WO2024066353A1 - 热水机组的控制方法、系统及计算机可读存储介质 - Google Patents

热水机组的控制方法、系统及计算机可读存储介质 Download PDF

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Publication number
WO2024066353A1
WO2024066353A1 PCT/CN2023/092034 CN2023092034W WO2024066353A1 WO 2024066353 A1 WO2024066353 A1 WO 2024066353A1 CN 2023092034 W CN2023092034 W CN 2023092034W WO 2024066353 A1 WO2024066353 A1 WO 2024066353A1
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WIPO (PCT)
Prior art keywords
temperature
water
expansion valve
comparison result
opening
Prior art date
Application number
PCT/CN2023/092034
Other languages
English (en)
French (fr)
Inventor
邓志扬
余凯
袁明征
邓伟彬
张勇
冯飞龙
Original Assignee
珠海格力电器股份有限公司
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Publication of WO2024066353A1 publication Critical patent/WO2024066353A1/zh

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H4/00—Fluid heaters characterised by the use of heat pumps
    • F24H4/02—Water heaters
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H15/00—Control of fluid heaters
    • F24H15/30—Control of fluid heaters characterised by control outputs; characterised by the components to be controlled
    • F24H15/375—Control of heat pumps
    • F24H15/385—Control of expansion valves of heat pumps
    • 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
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • 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
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • F25B41/24—Arrangement of shut-off valves for disconnecting a part of the refrigerant cycle, e.g. an outdoor part
    • 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
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/31—Expansion valves
    • F25B41/34—Expansion valves with the valve member being actuated by electric means, e.g. by piezoelectric actuators
    • 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

Definitions

  • the present disclosure relates to the field of heat pump systems, and in particular to a control method and system for a water heater unit and a computer-readable storage medium.
  • the throttling device of the heat pump hot water unit mostly adopts an expansion valve, and its control target is the superheat of the evaporating heat exchanger.
  • this control scheme can accurately control the refrigerant circulation volume to ensure the performance of the unit.
  • the evaporation environment temperature is low, due to the decrease in air enthalpy, the superheat of the refrigerant at the outlet of the evaporative heat exchanger under the same configuration cannot be guaranteed.
  • the usual practice is to set a lower limit opening of the expansion valve according to the temperature, so that the expansion valve will not be over-adjusted and cause insufficient refrigerant circulation.
  • a control method for a water heater comprising a compressor, a water-side heat exchanger, an evaporative heat exchanger and an expansion valve, wherein the expansion valve is located between the water-side heat exchanger and the evaporative heat exchanger, and the control method for the water heater comprises:
  • the refrigerant saturation temperature corresponding to the pressure at the refrigerant outlet pipe of the water-side heat exchanger record it as the first temperature, obtain the outlet water temperature of the water-side heat exchanger, compare the first temperature with the outlet water temperature, and obtain a first comparison result;
  • the opening degree of the expansion valve is adjusted according to the first comparison result and the second comparison result.
  • the water heater unit further includes a flash evaporator
  • the expansion valve includes a first expansion valve and a second expansion valve, and along the flow direction of the refrigerant discharged from the outlet of the compressor, the water side heat exchanger, the first expansion valve, the flash evaporator, the second expansion valve and the evaporative heat exchanger are sequentially arranged from upstream to downstream;
  • the adjusting the opening of the expansion valve according to the first comparison result and the second comparison result includes adjusting the opening of at least one of the first expansion valve and the second expansion valve.
  • the opening of the first expansion valve is increased and the opening of the second expansion valve is maintained.
  • the opening of the second expansion valve is increased to maintain the opening of the first expansion valve.
  • the opening of the first expansion valve is adjusted to decrease and the opening of the second expansion valve is maintained.
  • the actual ambient temperature is greater than or equal to the preset ambient temperature
  • the inlet temperature of the compressor recorded as the third temperature
  • the opening of the first expansion valve is adjusted to increase and the opening of the second expansion valve is maintained.
  • the opening of the first expansion valve when the opening of the first expansion valve is increased and the opening of the second expansion valve is maintained so that the first comparison result is that the first temperature is less than the outlet water temperature plus the first preset temperature plus the second floating temperature, the opening of the first expansion valve is decreased.
  • the opening of the first expansion valve is increased and the opening of the second expansion valve is decreased.
  • the opening of the first expansion valve when the opening of the first expansion valve is increased and the opening of the second expansion valve is decreased so that the first comparison result is that the first temperature is less than the outlet water temperature plus the first preset temperature plus the second floating temperature, the opening of the first expansion valve is decreased.
  • the value of the first preset temperature is as follows:
  • the outlet water temperature is ⁇ 40°C
  • the value range of the first preset temperature is 5°C to 15°C.
  • the value range of the first preset temperature is 4°C to 7°C.
  • the outlet water temperature is ⁇ 40°C
  • the value range of the first preset temperature is 5°C to 10°C.
  • the value range of the first preset temperature is 2°C to 5°C.
  • the second preset temperature ranges from [1° C. to 3° C.].
  • the first floating temperature has a value range of [-2° C., 2° C.].
  • the second floating temperature has a value range of [1° C., 5° C.].
  • the preset ambient temperature is 5°C.
  • a control system of a water heater including a memory and a processor, wherein the processor is signal-connected to the memory, and the processor is configured to execute the control method of the water heater based on instructions stored in the memory.
  • a computer-readable storage medium on which a computer program is stored, wherein the program implements the above-mentioned control method of the water heater when executed by a processor.
  • the refrigerant saturation temperature corresponding to the pressure at the refrigerant outlet pipe of the water side heat exchanger is obtained, recorded as the first temperature, the outlet water temperature of the water side heat exchanger is obtained, and the first temperature is compared with the outlet water temperature to obtain a first comparison result;
  • the temperature at the refrigerant outlet pipe of the water side heat exchanger is obtained, recorded as the second temperature, the inlet water temperature of the water side heat exchanger is obtained, and the second temperature is compared with the inlet water temperature to obtain a second comparison result;
  • the opening of the expansion valve is adjusted according to the first comparison result and the second comparison result; the opening of the expansion valve is adjusted by judging the heat exchange state of the water side heat exchanger, which can facilitate sufficient condensation of the water side heat exchanger and has high adjustment accuracy.
  • FIG1 is a schematic diagram of a water heater unit according to some embodiments of the present disclosure.
  • FIG2 is a flow chart of a control method for a water heater unit according to some embodiments of the present disclosure.
  • Some embodiments of the present disclosure provide a control method, system and computer-readable storage medium for a water heater unit, which are used to alleviate the problem of inaccurate expansion valve regulation.
  • FIG. 1 is a schematic structural diagram of some embodiments of a water heater according to the present disclosure
  • FIG. 2 is a schematic flow diagram of some embodiments of a control method of a water heater according to the present disclosure.
  • the water heater unit includes a compressor 1 , a water-side heat exchanger 2 , an evaporative heat exchanger 3 , and an expansion valve 4 , wherein the expansion valve 4 is located between the water-side heat exchanger 2 and the evaporative heat exchanger 3 .
