WO2017152444A1 - 空调器及其压缩机的停机控制方法和装置 - Google Patents

空调器及其压缩机的停机控制方法和装置 Download PDF

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Publication number
WO2017152444A1
WO2017152444A1 PCT/CN2016/078284 CN2016078284W WO2017152444A1 WO 2017152444 A1 WO2017152444 A1 WO 2017152444A1 CN 2016078284 W CN2016078284 W CN 2016078284W WO 2017152444 A1 WO2017152444 A1 WO 2017152444A1
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WIPO (PCT)
Prior art keywords
compressor
rotor
phase
air conditioner
shutdown
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/CN2016/078284
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English (en)
French (fr)
Inventor
黄招彬
张国柱
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
GD Midea Air Conditioning Equipment Co Ltd
Original Assignee
GD Midea Air Conditioning Equipment Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by GD Midea Air Conditioning Equipment Co Ltd filed Critical GD Midea Air Conditioning Equipment Co Ltd
Priority to PL16888598T priority Critical patent/PL3258182T3/pl
Priority to EP16888598.6A priority patent/EP3258182B1/en
Priority to BR112017017679-3A priority patent/BR112017017679B1/pt
Priority to ES16888598T priority patent/ES2866047T3/es
Priority to HRP20210666TT priority patent/HRP20210666T1/hr
Publication of WO2017152444A1 publication Critical patent/WO2017152444A1/zh
Priority to US15/910,923 priority patent/US10677241B2/en
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/02—Stopping, starting, unloading or idling control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/06—Control using electricity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/06—Control using electricity
    • F04B49/065—Control using electricity and making use of computers
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/30—Control or safety arrangements for purposes related to the operation of the system, e.g. for safety or monitoring
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/70—Control systems characterised by their outputs; Constructional details thereof
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02P—CONTROL OR REGULATION OF ELECTRIC MOTORS, ELECTRIC GENERATORS OR DYNAMO-ELECTRIC CONVERTERS; CONTROLLING TRANSFORMERS, REACTORS OR CHOKE COILS
    • H02P5/00—Arrangements specially adapted for regulating or controlling the speed or torque of two or more electric motors
    • H02P5/46—Arrangements specially adapted for regulating or controlling the speed or torque of two or more electric motors for speed regulation of two or more dynamo-electric motors in relation to one another
    • H02P5/50—Arrangements specially adapted for regulating or controlling the speed or torque of two or more electric motors for speed regulation of two or more dynamo-electric motors in relation to one another by comparing electrical values representing the speeds
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02P—CONTROL OR REGULATION OF ELECTRIC MOTORS, ELECTRIC GENERATORS OR DYNAMO-ELECTRIC CONVERTERS; CONTROLLING TRANSFORMERS, REACTORS OR CHOKE COILS
    • H02P5/00—Arrangements specially adapted for regulating or controlling the speed or torque of two or more electric motors
    • H02P5/46—Arrangements specially adapted for regulating or controlling the speed or torque of two or more electric motors for speed regulation of two or more dynamo-electric motors in relation to one another
    • H02P5/52—Arrangements specially adapted for regulating or controlling the speed or torque of two or more electric motors for speed regulation of two or more dynamo-electric motors in relation to one another additionally providing control of relative angular displacement
    • H02P5/56—Speed and position comparison between the motors by electrical means
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02P—CONTROL OR REGULATION OF ELECTRIC MOTORS, ELECTRIC GENERATORS OR DYNAMO-ELECTRIC CONVERTERS; CONTROLLING TRANSFORMERS, REACTORS OR CHOKE COILS
    • H02P6/00—Arrangements for controlling synchronous motors or other dynamo-electric motors using electronic commutation dependent on the rotor position; Electronic commutators therefor
    • H02P6/24—Arrangements for stopping
    • 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
    • F24F2140/50—Load

Definitions

  • the invention relates to the technical field of air conditioners, in particular to a shutdown control method for a compressor in an air conditioner, a shutdown control device for a compressor in an air conditioner, and an air conditioner having the same.
  • the refrigerant pressure and load are high during high-frequency operation. If the compressor is stopped directly, the refrigerant pressure and load energy will be released instantaneously, resulting in excessive vibration and stress of the piping, and even the danger of piping failure. .
  • the downsizing method is generally used to control the compressor stop, that is, the compressor is controlled to reduce the frequency of the compressor to the low frequency, and then the compressor operation is stopped to reduce the vibration and stress of the piping at the time of the stop, but the disadvantage is that At the moment when the compressor of the inverter air conditioner stops, there may still be large piping vibration and stress.
  • an object of the present invention is to provide a shutdown control method for a compressor in an air conditioner, which can effectively reduce piping vibration and stress at the moment of compressor stop.
  • Another object of the present invention is to provide a shutdown control device for a compressor in an air conditioner. Still another object of the present invention is to provide an air conditioner.
  • an embodiment of the present invention provides a method for controlling a shutdown of a compressor in an air conditioner, comprising the steps of: obtaining a rotor phase with a minimum load of the compressor; and acquiring an Determining the rotor position of the compressor, and determining, according to the rotor position of the compressor, whether the rotor of the compressor is at a rotor phase with a minimum load of the compressor; if it is determined that the rotor of the compressor is at a minimum load of the compressor The rotor phase controls the compressor to stop operating.
  • a method for controlling the shutdown of a compressor in an air conditioner in the process of stopping the air conditioner, acquiring the rotor position of the compressor, and controlling the compressor at a rotor phase in which the rotor of the compressor is at a minimum load of the compressor The operation is stopped, so that the generated pipe vibration and stress are small, thereby effectively reducing the vibration and stress of the pipe at the moment of stopping the compressor, thereby preventing the risk of pipe breakage.
  • the minimum rotor phase of the compressor load is the rotor position at which the compressor ends the exhaust in one mechanical cycle.
  • the rotor phase is minimized according to the compressor load and the rotor of the compressor The difference between the mechanical zero phases and by identifying the mechanical zero phase of the rotor of the compressor to obtain the rotor phase with the smallest compressor load.
  • the rotor phase with the smallest compressor load is obtained by acquiring the minimum value of the torque current amplitude of the compressor or by obtaining the minimum value of the torque compensation amplitude of the compressor .
  • a shutdown control device for a compressor in an air conditioner comprising: an acquisition module for acquiring a rotor phase with a minimum load of the compressor; and a rotor position acquisition module for Obtaining a rotor position of the compressor during a shutdown of the air conditioner; and a control module configured to determine, according to a rotor position of the compressor, whether the rotor of the compressor is at a rotor phase with a minimum load of the compressor, and The compressor is controlled to stop operating when it is determined that the rotor of the compressor is at a rotor phase with a minimum compressor load.
  • a shutdown control device for a compressor in an air conditioner obtains a rotor position of a compressor during a shutdown process of the air conditioner by a rotor position acquisition module, and the control module is at a rotor with a minimum compressor load at a rotor of the compressor
  • the compressor is controlled to stop running, so that the generated pipe vibration and stress are small, thereby effectively reducing the vibration and stress of the pipe at the moment of stopping the compressor, thereby preventing the risk of pipe breakage.
  • the minimum rotor phase of the compressor load is the rotor position at which the compressor ends the exhaust in one mechanical cycle.
  • the acquisition module is based on a difference between a rotor phase having a minimum compressor load and a mechanical zero phase of a rotor of the compressor, and by a mechanism identifying a rotor of the compressor Zero phase to obtain the rotor phase with the smallest compressor load.
  • the acquisition module acquires the compressor load by acquiring a minimum value of a torque current amplitude of the compressor or by acquiring a minimum value of a torque compensation amplitude of the compressor Minimum rotor phase.
  • an embodiment of the present invention provides an air conditioner including a shutdown control device for a compressor in the air conditioner.
  • the vibration and stress of the piping at the moment of stopping the compressor can be effectively reduced by the shutdown control device of the compressor, and the danger of the pipe breaking is prevented.
  • another embodiment of the present invention provides another method for controlling the shutdown of a compressor in an air conditioner, comprising the steps of: acquiring a preset compressor shutdown phase interval; during the shutdown of the air conditioner, acquiring the Determining the rotor position of the compressor, and determining whether the rotor of the compressor is in the preset compressor shutdown phase interval according to the rotor position of the compressor; if it is determined that the rotor of the compressor is in the preset compressor The shutdown phase interval controls the compressor to stop running to reduce the vibration and stress of the piping.
  • a shutdown control method for a compressor in an air conditioner obtains a rotor position of the compressor during a shutdown of the air conditioner, and controls the compressor when the rotor of the compressor is in a preset compressor shutdown phase interval stop The operation is stopped, so that the generated pipe vibration and stress are small, thereby effectively reducing the vibration and stress of the pipe at the moment of stopping the compressor, thereby preventing the risk of pipe breakage.
  • the preset compressor shutdown phase interval is obtained according to an experimental test and stored in the air conditioner for retrieval.
  • the preset compressor shutdown phase interval is preset according to a rotor phase with a minimum compressor load.
  • another embodiment of the present invention provides another shutdown control device for a compressor in an air conditioner, comprising: an acquisition module for acquiring a preset compressor shutdown phase interval; and a rotor position acquisition module for Obtaining a rotor position of the compressor during a shutdown of the air conditioner; and a control module, configured to determine, according to a rotor position of the compressor, whether the rotor of the compressor is in the preset compressor shutdown phase interval, and When it is determined that the rotor of the compressor is in the preset compressor shutdown phase interval, the compressor is controlled to stop running to reduce vibration and stress of the piping.
