WO2018072601A1 - 空调器及其控制方法 - Google Patents

空调器及其控制方法 Download PDF

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Publication number
WO2018072601A1
WO2018072601A1 PCT/CN2017/103464 CN2017103464W WO2018072601A1 WO 2018072601 A1 WO2018072601 A1 WO 2018072601A1 CN 2017103464 W CN2017103464 W CN 2017103464W WO 2018072601 A1 WO2018072601 A1 WO 2018072601A1
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WIPO (PCT)
Prior art keywords
compressor
superheat
duration
air conditioner
jet
Prior art date
Application number
PCT/CN2017/103464
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English (en)
French (fr)
Inventor
魏峰
林海东
孙思
王传华
张恩泉
赵鹏举
赵普
李华本
Original Assignee
珠海格力电器股份有限公司
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Publication date
Application filed by 珠海格力电器股份有限公司 filed Critical 珠海格力电器股份有限公司
Priority to US16/342,533 priority Critical patent/US20190242603A1/en
Priority to EP17863047.1A priority patent/EP3527903B1/en
Publication of WO2018072601A1 publication Critical patent/WO2018072601A1/zh
Priority to US17/713,051 priority patent/US20220228767A1/en

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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
    • F24F11/62—Control or safety arrangements characterised by the type of control or by internal processing, e.g. using fuzzy logic, adaptive control or estimation of values
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/30—Control or safety arrangements for purposes related to the operation of the system, e.g. for safety or monitoring
    • F24F11/41—Defrosting; Preventing freezing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F25B49/022—Compressor control arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/70—Control systems characterised by their outputs; Constructional details thereof
    • F24F11/80—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air
    • F24F11/86—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling compressors within refrigeration or heat pump circuits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/89—Arrangement or mounting of control or safety devices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F2110/00—Control inputs relating to air properties
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation 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
    • F24F11/62—Control or safety arrangements characterised by the type of control or by internal processing, e.g. using fuzzy logic, adaptive control or estimation of values
    • F24F11/63—Electronic processing
    • F24F11/64—Electronic processing using pre-stored data
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/70—Control systems characterised by their outputs; Constructional details thereof
    • F24F11/72—Control systems characterised by their outputs; Constructional details thereof for controlling the supply of treated air, e.g. its pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F2110/00—Control inputs relating to air properties
    • F24F2110/10—Temperature
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/04—Clogging
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/06—Damage
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2115—Temperatures of a compressor or the drive means therefor
    • F25B2700/21151—Temperatures of a compressor or the drive means therefor at the suction side of the compressor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2115—Temperatures of a compressor or the drive means therefor
    • F25B2700/21152—Temperatures of a compressor or the drive means therefor at the discharge side of the compressor

Definitions

  • the present invention relates to the field of air conditioner equipment, and in particular to an air conditioner and a control method thereof.
  • the air source heat pump absorbs the low temperature heat energy in the air and converts it into high temperature heat energy through the compressor.
  • air source heat pumps are increasingly used in China.
  • Conventional air-cooled air source heat pumps currently have a minimum ambient temperature of -15 ° C for most heating operations.
  • jet augmentation technology is often used.
  • the air-cooled heat pump with jet boosting has a heating range of at least -25 ° C to -30 ° C.
  • Air source heat pumps typically use an electronic expansion valve as a throttling mechanism.
  • the electronic expansion valve is a throttling device that controls the flow of the valve needle by controlling the voltage or current applied to the expansion valve to control the flow of the valve port to achieve automatic flow regulation.
  • Common failure modes of electronic expansion valves include stuck, which will result in no flow or uncontrolled flow in the relevant flow path.
  • the cause of the electronic expansion valve being stuck is usually that there are impurities in the system, and the electronic expansion valve is stuck, which has a great influence on the reliability of the unit. If the card is stuck, there will be low-voltage protection or high-temperature protection of the exhaust gas when there is no flow.
  • the unit can usually protect quickly and effectively protect the compressor. When the flow is not controlled (larger steps), it is usually difficult to judge. If the unit cannot be quickly protected and the long-term operation will cause damage to the compressor, then the analysis will find that the electronic expansion valve is stuck and the compressor is caused. It is too late to damage.
  • the air-cooled heat pump system with jet-enhanced air-cooling heat pump system is located in the condenser after the jet-enhanced branch, which acts as a throttling and anti-pressure for the sneezing circuit refrigerant.
  • the sneezing electronic expansion valve is stuck at 0B or a small number of steps, the superheat of the jet will be too large, the performance of the unit will be reduced, and the effect of reducing the exhaust temperature of the unit by increasing the amount of sneezing will be affected. Long-term jet operation will not be affected.