  • the control methods of the hot water unit include:
  • the refrigerant saturation temperature corresponding to the pressure at the refrigerant outlet pipe of the water side heat exchanger 2 record it as the first temperature, obtain the outlet water temperature of the water side heat exchanger 2, compare the first temperature with the outlet water temperature, and obtain a first comparison result;
  • the temperature at the refrigerant outlet pipe of the water-side heat exchanger 2 is obtained, recorded as the second temperature, the water inlet temperature of the water-side heat exchanger 2 is obtained, and the second temperature is compared with the water inlet temperature to obtain a second comparison result;
  • the opening degree of the expansion valve 4 is adjusted according to the first comparison result and the second comparison result.
  • the disclosed embodiment adjusts the opening of the expansion valve 4 by judging the heat exchange state of the water-side heat exchanger 2, which can facilitate sufficient condensation of the water-side heat exchanger 2 and accurate adjustment of the expansion valve 4. It is not only suitable for high-temperature operation of the unit, but also suitable for low-temperature operation of the unit, and solves the problem of abnormal adjustment failure caused by humidity differences and differences in detection accuracy of temperature sensing elements, thereby improving the operating performance and reliability of the unit.
  • the expansion valve 4 includes an electronic expansion valve.
  • the control method of the hot water unit can be to detect the temperature information and compare it after the compressor 1 starts for a preset time, and adjust the opening of the expansion valve 4 according to the comparison result.
  • the temperature information is detected and compared, and the opening of the expansion valve 4 is adjusted according to the comparison result.
  • the water heater unit further includes a pressure detection element 7 , and the pressure detection element 7 is configured to detect the pressure at the refrigerant outlet pipe of the water-side heat exchanger 2 .
  • the refrigerant saturation temperature corresponding to the pressure at the refrigerant outlet pipe of the water-side heat exchanger 2 can be obtained by looking up a table.
  • the state of the refrigerant after heat exchange can be judged, and further it can be judged whether the heat exchange of the water side heat exchanger 2 is sufficient.
  • the water heater unit further includes a first temperature sensing element 81 , and the first temperature sensing element 81 is configured to detect the outlet water temperature of the water-side heat exchanger 2 .
  • the water heater unit further includes a second temperature sensing element 82 , and the second temperature sensing element 82 is configured to detect the inlet water temperature of the water-side heat exchanger 2 .
  • the water heater unit further includes a third temperature sensing element 83 , and the third temperature sensing element 83 is configured to detect the temperature at the refrigerant outlet pipe of the water-side heat exchanger 2 .
  • the evaporative heat exchanger 3 comprises a fin heat exchanger.
  • the hot water unit also includes a flash evaporator 5,
  • the expansion valve 4 includes a first expansion valve 41 and a second expansion valve 42, and along the flow direction of the refrigerant discharged from the outlet of the compressor 1, the water side heat exchanger 2, the first expansion valve 41, the flash evaporator 5, the second expansion valve 42 and the evaporative heat exchanger 3 are arranged in sequence from upstream to downstream.
  • Adjusting the opening degree of the expansion valve 4 according to the first comparison result and the second comparison result includes adjusting the opening degree of at least one of the first expansion valve 41 and the second expansion valve 42 .
  • the first comparison result is that the first temperature is higher than the outlet water temperature plus the first preset temperature
  • the second comparison result is that the second temperature is lower than or equal to the inlet water temperature plus the first preset temperature
  • the disclosed embodiment adjusts the opening of the expansion valve 4 by judging the heat exchange state of the water-side heat exchanger 2, and adjusts the opening of the first expansion valve 41 and the second expansion valve 42 in combination with the situation that the actual ambient temperature is lower than the preset ambient temperature, thereby solving the problem of inaccurate expansion valve flow regulation under low-temperature conditions of the hot water unit in the related art, improving the reliability of the expansion valve flow regulation under low-temperature conditions of the hot water unit, and improving the operating performance of the unit.
  • the opening of the second expansion valve 42 is increased and the opening of the first expansion valve 41 is maintained.
  • the first temperature is greater than or equal to the outlet water temperature plus the first preset temperature
  • the second temperature is greater than or equal to the inlet water temperature.
  • the disclosed embodiment adjusts the opening of the expansion valve 4 by judging the heat exchange state of the water-side heat exchanger 2, and adjusts the opening of the first expansion valve 41 and the second expansion valve 42 in combination with the situation that the actual ambient temperature is lower than the preset ambient temperature, thereby solving the problem of inaccurate expansion valve flow regulation under low-temperature conditions of the hot water unit in the related art, improving the reliability of the expansion valve flow regulation under low-temperature conditions of the hot water unit, and improving the operating performance of the unit.
  • the opening of the first expansion valve 41 is adjusted to be reduced, and the opening of the second expansion valve 42 is maintained.
  • the first temperature is greater than or equal to the outlet water temperature + the first preset temperature, or until the second temperature is less than or equal to the inlet water temperature.
  • the disclosed embodiment adjusts the opening of the expansion valve 4 by judging the heat exchange state of the water-side heat exchanger 2, and adjusts the opening of the first expansion valve 41 and the second expansion valve 42 in combination with the situation that the actual ambient temperature is lower than the preset ambient temperature, thereby solving the problem of inaccurate expansion valve flow regulation under low-temperature conditions of the hot water unit in the related art, improving the reliability of the expansion valve flow regulation under low-temperature conditions of the hot water unit, and improving the operating performance of the unit.
  • the inlet temperature of the compressor 1 is obtained and recorded as the third temperature
  • the temperature at the refrigerant inlet pipe of the evaporative heat exchanger 3 is obtained and recorded as the fourth temperature
  • the third temperature is compared with the fourth temperature to obtain a third comparison result
  • the opening of at least one of the first expansion valve 41 and the second expansion valve 42 is adjusted according to the third comparison result and the first comparison result and the second comparison result.
  • the state of the refrigerant at the inlet of the compressor 1 can be determined, and the state of the refrigerant includes a gaseous state, a liquid state, and a gas-liquid two-phase state, wherein the gaseous state includes a just gaseous state and an overheated state. If the third temperature is too high, it indicates that the refrigerant at the inlet of the compressor 1 is overheated. Under ideal conditions, the state of the refrigerant at the inlet of the compressor 1 is a just gaseous state.
  • the water heater unit further includes a fourth temperature sensing element 84 , which is configured to detect the inlet temperature of the compressor 1 .
  • the water heater unit further includes a fifth temperature sensing element 85 , which is configured to detect the temperature at the refrigerant inlet pipe of the evaporative heat exchanger 3 .
  • the water heater unit further includes a sixth temperature sensing element 86 , which is configured to detect the outlet temperature of the compressor 1 .
  • the opening of the expansion valve 4 is too small and the refrigerant circulation is insufficient; or the actual ambient temperature is high and the heat exchange capacity of the evaporative heat exchanger 3 is in surplus, then the opening of the second expansion valve 42 is preferentially increased until the third temperature minus the fourth temperature is equal to the second preset temperature, or until the opening of the second expansion valve 42 reaches the maximum.
  • the opening of the first expansion valve 41 is adjusted to increase, and the opening of the second expansion valve 42 is maintained.
  • the first temperature is less than or equal to the outlet water temperature plus the first preset temperature.