  • a shutdown control device for a compressor in an air conditioner acquires a rotor position of a compressor during a shutdown process of the air conditioner by a rotor position acquisition module, and the control module is at a preset compressor shutdown phase at a rotor of the compressor In the interval, the compressor is controlled to stop running, so that the generated piping vibration and stress are small, thereby effectively reducing the vibration and stress of the piping at the moment of stopping the compressor, thereby preventing the risk of piping being broken.
  • the preset compressor shutdown phase interval is obtained according to an experimental test and stored in the air conditioner for retrieval.
  • the preset compressor shutdown phase interval is preset according to a rotor phase with a minimum compressor load.
  • still another embodiment of the present invention proposes another air conditioner including the shutdown control device for the compressor in the air conditioner.
  • the vibration and stress of the piping at the moment of stopping the compressor can be effectively reduced by the shutdown control device of the compressor, and the danger of the pipe breaking is prevented.
  • FIG. 1 is a flow chart of a method for controlling shutdown of a compressor in an air conditioner according to an embodiment of the present invention
  • FIG. 2 is a flow chart showing a method of controlling a shutdown of a compressor in an air conditioner according to another embodiment of the present invention
  • FIG. 3 is a flow chart of a method for controlling shutdown of a compressor in an air conditioner according to still another embodiment of the present invention
  • FIG. 4 is a schematic diagram of a load characteristic curve when the compressor is operated at 60 Hz;
  • FIG. 5 is a schematic diagram showing waveforms of a compressor phase current and a U-phase driving signal in a first shutdown process in the related art
  • FIG. 6 is a waveform diagram of a compressor phase current and a U-phase driving signal in a second shutdown process in the related art
  • FIG. 7 is a waveform diagram of a compressor phase current and a U-phase driving signal in a third shutdown process in the related art
  • FIG. 8 is a waveform diagram of a compressor phase current and a U-phase driving signal in a fourth shutdown process in the related art
  • FIG. 9 is a schematic diagram showing waveforms of a compressor phase current and a U-phase driving signal in a fifth shutdown process in the related art
  • FIG. 10 is a waveform diagram of a compressor phase current and a U-phase driving signal during a first shutdown process according to an embodiment of the present invention
  • FIG. 11 is a schematic diagram showing waveforms of a compressor phase current and a U-phase driving signal during a first shutdown process according to two embodiments of the present invention
  • FIG. 12 is a waveform diagram of a compressor phase current and a U-phase driving signal during a first shutdown process according to three embodiments of the present invention.
  • FIG. 13 is a waveform diagram of a compressor phase current and a U-phase driving signal during a first shutdown process in accordance with four embodiments of the present invention
  • Figure 14 is a block diagram showing a shutdown control device for a compressor in an air conditioner according to an embodiment of the present invention.
  • Figure 15 is a block diagram showing a shutdown control device for a compressor in an air conditioner according to another embodiment of the present invention.
  • Figure 16 is a block schematic diagram of a shutdown control device for a compressor in an air conditioner according to still another embodiment of the present invention.
  • the compressor may preferably be a single rotor compressor.
  • FIG. 1 is a flow chart of a method of controlling a shutdown of a compressor in an air conditioner according to an embodiment of the present invention. As shown in FIG. 1, the shutdown control method of the compressor in the air conditioner includes the following steps:
  • the rotor phase with the smallest compressor load is the rotor position of the compressor at the end of one intake and exhaust, i.e., the rotor position at the end of the exhaust of the compressor during one mechanical cycle.
  • the low temperature and low pressure refrigerant enters the suction pipe of the compressor from the condenser, is gradually compressed into a high temperature and high pressure refrigerant, and is quickly released to the exhaust port of the compressor to the compressor.
  • the load pressure of the compressor is minimized after the refrigerant is released. Therefore, the rotor phase with the smallest compressor load is the compressor rotor phase after the refrigerant is released, that is, at the end of the exhaust.
  • the rotor phase can be based on the compressor load and the rotor of the compressor
  • the difference between the zero phases and the rotor phase of the compressor load can be obtained by identifying the mechanical zero phase of the rotor of the compressor.
  • the rotor phase at which the compressor load is minimized may be obtained by obtaining a minimum value of the torque current magnitude of the compressor or by obtaining a minimum value of the torque compensation amplitude of the compressor.
  • the torque compensation technology may be used to torque compensate the compressor to reduce the vibration of the piping during operation.
  • the torque compensation amplitude varies with the refrigerant pressure and load cycle. When the refrigerant pressure and load are minimum, the corresponding torque compensation amplitude is also the smallest. At this time, the rotor of the compressor is considered to be at the minimum load. Rotor phase.
  • the rotor phase with the smallest compressor load can be obtained directly from the rotor position calibration of the compressor design, or it can be obtained indirectly from variables such as the torque current amplitude or the torque compensation amplitude of the compressor.
  • the phase difference of the mechanical zero phase of the rotor due to the minimum load phase of the rotor is known, and therefore, by identifying the mechanical zero phase of the rotor of the compressor, the rotor phase with the smallest compressor load can be obtained.
  • the minimum phase of the torque current amplitude or the minimum phase of the torque compensation amplitude is the compressor rotor phase with the smallest load, therefore, by obtaining the minimum value or torque of the torque current amplitude By compensating for the minimum value of the amplitude, the rotor phase with the smallest compressor load can be obtained.
  • the rotor position of the compressor can be obtained by two methods: one is directly measured by a sensor; and the other is obtained by detecting the current of the compressor and calculating the current according to the compressor.
  • the compressor is controlled to continue to operate.
  • the compressor is stopped at the rotor phase where the compressor load is the smallest.
  • the compressor pressure especially the single-rotor compressor, periodically changes in the refrigerant compression cycle during a refrigerant compression cycle.
  • the refrigerant pressure is also relatively small near the rotor phase where the compressor load is minimal. Thus, stopping the compressor at the rotor phase where the compressor load is the smallest will cause the piping to vibrate and stress less.
  • the control module of the air conditioner issues a compressor shutdown signal
  • the control module starts to control the compressor shutdown, and when the air conditioner, that is, the compressor is stopped, acquires the rotor position of the compressor, if the rotor of the compressor is at the compressor
  • the rotor phase with the least load controls the compressor to stop running immediately; otherwise, if the rotor of the compressor is not at the rotor phase with the smallest compressor load, the compressor is controlled to continue running until the compressor rotor is at the compressor load
  • the minimum rotor phase then controls the compressor to stop running.
  • the rotor position of the compressor is obtained, and the rotor phase of the compressor is at the rotor phase with the minimum compressor load.
  • the compressor is controlled to stop running, so that the generated pipe vibration and stress are small, thereby effectively reducing the vibration and stress of the pipe at the moment of stopping the compressor, thereby preventing the risk of pipe breakage.
  • the shutdown control method of the compressor in the air conditioner includes the following steps:
  • the preset compressor shutdown phase interval can be obtained from experimental tests and stored in an air conditioner for retrieval. Also, in accordance with an embodiment of the present invention, the preset compressor shutdown phase interval may be preset based on the rotor phase with the smallest compressor load.
  • the compressor in the air conditioner can be experimentally tested to determine the rotor phase with the smallest compressor load, and then the rotor phase with the smallest compressor load can be floated up by the first preset threshold and floated downward by the second preset.
  • the threshold value is used as the preset compressor shutdown phase interval, and the preset compressor shutdown phase interval can also be regarded as the rotor phase interval with a smaller compressor load. For example, as shown in FIG. 2, assuming that the compressor load at point A is detected to be the smallest, the rotor phase of point A can be obtained as the rotor phase P with the smallest compressor load, and then the rotor phase of the compressor load is minimized.
  • the threshold L1 is floated upward, and the rotor phase P having the smallest compressor load is floated downward by the threshold L2, thereby presetting the compressor stop phase interval [P-L2, P+L1].
  • the preset compressor shutdown phase interval may be [170°, 190°], and may further preferably be [175°, 185°].
  • the rotor phase with the smallest compressor load is the rotor position of the compressor at the end of one intake and exhaust, that is, the rotor position at the end of exhaust of the compressor in one mechanical cycle.
  • the low temperature and low pressure refrigerant enters the suction pipe of the compressor from the condenser, is gradually compressed into a high temperature and high pressure refrigerant, and is quickly released to the exhaust port of the compressor to the compressor.
  • the load pressure of the compressor is minimized after the refrigerant is released. Therefore, the rotor phase with the smallest compressor load is the compressor rotor phase after the refrigerant is released, that is, at the end of the exhaust.
  • the difference between the rotor phase of the compressor load and the mechanical zero phase of the rotor of the compressor can be obtained, and can be obtained by identifying the mechanical zero phase of the rotor of the compressor.
  • the rotor phase with the smallest compressor load may be obtained by obtaining a minimum value of the torque current magnitude of the compressor or by obtaining a minimum value of the torque compensation amplitude of the compressor.
  • the torque compensation technology may be used to torque compensate the compressor to reduce the vibration of the piping during operation.
  • the torque compensation amplitude varies with the refrigerant pressure and load cycle.
  • the corresponding torque compensation amplitude is also the smallest, that is, the rotor of the compressor is considered to be at the minimum load phase. .
  • the rotor phase with the smallest compressor load can be obtained directly from the rotor position calibration of the compressor design, or it can be obtained indirectly from variables such as the torque current amplitude or the torque compensation amplitude of the compressor.
  • the phase difference of the mechanical zero phase of the rotor due to the minimum load phase of the rotor is known, and therefore, by identifying the mechanical zero phase of the rotor of the compressor, the rotor phase with the smallest compressor load can be obtained.
  • the minimum phase of the torque current amplitude or the minimum phase of the torque compensation amplitude is the compressor rotor phase with the smallest load, therefore, by obtaining the minimum value or torque of the torque current amplitude By compensating for the minimum value of the amplitude, the rotor phase with the smallest compressor load can be obtained.