  • the unit operation and maintenance personnel may be promptly analyzed to check the cause of the failure, so as not to cause damage to the compressor.
  • the sneeze electronic expansion valve is stuck in a large number of steps, the sneezing circuit refrigerant increases, which causes the liquid to operate, and the superheat of the jet is negative. Long-term spray operation will cause the compressor to slam, and the compressor lubricant film will be diluted, resulting in insufficient lubrication and wear.
  • a primary object of the present invention is to provide an air conditioner and a control method thereof for solving the problem that the compressor is easily damaged in the prior art.
  • a method of controlling an air conditioner comprising the steps of: controlling a compressor to be in accordance with a superheat of a jet of an air conditioner and a duration of a superheat of the jet Working state or shutdown state; control the compressor in the shutdown maintenance state according to the number of compressor shutdowns to repair the compressor air supply pipeline.
  • the method includes: when the number of times the compressor is turned off is less than or equal to the first preset value, the compressor is in a working state, and when the number of times the compressor is turned off is greater than the first preset value, the compressor is in a shutdown maintenance state.
  • the duration includes a negative duration, the negative duration when the jet superheat continues to be negative reaches a second predetermined value, and the exhaust temperature of the compressor remains less than the compressor during the negative duration The exhaust gas temperature threshold is restored to the working state after the compressor stops.
  • the duration further includes a duration of deviation, and if the duration of the deviation of the superheat of the superheat of the compressor is greater than or equal to a third preset value, the duration of the deviation is counted as a negative duration.
  • the third preset value is t, where 0 ⁇ t ⁇ 60s.
  • the first preset value is N, where 0 ⁇ N ⁇ 2.
  • the duration is reset to zero, and the duration after the zero return setting is calculated from the first jet superheat degree being less than or equal to the superheat deviation value.
  • an air conditioner being the air conditioner, the air conditioner comprising: a compressor that communicates with each other, a first heat exchanger, a second heat exchanger, and an air supply device;
  • the first end of the gas supply line is in communication with the outlet end of the first heat exchanger, and the second end of the gas supply line is in communication with the gas supply port of the compressor, and at least part of the gas supply line is heat exchanged with the gas supply device.
  • the air supply line is provided with at least one of an electronic expansion valve, a pressure sensor, and a first temperature sensor.
  • a second temperature sensor is disposed on the discharge line of the compressor.
  • a third temperature sensor is disposed on the air supply line, and the third temperature sensor is located between the outlet end of the first heat exchanger and the air supply device.
  • a method for controlling an air conditioner comprising controlling a compressor to be in an active state or a stop state according to a jet superheat degree of a compressor of the air conditioner and a duration of a superheat of the jet.
  • the compressor is in the shutdown maintenance state according to the number of compressor shutdowns to repair the compressor air supply line.
  • Figure 1 is a schematic view showing an embodiment of an air conditioner system according to the present invention in a heating mode
  • Figure 2 is a schematic view showing an embodiment of the air conditioner system of Figure 1 in a cooling mode
  • FIG. 3 is a block diagram showing the compressor operation of the air conditioner of Figure 1;
  • Fig. 4 is a block diagram showing the operation of the air conditioner of Fig. 1 in the cooling and heating modes, respectively.
  • spatially relative terms such as “above”, “above”, “on top”, “above”, etc., may be used herein to describe as in the drawings.
  • the exemplary term “above” can include both “over” and "under”.
  • the device can also be positioned in other different ways (rotated 90 degrees or at other orientations) and the corresponding description of the space used herein is interpreted accordingly.
  • the air conditioner control method includes controlling the compressor to be in an active state or a stop state according to a jet superheat degree of the compressor of the air conditioner and a duration of the superheat of the jet.
  • the compressor is in the shutdown maintenance state according to the number of compressor shutdowns to repair the compressor air supply line.
  • such a setting mode can effectively judge the working condition of the compressor effectively, so that when the compressor can be timely maintained, the compressor is prevented from being damaged due to operation under severe working conditions, and the compression is increased.
  • the method further comprises: when the number of times the compressor is turned off is less than or equal to the first preset value, the compressor is in a working state, and when the number of times the compressor is turned off is greater than the first preset value, the compressor is in a shutdown maintenance state.
  • a setting can effectively avoid the misjudgment caused by the compressor itself being stopped under normal working conditions, and the shutdown will not cause damage to the normal operation of the air conditioner and the components of the compressor, and the control method can improve the air conditioner. The reliability of the operation of the device.
