化方向一致。该方法可阻止低负荷下排气温度限频程序失效。
Description
本发明涉及空调系统，具体地涉及一拖多空调器的压缩机频率的控制方法及一拖多空调器。
一拖多空调通常是指具有N台(N为大于1的整数)室内机的空调器。此种空调器在使用过程中，根据实际需要，用户会随机地开启一台、两台、三台、或者N台室内机。例如中国发明专利CN106352611B就公开了这样一种一拖多空调器。该一拖多空调器包括室外机和可与室外机形成制冷回路的至少两个室内换热器(相当于两个室内机)。室外机则包括布置在同一制冷回路中的一台压缩机、四通阀、室外换热器、和电子膨胀阀。室外机还可包括多于一台的压缩机，以便满足更大的负荷需求。
当空调器排气温度过高且达到一定温度后，该空调器的压缩机会发生保护性停机。为了避免发生保护性停机，为了配合压缩机排气温度过高的保护，需要根据排气温度限频值来控制压缩机的频率，以有效控制压缩机的排气温度，从而保证空调系统能正常运行。在现有技术中，排气温度限频值(也称为“排气温度阈值”)都是为在空调系统里预先设定的温度值。不管空调系统的实际负荷怎么变化，这些预先设定的温度值都保持不变。开启不同数量的室内机，意味着开机负荷也不相同。随着开机负荷的变化，排气温度与空调系统冷媒压力的关系也会相应地产生变化。在这种情况下，相同的排气温度限频值会造成低负荷下排气温度限频程序失效，进而无法起到排气温度限频作用。
相应地，本领域需要一种新的技术方案来解决上述问题。
发明内容
为了解决现有技术中的上述问题，即为了解决现有压缩机频率控制方法造成低负荷下排气温度限频程序失效的技术问题，本发明提供一种一 拖多空调器的压缩机频率的控制方法。一拖多空调器包括可变频的压缩机，并且该控制方法包括：
检测所述一拖多空调器的实时开机负荷KF；
基于所述实时开机负荷KF至少确定第一动态排气温度阈值和比第一动态排气阈值小的第二动态排气温度阈值；
测量所述压缩机的实时排气温度T
d；
将所述实时排气温度T
d分别与所述第一动态排气温度阈值和第二动态排气温度阈值进行比较；
当所述实时排气温度T
d大于所述第一动态排气温度阈值时，所述压缩机停机持续第一预定时间段；并且当所述实时排气温度T
d小于等于所述第一动态排气温度阈值并大于所述第二动态排气温度阈值时，降低所述压缩机的频率，
其中，所述第一动态排气温度阈值和第二动态排气温度阈值的变化方向与所述实时开机负荷KF的变化方向一致。
本领域技术人员能够理解的是，在本发明一拖多空调器的压缩机频率的控制方法中，用于控制压缩机停机的第一动态排气温度阈值和用于控制压缩机降频的第二动态排气温度阈值均基于实时开机负荷确定并且随实时开机负荷的变化而变化，因此可看作是“动态的”。进一步地，第一动态排气温度阈值和第二动态排气温度阈值的变化方向与实时开机负荷的变化方向保持一致。即，当实时开机负荷增大时，第一动态排气温度阈值和第二动态排气温度阈值都相应地升高；当实时开机负荷减小时，第一动态排气温度阈值和第二动态排气温度阈值也都相应地降低。因此，这样的控制方法能够避免一拖多空调器在低负荷下排气温度限频程序失效的问题。
在上述一拖多空调器的压缩机频率的控制方法的优选技术方案中，所述控制方法还包括：
基于所述实时开机负荷KF确定第三动态排气温度阈值，所述第三动态排气温度阈值小于所述第二动态排气温度阈值；
将所述实时排气温度T
d与所述第三动态排气温度阈值进行比较；
当所述实时排气温度T
d大于所述第三动态排气温度阈值并且小于等于所述第二动态排气温度阈值时，保持所述压缩机的频率不变，
其中，所述第三动态排气温度阈值的变化方向与所述实时开机负荷KF的变化方向一致。基于实时开机负荷KF确定的第三动态排气温度阈值用于确定在何种情形下可保持压缩机频率不变。具体地，在实时排气温度T
d大于第三动态排气温度阈值并小于等于第二动态排气温度阈值的条件下，压缩机频率可保持不变。
在上述一拖多空调器的压缩机频率的控制方法的优选技术方案中，所述控制方法还包括：
基于所述实时开机负荷KF确定第四动态排气温度阈值，所述第四动态排气温度阈值小于所述第三动态排气温度阈值；
将所述实时排气温度T
d与所述第四动态排气温度阈值进行比较；
当所述实时排气温度T
d大于所述第四动态排气温度阈值并小于等于第三动态排气温度阈值时，所述一拖多空调器进入压缩机频率自动控制模式；并且当所述实时排气温度T
d小于等于第四动态排气温度阈值时，升高所述压缩机的频率，
其中，所述第四动态排气温度阈值的变化方向与所述实时开机负荷KF的变化方向一致。基于实时开机负荷KF确定的第四动态排气温度阈值用于确定在何种情形下压缩机需要升频，以及在何种情形下压缩机(因此一拖多空调器)可进入正常控制模式，即基于室内制冷/制热需求进行的自动控制模式。具体地，在实时排气温度T
d大于第四动态排气温度阈值并小于等于第三动态排气温度阈值的条件下，说明当前的排气温度比较适合，因此一拖多空调器可根据室内制冷/制热需求进入压缩机频率自动控制模式。当实时排气温度T