  • S20 During the shutdown of the air conditioner, obtain the rotor position of the compressor, and determine whether the rotor of the compressor is in the preset compressor shutdown phase interval according to the rotor position of the compressor.
  • the rotor position of the compressor can be obtained by two methods: one is directly measured by a sensor; and the other is obtained by detecting the current of the compressor and calculating the current according to the compressor.
  • the compressor is controlled to continue to operate.
  • the compressor is stopped when the rotor of the compressor is in the preset compressor shutdown phase interval.
  • the compressor pressure especially the single-rotor compressor, periodically changes in the refrigerant compression cycle during a refrigerant compression cycle.
  • the refrigerant pressure is also relatively small near the rotor phase where the compressor load is minimal. Therefore, the preset compressor shutdown phase interval is set according to the upper and lower floating sections of the rotor phase with the smallest compressor load, and the compressor is stopped when the rotor of the compressor is in the preset compressor shutdown phase interval, which will cause the vibration of the piping and The stress is small.
  • the control module of the air conditioner issues a compressor shutdown signal
  • the control module starts to control the compressor shutdown, and the rotor position of the compressor is obtained in real time during the air conditioner, that is, during the compressor shutdown, if the rotor of the compressor is in advance Set the compressor stop phase interval, then control the compressor to stop running immediately; otherwise, if the rotor of the compressor is not in the preset compressor stop phase interval, then control the compressor to continue running until the compressor rotor is at the preset compressor stop The phase interval then controls the compressor to stop running.
  • the shutdown control method of the compressor in the air conditioner according to the embodiment of the present invention is stopped in the air conditioner
  • the rotor position of the compressor is obtained in the process, and when the rotor of the compressor is in the preset compressor stop phase interval, the compressor is stopped, so that the generated pipe vibration and stress are small, thereby effectively reducing the compressor stop instant.
  • the vibration and stress of the piping prevent the risk of piping breakage.
  • FIG. 3 is a flow chart of a method for controlling shutdown of a compressor in an air conditioner according to still another embodiment of the present invention. As shown in FIG. 3, the shutdown control method of the compressor in the air conditioner includes the following steps:
  • S200 The rotor of the compressor is controlled to stop between [170°, 190°] according to the stop command.
  • a shutdown control method for a compressor in an air conditioner after receiving a stop command, controls the rotor of the compressor to stop between [170°, 190°] according to the stop command, thereby causing vibration of the generated pipe and The stress is small, which effectively reduces the vibration and stress of the piping at the moment of stopping the compressor, and prevents the risk of pipe breakage.
  • the compressor is controlled to operate at 60 Hz, and the load characteristic curve when the compressor is operated at 60 Hz is shown in Fig. 4.
  • control module sends a compressor stop signal
  • the compressor is immediately stopped; otherwise, the compressor continues to run until the compressor rotor is in the preset compressor stop phase interval. Stop the compressor.
  • the rotor phase with the smallest compressor load is 180°
  • the preset compressor shutdown phase interval is set to 175-185°.
  • Figure 5-9 is a waveform diagram of the phase current and U-phase drive signals of the compressor during the 100ms shutdown process in the related art.
  • CH1, CH2 and MATH are the U-phase current, V-phase current and W-phase current (10A/div) of the compressor, respectively.
  • CH3 and CH4 are the U-phase upper arm (U+) drive signal and U-phase of the compressor, respectively. Lower arm (U-) drive signal. The moment when the U-phase drive signal is turned off is the moment when the compressor is stopped. As can be seen from Fig. 3-7, the stop phase of the three-phase current is not fixed at the stop time of the compressor.
  • FIGS. 10-13 are schematic diagrams showing waveforms of a compressor phase current and a U-phase driving signal during a 100 ms shutdown process according to an embodiment of the present invention.
  • CH1, CH2 and MATH are the U-phase current, V-phase current and W-phase current (10A/div) of the compressor, respectively.
  • CH3 and CH4 are the U-phase upper arm (U+) drive signal and U-phase of the compressor, respectively.
  • Lower arm (U-) drive signal The moment when the U-phase drive signal is turned off is the moment when the compressor stops, as shown in Figure 8-11, in the compressor At the time of shutdown, the phase of the shutdown of the three-phase current is basically fixed.
  • controlling the compressor to stop running in the preset compressor stop phase interval can minimize the vibration and stress of the piping.
  • FIG. 14 is a block schematic diagram of a shutdown control device for a compressor in an air conditioner in accordance with one embodiment of the present invention.
  • the shutdown control device of the compressor in the air conditioner includes an acquisition module 10, a rotor position acquisition module 20, and a control module 30.
  • the acquiring module 10 is configured to obtain a rotor phase with a minimum compressor load; the rotor position acquiring module 20 is configured to acquire a rotor position of the compressor during the shutdown of the air conditioner; and the control module 30 is configured to determine the compression according to the rotor position of the compressor. Whether the rotor of the machine is at the rotor phase with the smallest compressor load, and controlling the compressor to stop running when it is judged that the rotor of the compressor is at the rotor phase with the smallest compressor load.
  • control module 30 controls the compressor to continue operating when it is determined that the rotor of the compressor is not at the rotor phase where the compressor load is minimal.
  • the control module 30 stops the compressor at the rotor phase where the compressor load is minimal.
  • the compressor pressure especially the single-rotor compressor, periodically changes in the refrigerant compression cycle during a refrigerant compression cycle.
  • the refrigerant pressure is also relatively small near the rotor phase where the compressor load is minimal. Thus, stopping the compressor at the rotor phase where the compressor load is the smallest will cause the piping to vibrate and stress less.
  • the control module 30 After the control module 30 sends a compressor shutdown signal to the compressor, the control module 30 begins to control the compressor shutdown.
  • the rotor position acquisition module 20 can acquire the rotor position of the compressor. If the rotor of the compressor is at the rotor phase with the smallest compressor load, the control module 30 controls the compressor to immediately stop running; otherwise, if the rotor of the compressor is not at the rotor phase with the smallest compressor load, the control module 30 controls the compressor to continue. Run until the rotor of the compressor is at the rotor phase with the minimum compressor load and then control the compressor to stop running.
  • the rotor phase with the smallest compressor load is the rotor position of the compressor at the end of one intake and exhaust, i.e., the rotor position at the end of the exhaust of the compressor during one mechanical cycle.
  • the low temperature and low pressure refrigerant enters the suction pipe of the compressor from the condenser, is gradually compressed into a high temperature and high pressure refrigerant, and is quickly released to the exhaust port of the compressor to the compressor.
  • the load pressure of the compressor is minimized after the refrigerant is released. Therefore, the rotor phase with the smallest compressor load is the compressor rotor phase after the refrigerant is released, that is, the compressor rotor phase at the end of the exhaust, and the compressor rotor phase at the end of the exhaust gas, and the compressor is stopped, and the compressor can be stopped instantaneously. Vibration and stress are small.
  • the acquisition module 10 can obtain the compressor based on the difference between the rotor phase of the compressor load and the mechanical zero phase of the rotor of the compressor, and by identifying the mechanical zero phase of the rotor of the compressor. The rotor phase with the smallest load.
  • the acquisition module 10 obtains the torque of the compressor by The minimum value of the flow amplitude value or the minimum value of the torque compensation amplitude of the compressor is obtained to obtain the rotor phase with the smallest compressor load.
  • the torque compensation technology may be used to torque compensate the compressor to reduce the vibration of the piping during operation.
  • the torque compensation amplitude varies with the refrigerant pressure and load cycle. When the refrigerant pressure and load are minimum, the corresponding torque compensation amplitude is also the smallest. At this time, the rotor of the compressor is considered to be at the minimum load. Rotor phase.
  • the rotor phase with the smallest compressor load can be obtained directly from the rotor position calibration of the compressor design, or it can be obtained indirectly from variables such as the torque current amplitude or the torque compensation amplitude of the compressor.
  • the phase difference of the mechanical zero phase of the rotor due to the minimum load phase of the rotor is known, and therefore, the acquisition module 10 can obtain the minimum compressor load by identifying the mechanical zero phase of the rotor of the compressor.
  • the rotor position acquiring module 20 can obtain the rotor position of the compressor in two ways: one is directly measured by a sensor; the other is by detecting the current of the compressor and calculating according to the current of the compressor. .
  • a shutdown control device for a compressor in an air conditioner obtains a rotor position of a compressor during a shutdown process of the air conditioner through a rotor acquisition detection module, and the control module is at a compressor load in a rotor of the compressor.
  • the minimum rotor phase controls the compressor to stop running, so that the generated pipe vibration and stress are small, thereby effectively reducing the vibration and stress of the pipe at the moment of stopping the compressor, thereby preventing the risk of pipe breakage.
  • the embodiment of the invention further provides an air conditioner comprising the shutdown control device for the compressor in the air conditioner of the above embodiment.
  • the vibration and stress of the piping at the moment of stopping the compressor can be effectively reduced by the shutdown control device of the compressor, and the danger of the pipe breaking is prevented.
  • FIG. 15 is a block schematic diagram of a shutdown control device for a compressor in an air conditioner according to an embodiment of the present invention.
  • the shutdown control device of the compressor in the air conditioner includes an acquisition module 11, a rotor position acquisition module 21, and a control module 31.
  • the acquiring module 11 is configured to acquire a preset compressor shutdown phase interval; the rotor position acquiring module 21 is configured to The rotor position of the compressor is obtained during the shutdown of the air conditioner; the control module 31 is configured to determine whether the rotor of the compressor is in the preset compressor shutdown phase interval according to the rotor position of the compressor, and determine that the rotor of the compressor is in a preset compression The compressor is stopped when the machine stops the phase interval.