  • the compressor when the number of times the compressor is turned off is less than or equal to the first preset value, the compressor is in the continuous working state, and when the number of times the compressor is turned off is greater than the first preset value, the compressor is in the shutdown maintenance state.
  • the first preset value is N, where 0 ⁇ N ⁇ 2. That is, when the compressor has two or one shutdown, it can control the compressor to be in the shutdown maintenance state or continue to work.
  • the duration includes a negative duration, when the jet superheat continues to be negative, the negative duration reaches a second predetermined value, and during the negative duration, the compressor exhaust temperature remains less than the compressor exhaust temperature The critical value is restored to the working state after the compressor stops.
  • the compressor stops and then Return to working status.
  • the time tc at which the superheat of the jet continues to be negative is calculated, if the time when the superheated degree of the superheated jet is greater than or equal to the superheated offset value is less than or equal to the third preset value, the period of time is counted as the time when the superheat degree continues to be negative.
  • TG is the superheat of the jet
  • TP is the superheat deviation
  • t0 is the time when the superheat of the jet begins to be less than or equal to the superheat offset
  • t1 is the time when the superheat of the jet begins to be greater than the superheated bias after t0; It is known that t1>t0, that is, tc starts from TG ⁇ TP time t0.
  • the duration is reset to zero, and the duration after the zero return setting is calculated from the first jet superheat degree being less than or equal to the superheat deviation value.
  • the electronic expansion valve on the air supply line of the compressor can be repaired when the compressor is in the shutdown protection state. This can effectively improve the reliability of the air supply to the compressor line. Effectively improve the compression performance of the compressor.
  • an air conditioner which is the air conditioner in the above embodiment.
  • the air conditioner includes a compressor 10 that communicates with each other, a first heat exchanger 20, a second heat exchanger 30, and an air supply device 40.
  • the first end of the air supply line 50 is in communication with the outlet end of the first heat exchanger 20, and the second end of the air supply line 50 is in communication with the air supply port of the compressor 10, at least a portion of the air supply line 50 and the air supply device 40 performs heat exchange to increase the temperature of the refrigerant in the makeup line 50.
  • the use of the air conditioner can effectively improve the operational reliability and service life of the air conditioner.
  • the air supply line 50 is provided with an electronic expansion valve 51, a pressure sensor 52, and a first temperature sensor 53.
  • the electronic expansion valve 51 is used to control the size of the air supply opening on the air supply line 50
  • the pressure sensor 52 is used to detect the pressure on the air supply line 50
  • the first temperature sensor 53 is used to detect the temperature on the air supply line 50.
  • the jet superheat of the compressor is calculated according to a conventionally calculated calculation method.
  • a second temperature sensor 54 is also disposed on the discharge line of the compressor 10 and used to detect the exhaust gas temperature at the exhaust line of the compressor, when the second temperature sensor 54 The more accurate the measurement is near the compressor vent.
  • the pressure sensor 52 may not be disposed on the supplemental gas line 50, and a third temperature sensor may be disposed on the supplemental gas line 50.
  • the third temperature sensor is located between the electronic expansion valve 51 and the air supply device 40.
  • the temperature sensor T3, that is, the third temperature sensor is disposed on the pipeline before entering the plate heat exchanger, that is, the air supply device 40, and then the temperature sensor T1 disposed at the outlet of the plate heat exchanger and before the compressor air inlet is the first temperature sensor 53.
  • Determine the spray condition, at this time TG (T1-T3) (usually TG is controlled at 3 ° C ⁇ 5 ° C).
  • the determination method of determining the state of the squirting refrigerant by the temperature difference of the squirting circuit, that is, the air supply line 50 entering and leaving the heat exchanger (the air supply line 50) is suitable for a compressor system which is more resistant to the liquid discharge.
  • FIG. 1 is taken as an example.
  • the zero-degree Celsius superheat deviation value is TP, and its value is (0.5 ⁇ 2 °C).
  • the exhaust gas temperature threshold TL when the exhaust temperature is too high, can usually increase the sneeze. The amount of exhaust gas is reduced, but the exhaust gas temperature should not be lower than the exhaust gas temperature threshold.
  • the exhaust gas temperature threshold is determined by the compressor model or recommended by the compressor manufacturer, usually greater than 90 °C.
  • tc The time when the superheat of the jet continues to be negative
  • tMAX the maximum set value of the time when the superheat of the jet continues to be negative
  • the control program is controlled according to the optimum value of the superheat of the jet (3 ° C ⁇ 8 ° C in this embodiment), and the electronic expansion valve of the sneeze continuously adjusts the number of steps to maintain the optimum superheat of the jet.