d小于等于第四动态排气温度阈值时，根据室内制冷/制热需求判定是否需要升高压缩机的频率。
在上述一拖多空调器的压缩机频率的控制方法的优选技术方案中，所述控制方法还包括：
基于所述实时开机负荷KF确定第二附加动态排气温度阈值，所述第二附加动态排气温度阈值小于等于所述第一动态排气温度阈值并大于所述第二动态排气温度阈值；
将所述实时排气温度T
d与所述第二附加动态排气温度阈值进行比较；
当所述实时排气温度T
d大于所述第二附加动态排气温度阈值并小于等于第一动态排气温度阈值时，以较快速度降低所述压缩机的频率；并且当所 述实时排气温度T
d大于所述第二动态排气温度阈值并小于等于所述第二附加动态排气温度阈值时，以较慢速度降低所述压缩机的频率，
其中，所述第二附加动态排气温度阈值的变化方向与所述实时开机负荷KF的变化方向一致。基于实时开机负荷KF确定的第二附加动态排气温度阈值用于控制压缩机的降频速度。当实时排气温度T
d大于第二附加动态排气温度阈值并小于等于第一动态排气温度阈值时，压缩机的降频速度相对要快。当实时排气温度T
d大于第二动态排气温度阈值并小于等于第二附加动态排气温度阈值时，压缩机的降频速度相对要慢。这样可对压缩机降频过程进行更加精准的调节。
在上述一拖多空调器的压缩机频率的控制方法的优选技术方案中，当所述压缩机停机持续第一预定时间段后，压缩机重启并重新测量所述实时排气温度T
d，并且将当前的所述实时排气温度T
d与所述第一动态排气温度阈值进行比较，如果所述实时排气温度T
d大于所述第一动态排气温度阈值，所述压缩机停机持续第二预定时间段，所述第二预定时间段大于所述第一预定时间段。压缩机停机经过第一预定时间段后重新启动。这时需要重新测量压缩机的实时排气温度T
d，并且再次将当前的实时排气温度T
d与第一动态排气温度阈值进行比较。如果当前的实时排气温度T
d仍然大于第一动态排气温度阈值，说明达到第二动态排气温度阈值后，压缩机降频速度无法达到快速降低排气温度的效果，需要增加降频速度，以满足系统稳定运行。
在上述一拖多空调器的压缩机频率的控制方法的优选技术方案中，当所述压缩机停机持续第二预定时间段后，所述控制方法还包括：
判断所述压缩机在第三预定时间段内的重启次数是否小于预定次数，所述预定次数≧3；
如果所述重启次数小于预定次数，重启所述压缩机并且以低频运行所述压缩机持续第四预定时间段；
如果所述重启次数大于等于所述预定次数，发出高频排气故障警报，
其中，所述第二预定时间段大于所述第一预定时间段并小于所述第三预定时间段。在压缩机第二次停机并经过第二预定时间段后，先判断压缩机总重启次数是否小于预定次数。如果压缩机总重启次数小于预定次数，说明还可以继续尝试通过停机来降低压缩机的实时排气温度T
d。如果压缩机总重启次数已经达到预定次数，则说明单纯停机不能降低压缩机的实时排气温度 T
d，压缩机或一拖多空调器存在可导致高排气温度的故障，因此可发出高频排气故障警报。
在上述一拖多空调器的压缩机频率的控制方法的优选技术方案中，在降低所述压缩机的频率后，经过所述第五预定时间段，重新测量所述实时排气温度T
d，并且将当前的所述实时排气温度T
d与所述第二动态排气温度阈值进行比较，如果所述实时排气温度T
d大于所述第二动态排气温度阈值，重复降低所述压缩机的频率的步骤。降低压缩机频率后经过第五预定时间段，再重新测量压缩机的实时排气温度T
d，并将当前的实时排气温度T
d与第二动态排气温度阈值进行比较。如果实时排气温度T
d仍然大于第二动态排气温度阈值并小于等于第一动态排气温度阈值，则说明前一次的降频处理没有达到预期的降温效果，因此需要再次降低压缩机的频率。
在上述一拖多空调器的压缩机频率的控制方法的优选技术方案中，在升高所述压缩机的频率后，经过所述第六预定时间段，重新测量所述实时排气温度T
d，并且将当前的所述实时排气温度T
d与所述第四动态排气温度阈值进行比较，如果所述实时排气温度T
d小于等于所述第四动态排气温度阈值，重复升高所述压缩机的频率的步骤。在压缩机升频后，若测得的实时排气温度T
d仍然低于第四动态排气温度阈值，说明压缩机频率可以进一步增加以提高压缩机的排气温度。
在上述一拖多空调器的压缩机频率的控制方法的优选技术方案中，第一动态排气温度阈值、第二附加动态排气温度阈值、第二动态排气温度阈值、第三动态排气温度阈值、和第四动态排气温度阈值分别基于如下公式计算：
第一动态排气温度阈值＝第一基准温度+10KF(1)，
第二动态排气温度阈值＝第二基准温度+10KF(2)，
第三动态排气温度阈值＝第三基准温度+10KF(3)，
第四动态排气温度阈值＝第四基准温度+10KF(4)，
第二附加动态排气温度阈值＝第二附加基准温度+10KF(5)，
其中，KF是一拖多空调器的实时开机负荷，单位为％，
第一基准温度>第二附加基准温度>第二基准温度>第三基准温度>第四基准温度，并且都为常数。通过上述对应的公式，可保证每个动态排气温度 阈值都与实时开机负荷KF相关，并且与实时开机负荷KF的变化方向保持一致。