  • control module 30 controls the compressor to continue operating when it is determined that the rotor of the compressor is not in the preset compressor shutdown phase interval.
  • the control module 30 stops the compressor when the rotor of the compressor is in the preset compressor shutdown phase interval.
  • the compressor pressure especially the single-rotor compressor, periodically changes in the refrigerant compression cycle during a refrigerant compression cycle.
  • the refrigerant pressure is also relatively small near the rotor phase where the compressor load is minimal. Therefore, the preset compressor shutdown phase interval is set according to the upper and lower floating sections of the rotor phase with the smallest compressor load, and the compressor is stopped when the rotor of the compressor is in the preset compressor shutdown phase interval, which will cause the vibration of the piping and The stress is small.
  • the control module 30 After the control module 30 sends a compressor shutdown signal to the compressor, the control module 30 begins to control the compressor shutdown.
  • the air conditioner ie, the compressor shutdown
  • the rotor position acquisition module 20 can acquire the rotor position of the compressor. If the rotor of the compressor is in the preset compressor shutdown phase interval, the control module 30 controls the compressor to immediately stop running; otherwise, if the rotor of the compressor is not in the preset compressor shutdown phase interval, the control module 30 controls the compressor to continue. Run until the rotor of the compressor is in the preset compressor shutdown phase interval and then control the compressor to stop running.
  • a preset compressor shutdown phase interval may be obtained from experimental testing and stored in an air conditioner for retrieval, in accordance with an embodiment of the present invention. Also, in accordance with an embodiment of the present invention, the preset compressor shutdown phase interval may be preset based on the rotor phase with the smallest compressor load.
  • the compressor in the air conditioner can be experimentally tested to determine the rotor phase with the smallest compressor load, and then the rotor phase with the smallest compressor load can be floated up by the first preset threshold and floated downward by the second preset.
  • the threshold value is used as the preset compressor shutdown phase interval, and the preset compressor shutdown phase interval can also be regarded as the rotor phase interval with a smaller compressor load. For example, as shown in FIG. 2, assuming that the compressor load at point A is detected to be the smallest, the rotor phase of point A can be obtained as the rotor phase P with the smallest compressor load, and then the rotor phase of the compressor load is minimized.
  • the threshold L1 is floated upward, and the rotor phase P having the smallest compressor load is floated downward by the threshold L2, thereby presetting the compressor stop phase interval [P-L2, P+L1].
  • the preset compressor shutdown phase interval may be [170°, 190°], and may further preferably be [175°, 185°].
  • the rotor phase with the smallest compressor load is the rotor position of the compressor at the end of one intake and exhaust, that is, the rotor position at the end of exhaust of the compressor in one mechanical cycle.
  • the low temperature and low pressure refrigerant enters the suction pipe of the compressor from the condenser, is gradually compressed into a high temperature and high pressure refrigerant, and is quickly released to the exhaust port of the compressor to the compressor.
  • the load pressure of the compressor is minimized after the refrigerant is released. Therefore, the rotor phase with the smallest compressor load is the refrigerant release. The rotor phase of the compressor at the end of the exhaust after the release.
  • the difference between the rotor phase of the compressor load and the mechanical zero phase of the rotor of the compressor can be obtained, and can be obtained by identifying the mechanical zero phase of the rotor of the compressor.
  • the rotor phase with the smallest compressor load may be obtained by obtaining a minimum value of the torque current magnitude of the compressor or by obtaining a minimum value of the torque compensation amplitude of the compressor.
  • the torque compensation technology may be used to torque compensate the compressor to reduce the vibration of the piping during operation.
  • the torque compensation amplitude varies with the refrigerant pressure and load cycle.
  • the corresponding torque compensation amplitude is also the smallest, that is, the rotor of the compressor is considered to be at the minimum load phase. .
  • the rotor phase with the smallest compressor load can be obtained directly from the rotor position calibration of the compressor design, or it can be obtained indirectly from variables such as the torque current amplitude or the torque compensation amplitude of the compressor.
  • the phase difference of the mechanical zero phase of the rotor due to the minimum load phase of the rotor is known, and therefore, by identifying the mechanical zero phase of the rotor of the compressor, the rotor phase with the smallest compressor load can be obtained.
  • the minimum phase of the torque current amplitude or the minimum phase of the torque compensation amplitude is the compressor rotor phase with the smallest load, therefore, by obtaining the minimum value or torque of the torque current amplitude By compensating for the minimum value of the amplitude, the rotor phase with the smallest compressor load can be obtained.
  • the compressor stop control device of the air conditioner obtains the rotor position of the compressor during the shutdown process of the air conditioner by the rotor position acquisition module, and the control module is preset compression in the rotor of the compressor.
  • the machine stops the phase interval and controls the compressor to stop running, so that the generated pipe vibration and stress are small, thereby effectively reducing the vibration and stress of the pipe at the moment of stopping the compressor, thereby preventing the risk of pipe breakage.
  • the embodiment of the invention further provides an air conditioner comprising the shutdown control device for the compressor in the air conditioner of the above embodiment.
  • the vibration and stress of the piping at the moment of stopping the compressor can be effectively reduced by the shutdown control device of the compressor, and the danger of the pipe breaking is prevented.
  • FIG. 16 is a block schematic diagram of a shutdown control device for a compressor in an air conditioner according to still another embodiment of the present invention.
  • the shutdown control device of the compressor in the air conditioner includes a receiving module 12 and a control module 32.
  • the receiving module 12 is configured to receive a shutdown command; the control module 32 is configured to control the rotor of the compressor to stop between [170°, 190°] according to the shutdown instruction.
  • the control module controls the rotor of the compressor to stop between [170°, 190°] according to the stop command, thereby generating
  • the vibration and stress of the piping are small, thereby effectively reducing the vibration and stress of the piping at the moment of stopping the compressor, thereby preventing the risk of piping being broken.
  • the embodiment of the invention further provides an air conditioner comprising the shutdown control device for the compressor in the air conditioner of the above embodiment.
  • the vibration and stress of the piping at the moment of stopping the compressor can be effectively reduced by the shutdown control device of the compressor, and the danger of the pipe breaking is prevented.
  • first and second are used for descriptive purposes only and are not to be construed as indicating or implying a relative importance or implicitly indicating the number of technical features indicated.
  • features defining “first” or “second” may include at least one of the features, either explicitly or implicitly.
  • the meaning of "a plurality” is at least two, such as two, three, etc., unless specifically defined otherwise.
  • the terms “installation”, “connected”, “connected”, “fixed” and the like shall be understood broadly, and may be either a fixed connection or a detachable connection, unless explicitly stated and defined otherwise. , or integrated; can be mechanical or electrical connection; can be directly connected, or indirectly connected through an intermediate medium, can be the internal communication of two elements or the interaction of two elements, unless otherwise specified Limited.
  • the specific meanings of the above terms in the present invention can be understood on a case-by-case basis.
  • the first feature "on” or “under” the second feature may be a direct contact of the first and second features, or the first and second features may be indirectly through an intermediate medium, unless otherwise explicitly stated and defined. contact.
  • the first feature "above”, “above” and “above” the second feature may be that the first feature is directly above or above the second feature, or merely that the first feature level is higher than the second feature.
  • the first feature “below”, “below” and “below” the second feature may be that the first feature is directly below or obliquely below the second feature, or merely that the first feature level is less than the second feature.