  • the superheat of the jet can be quickly controlled within the optimal range, usually the adjustment time is ⁇ 15min. At this point, the unit's jet boosting effect is the best.
  • the sneezing electronic expansion valve is stuck in a relatively large number of steps, it will cause a liquid discharge. At this time, the failure behavior is judged by the following processing method.

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  • General Engineering & Computer Science (AREA)
  • Combustion & Propulsion (AREA)
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Abstract

一种空调器及其控制方法，其中控制方法包括以下步骤：根据空调器的压缩机（10）的喷气过热度以及喷气过热度的持续时间，控制压缩机（10）处于工作状态或停机状态；根据压缩机（10）的停机次数控制压缩机（10）处于停机维修状态以对压缩机（10）的补气管路（50）进行维修。采用这样的设置方式能够有效地对压缩机（10）工况进行正确的判断，使得压缩机（10）能够得到及时的维护，避免压缩机（10）因在恶劣工况下运行造成损坏，增加了压缩机（10）及空调器运行的可靠性。

Description

空调器及其控制方法 技术领域
本发明涉及空调器设备技术领域，具体而言，涉及一种空调器及其控制方法。
背景技术
空气源热泵吸收空气中的低温热能，通过压缩机做功转换为高温热能。作为一种高效、节能环保供暖技术，空气源热泵在我国得到越来越多的应用。普通风冷空气源热泵目前大部分制热运行最低环境温度为-15℃，为了拓宽风冷空气源热泵制热的运行范围，多采用喷气增焓技术。采用喷气增焓的风冷热泵制热运行范围最低可达-25℃～-30℃。
空气源热泵通常采用电子膨胀阀作为节流机构。电子膨胀阀是一种通过控制施加于膨胀阀上的电压或电流，从而控制阀针的动作实现阀口流通面积改变达到流量自动调节目的的节流器件。电子膨胀阀常见失效方式包括卡死，此时会造成相关流路没有流量或是流量不受控制。造成电子膨胀阀卡死原因通常为系统内有杂质等，电子膨胀阀卡死对机组可靠性影响较大。卡死在没有流量时很快出现低压保护或者排气高温保护等，机组通常可以快速保护，有效保护压缩机。卡死在流量不受控制时(较大的步数)通常不易判断，若机组无法快速保护而长时间运行会导致压缩机损坏，这时再排查分析发现为电子膨胀阀卡死而导致压缩机损坏为时已晚。
采用喷气增焓的风冷热泵系统喷焓电子膨胀阀位于冷凝器后喷气增焓支路，对喷焓回路冷媒起节流降压作用。当喷焓电子膨胀阀卡死在0B或者较小的步数时喷气过热度会偏大，机组性能会降低，通过提高喷焓量来降低机组排气温度的作用受到影响，长久喷气运行不会对压缩机可靠性造成影响，若导致排气高温保护也可提示机组运行维护人员及时分析排查故障原因，不至于导致压缩机损坏。但是，当喷焓电子膨胀阀卡死在较大的步数时，喷焓回路冷媒增多，会导致喷液运行，喷气过热度为负值。长久喷液运行会造成压缩机液击、因压缩机润滑油膜被稀释导致润滑不足出现磨损等损坏。因而需要及时判断这种喷焓电子膨胀阀卡死在较大步数时的失效行为，及时保护机组停掉压缩机，排查分析喷焓电子膨胀阀卡死原因，及时更换喷焓电子膨胀阀，不至于出现压缩机损坏的严重售后故障。
发明内容
本发明的主要目的在于提供一种空调器及其控制方法，以解决现有技术中压缩机容易损坏的问题。
为了实现上述目的，根据本发明的一个方面，提供了一种空调器控制的方法，方法包括以下步骤：根据空调器的压缩机的喷气过热度以及喷气过热度的持续时间，控制压缩机处于 工作状态或停机状态；根据压缩机的停机次数控制压缩机处于停机维修状态以对压缩机的补气管路进行维修。