为了解决现有技术中的上述问题，即为了解决现有一拖多空调器在对压缩机实施高排气温度保护时造成低负荷下排气温度限频程序失效的技术问题，本发明还提供一种一拖多空调器，所述一拖多空调器包括可变频的压缩机，并且所述一拖多空调器使用根据上面任一项所述的控制方法控制所述压缩机的频率。通过使用上述的压缩机频率的控制方法，本发明一拖多空调器可克服低负荷下排气温度限频程序失效的技术问题。
下面参照附图来描述本发明的优选实施方式，附图中：
图1是本发明一拖多空调器的实施例的系统示意图；
图2是本发明一拖多空调器的压缩机频率的控制方法的流程图；
图3是本发明一拖多空调器的压缩机频率的控制方法的第一实施例的流程图；
图4是本发明一拖多空调器的压缩机频率的控制方法的第二实施例的流程图；
图5是本发明一拖多空调器的压缩机频率的控制方法的第三实施例的流程图的第一部分；
图6是本发明一拖多空调器的压缩机频率的控制方法的第三实施例的流程图的第二部分。
附图标记：
1、一拖多空调器；11、室外单元；111、压缩机；112、气液分离器；113、室外换热器；114、室外换热器风机；115、分配器；116、四通阀；117、液体截止阀；118、气体截止阀；119、气态冷媒集管；120、液态冷媒集管；121a、第一过滤器；121b、第二过滤器；121c、第三过滤器；121d、第四过滤器；122a、第一电子膨胀阀；122b、第二电子膨胀阀；122c、第三电子膨胀阀；122d、第四电子膨胀阀；123a、第一气管连接分支；123b、第二气管连接分支；123c、第三气管连接分支；123d、第四气管连接分支；124a、第一液管连接分支；124b、第二液管连接分支；124c、第三液管连接分支；124d、第四液管连接分支；125、排气温度传感器；126、室外换热器温度传 感器；127、除霜传感器；21、室内单元A；211、室内换热器；212、室内换热器风机；213、室内换热器温度传感器。
下面参照附图来描述本发明的优选实施方式。本领域技术人员应当理解的是，这些实施方式仅仅用于解释本发明的技术原理，并非旨在限制本发明的保护范围。
为了解决现有一拖多空调器出现低负荷下排气温度限频程序失效的技术问题，本发明提供一种一拖多空调器的压缩机频率的控制方法。一拖多空调器1包括可变频的压缩机，该控制方法包括：
检测所述一拖多空调器的实时开机负荷KF(步骤S1)；
基于实时开机负荷KF至少确定第一动态排气温度阈值和比第一动态排气阈值小的第二动态排气温度阈值(步骤S2)；
测量压缩机的实时排气温度T
d(步骤S3)；
将实时排气温度T
d分别与第一动态排气温度阈值和第二动态排气温度阈值进行比较(步骤S4)；
当实时排气温度T
d大于第一动态排气温度阈值时，压缩机停机持续第一预定时间段；并且当实时排气温度T
d小于等于第一动态排气温度阈值并大于第二动态排气温度阈值时，降低压缩机的频率(步骤S5)，
其中，第一动态排气温度阈值和第二动态排气温度阈值的变化方向与实时开机负荷KF的变化方向一致。
图1是本发明一拖多空调器的实施例的系统示意图。如图1所示，一拖多空调器1包括可互联成允许冷媒在其中流动的制冷回路的室外单元11(其一般被布置在室外环境中)和多个并联的室内单元21(其一般被布置在室内或房间内)。在一种或多种实施例中，一拖多空调器1具有四个并联的室内单元：室内单元A、室内单元B、室内单元C、和室内单元D。图1只示出室内单元A，即室内单元21，其余三个室内单元被省略。根据实际需要，四个室内单元的配置可以相同，也可以不相同。替代地，一拖多空调器1可以具有两个室内单元、三个室内单元或多于四个的室内单元。
如图1所示，在一种或多种实施例中，室外单元11主要包括压缩机111、气液分离器112、室外换热器113、室外换热器风机114、四通阀116、 和电子膨胀阀。由于四通阀116的存在，本发明一拖多空调器1至少具有制冷和制热功能。替代地，室外单元11可以不包括四通阀116，这意味着一拖多空调器不具有制热功能。在一种或多种实施例中，压缩机111为一台变频压缩机。替代地，压缩机111可包括两台或更多台并联的压缩机。这些压缩机可以全部是变频压缩机，也可以包括部分变频压缩机。压缩机111具有吸气口和排气口(图中未标注)。压缩机111的排气口通过冷媒管(即允许冷媒在其中流动的管道)连接到四通阀116上的压缩机连接端口。在靠近压缩机111的排气口的冷媒管上布置有测量压缩机111的排气温度的排气温度传感器125。压缩机111的吸气口通过冷媒管连接到气液分离器112上的出气口，而气液分离器112的进气口通过冷媒管连接到四通阀116上的气液分离器连接端口。四通阀116上还设有室外换热器连接端口和室内换热器连接端口。室外换热器113的一端通过冷媒管连接到四通阀116的室外换热器连接端口。室外换热器113可以是但不限于翅片盘管式换热器和板式换热器，并且配有室外换热器风机114。室外换热器113的另一端连接到分配器115。在室外换热器113上还分别设有室外换热器温度传感器126和除霜传感器127。