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  • Control Of Ac Motors In General (AREA)
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Abstract

公开了一种空调器及其压缩机的停机控制方法和装置。方法包括以下步骤：获取压缩机负载最小的转子相位（S1）；在空调器的停机过程中，获取压缩机的转子位置，并根据压缩机的转子位置判断压缩机的转子是否处于压缩机负载最小的转子相位（S2）；如果判断压缩机的转子处于压缩机负载最小的转子相位，则控制压缩机停止运行（S3）。该方法可有效减小压缩机停止瞬间的配管振动与应力，防止发生配管断管的危险。

Description

空调器及其压缩机的停机控制方法和装置 技术领域
本发明涉及空调器技术领域，特别涉及一种空调器中压缩机的停机控制方法、一种空调器中压缩机的停机控制装置以及一种具有该装置的空调器。
背景技术
相关的变频空调器中，高频运行时冷媒压力和负载较大，如果直接停止压缩机，则冷媒压力和负载能量会瞬间释放出来，导致配管振动与应力过大，甚至存在配管断管的危险。在相关技术中，通常采用降频方式控制压缩机停机，即控制压缩机降频运行至低频时再停止压缩机运行，以减小停机时刻的配管振动与应力，但是，其存在的缺点是，在变频空调器的压缩机停止瞬间，仍然可能会有较大的配管振动与应力。
因此，相关技术需要进行改进。
发明内容
本发明旨在至少在一定程度上解决相关技术中的技术问题之一。为此，本发明的一个目的在于提出一种空调器中压缩机的停机控制方法，该方法可有效减小压缩机停止瞬间的配管振动与应力。
本发明的另一个目的在于提出一种空调器中压缩机的停机控制装置。本发明的又一个目的在于提出一种空调器。
为达到上述目的，本发明一方面实施例提出了一种空调器中压缩机的停机控制方法，包括以下步骤：获取所述压缩机负载最小的转子相位；在空调器的停机过程中，获取所述压缩机的转子位置，并根据所述压缩机的转子位置判断所述压缩机的转子是否处于所述压缩机负载最小的转子相位；如果判断所述压缩机的转子处于所述压缩机负载最小的转子相位，则控制所述压缩机停止运行。
根据本发明实施例提出的空调器中压缩机的停机控制方法，在空调器的停机过程中，获取压缩机的转子位置，并在压缩机的转子处于压缩机负载最小的转子相位，控制压缩机停止运行，从而使得产生的配管振动与应力较小，进而有效减小压缩机停止瞬间的配管振动与应力，防止发生配管断管的危险。
根据本发明的一个实施例，所述压缩机负载最小的转子相位为所述压缩机在一个机械周期内排气结束的转子位置。
根据本发明的一个实施例，根据所述压缩机负载最小的转子相位与所述压缩机的转子 的机械零相位之间的差值，并通过识别所述压缩机的转子的机械零相位以获取所述压缩机负载最小的转子相位。
根据本发明的一个实施例，通过获取所述压缩机的转矩电流幅值的最小值或通过获取所述压缩机的转矩补偿幅值的最小值以获取所述压缩机负载最小的转子相位。
为达到上述目的，本发明另一方面实施例提出了一种空调器中压缩机的停机控制装置，包括：获取模块，用于获取所述压缩机负载最小的转子相位；转子位置获取模块，用于在空调器的停机过程中获取所述压缩机的转子位置；控制模块，用于根据所述压缩机的转子位置判断所述压缩机的转子是否处于所述压缩机负载最小的转子相位，并在判断所述压缩机的转子处于所述压缩机负载最小的转子相位时控制所述压缩机停止运行。
根据本发明实施例提出的空调器中压缩机的停机控制装置，通过转子位置获取模块在空调器的停机过程中获取压缩机的转子位置，控制模块在压缩机的转子处于压缩机负载最小的转子相位时，控制压缩机停止运行，从而使得产生的配管振动与应力较小，进而有效减小压缩机停止瞬间的配管振动与应力，防止发生配管断管的危险。
根据本发明的一个实施例，所述压缩机负载最小的转子相位为所述压缩机在一个机械周期内排气结束的转子位置。
根据本发明的一个实施例，所述获取模块根据所述压缩机负载最小的转子相位与所述压缩机的转子的机械零相位之间的差值，并通过识别所述压缩机的转子的机械零相位以获取所述压缩机负载最小的转子相位。
根据本发明的一个实施例，所述获取模块通过获取所述压缩机的转矩电流幅值的最小值或通过获取所述压缩机的转矩补偿幅值的最小值以获取所述压缩机负载最小的转子相位。
为达到上述目的，本发明又一方面实施例提出了一种空调器，包括所述的空调器中压缩机的停机控制装置。
根据本发明实施例提出的空调器，通过上述压缩机的停机控制装置可有效减小压缩机停止瞬间的配管振动与应力，防止发生配管断管的危险。
为达到上述目的，本发明再一方面实施例提出了另一种空调器中压缩机的停机控制方法，包括以下步骤：获取预设压缩机停机相位区间；在空调器的停机过程中，获取所述压缩机的转子位置，并根据所述压缩机的转子位置判断所述压缩机的转子是否处于所述预设压缩机停机相位区间；如果判断所述压缩机的转子处于所述预设压缩机停机相位区间，则控制所述压缩机停止运行，以降低配管的振动和应力。
根据本发明实施例提出的空调器中压缩机的停机控制方法，在空调器的停机过程中获取压缩机的转子位置，并在压缩机的转子处于预设压缩机停机相位区间时，控制压缩机停 止运行，从而使得产生的配管振动与应力较小，进而有效减小压缩机停止瞬间的配管振动与应力，防止发生配管断管的危险。
根据本发明的一个实施例，所述预设压缩机停机相位区间根据实验测试获得，并存储在所述空调器中以供调取。
根据本发明的一个实施例，所述预设压缩机停机相位区间根据所述压缩机负载最小的转子相位预设。
为到达上述目的，本发明再一方面实施例提出了另一种空调器中压缩机的停机控制装置，包括：获取模块，用于获取预设压缩机停机相位区间；转子位置获取模块，用于在空调器的停机过程中获取所述压缩机的转子位置；控制模块，用于根据所述压缩机的转子位置判断所述压缩机的转子是否处于所述预设压缩机停机相位区间，并在判断所述压缩机的转子处于所述预设压缩机停机相位区间时，控制所述压缩机停止运行，以降低配管的振动和应力。
根据本发明实施例提出的空调器中压缩机的停机控制装置，通过转子位置获取模块在空调器的停机过程中获取压缩机的转子位置，控制模块在压缩机的转子处于预设压缩机停机相位区间时，控制压缩机停止运行，从而使得产生的配管振动与应力较小，进而有效减小压缩机停止瞬间的配管振动与应力，防止发生配管断管的危险。
根据本发明的一个实施例，所述预设压缩机停机相位区间根据实验测试获得，并存储在所述空调器中以供调取。
根据本发明的一个实施例，所述预设压缩机停机相位区间根据所述压缩机负载最小的转子相位预设。
为到达上述目的，本发明再一方面实施例提出了另一种空调器，包括所述的空调器中压缩机的停机控制装置。
根据本发明实施例提出的空调器，通过上述压缩机的停机控制装置可有效减小压缩机停止瞬间的配管振动与应力，防止发生配管断管的危险。
附图说明
图1是根据本发明一个实施例的空调器中压缩机的停机控制方法的流程图；
图2是根据本发明另一个实施例的空调器中压缩机的停机控制方法的流程图；
图3是根据本发明又一个实施例的空调器中压缩机的停机控制方法的流程图；图4是压缩机60Hz运行时的负载特性曲线的示意图；
图5是相关技术中第一停机过程内压缩机相电流与U相驱动信号的波形示意图；
图6是相关技术中第二停机过程内压缩机相电流与U相驱动信号的波形示意图；
图7是相关技术中第三停机过程内压缩机相电流与U相驱动信号的波形示意图；
图8是相关技术中第四停机过程内压缩机相电流与U相驱动信号的波形示意图；
图9是相关技术中第五停机过程内压缩机相电流与U相驱动信号的波形示意图；
图10是根据本发明一个具体实施例的第一停机过程内压缩机相电流与U相驱动信号的波形示意图；
图11是根据本发明二个具体实施例的第一停机过程内压缩机相电流与U相驱动信号的波形示意图；
图12是根据本发明三个具体实施例的第一停机过程内压缩机相电流与U相驱动信号的波形示意图；
图13是根据本发明四个具体实施例的第一停机过程内压缩机相电流与U相驱动信号的波形示意图；
图14是根据本发明一个实施例的空调器中压缩机的停机控制装置的方框示意图；
图15是根据本发明另一个实施例的空调器中压缩机的停机控制装置的方框示意图；
图16是根据本发明又一个实施例的空调器中压缩机的停机控制装置的方框示意图。
具体实施方式
下面详细描述本发明的实施例，所述实施例的示例在附图中示出，其中自始至终相同或类似的标号表示相同或类似的元件或具有相同或类似功能的元件。下面通过参考附图描述的实施例是示例性的，旨在用于解释本发明，而不能理解为对本发明的限制。
下面参考附图来描述本发明实施例提出的空调器中压缩机的停机控制方法、空调器中压缩机的停机控制装置以及具有该装置的空调器。在本发明的一个实施例中，压缩机可优选为单转子压缩机。
图1是根据本发明一个实施例的空调器中压缩机的停机控制方法的流程图。如图1所示，空调器中压缩机的停机控制方法包括以下步骤：
S1：获取压缩机负载最小的转子相位。
根据本发明的一个实施例，压缩机负载最小的转子相位为压缩机在一个吸气和排气结束时的转子位置，即压缩机在一个机械周期内排气结束时的转子位置。
需要说明的是，在一个压缩机的冷媒压缩周期中，低温低压的冷媒从冷凝器进入压缩机的吸气管，被逐渐压缩成高温高压的冷媒，然后通过压缩机的排气口迅速释放至蒸发器，压缩机的负载压力在冷媒释放之后达到最小。因此，压缩机负载最小的转子相位为冷媒释放之后即排气结束时的压缩机转子相位。
根据本发明的一个实施例，可根据压缩机负载最小的转子相位与压缩机的转子的机械 零相位之间的差值，并可通过识别压缩机的转子的机械零相位以获取压缩机负载最小的转子相位。或者，根据本发明的一个实施例，可通过获取压缩机的转矩电流幅值的最小值或通过获取压缩机的转矩补偿幅值的最小值以获取压缩机负载最小的转子相位。