进一步地，方法包括：当压缩机关机的次数小于或等于第一预设值时，压缩机处于继续工作状态，当压缩机关机的次数大于第一预设值时，压缩机处于停机维修状态。
进一步地，持续时间包括负值持续时间，当喷气过热度持续为负值的负值持续时间达到第二预设值，且在负值持续时间内，压缩机的排气温度保持小于压缩机的排气温度临界值，压缩机停机后自行恢复至工作状态。
进一步地，持续时间还包括偏差持续时间，若喷气过热度持续大于压缩机的过热度偏差值的偏差持续时间小于或等于第三预设值时，偏差持续时间计入负值持续时间。
进一步地，第三预设值为t，其中，0＜t≤60s。
进一步地，第一预设值为N，其中，0＜N≤2。
进一步地，在空调器的制热模式和/或制冷模式中，持续时间为tc，其中，tc＝t1-t0，其中，t1＞t0，t0为喷气过热度开始小于过热度偏差值时的时间；或tc＝(t1-t0+t)，其中，t1为继t0之后喷气过热度开始大于过热度偏差值时的时间，t为喷气过热度大于过热度偏差值的持续时间，当t大于第四预设值时，tc的值清零，tc的值从下一次喷气过热度开始小于过热度偏差值时的时间开始计时。
进一步地，在制冷模式中，当空调器进行化霜模式时，持续时间归零设置，归零设置后的持续时间从第一次喷气过热度开始小于或等于过热度偏差值时计算。
进一步地，压缩机处于停机保护状态时，对压缩机的补气管路上的电子膨胀阀进行维修。
根据本发明的另一方面，提供了一种空调器，空调器为上述空调器，空调器包括：相互连通的压缩机、第一换热器、第二换热器以及补气装置；补气管路，补气管路的第一端与第一换热器的出口端相连通，补气管路的第二端与压缩机的补气口相连通，至少部分的补气管路与补气装置进行热交换以提高补气管路内冷媒的温度。
进一步地，补气管路上设置有电子膨胀阀、压力传感器，第一温度传感器中的至少一个。
进一步地，压缩机的排管路上设置有第二温度传感器。
进一步地，补气管路上设置有第三温度传感器，第三温度传感器位于第一换热器的出口端与补气装置之间。
应用本发明的技术方案，空调器控制的方法，该方法包括根据空调器的压缩机的喷气过热度以及喷气过热度的持续时间，控制压缩机处于工作状态或停机状态。根据压缩机的停机次数控制压缩机处于停机维修状态以对压缩机的补气管路进行维修。采用这样的设置方式能够有效地对压缩机工况进行正确的判断，使得当压缩机能够得到及时的维护，避免压缩机因在恶劣工况下运行造成损坏，增加了压缩机及空调器运行的可靠性。
附图说明
构成本申请的一部分的说明书附图用来提供对本发明的进一步理解，本发明的示意性实施例及其说明用于解释本发明，并不构成对本发明的不当限定。在附图中：
图1示出了根据本发明的空调器系统在制热模式下的实施例的示意图；
图2示出了图1中的空调器系统在制冷模式下的实施例的示意图；
图3示出了图1中的空调器的压缩机工作流程框图；
图4示出了图1中的空调器分别在制冷和制热模式下的工作流程框图。
其中，上述附图包括以下附图标记：
10、压缩机；20、第一换热器；30、第二换热器；40、补气装置；50、补气管路；51、电子膨胀阀；52、压力传感器；53、第一温度传感器；54、第二温度传感器。
具体实施方式
需要说明的是，在不冲突的情况下，本申请中的实施例及实施例中的特征可以相互组合。下面将参考附图并结合实施例来详细说明本发明。
需要注意的是，这里所使用的术语仅是为了描述具体实施方式，而非意图限制根据本申请的示例性实施方式。如在这里所使用的，除非上下文另外明确指出，否则单数形式也意图包括复数形式，此外，还应当理解的是，当在本说明书中使用术语“包含”和/或“包括”时，其指明存在特征、步骤、操作、器件、组件和/或它们的组合。
需要说明的是，本申请的说明书和权利要求书及上述附图中的术语“第一”、“第二”等是用于区别类似的对象，而不必用于描述特定的顺序或先后次序。应该理解这样使用的术语在适当情况下可以互换，以便这里描述的本申请的实施方式例如能够以除了在这里图示或描述的那些以外的顺序实施。此外，术语“包括”和“具有”以及他们的任何变形，意图在于覆盖不排他的包含，例如，包含了一系列步骤或单元的过程、方法、系统、产品或设备不必限于清楚地列出的那些步骤或单元，而是可包括没有清楚地列出的或对于这些过程、方法、产品或设备固有的其它步骤或单元。