如图1所示，四通阀116的室内换热器连接端口通过冷媒管连接到气态冷媒集管119，并且在该冷媒管设有气体截止阀118。气态冷媒集管119设有四个气管连接分支：第一气管连接分支123a，其配置成可连接到室内单元A；第二气管连接分支123b，其配置成可连接到室内单元B；第三气管连接分支123c，其配置成可连接到室内单元C；第四气管连接分支123d，其配置成可连接到室内单元D。如图1所示，分配器115通过冷媒管连接到液态冷媒集管120，并且在该冷媒管上设有液体截止阀117。液态冷媒集管120设有四个液管连接分支：第一液管连接分支124a，其配置成可连接到室内单元A；第二液管连接分支124b，其配置成可连接到室内单元B；第三液管连接分支124c，其配置成可连接到室内单元C；第四液管连接分支124d，其配置成可连接到室内单元D。在第一液管连接分支124a上布置有第一过滤器121a和第一电子膨胀阀122a，其中，第一过滤器121a位于室内单元A与第一电子膨胀阀122a之间。在第二液管连接分支124b上布置有第二过滤器121b和第二电子膨胀阀122b，其中，第二过滤器121b位于室内单元B与第二电子膨胀阀122b之间。在第三液管连接分支124c上布置有第三过滤器121c和第三电子膨胀阀122c，其中，第三过滤器121c位于室内单元C与第三电子膨胀阀122c之间。 在第四液管连接分支124d上布置有第四过滤器121d和第四电子膨胀阀122d，其中，第四过滤器121d位于室内单元D与第四电子膨胀阀122d之间。
如图1所示，室内单元A21包括室内换热器211、室内换热器风机212、和测量室内换热器211的温度的室内换热器温度传感器213。室内换热器211包括但不限于翅片-管式换热器。室内换热器211的两端分别可连接到第一气管连接分支123a和第一液管连接分支124a。
借助四通阀116，一拖多空调器1可进行制冷和制热循环。在制冷循环中，室外换热器113充当冷凝器，而室内换热器211充当蒸发器。当一拖多空调器接收到制冷指令时，压缩机111开始启动，冷媒(例如R410a)被压缩机111压缩后以高温高压的气体形式经由四通阀116的相互连通的端口进入室外换热器113(其充当冷凝器)。在室外换热器113中，高温高压的气态冷媒通过向由室外换热器风机114所引起的空气流传递热量而被冷凝成高温高压的液态冷媒。高温高压的液态冷媒依次流过分配器115、液体截止阀117而进入液态冷媒集管120。然后，高温高压的液态冷媒分配到连接已开机室内单元的第一、第二、第三、和第四液管连接分支124a、124b、124c、124d中的一个或多个中，并被该一个或多个液管连接分支上的对应电子膨胀阀膨胀为低温低压的液态冷媒。该低温低压的液态冷媒然后分别流入已开机的室内单元的室内换热器中，例如室内换热器211。低温低压的液态冷媒通过吸收室内空气的热量而被蒸发成低温低压的气态冷媒，室内空气因此被冷却降温。低温低压的气态冷媒离开室内换热器211后再依次流过对应的气管连接分支、气管集管119、气体截止阀118、四通阀116，然后进入到气液分离器112中。经过气液分离的气态冷媒又被压缩机111通过吸气口吸入其中。一个完整的制冷循环得以完成，并且这样的制冷循环可不间断地进行，以便实现目标制冷温度。如图1中的箭头所示，在制热循环中，冷媒在室外单元11和室内单元21中的流向与制冷循环时的流向正好相反，并且室外换热器113充当蒸发器，而室内换热器211充当冷凝器。
压缩机111在工作时，其排气温度需要控制在适当的范围内，否则当排气温度超过一定的温度值，压缩机就容易发生保护性停机。因此，一拖多空调器都设有排气温度限频控制程序。为了避免低负荷下排气温度限频程序失效的技术问题，本发明的一拖多空调器的压缩机频率采用如下的控制方法。
图2是本发明一拖多空调器的压缩机频率的控制方法的流程图。如图2所示，该一拖多空调器的压缩机频率的控制方法在开始后，在步骤S1中检测一拖多空调器的实时开机负荷KF。例如，一拖多空调器具有四台室内机，并且四台室内机的负荷功率分别为2.5KW，2.5KW，3.5KW，和5.0KW。当只有3.5KW的室内机开机时，则一拖多空调器1的实时开机负荷KF为：KF＝3.5/(2.5+2.5+3.5+5.0)＝0.26*100％＝26％。当两台2.5KW的室内机开机时，则实时开机负荷KF为：KF＝(2.5+2.5)/(2.5+2.5+3.5+5)＝37％。因此，实时开机负荷KF是变化的。在步骤S2中，基于检测到的实时开机负荷KF，确定第一动态排气温度阈值和第二排气温度阈值，其中，第二动态排气温度阈值比第一动态排气温度阈值小。第一动态排气温度阈值和第二动态排气温度阈值分别使用如下公式(1)和(2)计算：
第一动态排气温度阈值＝第一基准温度+10KF，(1)