应当理解的是，当压缩机运行在负载最小的转子相位附近时，对应的转矩电流幅值也应该会较小。因此，在转速控制平稳的情况下，如果压缩机的转矩电流幅值最小，则认为压缩机的转子处于负载最小的转子相位。
在空调器以低频运行的过程中，可能会采用转矩补偿技术对压缩机进行转矩补偿控制，以减小运行过程中配管振动。在一个冷媒压缩周期内，转矩补偿幅值随冷媒压力与负载周期变化，当冷媒压力与负载最小时，对应的转矩补偿幅值也最小，此时即认为压缩机的转子处于负载最小的转子相位。
如上所述，压缩机负载最小的转子相位可以直接通过压缩机设计的转子位置标定来获得，也可以间接根据压缩机的转矩电流幅值或者转矩补偿幅值等变量来获得。其中，对于直接转子相位标定方法，因负载最小的转子相位距离转子的机械零相位的相位差已知，因此，通过识别压缩机的转子的机械零相位，即可获得压缩机负载最小的转子相位；对于间接转子相位获取方法，转矩电流幅值的最小或者转矩补偿幅值的最小的相位即为负载最小的压缩机转子相位，因此，通过获取转矩电流幅值的最小值或转矩补偿幅值的最小值，即可获取压缩机负载最小的转子相位。
S2：在空调器的停机过程中，获取压缩机的转子位置，并根据压缩机的转子位置判断压缩机的转子是否处于压缩机负载最小的转子相位。
根据本发明的一个实施例，压缩机的转子位置可通过以下两种方式获取：一是通过传感器直接测量得到；二是通过检测压缩机的电流并根据压缩机的电流计算得到。
S3：如果判断压缩机的转子处于压缩机负载最小的转子相位，则控制压缩机停止运行。
进一步地，根据本发明的一个实施例，如果判断压缩机的转子未处于压缩机负载最小的转子相位，则控制压缩机继续运行。
也就是说，在压缩机负载最小的转子相位才停止压缩机。需要说明的是，压缩机特别是单转子压缩机在一个冷媒压缩周期内，冷媒压力和负载呈周期性变化，在压缩机负载最小的转子相位附近，冷媒压力也相应的较小。由此，在压缩机负载最小的转子相位停止压缩机，将会使配管振动与应力较小。
具体而言，当空调器的控制模块发出压缩机停机信号之后，控制模块开始控制压缩机停机，在空调器即压缩机停机过程中，获取压缩机的转子位置，如果压缩机的转子处于压缩机负载最小的转子相位，则控制压缩机立即停止运行；否则，如果压缩机的转子未处于压缩机负载最小的转子相位，则控制压缩机继续运行，直到压缩机的转子处于压缩机负载 最小的转子相位再控制压缩机停止运行。
由此，根据本发明实施例提出的空调器中压缩机的停机控制方法，在空调器的停机过程中，获取压缩机的转子位置，并在压缩机的转子处于压缩机负载最小的转子相位，控制压缩机停止运行，从而使得产生的配管振动与应力较小，进而有效减小压缩机停止瞬间的配管振动与应力，防止发生配管断管的危险。
图2是根据本发明另一个实施例的空调器中压缩机的停机控制方法的流程图。如图2所示，空调器中压缩机的停机控制方法包括以下步骤：
S10：获取预设压缩机停机相位区间。
根据本发明的一个实施例，预设压缩机停机相位区间可根据实验测试获得，并存储在空调器中以供调取。并且，根据本发明的一个实施例，预设压缩机停机相位区间可根据压缩机负载最小的转子相位预设。
具体来说，可对空调器中的压缩机进行实验测试以确定压缩机负载最小的转子相位，然后可将压缩机负载最小的转子相位向上浮动第一预设阈值并向下浮动第二预设阈值，以作为预设压缩机停机相位区间，预设压缩机停机相位区间也可看作是压缩机负载较小的转子相位区间。举例来说，如图2所示，假设检测出A点的压缩机负载最小，那么可获取A点的转子相位以作为压缩机负载最小的转子相位P，然后将压缩机负载最小的转子相位P向上浮动阈值L1，并将压缩机负载最小的转子相位P向下浮动阈值L2，从而预设压缩机停机相位区间[P-L2，P+L1]。
根据本发明的一个具体示例，预设压缩机停机相位区间可以为[170°，190°]，可进一步优选为[175°，185°]。
更具体地，根据本发明的一个实施例，压缩机负载最小的转子相位为压缩机在一个吸气和排气结束时的转子位置，即压缩机在一个机械周期内排气结束时的转子位置。
需要说明的是，在一个压缩机的冷媒压缩周期中，低温低压的冷媒从冷凝器进入压缩机的吸气管，被逐渐压缩成高温高压的冷媒，然后通过压缩机的排气口迅速释放至蒸发器，压缩机的负载压力在冷媒释放之后达到最小。因此，压缩机负载最小的转子相位为冷媒释放之后即排气结束时的压缩机转子相位。
更具体地，根据本发明的一个实施例，可根据压缩机负载最小的转子相位与压缩机的转子的机械零相位之间的差值，并可通过识别压缩机的转子的机械零相位以获取压缩机负载最小的转子相位。或者，根据本发明的一个实施例，可通过获取压缩机的转矩电流幅值的最小值或通过获取压缩机的转矩补偿幅值的最小值以获取压缩机负载最小的转子相位。
应当理解的是，当压缩机运行在负载最小的转子相位附近时，对应的转矩电流幅值也 应该会较小。因此，在转速控制平稳的情况下，如果转矩电流幅值最小，则认为压缩机的转子处于负载最小的转子相位。
在空调器以低频运行的过程中，可能会采用转矩补偿技术对压缩机进行转矩补偿控制，以减小运行过程中配管振动。在一个冷媒压缩周期内，转矩补偿幅值随冷媒压力与负载周期变化，当冷媒压力与负载最小时，对应的转矩补偿幅值也最小，即认为压缩机的转子处于负载最小的转子相位。
如上所述，压缩机负载最小的转子相位可以直接通过压缩机设计的转子位置标定来获得，也可以间接根据压缩机的转矩电流幅值或者转矩补偿幅值等变量来获得。其中，对于直接转子相位标定方法，因负载最小的转子相位距离转子的机械零相位的相位差已知，因此，通过识别压缩机的转子的机械零相位，即可获得压缩机负载最小的转子相位；对于间接转子相位获取方法，转矩电流幅值的最小或者转矩补偿幅值的最小的相位即为负载最小的压缩机转子相位，因此，通过获取转矩电流幅值的最小值或转矩补偿幅值的最小值，即可获取压缩机负载最小的转子相位。
S20：在空调器的停机过程中，获取压缩机的转子位置，并根据压缩机的转子位置判断压缩机的转子是否处于预设压缩机停机相位区间。
根据本发明的一个实施例，压缩机的转子位置可通过以下两种方式获取：一是通过传感器直接测量得到；二是通过检测压缩机的电流并根据压缩机的电流计算得到。
S30：如果判断压缩机的转子处于预设压缩机停机相位区间，则控制压缩机停止运行，以降低配管的振动和应力。
进一步地，根据本发明的一个实施例，如果判断压缩机的转子未处于预设压缩机停机相位区间，则控制压缩机继续运行。
也就是说，在压缩机的转子处于预设压缩机停机相位区间才停止压缩机。需要说明的是，压缩机特别是单转子压缩机在一个冷媒压缩周期内，冷媒压力和负载呈周期性变化，在压缩机负载最小的转子相位附近，冷媒压力也相应的较小。由此，根据压缩机负载最小的转子相位的上下浮动区间设定预设压缩机停机相位区间，并在压缩机的转子处于预设压缩机停机相位区间时停止压缩机，将会使配管振动与应力较小。
具体而言，当空调器的控制模块发出压缩机停机信号之后，控制模块开始控制压缩机停机，在空调器即压缩机停机过程中，实时获取压缩机的转子位置，如果压缩机的转子处于预设压缩机停机相位区间，则控制压缩机立即停止运行；否则，如果压缩机的转子未处于预设压缩机停机相位区间，则控制压缩机继续运行，直到压缩机的转子处于预设压缩机停机相位区间再控制压缩机停止运行。
由此，根据本发明实施例提出的空调器中压缩机的停机控制方法，在空调器的停机过 程中获取压缩机的转子位置，并在压缩机的转子处于预设压缩机停机相位区间时，控制压缩机停止运行，从而使得产生的配管振动与应力较小，进而有效减小压缩机停止瞬间的配管振动与应力，防止发生配管断管的危险。
图3是根据本发明又一个实施例的空调器中压缩机的停机控制方法的流程图。如图3所示，空调器中压缩机的停机控制方法包括以下步骤：
S100：接收停机指令。
S200：根据停机指令控制压缩机的转子在[170°，190°]之间停机。
根据本发明实施例提出的空调器中压缩机的停机控制方法，在接收停机指令之后，根据停机指令控制压缩机的转子在[170°，190°]之间停机，从而使得产生的配管振动与应力较小，进而有效减小压缩机停止瞬间的配管振动与应力，防止发生配管断管的危险。
下面结合图4-13的实验结果来验证本发明实施例的空调器中压缩机的停机控制方法的有效性。
以型号为ASK103的压缩机为例，控制压缩机以60Hz运行，压缩机60Hz运行时的负载特性曲线如图4所示。
当控制模块发出压缩机停机信号，如果压缩机的转子处于预设压缩机停机相位区间，则立即停止压缩机；否则，压缩机继续运行，直到压缩机的转子处于预设压缩机停机相位区间再停止压缩机。
具体地，在本实施例中，压缩机负载最小的转子相位为180°，进而设定预设压缩机停机相位区间为175～185°，当控制模块发出压缩机停机信号且压缩机的转子处于175～185°相位区间内时，立即停止压缩机；否则，压缩机继续运行，直到下一个机械周期进入175～185°相位区间时才停止压缩机。
图5-9为相关技术中100ms停机过程内压缩机相电流与U相驱动信号的波形示意图。其中，CH1、CH2和MATH分别为压缩机的U相电流、V相电流和W相电流(10A/div)，CH3和CH4分别为压缩机的U相上桥臂(U+)驱动信号和U相下桥臂(U-)驱动信号。U相驱动信号关闭瞬间为压缩机停机瞬间，由图3-7可知，在压缩机的停机时刻，三相电流的停机相位并不固定。
图10-13为本发明一个具体实施例的100ms停机过程内压缩机相电流与U相驱动信号的波形示意图。其中，CH1、CH2和MATH分别为压缩机的U相电流、V相电流和W相电流(10A/div)，CH3和CH4分别为压缩机的U相上桥臂(U+)驱动信号和U相下桥臂(U-)驱动信号。U相驱动信号关闭瞬间为压缩机停机瞬间，由图8-11可知，在压缩机的 停机时刻，三相电流的停机相位基本固定不变。