  • the third temperature minus the fourth temperature is greater than the second preset temperature, it can be determined that the refrigerant at the inlet of the compressor 1 is overheated.
  • the opening of the first expansion valve 41 is decreased.
  • the opening of the first expansion valve 41 is decreased.
  • the third comparison result is that the third temperature minus the fourth temperature is less than the second preset temperature, and the actual ambient temperature is greater than or equal to the preset ambient temperature, it is judged that the opening of the expansion valve 4 is too large, and the refrigerant evaporation heat exchange is insufficient. At this time, corresponding control is performed according to the following judgment:
  • the second comparison result is When the second temperature is less than or equal to the inlet water temperature plus the first floating temperature, the opening of the first expansion valve 41 is increased and the opening of the second expansion valve 42 is decreased. Optionally, until the third temperature minus the fourth temperature is equal to the second preset temperature, the opening of the second expansion valve 42 is maintained; until the first temperature is less than or equal to the outlet water temperature plus the first preset temperature, the opening of the first expansion valve 41 is maintained.
  • the opening of the first expansion valve 41 is decreased.
  • the opening of the first expansion valve 41 is decreased.
  • the selection range of the first preset temperature is narrower than the selection range when the actual ambient temperature is high, and the selection range value is lower.
  • the accuracy of the value of this first preset temperature directly affects the control result.
  • the optimal value of this first preset temperature is determined by the selection of the heat exchanger, and its value needs to be obtained through experiments.
  • the value law of the first preset temperature is generally proportional to the actual ambient temperature and inversely proportional to the outlet water temperature. After the first preset temperature is determined, since the water temperature will not be lower than 0°C, the temperature detection accuracy remains at a high level. Therefore, the control method provided in the embodiment of the present disclosure can ensure accurate control of the refrigeration cycle volume.
  • the preset ambient temperature is 5° C.
  • the value of the first preset temperature is as follows:
  • the outlet water temperature is ⁇ 40°C
  • the value range of the first preset temperature is 5°C to 15°C.
  • the value range of the first preset temperature is 4°C to 7°C.
  • the outlet water temperature is ⁇ 40°C
  • the value range of the first preset temperature is 5°C to 10°C.
  • the value range of the first preset temperature is 2°C to 5°C.
  • the second preset temperature ranges from [1° C., 3° C.].
  • the first floating temperature ranges from -2°C to 2°C.
  • the first floating temperature is set in the embodiment of the present disclosure to ensure that the refrigerant and water are fully exchanged with each other in the water-side heat exchanger 2. If the temperature of the refrigerant and the water are close, it means that the heat exchange is complete.
  • the second floating temperature ranges from [1° C. to 5° C.].
  • the second floating temperature is set to buffer and avoid slight fluctuations in system parameters that may cause frequent valve movements.
  • the preset ambient temperature is 5°C.
  • the water heater unit further includes a first valve 61 , which is configured to control the flow direction of the refrigerant at the outlet of the compressor 1 and to guide the refrigerant to the inlet of the compressor 1 .
  • the first valve 61 comprises a four-way valve.
  • the hot water unit further includes an enthalpy increasing pipeline connecting the compressor 1 and the flash evaporator 5 and a second valve 62, and the second valve 62 is arranged on the enthalpy increasing pipeline.
  • the second valve 62 includes a solenoid valve.
  • the hot water unit also includes a gas-liquid separator 9, which is arranged on the pipeline at the inlet of the compressor 1.
  • the refrigerant flowing to the inlet of the compressor 1 first enters the gas-liquid separator 9, and then flows to the inlet of the compressor 1 through the pipeline.
  • the control method of the hot water unit provided in the embodiment of the present disclosure can adjust the opening of the expansion valve by detecting the operating parameters 3 minutes after the compressor is started.
  • the refrigerant saturation temperature corresponding to the pressure at the refrigerant outlet pipe of the water-side heat exchanger 2 is recorded as the first temperature
  • the temperature at the refrigerant outlet pipe of the water-side heat exchanger 2 is recorded as the second temperature
  • the inlet temperature of compressor 1 is recorded as the third temperature
  • the temperature at the refrigerant inlet pipe of the evaporative heat exchanger 3 is recorded as the fourth temperature.
  • Case 1 If the actual ambient temperature is less than the preset ambient temperature, optionally, the preset ambient temperature is 5°C. Due to the low ambient temperature, the detection accuracy of the inlet temperature of the compressor 1 and the temperature at the refrigerant inlet pipe of the evaporative heat exchanger 3 is insufficient.
  • the first expansion valve 41 and the second expansion valve 42 are adjusted according to the following cases:
  • Case 11 If the first temperature is greater than the outlet water temperature + the first preset temperature, and the second temperature is less than or equal to the inlet water temperature + the first floating temperature, optionally, the first floating temperature is 2°C, then the opening of the first expansion valve 41 is increased and the opening of the second expansion valve 42 is maintained until the first temperature is less than or equal to the outlet water temperature + the first preset temperature or the second temperature is greater than or equal to the inlet water temperature.
  • Case 12 If the first temperature is less than the outlet water temperature + the first preset temperature, and the second temperature is less than or equal to the inlet water temperature + the first floating temperature, optionally, the first floating temperature is 2°C, then the opening of the second expansion valve 42 is adjusted to increase until the first temperature is greater than or equal to the outlet water temperature + the first preset temperature or the second temperature is greater than or equal to the inlet water temperature.
  • Case 13 If the first temperature is less than the outlet water temperature + the first preset temperature, and the second temperature is greater than the inlet water temperature + the first floating temperature, optionally, the first floating temperature is 2°C, then the opening of the first expansion valve 41 is adjusted to be reduced, and the opening of the second expansion valve 42 is maintained until the first temperature is ⁇ the outlet water temperature + the first preset temperature or the second temperature is ⁇ the inlet water temperature.
  • Case 14 If the situation is other than cases 11), 12), or 13), the first expansion valve 41 and the second expansion valve 42 maintain their current corresponding openings.
  • Case 21 If the first temperature is greater than the outlet water temperature + the first preset temperature, and the second temperature is less than or equal to the inlet water temperature + the first floating temperature, optionally, the first floating temperature is 2°C, then the opening of the first expansion valve 41 is increased until the first temperature is less than or equal to the outlet water temperature + the first preset temperature.
  • Case 23 If it is a case other than Case 21) and Case 22), the current opening degree of the first expansion valve 41 is maintained.
  • situation 21 by adjusting and increasing the opening of the first expansion valve 41, the pressure at the refrigerant outlet pipe of the water side heat exchanger 2 will decrease, and the corresponding refrigerant saturation temperature will decrease, that is, the first temperature will decrease, and then the inlet temperature (intake temperature) of the compressor 1 will decrease, that is, the intake superheat of the compressor 1 will decrease. Therefore, situation 22) or situation 23) can be met, and the ultimate goal is to stay in situation 23).
  • situation 21 the purpose is to bring the system into the predetermined area, which is a rough adjustment; situation 22) is to adjust the system to the optimal state, which is a fine adjustment.
  • the adjustment process is dynamic and oscillating. It is allowed to adjust situation 22) to situation 21) and other situations. The ultimate goal is to stay in situation 23).