第二动态排气温度阈值＝第二基准温度+10KF，(2)
其中，KF为一拖多空调器的实时开机负荷，单位是％，第一基准温度大于第二基准温度并且都为常数。例如，第一基准温度为95℃，而第二基准温度为85℃。针对不同配置的一拖多空调器，该公式中的第一基准温度和第二基准温度常数都可能会发生变化，因此可能为其它合适的温度值，并且每个常数可通过实验确定。在步骤S3中，测量一拖多空调器的实时排气温度T
d。实时排气温度T
d通常在靠近压缩机排气口的位置处测得。在确定了第一动态排气温度阈值、第二动态排气温度阈值、和实时排气温度T
d后，控制方法前进到步骤S4，将实时排气温度T
d分别与第一动态排气温度阈值和第二动态排气温度阈值进行比较。在步骤S5中，当实时排气温度T
d大于第一动态排气温度阈值时，压缩机停机持续第一预定时间段；并且当实时排气温度T
d小于等于第一动态排气温度阈值并大于第二动态排气温度阈值时，降低压缩机的频率。第一预定时间段例如是1分钟、2分钟、其它合适的时间段。第一预定时间段可通过实验确定。该控制方法按照一定的时间间隔可重复地实施。
图3是本发明一拖多空调器的压缩机频率的控制方法的第一实施例的流程图。如图3所示，在该实施例中，控制方法在开始后检测一拖多空调器的实时开机负荷KF(步骤S1)。然后，控制方法前进到步骤S2a，基于实时开机负荷KF确定第一动态排气温度阈值、第二动态排气温度阈值、和第三动态排气温度阈值。第二动态排气温度阈值小于第一动态排气温度阈值并大 于第三动态排气温度阈值，并且第一动态排气温度阈值、第二动态排气温度阈值、和第三动态排气温度阈值的变化方向与实时开机负荷的变化方向一致。第一动态排气温度阈值和第二排气温度阈值可分别根据上述公式(1)和(2)进行确定。第三动态排气温度阈值根据如下的公式计算：
第三动态排气温度阈值＝第三基准温度+10KF，(3)
其中，KF为一拖多空调器的实时开机负荷，单位是％，第三基准温度小于上述的第一和第二基准温度并且也为常数。例如，第三基准温度为80℃或其它合适的温度值。针对不同配置的一拖多空调器，该公式中的第三基准温度可能会发生变化并且可通过实验确定。该控制方法在步骤S3中测量一拖多空调器的实时排气温度T
d。然后，控制方法前进到步骤S4a。在步骤S4a中，将实时排气温度T
d分别与第一动态排气温度阈值、第二动态排气温度阈值、和第三动态排气温度阈值进行比较。根据比较的结果对压缩机频率实施不同的控制措施，因此该控制方法前进到步骤S5a。
在步骤S5a中，对压缩机频率实施如下的控制措施。当实时排气温度T
d大于第一动态排气温度阈值时，压缩机停机持续第一预定时间段。第一预定时间段例如是1分钟、2分钟、或其它合适的时间段。当实时排气温度T
d小于等于第一动态排气温度阈值并大于第二动态排气温度阈值时，降低压缩机的频率，例如以0.8Hz/s、1Hz/s、2Hz/s、或其它合适的速度降低压缩机频率。当实时排气温度T
d小于等于第二动态排气温度阈值并大于第三动态排气温度阈值时，保持压缩机的频率不变。
图4是本发明一拖多空调器的压缩机频率的控制方法的第二实施例的流程图。如图4所示，在该实施例中，控制方法在开始后同样地检测一拖多空调器的实时开机负荷KF(步骤S1)。然后，控制方法前进到步骤S2b，基于实时开机负荷KF确定第一动态排气温度阈值、第二动态排气温度阈值、第三动态排气温度阈值、和第四动态排气温度阈值。第二动态排气温度阈值小于第一动态排气温度阈值并大于第三动态排气温度阈值，而第三动态排气温度阈值又大于第四动态排气温度阈值。第一动态排气温度阈值、第二动态排气温度阈值、第三动态排气温度阈值、和第四动态排气温度阈值每一个的变化方向都与实时开机负荷KF的变化方向一致。第一动态排气温度阈值、第二动态排气温度阈值、和第三动态排气温度阈值可分别根据上述公式(1)、(2)、和(3)进行确定。第四动态排气温度阈值根据如下的公式计算：
第四动态排气温度阈值＝第四基准温度+10KF，(4)
其中，KF为一拖多空调器的实时开机负荷，单位是％，第四基准温度小于上述的第四基准温度并且也为常数。例如，第四基准温度为75℃或其它合适的温度值。针对不同配置的一拖多空调器，该公式中的第四基准温度可能会发生变化并且可通过实验确定。该控制方法接着前进到步骤S3。在步骤S3中测量一拖多空调器的实时排气温度T
d。然后，该控制方法前进到步骤S4b。在步骤S4b中，将实时排气温度T
d分别与第一动态排气温度阈值、第二动态排气温度阈值、第三动态排气温度阈值、和第四动态排气温度阈值进行比较。根据比较的结果对压缩机频率实施不同的控制措施，因此该控制方法前进到步骤S5b。
在步骤S5b中，对压缩机频率实施如下的控制措施。当实时排气温度T
d大于第一动态排气温度阈值时，压缩机停机持续第一预定时间段。第一预定时间段例如是1分钟、2分钟、或其它合适的时间段。当实时排气温度T
d小于等于第一动态排气温度阈值并大于第二动态排气温度阈值时，降低压缩机的频率，例如以0.8Hz/s、1Hz/s、2Hz/s、或其它合适的速度降低压缩机频率。当实时排气温度T