由此，在预设压缩机停机相位区间控制压缩机停止运行，可使得配管振动与应力最小。
图14是根据本发明一个实施例的空调器中压缩机的停机控制装置的方框示意图。如图14所示，该空调器中压缩机的停机控制装置包括：获取模块10、转子位置获取模块20和控制模块30。
其中，获取模块10用于获取压缩机负载最小的转子相位；转子位置获取模块20用于在空调器的停机过程中获取压缩机的转子位置；控制模块30用于根据压缩机的转子位置判断压缩机的转子是否处于压缩机负载最小的转子相位，并在判断压缩机的转子处于压缩机负载最小的转子相位时控制压缩机停止运行。
进一步地，根据本发明的一个实施例，当判断压缩机的转子未处于压缩机负载最小的转子相位时，控制模块30控制压缩机继续运行。
也就是说，控制模块30在压缩机负载最小的转子相位才停止压缩机。需要说明的是，压缩机特别是单转子压缩机在一个冷媒压缩周期内，冷媒压力和负载呈周期性变化，在压缩机负载最小的转子相位附近，冷媒压力也相应的较小。由此，在压缩机负载最小的转子相位停止压缩机，将会使配管振动与应力较小。
具体而言，当控制模块30向压缩机发出压缩机停机信号之后，控制模块30开始控制压缩机停机，在空调器即压缩机停机过程中，转子位置获取模块20可获取压缩机的转子位置，如果压缩机的转子处于压缩机负载最小的转子相位，控制模块30则控制压缩机立即停止运行；否则，如果压缩机的转子未处于压缩机负载最小的转子相位，控制模块30则控制压缩机继续运行，直到压缩机的转子处于压缩机负载最小的转子相位再控制压缩机停止运行。
根据本发明的一个实施例，压缩机负载最小的转子相位为压缩机在一个吸气和排气结束时的转子位置，即压缩机在一个机械周期内排气结束时的转子位置。
需要说明的是，在一个压缩机的冷媒压缩周期中，低温低压的冷媒从冷凝器进入压缩机的吸气管，被逐渐压缩成高温高压的冷媒，然后通过压缩机的排气口迅速释放至蒸发器，压缩机的负载压力在冷媒释放之后达到最小。因此，压缩机负载最小的转子相位为冷媒释放之后即排气结束时的压缩机转子相位，在排气结束时的压缩机转子相位，控制压缩机停止运行，可使压缩机停止瞬间产生的配管振动与应力较小。
根据本发明的一个实施例，获取模块10可根据压缩机负载最小的转子相位与压缩机的转子的机械零相位之间的差值，并通过识别压缩机的转子的机械零相位以获取压缩机负载最小的转子相位。或者，根据本发明的一个实施例，获取模块10通过获取压缩机的转矩电 流幅值的最小值或通过获取压缩机的转矩补偿幅值的最小值以获取压缩机负载最小的转子相位。
应当理解的是，当压缩机运行在负载最小的转子相位附近时，对应的转矩电流幅值也应该会较小。因此，在转速控制平稳的情况下，如果压缩机的转矩电流幅值最小，则认为压缩机的转子处于负载最小的转子相位。
在空调器以低频运行的过程中，可能会采用转矩补偿技术对压缩机进行转矩补偿控制，以减小运行过程中配管振动。在一个冷媒压缩周期内，转矩补偿幅值随冷媒压力与负载周期变化，当冷媒压力与负载最小时，对应的转矩补偿幅值也最小，此时即认为压缩机的转子处于负载最小的转子相位。
如上所述，压缩机负载最小的转子相位可以直接通过压缩机设计的转子位置标定来获得，也可以间接根据压缩机的转矩电流幅值或者转矩补偿幅值等变量来获得。其中，对于直接转子相位标定方法，因负载最小的转子相位距离转子的机械零相位的相位差已知，因此，获取模块10通过识别压缩机的转子的机械零相位，即可获得压缩机负载最小的转子相位；对于间接转子相位获取方法，转矩电流幅值的最小或者转矩补偿幅值的最小的相位即为负载最小的压缩机转子相位，因此，获取模块10通过获取转矩电流幅值的最小值或转矩补偿幅值的最小值，即可获取压缩机负载最小的转子相位。
根据本发明的一个实施例，转子位置获取模块20可通过以下两种方式获取压缩机的转子位置：一是通过传感器直接测量得到；二是通过检测压缩机的电流并根据压缩机的电流计算得到。
综上，根据本发明实施例提出的空调器中压缩机的停机控制装置，通过转子获取检测模块在空调器的停机过程中获取压缩机的转子位置，控制模块在压缩机的转子处于压缩机负载最小的转子相位，控制压缩机停止运行，从而使得产生的配管振动与应力较小，进而有效减小压缩机停止瞬间的配管振动与应力，防止发生配管断管的危险。
本发明实施例还提出了一种空调器，包括上述实施例的空调器中压缩机的停机控制装置。
根据本发明实施例提出的空调器，通过上述压缩机的停机控制装置可有效减小压缩机停止瞬间的配管振动与应力，防止发生配管断管的危险。
图15是根据本发明实施例的空调器中压缩机的停机控制装置的方框示意图。如图15所示，该空调器中压缩机的停机控制装置包括：获取模块11、转子位置获取模块21和控制模块31。
其中，获取模块11用于获取预设压缩机停机相位区间；转子位置获取模块21用于在 空调器的停机过程中获取压缩机的转子位置；控制模块31用于根据压缩机的转子位置判断压缩机的转子是否处于预设压缩机停机相位区间，并在判断压缩机的转子处于预设压缩机停机相位区间时控制压缩机停止运行。
进一步地，根据本发明的一个实施例，当判断压缩机的转子未处于预设压缩机停机相位区间时，控制模块30控制压缩机继续运行。
也就是说，控制模块30在压缩机的转子处于预设压缩机停机相位区间才停止压缩机。需要说明的是，压缩机特别是单转子压缩机在一个冷媒压缩周期内，冷媒压力和负载呈周期性变化，在压缩机负载最小的转子相位附近，冷媒压力也相应的较小。由此，根据压缩机负载最小的转子相位的上下浮动区间设定预设压缩机停机相位区间，并在压缩机的转子处于预设压缩机停机相位区间时停止压缩机，将会使配管振动与应力较小。
具体而言，当控制模块30向压缩机发出压缩机停机信号之后，控制模块30开始控制压缩机停机，在空调器即压缩机停机过程中，转子位置获取模块20可获取压缩机的转子位置，如果压缩机的转子处于预设压缩机停机相位区间，控制模块30则控制压缩机立即停止运行；否则，如果压缩机的转子未处于预设压缩机停机相位区间，控制模块30则控制压缩机继续运行，直到压缩机的转子处于预设压缩机停机相位区间再控制压缩机停止运行。
根据本发明的一个实施例，根据本发明的一个实施例，预设压缩机停机相位区间可根据实验测试获得，并存储在空调器中以供调取。并且，根据本发明的一个实施例，预设压缩机停机相位区间可根据压缩机负载最小的转子相位预设。
具体来说，可对空调器中的压缩机进行实验测试以确定压缩机负载最小的转子相位，然后可将压缩机负载最小的转子相位向上浮动第一预设阈值并向下浮动第二预设阈值，以作为预设压缩机停机相位区间，预设压缩机停机相位区间也可看作是压缩机负载较小的转子相位区间。举例来说，如图2所示，假设检测出A点的压缩机负载最小，那么可获取A点的转子相位以作为压缩机负载最小的转子相位P，然后将压缩机负载最小的转子相位P向上浮动阈值L1，并将压缩机负载最小的转子相位P向下浮动阈值L2，从而预设压缩机停机相位区间[P-L2，P+L1]。
根据本发明的一个具体示例，预设压缩机停机相位区间可以为[170°，190°]，可进一步优选为[175°，185°]。
更具体地，根据本发明的一个实施例，压缩机负载最小的转子相位为压缩机在一个吸气和排气结束时的转子位置，即压缩机在一个机械周期内排气结束时的转子位置。
需要说明的是，在一个压缩机的冷媒压缩周期中，低温低压的冷媒从冷凝器进入压缩机的吸气管，被逐渐压缩成高温高压的冷媒，然后通过压缩机的排气口迅速释放至蒸发器，压缩机的负载压力在冷媒释放之后达到最小。因此，压缩机负载最小的转子相位为冷媒释 放之后即排气结束时的压缩机转子相位。
更具体地，根据本发明的一个实施例，可根据压缩机负载最小的转子相位与压缩机的转子的机械零相位之间的差值，并可通过识别压缩机的转子的机械零相位以获取压缩机负载最小的转子相位。或者，根据本发明的一个实施例，可通过获取压缩机的转矩电流幅值的最小值或通过获取压缩机的转矩补偿幅值的最小值以获取压缩机负载最小的转子相位。
应当理解的是，当压缩机运行在负载最小的转子相位附近时，对应的转矩电流幅值也应该会较小。因此，在转速控制平稳的情况下，如果转矩电流幅值最小，则认为压缩机的转子处于负载最小的转子相位。
在空调器以低频运行的过程中，可能会采用转矩补偿技术对压缩机进行转矩补偿控制，以减小运行过程中配管振动。在一个冷媒压缩周期内，转矩补偿幅值随冷媒压力与负载周期变化，当冷媒压力与负载最小时，对应的转矩补偿幅值也最小，即认为压缩机的转子处于负载最小的转子相位。
如上所述，压缩机负载最小的转子相位可以直接通过压缩机设计的转子位置标定来获得，也可以间接根据压缩机的转矩电流幅值或者转矩补偿幅值等变量来获得。其中，对于直接转子相位标定方法，因负载最小的转子相位距离转子的机械零相位的相位差已知，因此，通过识别压缩机的转子的机械零相位，即可获得压缩机负载最小的转子相位；对于间接转子相位获取方法，转矩电流幅值的最小或者转矩补偿幅值的最小的相位即为负载最小的压缩机转子相位，因此，通过获取转矩电流幅值的最小值或转矩补偿幅值的最小值，即可获取压缩机负载最小的转子相位。
综上，根据本发明实施例提出的空调器中压缩机的停机控制装置，通过转子位置获取模块在空调器的停机过程中获取压缩机的转子位置，控制模块在压缩机的转子处于预设压缩机停机相位区间，控制压缩机停止运行，从而使得产生的配管振动与应力较小，进而有效减小压缩机停止瞬间的配管振动与应力，防止发生配管断管的危险。
本发明实施例还提出了一种空调器，包括上述实施例的空调器中压缩机的停机控制装置。
根据本发明实施例提出的空调器，通过上述压缩机的停机控制装置可有效减小压缩机停止瞬间的配管振动与应力，防止发生配管断管的危险。
图16是根据本发明又一个实施例的空调器中压缩机的停机控制装置的方框示意图。如图16所示，该空调器中压缩机的停机控制装置包括：接收模块12和控制模块32。