  • the refrigerant in the evaporative heat exchanger 3 cannot be fully evaporated, and the amount of refrigerant entering the evaporative heat exchanger 3 needs to be reduced. Therefore, the opening of the second expansion valve 42 is adjusted to be reduced; while the heat exchange of the water side heat exchanger 2 is normal, but the pressure is too high and needs to be released, then the opening of the first expansion valve 41 is adjusted to be increased.
  • Case 32 If the first temperature is less than the outlet water temperature + the first preset temperature + the second floating temperature, optionally, the second floating temperature is 1°C, or, after adjusting to increase the opening of the first expansion valve 41 and adjusting to decrease the opening of the second expansion valve 42, the first temperature is made less than the outlet water temperature + the first preset temperature + the second floating temperature, optionally, the second floating temperature is 1°C, then adjust to decrease the opening of the first expansion valve 41 until the first temperature is ⁇ the outlet water temperature + the first preset temperature, and the second temperature is ⁇ the inlet water temperature.
  • situation 31 the purpose is to bring the system into the predetermined area, which is a rough adjustment; situation 32) is to adjust the system to the optimal state, which is a fine adjustment.
  • the adjustment process is dynamic and oscillating. It is allowed to adjust situation 32) to situation 31) after adjustment, and the ultimate goal is to stay in situation 33).
  • the preset ambient temperature is set to 5°C based on the error accuracy of the temperature sensing element. Below 5°C, the accuracy of the temperature sensing element is low, and the lower the ambient temperature, the greater the deviation. 40°C is the design water temperature of the product.
  • the control method of the water heater provided in the embodiment of the present disclosure adjusts the opening of the first expansion valve 41 and the second expansion valve 42 to make the evaporation heat exchanger 3 fully evaporate and the water side heat exchanger 2 fully condense.
  • the third temperature - the fourth temperature the second preset temperature, which can help the refrigerant to fully absorb the heat in the environment and fully vaporize the refrigerant, thereby ensuring the energy efficiency of the unit and preventing the suction liquid from causing harm to the compressor 1.
  • the third temperature - the fourth temperature ⁇ the second preset temperature there is a risk of liquid return, and the liquid return will damage the service life of the compressor 1.
  • Some embodiments further provide a control system for a water heater unit, which includes a memory and a processor.
  • the processor is connected to the memory signal, and is configured to execute the control method of the water heater unit based on the instructions stored in the memory.
  • Some embodiments further provide a computer-readable storage medium having a computer program stored thereon, wherein the program, when executed by a processor, implements the above-mentioned control method of the water heater unit.