d小于等于第二动态排气温度阈值并大于第三动态排气温度阈值时，保持压缩机的频率不变。当实时排气温度T
d小于等于第三动态排气温度阈值并大于第四动态排气温度阈值时，一拖多空调器进入压缩机频率自动控制模式，即一拖多空调器基于室内制冷/制热需求进入压缩机频率自动控制。
图5是本发明一拖多空调器的压缩机频率的控制方法的第三实施例的流程图的第一部分，而图6是本发明一拖多空调器的压缩机频率的控制方法的第、三实施例的流程图的第二部分。如图5所示，在该实施例中，控制方法在开始后同样地先检测一拖多空调器的实时开机负荷KF(步骤S1)。然后，控制方法前进到步骤S2c。在步骤S2c中，基于实时开机负荷KF确定第一动态排气温度阈值T
t1、第二附加动态排气温度阈值T
t2、第二动态排气温度阈值T
t3、第三动态排气温度阈值T
t4、和第四动态排气温度阈值T
t5。第一动态排气温度阈值T
t1、第二附加动态排气温度阈值T
t2、第二动态排气温度阈值T
t3、第三动态排气温度阈值T
t4、和第四动态排气温度阈值T
t5的大小顺序为：
T
t1>T
t2>T
t3>T
t4>T
t5，
第一动态排气温度阈值、第二附加动态排气温度阈值、第二动态排气温度阈值、第三动态排气温度阈值、和第四动态排气温度阈值每一个的变化方向都与实时开机负荷KF的变化方向一致。第一动态排气温度阈值、第二动态排气温度阈值、第三动态排气温度阈值、和第四动态排气温度阈值可分别根据上述公式(1)、(2)、(3)、和(4)进行确定。第二附加动态排气温度阈值根据如下的公式计算：
第二附加动态排气温度阈值＝第二附加基准温度+10KF，(5)
其中，KF为一拖多空调器的实时开机负荷，单位是％，第二附加基准温度为小于上述第一基准温度并大于第二基准温度的常数。例如，第二附加基准温度为90℃或其它合适的温度值。针对不同配置的一拖多空调器，该公式中的第二附加基准温度可能会发生变化并且可通过实验确定。该控制方法接着前进到步骤S3。在步骤S3中测量一拖多空调器的实时排气温度T
d。然后控制方法前进到步骤S41。
如图5所示，在步骤S41中，将实时排气温度T
d与第一动态排气温度阈值T
t1进行比较。如果实时排气温度T
d小于等于第一动态排气温度阈值T
t1，控制方法就前进到步骤S42。如果实时排气温度T
d大于第一动态排气温度阈值T
t1，控制方法就前进到步骤S51，将压缩机停机。压缩机停机后经过第一预定时间段，例如2分钟或其它合适的时间段，控制方法前进到到步骤61，重启压缩机，并重新测量实时排气温度T
d。然后，控制方法前进到步骤S71，将当前得到的T
d与第一动态排气温度阈值T
t1进行比较。如果当前得到的T
d小于等于第一动态排气温度阈值T
t1，控制方法就前进到步骤S42。如果当前得到的T
d仍然大于第一动态排气温度阈值T
t1，控制方法就前进到步骤S81，再次将压缩机停机并持续比第一预定时间段长的第二预定时间段，例如3分钟或其它合适的时间段。在经过第二预定时间段后，控制方法前进到步骤S91，判断在第三预定时间段(例如1小时或其它合适的时间)内压缩机的重启次数是否小于预定次数，例如3次。第三预定时间段要长于第二预定时间段。如果压缩机的重启次数已经达到预定次数，则该控制方法就前进到步骤S121，发出故障警报，提示一拖多空调器存在高频排气故障。如果压缩机的重启次数少于预定次数，控制方法就前进到步骤S101，重启压缩机，然后以预设的低频将压缩机运转第四预定时间段，例如3分钟或其它合适的时 间段(步骤S111)。压缩机低频运行持续第四预定时间段后，控制方法返回到步骤S1。
如图5所示，如果实时排气温度T
d小于等于第一动态排气温度阈值T
t1，控制方法就前进到步骤S42。在步骤S42中，将实时排气温度T
d与第二附加动态排气温度阈值T
t2进行比较。如果实时排气温度T
d小于等于第二附加动态排气温度阈值T
t2，控制方法就前进到步骤S43。如果实时排气温度T
d大于第二附加动态排气温度阈值T
t2，控制方法就前进到步骤S52，以较高的速度降低压缩机的频率，例如以2Hz/s的速度降低压缩机的频率。在压缩机降频经过第五预定时间段，例如10秒、20秒、或其它合适的时间段后，控制方法就前进到步骤S62，重新测量实时排气温度T
d。然后，控制方法前进到步骤S72，将当前得到的T
d与第二附加动态排气温度阈值T
t2进行比较。如果当前得到的T
d小于等于第二附加动态排气温度阈值T
t2，控制方法就前进到步骤S43。如果当前得到的T
d仍然大于第二附加动态排气温度阈值T
t2，控制方法就返回到步骤S52，重新实施降频措施。
如图6所示，如果实时排气温度T
d小于等于第二附加动态排气温度阈值T
t2，控制方法就前进到步骤S43。在步骤S43中，将实时排气温度T
d与第二动态排气温度阈值T
t3进行比较。如果实时排气温度T
d小于等于第二动态排气温度阈值T