为了便于描述，在这里可以使用空间相对术语，如“在……之上”、“在……上方”、“在……上表面”、“上面的”等，用来描述如在图中所示的一个器件或特征与其他器件或特征的空间位置关系。应当理解的是，空间相对术语旨在包含除了器件在图中所描述的方位之外的在使用或操作中的不同方位。例如，如果附图中的器件被倒置，则描述为“在其他器件或构造上方”或“在其他器件或构造之上”的器件之后将被定位为“在其他器件或构造下方”或“在其他器件或构造之下”。因而，示例性术语“在……上方”可以包括“在……上方”和“在……下方”两种方位。该器件也可以其他不同方式定位(旋转90度或处于其他方位)，并且对这里所使用的空间相对描述作出相应解释。
现在，将参照附图更详细地描述根据本申请的示例性实施方式。然而，这些示例性实施方式可以由多种不同的形式来实施，并且不应当被解释为只限于这里所阐述的实施方式。应当理解的是，提供这些实施方式是为了使得本申请的公开彻底且完整，并且将这些示例性实施方式的构思充分传达给本领域普通技术人员，在附图中，为了清楚起见，有可能扩大了层和区域的厚度，并且使用相同的附图标记表示相同的器件，因而将省略对它们的描述。
结合图1至图4所示，根据本发明的实施例，提供了一种空调器控制的方法。
具体地，该空调器控制的方法，包括根据空调器的压缩机的喷气过热度以及喷气过热度的持续时间，控制压缩机处于工作状态或停机状态。根据压缩机的停机次数控制压缩机处于停机维修状态以对压缩机的补气管路进行维修。
在本实施例中，采用这样的设置方式能够有效地对压缩机工况进行正确的判断，使得当压缩机能够得到及时的维护，避免压缩机因在恶劣工况下运行造成损坏，增加了压缩机及空调器运行的可靠性。
其中，该方法还包括当压缩机关机的次数小于或等于第一预设值时，压缩机处于继续工作状态，当压缩机关机的次数大于第一预设值时，压缩机处于停机维修状态。这样设置能够有效避免由于压缩机自身在正常工况下发生停机，且该停机不会对空调器的正常运行和压缩机的零件造成损伤的情况下产生误判，采用这样的控制方式能够提高空调器运行的可靠性。
进一步地，当压缩机关机的次数小于或等于第一预设值时，压缩机处于继续工作状态，当压缩机关机的次数大于第一预设值时，压缩机处于停机维修状态。这样设置能够有效地达到对压缩机工况的检测和控制的作用，能够对压缩机及空调器管路进行及时的维护处理。
其中，第一预设值为N，其中，0＜N≤2。即当压缩机存在两次或一次停机时，可以控制压缩机处于停机维修状态或是继续的工作状态。
持续时间包括负值持续时间，当喷气过热度持续为负值的负值持续时间达到第二预设值，且在负值持续时间内，压缩机的排气温度保持小于压缩机的排气温度临界值，压缩机停机后自行恢复至工作状态。
当计算的喷气过热度持续为负值的时间达到最大设定值并且在计算的喷气过热度持续为负值的时间内一直保持排气温度小于排气温度临界值时，压缩机停机后并自行恢复至工作状态。计算喷气过热度持续为负值的时间tc时，若持续喷气过热度大于过热度偏差值的时间小于或等于第三预设值，这段时间计入过热度持续为负值的时间。这样设置能够起到有效地保证空调器运行的可靠性，避免了因运行工况等而造成误判的情况。
其中，第三预设值为t，其中，0＜t≤60s。本实施例中t＝60s。
如图3和图4所示，在空调器的制热模式和制冷模式中，持续时间记为tc，其中，tc的计算方式如下：
Figure PCTCN2017103464-appb-000001
其中，TG为喷气过热度；TP为过热度偏差值；t0为喷气过热度开始小于或等于过热度偏差值时的时间；t1为t0之后喷气过热度开始大于过热度偏差值时的时间；已知t1＞t0，即tc从TG≤TP时刻t0开始计时，若一直保持TG≤TP到时间t1，则时间(t1-t0)计入tc；若t1时刻TG＞TP且此后TG＞TP持续时间没有超过t，则继续计时即tc＝(t1-t0+t)；若t1时刻TG＞TP且此后TG＞TP持续时间有超过t，则已计算tc清零，tc重新从下一个TG≤TP时刻开始计时，此后按照以上方法计算。
在制热模式中，当空调器进行化霜模式时，持续时间归零设置，归零设置后的持续时间从第一次喷气过热度开始小于或等于过热度偏差值时计算。