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  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
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  • Combustion & Propulsion (AREA)
  • Heat-Pump Type And Storage Water Heaters (AREA)

Abstract

本公开涉及一种热水机组的控制方法、系统及计算机可读存储介质。其中，热水机组包括压缩机、水侧换热器、蒸发换热器和膨胀阀，膨胀阀位于水侧换热器与蒸发换热器之间，热水机组的控制方法包括：获取水侧换热器的冷媒出管处的压力对应的冷媒饱和温度，记为第一温度，获取水侧换热器的出水温度，将第一温度与出水温度进行比较，获得第一比较结果；获取水侧换热器的冷媒出管处的温度，记为第二温度，获取水侧换热器的进水温度，将第二温度与进水温度进行比较，获得第二比较结果；根据第一比较结果和第二比较结果调节膨胀阀的开度。通过判断水侧换热器的换热状态来调节膨胀阀的开度，能够利于水侧换热器冷凝充分，调节准确性高。

Description

热水机组的控制方法、系统及计算机可读存储介质
本公开是以CN申请号为202211175680.1，申请日为2022年9月26日的申请为 基础，并主张其优先权，该CN申请的公开内容在此作为整体引入本申请中。
技术领域
本公开涉及热泵系统领域，尤其涉及一种热水机组的控制方法、系统及计算机可读存储介质。
背景技术
在一些相关技术中，热泵热水机组节流装置多采用膨胀阀，其控制目标是蒸发换热器的过热度，该控制方案在蒸发环境温度高时，能准确控制冷媒循环量，确保机组性能发挥。但在蒸发环境温度低时，由于空气焓值下降，同等配置下蒸发换热器出口冷媒过热度将无法保证，此时通常的做法是按温度给定一个膨胀阀下限开度，令膨胀阀不至于过调导致冷媒循环量不足，该做法带来两个问题：一是空气焓值受湿度影响较大，无法通过温度来确定焓值，所以制定膨胀阀下限后，无法验证其准确性，即使增加湿度传感器，也无法面面俱到的将所有情形验证完；二是温度传感器无法兼顾高温环境和低温环境的检测精度，总体呈现中间精度高、两端精度低的趋势，精度最高在25℃附近，对常温热泵此精度可以满足使用，而对于运行范围更宽的低温热泵来说，温度传感器的精度就相形见绌，低温运行时无法精确检测出蒸发换热器出口冷媒的过热度，导致膨胀阀调节失效。
发明内容
在本公开的一个方面，提供一种热水机组的控制方法，其中，热水机组包括压缩机、水侧换热器、蒸发换热器和膨胀阀，所述膨胀阀位于所述水侧换热器与所述蒸发换热器之间，所述热水机组的控制方法包括：
获取水侧换热器的冷媒出管处的压力对应的冷媒饱和温度，记为第一温度，获取水侧换热器的出水温度，将第一温度与出水温度进行比较，获得第一比较结果；
获取水侧换热器的冷媒出管处的温度，记为第二温度，获取水侧换热器的进水温 度，将第二温度与进水温度进行比较，获得第二比较结果；
根据第一比较结果和第二比较结果调节膨胀阀的开度。
在一些实施例中，所述热水机组还包括闪蒸器，所述膨胀阀包括第一膨胀阀和第二膨胀阀，沿所述压缩机的出口排出的冷媒流向，所述水侧换热器、所述第一膨胀阀、所述闪蒸器、所述第二膨胀阀和所述蒸发换热器依次从上游至下游设置；
所述根据第一比较结果和第二比较结果调节膨胀阀的开度，包括调节第一膨胀阀和第二膨胀阀至少之一的开度。
在一些实施例中，如果实际环境温度小于预设环境温度，且第一比较结果为第一温度大于出水温度加第一预设温度，第二比较结果为第二温度小于等于进水温度加第一浮动温度，则调节增大第一膨胀阀的开度，维持第二膨胀阀的开度。
在一些实施例中，如果实际环境温度小于预设环境温度，且第一比较结果为第一温度小于出水温度加第一预设温度，第二比较结果为第二温度小于等于进水温度加第一浮动温度，则调节增大第二膨胀阀的开度，维持第一膨胀阀的开度。
在一些实施例中，如果实际环境温度小于预设环境温度，且第一比较结果为第一温度小于出水温度加第一预设温度，第二比较结果为第二温度大于进水温度加第一浮动温度，则调节减小第一膨胀阀的开度，维持第二膨胀阀的开度。
在一些实施例中，如果实际环境温大于等于预设环境温度，
获取压缩机的进口温度，记为第三温度，获取蒸发换热器的冷媒入管处的温度，记为第四温度，将第三温度与第四温度进行比较，获得第三比较结果，根据第三比较结果以及第一比较结果和第二比较结果调节第一膨胀阀和第二膨胀阀至少之一的开度。
在一些实施例中，如果第三比较结果为第三温度减第四温度大于第二预设温度，且第二膨胀阀已经达到最大开度，且第一比较结果为第一温度大于出水温度加第一预设温度，第二比较结果为第二温度小于等于进水温度加第一浮动温度，则调节增大第一膨胀阀的开度，维持第二膨胀阀的开度。
在一些实施例中，在调节增大第一膨胀阀的开度，维持第二膨胀阀的开度，使第一比较结果为第一温度小于出水温度加第一预设温度加第二浮动温度时，则调节减小第一膨胀阀的开度。
在一些实施例中，如果第三比较结果为第三温度减第四温度小于第二预设温度， 且第一比较结果为第一温度大于出水温度加第一预设温度，第二比较结果为第二温度小于等于进水温度加第一浮动温度，则调节增大第一膨胀阀的开度，调节减小第二膨胀阀的开度。
在一些实施例中，在调节增大第一膨胀阀的开度，调节减小第二膨胀阀的开度，使第一比较结果为第一温度小于出水温度加第一预设温度加第二浮动温度时，则调节减小第一膨胀阀的开度。
在一些实施例中，预设环境温度为5℃时，第一预设温度的取值如下：
实际环境温度≥5℃时，出水温度≤40℃，第一预设温度的取值范围为5℃～15℃，出水温度＞40℃，第一预设温度的取值范围为4℃～7℃；
实际环境温度＜5℃时，出水温度≤40℃，第一预设温度的取值范围为5℃～10℃，出水温度＞40℃，第一预设温度的取值范围为2℃～5℃。
在一些实施例中，所述第二预设温度的取值范围为[1℃,3℃]。
在一些实施例中，所述第一浮动温度的取值范围为[-2℃,2℃]。
在一些实施例中，所述第二浮动温度的取值范围为[1℃,5℃]。
在一些实施例中，所述预设环境温度为5℃。
在本公开的另一个方面，提供一种热水机组的控制系统，包括存储器和处理器，所述处理器与所述存储器信号连接，所述处理器被配置为基于存储在所述存储器中的指令，执行上述热水机组的控制方法。
在本公开的另一个方面，提供一种计算机可读存储介质，其上存储有计算机程序，其中，该程序被处理器执行时实现上述的热水机组的控制方法。
基于上述技术方案，本公开至少具有以下有益效果：
在一些实施例中，获取水侧换热器的冷媒出管处的压力对应的冷媒饱和温度，记为第一温度，获取水侧换热器的出水温度，将第一温度与出水温度进行比较，获得第一比较结果；获取水侧换热器的冷媒出管处的温度，记为第二温度，获取水侧换热器的进水温度，将第二温度与进水温度进行比较，获得第二比较结果；根据第一比较结果和第二比较结果调节膨胀阀的开度；通过判断水侧换热器的换热状态来调节膨胀阀的开度，能够利于水侧换热器冷凝充分，调节准确性高，不仅适用于机组的高温运行，且适用于机组的低温运行，解决了因湿度差异和感温元件检测精度差异产生的调节失效异常的问题，提高了机组的运行性能和可靠性。
附图说明
此处所说明的附图用来提供对本公开的进一步理解，构成本申请的一部分，本公开的示意性实施例及其说明用于解释本公开，并不构成对本公开的不当限定。在附图中：
图1为根据本公开一些实施例提供的热水机组的示意图；