t3，控制方法就前进到步骤S44。如果实时排气温度T
d大于第二动态排气温度阈值T
t3，控制方法就前进到步骤S53。在步骤S53中，以较低的速度降低压缩机的频率，例如以1Hz/s的速度降低压缩机的频率。在压缩机降频经过第五预定时间段，例如10秒、20秒、或其它合适的时间段后，控制方法就前进到步骤S63，重新测量实时排气温度T
d。然后，控制方法前进到步骤S73，将当前得到的T
d与第二动态排气温度阈值T
t3进行比较。如果当前得到的T
d小于等于第二附加动态排气温度阈值T
t2，控制方法就前进到步骤S44。如果当前得到的T
d仍然大于第二动态排气温度阈值T
t3，控制方法就返回到步骤S53，重新实施降频措施。
如图6所示，如果实时排气温度T
d小于等于第二动态排气温度阈值T
t3，控制方法就前进到步骤S44。在步骤S44中，将实时排气温度T
d与第三动态排气温度阈值T
t4进行比较。如果实时排气温度T
d小于等于第三动态排气温度阈值T
t4，控制方法就前进到步骤S45。如果实时排气温度T
d大于第三动态排气温度阈值T
t4，控制方法就前进到步骤S54，保持压缩机的频率不变。
如图6所示，如果实时排气温度T
d小于等于第三动态排气温度阈值T
t4，控制方法就前进到步骤S45。在步骤S45中，将实时排气温度T
d与第四动态排气温度阈值T
t5进行比较。如果实时排气温度T
d大于第四动态排气温度阈值T
t5，控制方法就前进到步骤S56，一拖多空调器进入正常控制模式，即基于室内制冷/制热需求进入压缩机频率自动控制。如果实时排气温度T
d小于等于第四动态排气温度阈值T
t5，控制方法就前进到步骤S55。在步骤S55中，以预定的速度升高压缩机的频率，例如以1Hz/s或其它合适的速度降低压缩机的频率。在压缩机升频经过第六预定时间段，例如10秒、20秒、或其它合适的时间段后，控制方法就前进到步骤S65，重新测量实时排气温度T
d。然后，控制方法前进到步骤S75，将当前得到的T
d与第四动态排气温度阈值T
t5进行比较。如果当前得到的T
d大于第四动态排气温度阈值T
t5，控制方法就前进到步骤S56，一拖多空调器进入正常控制模式。如果当前得到的T
d仍然小于等于第四动态排气温度阈值T
t3，控制方法就返回到步骤S55，重新实施升频措施。
至此，已经结合附图所示的优选实施方式描述了本发明的技术方案，但是，本领域技术人员容易理解的是，本发明的保护范围显然不局限于这些具体实施方式。在不偏离本发明的原理的前提下，本领域技术人员可以对相关技术特征作出等同的更改或替换，这些更改或替换之后的技术方案都将落入本发明的保护范围之内。
Claims (10)
- 一种一拖多空调器的压缩机频率的控制方法，其特征在于，所述一拖多空调器包括可变频的压缩机，并且所述控制方法包括：检测所述一拖多空调器的实时开机负荷KF；基于所述实时开机负荷KF至少确定第一动态排气温度阈值和比第一动态排气阈值小的第二动态排气温度阈值；测量所述压缩机的实时排气温度T d；将所述实时排气温度T d分别与所述第一动态排气温度阈值和第二动态排气温度阈值进行比较；当所述实时排气温度T d大于所述第一动态排气温度阈值时，所述压缩机停机持续第一预定时间段；并且当所述实时排气温度T d小于等于所述第一动态排气温度阈值并大于所述第二动态排气温度阈值时，降低所述压缩机的频率，其中，所述第一动态排气温度阈值和第二动态排气温度阈值的变化方向与所述实时开机负荷KF的变化方向一致。
- 根据权利要求1所述的一拖多空调器的压缩机频率的控制方法，其特征在于，所述控制方法还包括：基于所述实时开机负荷KF确定第三动态排气温度阈值，所述第三动态排气温度阈值小于所述第二动态排气温度阈值；将所述实时排气温度T d与所述第三动态排气温度阈值进行比较；当所述实时排气温度T d大于所述第三动态排气温度阈值并且小于等于所述第二动态排气温度阈值时，保持所述压缩机的频率不变，其中，所述第三动态排气温度阈值的变化方向与所述实时开机负荷KF的变化方向一致。
- 根据权利要求2所述的一拖多空调器的压缩机频率的控制方法，其特征在于，所述控制方法还包括：基于所述实时开机负荷KF确定第四动态排气温度阈值，所述第四动态排气温度阈值小于所述第三动态排气温度阈值；将所述实时排气温度T d与所述第四动态排气温度阈值进行比较；当所述实时排气温度T d大于所述第四动态排气温度阈值并小于等于第三动态排气温度阈值时，所述一拖多空调器进入压缩机频率自动控制模式；并且当所述实时排气温度T d小于等于第四动态排气温度阈值时，升高所述压缩机的频率，其中，所述第四动态排气温度阈值的变化方向与所述实时开机负荷KF的变化方向一致。