其中，接收模块12用于接收停机指令；控制模块32用于根据停机指令控制所述压缩机的转子在[170°，190°]之间停机。
根据本发明实施例提出的空调器中压缩机的停机控制装置，在接收模块接收停机指令之后，控制模块根据停机指令控制压缩机的转子在[170°，190°]之间停机，从而使得产生的配管振动与应力较小，进而有效减小压缩机停止瞬间的配管振动与应力，防止发生配管断管的危险。
本发明实施例还提出了一种空调器，包括上述实施例的空调器中压缩机的停机控制装置。
根据本发明实施例提出的空调器，通过上述压缩机的停机控制装置可有效减小压缩机停止瞬间的配管振动与应力，防止发生配管断管的危险。
在本发明的描述中，需要理解的是，术语“中心”、“纵向”、“横向”、“长度”、“宽度”、“厚度”、“上”、“下”、“前”、“后”、“左”、“右”、“竖直”、“水平”、“顶”、“底”“内”、“外”、“顺时针”、“逆时针”、“轴向”、“径向”、“周向”等指示的方位或位置关系为基于附图所示的方位或位置关系，仅是为了便于描述本发明和简化描述，而不是指示或暗示所指的装置或元件必须具有特定的方位、以特定的方位构造和操作，因此不能理解为对本发明的限制。
此外，术语“第一”、“第二”仅用于描述目的，而不能理解为指示或暗示相对重要性或者隐含指明所指示的技术特征的数量。由此，限定有“第一”、“第二”的特征可以明示或者隐含地包括至少一个该特征。在本发明的描述中，“多个”的含义是至少两个，例如两个，三个等，除非另有明确具体的限定。
在本发明中，除非另有明确的规定和限定，术语“安装”、“相连”、“连接”、“固定”等术语应做广义理解，例如，可以是固定连接，也可以是可拆卸连接，或成一体；可以是机械连接，也可以是电连接；可以是直接相连，也可以通过中间媒介间接相连，可以是两个元件内部的连通或两个元件的相互作用关系，除非另有明确的限定。对于本领域的普通技术人员而言，可以根据具体情况理解上述术语在本发明中的具体含义。
在本发明中，除非另有明确的规定和限定，第一特征在第二特征“上”或“下”可以是第一和第二特征直接接触，或第一和第二特征通过中间媒介间接接触。而且，第一特征在第二特征“之上”、“上方”和“上面”可是第一特征在第二特征正上方或斜上方，或仅仅表示第一特征水平高度高于第二特征。第一特征在第二特征“之下”、“下方”和“下面”可以是第一特征在第二特征正下方或斜下方，或仅仅表示第一特征水平高度小于第二特征。
在本说明书的描述中，参考术语“一个实施例”、“一些实施例”、“示例”、“具体示例”、或“一些示例”等的描述意指结合该实施例或示例描述的具体特征、结构、材料或者特点包含于本发明的至少一个实施例或示例中。在本说明书中，对上述术语的示意 性表述不必须针对的是相同的实施例或示例。而且，描述的具体特征、结构、材料或者特点可以在任一个或多个实施例或示例中以合适的方式结合。此外，在不相互矛盾的情况下，本领域的技术人员可以将本说明书中描述的不同实施例或示例以及不同实施例或示例的特征进行结合和组合。
尽管上面已经示出和描述了本发明的实施例，可以理解的是，上述实施例是示例性的，不能理解为对本发明的限制，本领域的普通技术人员在本发明的范围内可以对上述实施例进行变化、修改、替换和变型。

Claims (16)

  1. 一种空调器中压缩机的停机控制方法，其特征在于，包括以下步骤：
    获取所述压缩机负载最小的转子相位；
    在空调器的停机过程中，获取所述压缩机的转子位置，并根据所述压缩机的转子位置判断所述压缩机的转子是否处于所述压缩机负载最小的转子相位；
    如果判断所述压缩机的转子处于所述压缩机负载最小的转子相位，则控制所述压缩机停止运行。
  2. 如权利要求1所述的空调器中压缩机的停机控制方法，其特征在于，所述压缩机负载最小的转子相位为所述压缩机在一个机械周期内排气结束的转子位置。
  3. 如权利要求1所述的空调器中压缩机的停机控制方法，其特征在于，根据所述压缩机负载最小的转子相位与所述压缩机的转子的机械零相位之间的差值，并通过识别所述压缩机的转子的机械零相位以获取所述压缩机负载最小的转子相位。
  4. 如权利要求1所述的空调器中压缩机的停机控制方法，其特征在于，通过获取所述压缩机的转矩电流幅值的最小值或通过获取所述压缩机的转矩补偿幅值的最小值以获取所述压缩机负载最小的转子相位。
  5. 一种空调器中压缩机的停机控制装置，其特征在于，包括：
    获取模块，用于获取所述压缩机负载最小的转子相位；
    转子位置获取模块，用于在空调器的停机过程中获取所述压缩机的转子位置；
    控制模块，用于根据所述压缩机的转子位置判断所述压缩机的转子是否处于所述压缩机负载最小的转子相位，并在判断所述压缩机的转子处于所述压缩机负载最小的转子相位时控制所述压缩机停止运行。
  6. 如权利要求5所述的空调器中压缩机的停机控制装置，其特征在于，所述压缩机负载最小的转子相位为所述压缩机在一个机械周期内排气结束的转子位置。
  7. 如权利要求5所述的空调器中压缩机的停机控制装置，其特征在于，所述获取模块根据所述压缩机负载最小的转子相位与所述压缩机的转子的机械零相位之间的差值，并通过识别所述压缩机的转子的机械零相位以获取所述压缩机负载最小的转子相位。
  8. 如权利要求5所述的空调器中压缩机的停机控制装置，其特征在于，所述获取模块通过获取所述压缩机的转矩电流幅值的最小值或通过获取所述压缩机的转矩补偿幅值的最小值以获取所述压缩机负载最小的转子相位。
  9. 一种空调器，其特征在于，包括如权利要求5-8中任一项所述的空调器中压缩机的停机控制装置。
  10. 一种空调器中压缩机的停机控制方法，其特征在于，包括以下步骤：
    获取预设压缩机停机相位区间；
    在空调器的停机过程中，获取所述压缩机的转子位置，并根据所述压缩机的转子位置判断所述压缩机的转子是否处于所述预设压缩机停机相位区间；
    如果判断所述压缩机的转子处于所述预设压缩机停机相位区间，则控制所述压缩机停止运行，以降低配管的振动和应力。
  11. 如权利要求10所述的空调器中压缩机的停机控制方法，其特征在于，所述预设压缩机停机相位区间根据实验测试获得，并存储在所述空调器中以供调取。
  12. 如权利要求10或11所述的空调器中压缩机的停机控制方法，其特征在于，所述预设压缩机停机相位区间根据所述压缩机负载最小的转子相位预设。
  13. 一种空调器中压缩机的停机控制装置，其特征在于，包括：
    获取模块，用于获取预设压缩机停机相位区间；
    转子位置获取模块，用于在空调器的停机过程中获取所述压缩机的转子位置；
    控制模块，用于根据所述压缩机的转子位置判断所述压缩机的转子是否处于所述预设压缩机停机相位区间，并在判断所述压缩机的转子处于所述预设压缩机停机相位区间时，控制所述压缩机停止运行，以降低配管的振动和应力。
  14. 如权利要求13所述的空调器中压缩机的停机控制装置，其特征在于，所述预设压缩机停机相位区间根据实验测试获得，并存储在所述空调器中以供调取。
  15. 如权利要求13或14所述的空调器中压缩机的停机控制装置，其特征在于，所述预设压缩机停机相位区间根据所述压缩机负载最小的转子相位预设。
  16. 一种空调器，其特征在于，包括如权利要求13-15中任一项所述的空调器中压缩机的停机控制装置。
PCT/CN2016/078284 2016-03-09 2016-04-01 空调器及其压缩机的停机控制方法和装置 Ceased WO2017152444A1 (zh)

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EP16888598.6A EP3258182B1 (en) 2016-03-09 2016-04-01 Air conditioner, and shutdown control method and device for compressor thereof
BR112017017679-3A BR112017017679B1 (pt) 2016-03-09 2016-04-01 Método para controlar a interrupção de um compressor em um condicionador de ar; dispositivo para controle de interrupção de um compressor em um condicionador de ar; e condicionador de ar
ES16888598T ES2866047T3 (es) 2016-03-09 2016-04-01 Aire acondicionado, y procedimiento de control de apagado y dispositivo para el compresor de los mismos
HRP20210666TT HRP20210666T1 (hr) 2016-03-09 2016-04-01 Klima uređaj, upravljanje postupkom isključivanja i uređaj za njegov kompresor
US15/910,923 US10677241B2 (en) 2016-03-09 2018-03-02 Air conditioner, and method and device for controlling its compressor to stop

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