图2为根据本公开一些实施例提供的热水机组的控制方法的流程示意图。
具体实施方式
下面将结合本公开实施例中的附图，对实施例中的技术方案进行清楚、完整地描述。显然，所描述的实施例仅仅是本公开的一部分实施例，而不是全部的实施例。基于本公开的实施例，本领域普通技术人员在没有作出创造性劳动前提下所获得的所有其他实施例，都属于本公开保护的范围。
在本公开的描述中，需要理解的是，术语“中心”、“纵向”、“横向”、“前”、“后”、“左”、“右”、“竖直”、“水平”、“顶”、“底”、“内”、“外”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公开和简化描述，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公开保护范围的限制。
本公开的一些实施例提出一种热水机组的控制方法、系统及计算机可读存储介质，用于缓解膨胀阀调节不准确的问题。
图1是根据本公开热水机组的一些实施例的结构示意图，图2是根据本公开热水机组的控制方法的一些实施例的流程示意图。
参考图1和图2，在一些实施例中，热水机组包括压缩机1、水侧换热器2、蒸发换热器3和膨胀阀4，膨胀阀4位于水侧换热器2与蒸发换热器3之间。
热水机组的控制方法包括：
获取水侧换热器2的冷媒出管处的压力对应的冷媒饱和温度，记为第一温度，获取水侧换热器2的出水温度，将第一温度与出水温度进行比较，获得第一比较结果；
获取水侧换热器2的冷媒出管处的温度，记为第二温度，获取水侧换热器2的进水温度，将第二温度与进水温度进行比较，获得第二比较结果；
根据第一比较结果和第二比较结果调节膨胀阀4的开度。
本公开实施例通过判断水侧换热器2的换热状态来调节膨胀阀4的开度，能够利于水侧换热器2冷凝充分，膨胀阀4调节准确，不仅适用于机组的高温运行，且适用于机组的低温运行，解决了因湿度差异和感温元件检测精度差异产生的调节失效异常的问题，提高了机组的运行性能和可靠性。
可选地，膨胀阀4包括电子膨胀阀。
热水机组的控制方法可以在压缩机1启动预设时间后，再通过检测温度信息进行比较，根据比较结果调节膨胀阀4的开度。
可选地，在压缩机启动3分钟后，检测温度信息进行比较，根据比较结果调节膨胀阀4的开度。
在一些实施例中，热水机组还包括压力检测元件7，压力检测元件7被配置为检测水侧换热器2的冷媒出管处的压力。
水侧换热器2的冷媒出管处的压力对应的冷媒饱和温度可以通过查表获得。
根据水侧换热器2的冷媒出管处的压力对应的冷媒饱和温度，能够来判断冷媒换热之后的状态，进而能够判断水侧换热器2的换热是否充分。
在一些实施例中，热水机组还包括第一感温元件81，第一感温元件81被配置为检测水侧换热器2的出水温度。
在一些实施例中，热水机组还包括第二感温元件82，第二感温元件82被配置为检测水侧换热器2的进水温度。
在一些实施例中，热水机组还包括第三感温元件83，第三感温元件83被配置为检测水侧换热器2的冷媒出管处的温度。
在一些实施例中，蒸发换热器3包括翅片换热器。
在一些实施例中，热水机组还包括闪蒸器5，膨胀阀4包括第一膨胀阀41和第二膨胀阀42，沿压缩机1的出口排出的冷媒流向，水侧换热器2、第一膨胀阀41、闪蒸器5、第二膨胀阀42和蒸发换热器3依次从上游至下游设置。
根据第一比较结果和第二比较结果调节膨胀阀4的开度，包括调节第一膨胀阀41和第二膨胀阀42至少之一的开度。
在一些实施例中，如果实际环境温度小于预设环境温度，且第一比较结果为第一温度大于出水温度加第一预设温度，第二比较结果为第二温度小于等于进水温度加第 一浮动温度，则调节增大第一膨胀阀41的开度，维持第二膨胀阀42的开度。可选地，直至第一温度小于等于出水温度加第一预设温度，或者，直至第二温度大于等于进水温度。
本公开实施例通过判断水侧换热器2的换热状态来调节膨胀阀4的开度，且结合实际环境温度小于预设环境温度的情况，对第一膨胀阀41和第二膨胀阀42的开度进行调节，解决了相关技术中热水机组低温工况下膨胀阀流量调节不准确的问题，提高了热水机组低温工况膨胀阀流量调节的可靠性，提高了机组运行性能。
在一些实施例中，如果实际环境温度小于预设环境温度，且第一比较结果为第一温度小于出水温度加第一预设温度，第二比较结果为第二温度小于等于进水温度加第一浮动温度，则调节增大第二膨胀阀42的开度，维持第一膨胀阀41的开度。可选地，直至第一温度大于等于出水温度加第一预设温度，或者，直至第二温度大于等于进水温度。
本公开实施例通过判断水侧换热器2的换热状态来调节膨胀阀4的开度，且结合实际环境温度小于预设环境温度的情况，对第一膨胀阀41和第二膨胀阀42的开度进行调节，解决了相关技术中热水机组低温工况下膨胀阀流量调节不准确的问题，提高了热水机组低温工况膨胀阀流量调节的可靠性，提高了机组运行性能。
在一些实施例中，如果实际环境温度小于预设环境温度，且第一比较结果为第一温度小于出水温度加第一预设温度，第二比较结果为第二温度大于进水温度加第一浮动温度，则调节减小第一膨胀阀41的开度，维持第二膨胀阀42的开度。可选地，直至第一温度大于等于出水温度+第一预设温度，或者，直至第二温度小于等于进水温度。
本公开实施例通过判断水侧换热器2的换热状态来调节膨胀阀4的开度，且结合实际环境温度小于预设环境温度的情况，对第一膨胀阀41和第二膨胀阀42的开度进行调节，解决了相关技术中热水机组低温工况下膨胀阀流量调节不准确的问题，提高了热水机组低温工况膨胀阀流量调节的可靠性，提高了机组运行性能。
在一些实施例中，如果实际环境温大于等于预设环境温度，则获取压缩机1的进口温度，记为第三温度，获取蒸发换热器3的冷媒入管处的温度，记为第四温度，将第三温度与第四温度进行比较，获得第三比较结果，根据第三比较结果以及第一比较结果和第二比较结果调节第一膨胀阀41和第二膨胀阀42至少之一的开度。
根据比较第三温度与第四温度，能够判断压缩机1的进口处的冷媒的状态，冷媒的状态包括气态、液态和气液两相的状态，其中，气态包括刚好气态和过热。如果第三温度过大，则表明压缩机1的进口处的冷媒过热。理想状态下，压缩机1的进口处的冷媒的状态为刚好气态。
在一些实施例中，热水机组还包括第四感温元件84，第四感温元件84被配置为检测压缩机1的进口温度。
在一些实施例中，热水机组还包括第五感温元件85，第五感温元件85被配置为检测蒸发换热器3的冷媒入管处的温度。
在一些实施例中，热水机组还包括第六感温元件86，第六感温元件86被配置为检测压缩机1的出口温度。
在一些实施例中，如果第三比较结果为第三温度减第四温度大于第二预设温度，实际环境温大于等于预设环境温度，判断为膨胀阀4的开度过小，冷媒流通量不足；或者实际环境温度高，蒸发换热器3的换热量有盈余，此时优先调节增大第二膨胀阀42的开度，直至第三温度减第四温度等于第二预设温度，或者直至第二膨胀阀42的开度达到最大。
如果第二膨胀阀42已经达到最大开度，且第一比较结果为第一温度大于出水温度加第一预设温度，第二比较结果为第二温度小于等于进水温度加第一浮动温度，则调节增大第一膨胀阀41的开度，维持第二膨胀阀42的开度。可选地，直至第一温度小于等于出水温度加第一预设温度。
第三温度减第四温度大于第二预设温度则可判断出压缩机1的进口处的冷媒过热。
在一些实施例中，如果第二膨胀阀42已经达到最大开度，且第一比较结果为第一温度小于出水温度加第一预设温度加第二浮动温度时，或者，在调节增大第一膨胀阀41的开度，维持第二膨胀阀42的开度，使第一比较结果为第一温度小于出水温度加第一预设温度加第二浮动温度时，则调节减小第一膨胀阀41的开度。可选地，直至第二温度小于等于进水温度。