- 根据权利要求3所述的一拖多空调器的压缩机频率的控制方法，其特征在于，所述控制方法还包括：基于所述实时开机负荷KF确定第二附加动态排气温度阈值，所述第二附加动态排气温度阈值小于等于所述第一动态排气温度阈值并大于所述第二动态排气温度阈值；将所述实时排气温度T d与所述第二附加动态排气温度阈值进行比较；当所述实时排气温度T d大于所述第二附加动态排气温度阈值并小于等于第一动态排气温度阈值时，以较快速度降低所述压缩机的频率；并且当所述实时排气温度T d大于所述第二动态排气温度阈值并小于等于所述第二附加动态排气温度阈值时，以较慢速度降低所述压缩机的频率，其中，所述第二附加动态排气温度阈值的变化方向与所述实时开机负荷KF的变化方向一致。
- 根据权利要求1-4任一项所述的一拖多空调器的压缩机频率的控制方法，其特征在于，当所述压缩机停机持续第一预定时间段后，压缩机重启并重新测量所述实时排气温度T d，并且将当前的所述实时排气温度T d与所述第一动态排气温度阈值进行比较，如果所述实时排气温度T d大于所述第一动态排气温度阈值，所述压缩机停机持续第二预定时间段，所述第二预定时间段大于所述第一预定时间段。
- 根据权利要求5所述的一拖多空调器的压缩机频率的控制方法，其特征在于，当所述压缩机停机持续第二预定时间段后，所述控制方法还包括：判断所述压缩机在第三预定时间段内的重启次数是否小于预定次数，所述预定次数≧3；如果所述重启次数小于预定次数，重启所述压缩机并且以低频运行所述压缩机持续第四预定时间段；如果所述重启次数达到所述预定次数，发出高频排气故障警报，其中，所述第二预定时间段大于所述第一预定时间段并小于所述第三预定时间段。
- 根据权利要求1所述的一拖多空调器的压缩机频率的控制方法，其特征在于，在降低所述压缩机的频率后，经过第五预定时间段，重新测量所述实时排气温度Td，并且将当前的所述实时排气温度T d与所述第二动态排气温度阈值进行比较，如果所述实时排气温度T d大于所述第二动态排气温度阈值，重复降低所述压缩机的频率的步骤。
- 根据权利要求3所述的一拖多空调器的压缩机频率的控制方法，其特征在于，在升高所述压缩机的频率后，经过第六预定时间段，重新测量所述实时排气温度Td，并且将当前的所述实时排气温度T d与所述第四动态排气温度阈值进行比较，如果所述实时排气温度T d小于等于所述第四动态排气温度阈值，重复升高所述压缩机的频率的步骤。
- 根据权利要求4所述的一拖多空调器的压缩机频率的控制方法，其特征在于，第一动态排气温度阈值、第二附加动态排气温度阈值、第二动态排气温度阈值、第三动态排气温度阈值、和第四动态排气温度阈值分别基于如下公式计算：第一动态排气温度阈值＝第一基准温度+10KF(1)，第二动态排气温度阈值＝第二基准温度+10KF(2)，第三动态排气温度阈值＝第三基准温度+10KF(3)，第四动态排气温度阈值＝第四基准温度+10KF(4)，第二附加动态排气温度阈值＝第二附加基准温度+10KF(5)，其中，KF是一拖多空调器的实时开机负荷，单位为％，第一基准温度>第二附加基准温度>第二基准温度>第三基准温度>第四基准温度，并且都为常数。
- 一种一拖多空调器，其特征在于，所述一拖多空调器包括可变频的压缩机，并且所述一拖多空调器使用根据权利要求1-9任一项所述的控制方法控制所述压缩机的频率。
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| CN107940694A (zh) * | 2017-11-16 | 2018-04-20 | 珠海格力电器股份有限公司 | 一种空调器的排气保护控制方法及系统 |
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| CN107036256B (zh) * | 2017-05-31 | 2019-06-11 | 广东美的制冷设备有限公司 | 排气温度的控制方法、排气温度的控制装置和空调器 |
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| CN110410972A (zh) * | 2019-07-25 | 2019-11-05 | 宁波奥克斯电气股份有限公司 | 一种空调器排气温度的控制方法、装置以及空调器 |
| CN111023270A (zh) * | 2019-12-31 | 2020-04-17 | 宁波奥克斯电气股份有限公司 | 一种电子膨胀阀的控制方法、装置、空调器及存储介质 |
| CN111380185B (zh) * | 2020-03-27 | 2021-10-26 | 广东美的制冷设备有限公司 | 压缩机排气温度限频控制方法、空调器及可读存储介质 |
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| CN113137715A (zh) * | 2021-03-16 | 2021-07-20 | 青岛海尔空调电子有限公司 | 一拖多空调器的压缩机频率的控制方法及一拖多空调器 |
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