优选地，压缩机处于停机保护状态时，可以对压缩机的补气管路上的电子膨胀阀进行维修。这样能够有效地提高了压缩机管路的补气的可靠性。有效地提高了压缩机的压缩性能。
根据本发明的另一方面，提供了一种空调器，空调器为上述实施例中的空调器。该空调器包括相互连通的压缩机10、第一换热器20、第二换热器30以及补气装置40。补气管路50的第一端与第一换热器20的出口端相连通，补气管路50的第二端与压缩机10的补气口相连通，至少部分的补气管路50与补气装置40进行热交换以提高补气管路50内冷媒的温度。采用该空调器能够有效地提高空调器的运行可靠性和使用寿命。
如图1和图2所示，补气管路50上设置有电子膨胀阀51、压力传感器52以及第一温度传感器53。其中电子膨胀阀51用于控制补气管路50上的补气开度的大小，压力传感器52用于检测补气管路50上的压力，第一温度传感器53用于检测补气管路50上的温度，根据常规计算的计算方法计算压缩机的喷气过热度。
进一步地，为了提高计算结果的准确性，还在压缩机10的排管路上设置有第二温度传感器54并用于检测压缩机的排气管路处的排气温度，当第二温度传感器54越靠近压缩机排气口时测量结果越精确。
当然，可以不在补气管路50上设置压力传感器52，改在补气管路50上设置第三温度传感器。第三温度传感器位于电子膨胀阀51与补气装置40之间。
进入板式换热器即补气装置40前的管路上设置温度传感器T3即第三温度传感器，然后和设置在板式换热器出口，压缩机补气口前的温度传感器T1即第一温度传感器53来确定喷液情况，此时TG＝(T1-T3)(通常TG控制在3℃～5℃)。这种通过喷焓回路即补气管路50进出换热器(补气管路50)的温差来确定喷焓冷媒状态的判断方法适合对喷液耐受能力更强的压缩机系统。
具体地，对于喷焓节流装置为电子膨胀阀的喷气增焓系统，以附图1为例。补气装置40出口和压缩机入口间设置有温度传感器T1，压力传感器P1，压缩机出口排气管上设置有温度传感器T2，喷气过热度为喷焓温度减去喷气压力对应饱和温度即TG＝T1-TB(P1)。
零摄氏度过热度偏差值为TP，其值为(0.5～2℃)，依据温度传感器T1精度和实际情况而定，排气温度临界值TL，排气温度过高时通常可通过增大喷焓量来降低排气温度，但排气温度降低后不应低于排气温度临界值，排气温度临界值因压缩机型号不同而定或者由压缩机厂家推荐规定，通常大于90℃。
喷气过热度持续为负值的时间记为tc，喷气过热度持续为负值的时间最大设定值记为tMAX，由试验匹配获得，本实施例中tMAX＝20min。
机组正常运行时，控制程序按照喷气过热度最佳值(本实施例中为3℃～8℃)控制，喷焓电子膨胀阀不断调节步数来保持最佳喷气过热度。当喷焓电子膨胀阀正常时，可快速控制喷气过热度在最佳值范围内，通常调节时间＜15min。此时机组喷气增焓效果最佳。当喷焓电子膨胀阀卡死在比较大的步数时，会导致喷液情况。此时通过以下处理方法判断这种失效行为。具体地，机组压缩机启动运行后，若tc等于tMAX，并且这个过程中(tc时间内)一直保持排气温度T2＜TL，则立即关闭相应系统压缩机，出现此种状况前两次压缩机会自动恢复运行，累计三次后彻底锁定相应系统压缩机，报喷焓电子膨胀阀失效故障，提示运行维护人员及时排查分析，及时更换喷焓电子膨胀阀，保护压缩机。采用此种控制方法基本上不会出现误报情况。具体如流程图3所示。
喷气过热度持续为负值的时间tc计算方法如下，已知t1＞t0：制冷运行，压缩机启动，喷焓电子膨胀阀开启后开始统计，tc从TG≤TP时刻t0开始计时，若一直保持TG≤TP到时间t1，则时间(t1-t0)计入tc。若t1时刻TG＞TP且此后TG＞TP持续时间没有超过一分钟，则继续计时即tc＝(t1+-t0+60s)。若t1时刻TG＞TP且此后TG＞TP持续时间有超过一分钟，则已计算的tc清零，tc重新从下一个TG≤TP时刻开始计时，此后按照以上方法计算。
制热运行，压缩机启动，喷焓电子膨胀阀开启后开始统计，tc从TG≤TP时刻t0开始计时，若一直保持TG≤TP到时间t1，则时间(t1-t0)计入tc。若t1时刻TG＞TP且此后TG＞TP持续时间没有超过一分钟，则继续计时即tc＝(t1-t0+60s)。若t1时刻TG＞TP且此后TG＞TP持续时间有超过一分钟，则已计算tc清零，tc重新从下一个TG≤TP时刻开始计时，此后按照以上方法计算。若机组制热运行中进入化霜则已计时tc清零，退出化霜转制热运行后tc重新从TG≤TP时刻开始计时计算，此后按照前述方法计算。