在一些实施例中，如果第三比较结果为第三温度减第四温度小于第二预设温度，实际环境温大于等于预设环境温度，则判断膨胀阀4的开度过大，冷媒蒸发换热不充分，此时根据如下判断进行相应控制：
如果第一比较结果为第一温度大于出水温度加第一预设温度，第二比较结果为第 二温度小于等于进水温度加第一浮动温度，则调节增大第一膨胀阀41的开度，调节减小第二膨胀阀42的开度。可选地，直至第三温度减第四温度等于第二预设温度，维持第二膨胀阀42的开度；直至第一温度小于等于出水温度加第一预设温度，维持第一膨胀阀41的开度。
在一些实施例中，如果第一比较结果为第一温度小于出水温度加第一预设温度加第二浮动温度，或者，在调节增大第一膨胀阀41的开度，调节减小第二膨胀阀42的开度，使第一比较结果为第一温度小于出水温度加第一预设温度加第二浮动温度时，则调节减小第一膨胀阀41的开度。可选地，直至第一温度大于等于出水温度加第一预设温度，第二温度小于等于进水温度。
在实际环境温度较低时，第一预设温度的选取范围比实际环境温度较高时的选取范围窄，且选取范围值较低，此第一预设温度的取值的准确与否，直接影响控制结果，此第一预设温度的最优值由换热器的选型决定，其值需经过实验获取，第一预设温度的取值规律大体为与实际环境温度成正比与出水温成反比，当第一预设温度确定好以后，由于水温不会低于0℃，温度检测精确度保持较高水平，因此采用本公开实施例提供的控制方法可以确保制冷循环量控制准确。
在一些实施例中，预设环境温度为5℃，第一预设温度的取值如下：
实际环境温度≥5℃时，出水温度≤40℃，第一预设温度的取值范围为5℃～15℃，出水温度＞40℃，第一预设温度的取值范围为4℃～7℃；
实际环境温度＜5℃时，出水温度≤40℃，第一预设温度的取值范围为5℃～10℃，出水温度＞40℃，第一预设温度的取值范围为2℃～5℃。
在一些实施例中，第二预设温度的取值范围为[1℃,3℃]。
在一些实施例中，第一浮动温度的取值范围为[-2℃,2℃]。
本公开实施例设置第一浮动温度是为了确保冷媒与水在水侧换热器2内充分换热，冷媒与水温接近，说明已经换热完全。
在一些实施例中，第二浮动温度的取值范围为[1℃,5℃]。
第二浮动温度的设置是用于缓冲，避免系统参数细微波动，引起阀件频繁动作。
在一些实施例中，预设环境温度为5℃。
在一些实施例中，热水机组还包括第一阀61，第一阀61被配置为控制压缩机1的出口冷媒的流向，以及将冷媒导向压缩机1的进口。
可选地，第一阀61包括四通阀。
在一些实施例中，热水机组还包括连接压缩机1与闪蒸器5的增焓管路和第二阀62，第二阀62设于增焓管路。
可选地，第二阀62包括电磁阀。
在一些实施例中，热水机组还包括气液分离器9，气液分离器9设于压缩机1的进口处的管路上，流向压缩机1的进口的冷媒首先进入气液分离器9，然后再通过管路流向压缩机1的进口。
下面根据图1和图2详细说明热水机组的控制方法的一些具体实施例包括的情况和步骤。
本公开实施例提供的热水机组的控制方法可以在压缩机启动3分钟后，通过检测运行参数调整膨胀阀的开度。
定义：水侧换热器2的冷媒出管处的压力对应的冷媒饱和温度，记为第一温度；
水侧换热器2的冷媒出管处的温度，记为第二温度；
压缩机1的进口温度，记为第三温度；
蒸发换热器3的冷媒入管处的温度，记为第四温度。
情况1：如果实际环境温度＜预设环境温度，可选地，预设环境温度为5℃，由于环境温度低，检测压缩机1的进口温度和蒸发换热器3的冷媒入管处的温度检测精度不足，则按照以下情况对第一膨胀阀41和第二膨胀阀42进行调整：
情况11)：若第一温度＞出水温度+第一预设温度，且第二温度≤进水温度+第一浮动温度，可选地，第一浮动温度为2℃，则调节增大第一膨胀阀41的开度，维持第二膨胀阀42的开度，直至第一温度≤出水温度+第一预设温度或第二温度≥进水温度。
情况12)：若第一温度＜出水温度+第一预设温度，且第二温度≤进水温度+第一浮动温度，可选地，第一浮动温度为2℃，则调节增大第二膨胀阀42的开度，直至第一温度≥出水温度+第一预设温度或第二温度≥进水温度。
情况13)：若第一温度＜出水温度+第一预设温度，且第二温度＞进水温度+第一浮动温度，可选地，第一浮动温度为2℃，则调节减少第一膨胀阀41的开度，维持第二膨胀阀42的开度，直至第一温度≥出水温度+第一预设温度或第二温度≤进水温度。
情况14)：若在情况11)、情况12)、情况13)之外的情况，则第一膨胀阀41和第二膨胀阀42维持当前对应的开度。
情况2：当第三温度-第四温度＞第二预设温度(优选值为1℃～3℃)，且实际环境温度≥预设环境温度，可选地，预设环境温度为5℃，判断为膨胀阀4的开度过小，冷媒流通量不足；或是环境温度高，蒸发换热器3的换热量有盈余。此时优先调节增大第二膨胀阀42的开度，直至第三温度-第四温度＝第二预设温度或第二膨胀阀42的开度达到上限值。若第二膨胀阀42的开度已达上限值，则需进一步判断：
情况21)：若第一温度＞出水温度+第一预设温度，且第二温度≤进水温度+第一浮动温度，可选地，第一浮动温度为2℃，则调节增大第一膨胀阀41的开度，直至第一温度≤出水温度+第一预设温度。
情况22)：若第一温度＜出水温度+第一预设温度+第二浮动温度，可选地，第二浮动温度为1℃，或者，在调节增大第一膨胀阀41的开度，维持第二膨胀阀42的开度，使第一温度＜出水温度+第一预设温度+第二浮动温度，可选地，第二浮动温度为1℃(目标是使第一温度-出水温差＝第一预设温度，离第一预设温度1℃以内认为已经很接近目标，不需要调整)，则调节减小第一膨胀阀41的开度，直至第一温度≥出水温度+第一预设温度，且第二温度≤进水温度。
情况23)：若在情况21)和情况22)之外的情况，则维持第一膨胀阀41的当前开度。
对于情况21)，调节增大第一膨胀阀41的开度，水侧换热器2的冷媒出管处的压力会降低，对应的冷媒饱和温度会降低，也就是第一温度降低，进而压缩机1的进口温度(吸气温度)会下降，即压缩机1的吸气过热度会下降，因此，可满足情况22)或情况23)，最终目的是停留在情况23)。
对于情况21)是为了将系统引入预定的区域，属于粗调；情况22)则是将系统调整至最优状态，属于细调。调整过程是动态和震荡的，情况22)调整后转情况21)等情况都是被允许的，最终目的是停留在情况23)。
情况3：当第三温度-第四温度＜第二预设温度，且实际环境温度≥预设环境温度，可选地，预设环境温度为5℃时，判断为膨胀阀4的开度过大，冷媒蒸发换热不充分，此时需根据如下判断进行相应控制：
情况31)：若第一温度＞出水温度+第一预设温度，且第二温度≤进水温度+第一浮动温度，可选地，第一浮动温度为2℃，则调节增大第一膨胀阀41的开度，调节减少第二膨胀阀42的开度；至第三温度-第四温度＝第二预设温度，维持第二膨胀阀42 的开度；直至第一温度≤出水温度+第一预设温度，维持第一膨胀阀41的开度。
对于情况31)，蒸发换热器3内的冷媒无法充分蒸发，需要减少进入蒸发换热器3的冷媒量，因此，调节减少第二膨胀阀42的开度；而水侧换热器2的换热正常，但压力过高，需要释放压力，则调节增大第一膨胀阀41的开度。
情况32)：若第一温度＜出水温度+第一预设温度+第二浮动温度，可选地，第二浮动温度为1℃，或者，在调节增大第一膨胀阀41的开度，调节减少第二膨胀阀42的开度后，使第一温度＜出水温度+第一预设温度+第二浮动温度，可选地，第二浮动温度为1℃，则调节减少第一膨胀阀41的开度，直至第一温度≥出水温度+第一预设温度，且第二温度≤进水温度。
情况33)：若在情况31)和情况32)之外的情况，维持第一膨胀阀41的当前开度，调节减少第二膨胀阀42的开度，直至第三温度-第四温度＝第二预设温度。
对于情况31)是为了将系统引入预定的区域，属于粗调；情况32)则是将系统调整至最优状态，属于细调。调整过程是动态和震荡的，情况32)调整后转情况31)等情况都是被允许的，最终目的是停留在情况33)。
对于情况2和情况3，在第三温度-第四温度＝第二预设温度，且第一温度＝出水温度+第一预设温度，则认为机组此时不需要再做调整。
预设环境温度设为5℃是根据感温元件的误差精度来确定的，低于5℃感温元件的精度偏低，环境温度越低偏差越大。40℃是产品的设计水温。
本公开实施例提供的热水机组的控制方法，通过调节第一膨胀阀41和第二膨胀阀42的开度，以使蒸发换热器3蒸发充分、水侧换热器2冷凝充分。对于情况2和情况3，蒸发充分和冷凝充分的判定条件分别是第三温度-第四温度＝第二预设温度，第一温度＝出水温度+第一预设温度。
第三温度-第四温度＝第二预设温度，能够利于冷媒充分吸收环境中的热量，使冷媒充分气化，既能确保机组运行能效，也能防止吸气带液对压缩机1产生危害。
第三温度-第四温度＞第二预设温度，冷媒流量小，没有充分发挥换热器的作用；有害过热，影响运行效率。
第三温度-第四温度＜第二预设温度，存在回液风险，回液会损害压缩机1的运行寿命。
一些实施例还提供了一种热水机组的控制系统，其包括存储器和处理器，处理器 与存储器信号连接，处理器被配置为基于存储在存储器中的指令，执行上述热水机组的控制方法。
一些实施例还提供了一种计算机可读存储介质，其上存储有计算机程序，其中，该程序被处理器执行时实现上述的热水机组的控制方法。
基于上述本公开的各实施例，在没有明确否定或冲突的情况下，其中一个实施例的技术特征可以有益地与其他一个或多个实施例相互结合。
最后应当说明的是:以上实施例仅用以说明本公开的技术方案而非对其限制；尽管参照较佳实施例对本公开进行了详细的说明，所属领域的普通技术人员应当理解：依然可以对本公开的具体实施方式进行修改或者对部分技术特征进行等同替换；而不脱离本公开技术方案的精神，其均应涵盖在本公开请求保护的技术方案范围当中。

Claims (17)

  1. 一种热水机组的控制方法，其中热水机组包括压缩机(1)、水侧换热器(2)、蒸发换热器(3)和膨胀阀(4)，所述膨胀阀(4)位于所述水侧换热器(2)与所述蒸发换热器(3)之间，所述热水机组的控制方法包括：
    获取水侧换热器(2)的冷媒出管处的压力对应的冷媒饱和温度，记为第一温度，获取水侧换热器(2)的出水温度，将第一温度与出水温度进行比较，获得第一比较结果；
    获取水侧换热器(2)的冷媒出管处的温度，记为第二温度，获取水侧换热器(2)的进水温度，将第二温度与进水温度进行比较，获得第二比较结果；
    根据第一比较结果和第二比较结果调节膨胀阀(4)的开度。
  2. 如权利要求1所述的热水机组的控制方法，其中所述热水机组还包括闪蒸器(5)，所述膨胀阀(4)包括第一膨胀阀(41)和第二膨胀阀(42)，沿所述压缩机(1)的出口排出的冷媒流向，所述水侧换热器(2)、所述第一膨胀阀(41)、所述闪蒸器(5)、所述第二膨胀阀(42)和所述蒸发换热器(3)依次从上游至下游设置；
    所述根据第一比较结果和第二比较结果调节膨胀阀(4)的开度，包括调节第一膨胀阀(41)和第二膨胀阀(42)至少之一的开度。
  3. 如权利要求2所述的热水机组的控制方法，其中如果实际环境温度小于预设环境温度，且第一比较结果为第一温度大于出水温度加第一预设温度，第二比较结果为第二温度小于等于进水温度加第一浮动温度，则调节增大第一膨胀阀(41)的开度，维持第二膨胀阀(42)的开度。
  4. 如权利要求2或3所述的热水机组的控制方法，其中如果实际环境温度小于预设环境温度，且第一比较结果为第一温度小于出水温度加第一预设温度，第二比较结果为第二温度小于等于进水温度加第一浮动温度，则调节增大第二膨胀阀(42)的开度，维持第一膨胀阀(41)的开度。
  5. 如权利要求2至4任一项所述的热水机组的控制方法，其中如果实际环境温度小于预设环境温度，且第一比较结果为第一温度小于出水温度加第一预设温度，第二比较结果为第二温度大于进水温度加第一浮动温度，则调节减小第一膨胀阀(41)的开度，维持第二膨胀阀(42)的开度。
  6. 如权利要求2至5任一项所述的热水机组的控制方法，其中如果实际环境温大于等于预设环境温度，
    获取压缩机(1)的进口温度，记为第三温度，获取蒸发换热器(3)的冷媒入管处的温度，记为第四温度，将第三温度与第四温度进行比较，获得第三比较结果，根据第三比较结果以及第一比较结果和第二比较结果调节第一膨胀阀(41)和第二膨胀阀(42)至少之一的开度。
  7. 如权利要求6所述的热水机组的控制方法，其中如果第三比较结果为第三温度减第四温度大于第二预设温度，且第二膨胀阀(42)已经达到最大开度，且第一比较结果为第一温度大于出水温度加第一预设温度，第二比较结果为第二温度小于等于进水温度加第一浮动温度，则调节增大第一膨胀阀(41)的开度，维持第二膨胀阀(42)的开度。
  8. 如权利要求7所述的热水机组的控制方法，其中在调节增大第一膨胀阀(41)的开度，维持第二膨胀阀(42)的开度，使第一比较结果为第一温度小于出水温度加第一预设温度加第二浮动温度时，则调节减小第一膨胀阀(41)的开度。
  9. 如权利要求6至8任一项所述的热水机组的控制方法，其中如果第三比较结果为第三温度减第四温度小于第二预设温度，且第一比较结果为第一温度大于出水温度加第一预设温度，第二比较结果为第二温度小于等于进水温度加第一浮动温度，则调节增大第一膨胀阀(41)的开度，调节减小第二膨胀阀(42)的开度。
  10. 如权利要求9所述的热水机组的控制方法，其中在调节增大第一膨胀阀(41)的开度，调节减小第二膨胀阀(42)的开度，使第一比较结果为第一温度小于出水温度加第一预设温度加第二浮动温度时，则调节减小第一膨胀阀(41)的开度。
  11. 如权利要求3至10任一项所述的热水机组的控制方法，其中预设环境温度为5℃时，第一预设温度的取值如下：
    实际环境温度≥5℃时，出水温度≤40℃，第一预设温度的取值范围为5℃～15℃，出水温度＞40℃，第一预设温度的取值范围为4℃～7℃；
    实际环境温度＜5℃时，出水温度≤40℃，第一预设温度的取值范围为5℃～10℃，出水温度＞40℃，第一预设温度的取值范围为2℃～5℃。
  12. 如权利要求7至11任一项所述的热水机组的控制方法，其中所述第二预设温度的取值范围为[1℃,3℃]。
  13. 如权利要求3至12任一项所述的热水机组的控制方法，其中所述第一浮动温度的取值范围为[-2℃,2℃]。
  14. 如权利要求8或13所述的热水机组的控制方法，其中所述第二浮动温度的取值范围为[1℃,5℃]。
  15. 如权利要求3至14任一项所述的热水机组的控制方法，其中所述预设环境温度为5℃。
  16. 一种热水机组的控制系统，包括存储器和处理器，所述处理器与所述存储器信号连接，所述处理器被配置为基于存储在所述存储器中的指令，执行如权利要求1至15任一项所述的控制方法。
  17. 一种计算机可读存储介质，其上存储有计算机程序，其中，该程序被处理器执行时实现如权利要求1至15任一所述的控制方法。
PCT/CN2023/092034 2022-09-26 2023-05-04 热水机组的控制方法、系统及计算机可读存储介质 WO2024066353A1 (zh)

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