精确、快速及时判断喷焓电子膨胀阀卡死在较大步数时的失效情况，及时停掉出现电子膨胀阀失效系统压缩机，提示运行维护人员及时分析、排查、更换喷焓电子膨胀阀，避免压缩机损坏的更严重后果。减少经济损失，避免压缩机损毁重大售后故障。
以上所述仅为本发明的优选实施例而已，并不用于限制本发明，对于本领域的技术人员来说，本发明可以有各种更改和变化。凡在本发明的精神和原则之内，所作的任何修改、等同替换、改进等，均应包含在本发明的保护范围之内。

Claims (13)

  1. 一种空调器的控制方法，其特征在于，所述控制方法包括以下步骤：
    根据空调器的压缩机的喷气过热度以及所述喷气过热度的持续时间，控制所述压缩机处于工作状态或停机状态；
    根据所述压缩机的停机次数控制所述压缩机处于停机维修状态以对所述压缩机的补气管路进行维修。
  2. 根据权利要求1所述的控制方法，其特征在于，所述方法包括：
    当所述压缩机关机的次数小于或等于第一预设值时，所述压缩机处于继续工作状态，当所述压缩机关机的次数大于所述第一预设值时，所述压缩机处于停机维修状态。
  3. 根据权利要求1所述的控制方法，其特征在于，所述持续时间包括负值持续时间，当所述喷气过热度持续为负值的所述负值持续时间达到第二预设值，且在所述负值持续时间内，所述压缩机的排气温度保持小于所述压缩机的排气温度临界值，所述压缩机停机后自行恢复至工作状态。
  4. 根据权利要求3所述的控制方法，其特征在于，所述持续时间还包括偏差持续时间，若所述喷气过热度持续大于所述压缩机的过热度偏差值的所述偏差持续时间小于或等于第三预设值时，所述偏差持续时间计入所述负值持续时间。
  5. 根据权利要求4所述的控制方法，其特征在于，所述第三预设值为t，其中，0＜t≤60s。
  6. 根据权利要求2所述的控制方法，其特征在于，所述第一预设值为N，其中，0＜N≤2。
  7. 根据权利要求1所述的控制方法，其特征在于，在所述空调器的制热模式和/或制冷模式中，所述持续时间为tc，其中，
    tc＝t1-t0，其中，t1＞t0，所述t0为所述喷气过热度开始小于过热度偏差值时的时间；或
    tc＝(t1-t0+t)，其中，所述t1为继所述t0之后所述喷气过热度开始大于所述过热度偏差值时的时间，所述t为所述喷气过热度大于所述过热度偏差值的持续时间，当所述t大于第四预设值时，所述tc的值清零，所述tc的值从下一次所述喷气过热度开始小于过热度偏差值时的时间开始计时。
  8. 根据权利要求7所述的控制方法，其特征在于，在所述制冷模式中，当所述空调器进行化霜模式时，所述持续时间归零设置，归零设置后的所述持续时间从第一次所述喷气过热度开始小于或等于所述过热度偏差值时计算。
  9. 根据权利要求1所述的控制方法，其特征在于，所述压缩机处于停机保护状态时，对所述压缩机的补气管路上的电子膨胀阀进行维修。
  10. 一种空调器，其特征在于，所述空调器为权利要求1至9中任一项所述空调器，所述空调器包括：相互连通的压缩机(10)、第一换热器(20)、第二换热器(30)以及补气装置(40)；
    补气管路(50)，所述补气管路(50)的第一端与所述第一换热器(20)的出口端相连通，所述补气管路(50)的第二端与所述压缩机(10)的补气口相连通，至少部分的所述补气管路(50)与所述补气装置(40)进行热交换以提高所述补气管路(50)内冷媒的温度。
  11. 根据权利要求10所述的空调器，其特征在于，所述补气管路(50)上设置有电子膨胀阀(51)、压力传感器(52)，第一温度传感器(53)中的至少一个。
  12. 根据权利要求10所述的空调器，其特征在于，所述压缩机(10)的排管路上设置有第二温度传感器(54)。
  13. 根据权利要求10所述的空调器，其特征在于，所述补气管路(50)上设置有第三温度传感器，所述第三温度传感器位于所述第一换热器(20)的出口端与补气装置(40)之间。
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