EP4027070B1 - Total heat recovery defrosting control method and control device, and air conditioning apparatus - Google Patents

Total heat recovery defrosting control method and control device, and air conditioning apparatus Download PDF

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Publication number
EP4027070B1
EP4027070B1 EP20860254.0A EP20860254A EP4027070B1 EP 4027070 B1 EP4027070 B1 EP 4027070B1 EP 20860254 A EP20860254 A EP 20860254A EP 4027070 B1 EP4027070 B1 EP 4027070B1
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EP
European Patent Office
Prior art keywords
heat recovery
temperature
demand
heated water
heating
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.)
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Application number
EP20860254.0A
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German (de)
English (en)
French (fr)
Other versions
EP4027070C0 (en
EP4027070A1 (en
EP4027070A4 (en
Inventor
Yu LENG
Hui Sun
Lei Zhao
Zhenhong Li
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.)
Qingdao Haier Air Conditioning Electric Co Ltd
Haier Smart Home Co Ltd
Original Assignee
Qingdao Haier Air Conditioning Electric Co Ltd
Haier Smart Home Co Ltd
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Application filed by Qingdao Haier Air Conditioning Electric Co Ltd, Haier Smart Home Co Ltd filed Critical Qingdao Haier Air Conditioning Electric Co Ltd
Publication of EP4027070A1 publication Critical patent/EP4027070A1/en
Publication of EP4027070A4 publication Critical patent/EP4027070A4/en
Application granted granted Critical
Publication of EP4027070C0 publication Critical patent/EP4027070C0/en
Publication of EP4027070B1 publication Critical patent/EP4027070B1/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F12/00—Use of energy recovery systems in air conditioning, ventilation or screening
    • F24F12/001—Use of energy recovery systems in air conditioning, ventilation or screening with heat-exchange between supplied and exhausted air
    • 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
    • F24F11/42—Defrosting; Preventing freezing of outdoor units
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/62—Control or safety arrangements characterised by the type of control or by internal processing, e.g. using fuzzy logic, adaptive control or estimation of values
    • F24F11/63—Electronic processing
    • F24F11/64—Electronic processing using pre-stored data
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/62—Control or safety arrangements characterised by the type of control or by internal processing, e.g. using fuzzy logic, adaptive control or estimation of values
    • F24F11/63—Electronic processing
    • F24F11/65—Electronic processing for selecting an operating mode
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/70—Control systems characterised by their outputs; Constructional details thereof
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/88—Electrical aspects, e.g. circuits
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
    • F24D3/00—Hot-water central heating systems
    • F24D3/08—Hot-water central heating systems in combination with systems for domestic hot-water supply
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F2140/00—Control inputs relating to system states
    • F24F2140/20—Heat-exchange fluid temperature
    • 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
    • F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
    • F25B47/02—Defrosting cycles

Definitions

  • the invention belongs to the technical field of air conditioning, and in particular relates to a total heat recovery defrosting control method, a total heat recovery defrosting control system and an air conditioning device.
  • An air conditioning device with total heat recovery function refers to an air conditioning unit that integrates functions such as cooling, heating and supplying domestic heated water.
  • this type of air conditioning device includes a compressor, an outdoor air-side fin heat exchanger that exchanges heat with air, a water-side heat exchanger, a total heat recovery heat exchanger that recovers wasted heat, a four-way valve, an electronic expansion valve, an accumulator and a plurality of execution components arranged in the refrigerant system configured to adjust refrigerant flow and directions to perform different functions such as solenoid valves and one-way valves.
  • the air conditioning device with total heat recovery function could have multiple function modes, such as heating mode, cooling mode, heated water supply mode and the like.
  • Chinese Patent CN201212721Y ) discloses the refrigerant circulation structure and working process of the air conditioning device with total heat recovery mechanism.
  • Document GB2537453A discloses the implementation of a defrosting operation put in relation with a selected operation mode of the heat pump, namely hot water production or heating and hot water production.
  • frost may build up on the surface of the outdoor air-side fin heat exchanger.
  • the heat capacity of the outdoor air-side fin heat exchanger is gradually reduced as the thermal resistance increases, which is caused by the accumulation of frost and drops rapidly if the frost grows to a certain thickness.
  • a corresponding heating defrost mode and a heated water defrost mode are pre-established.
  • high-temperature and high-pressure refrigerant discharged from the compressor flows into the outdoor air-side fin heat exchanger through the four-way valve to defrost and condenses to a medium-temperature and medium-pressure liquid refrigerant; the medium-temperature and medium-pressure refrigerant is supercooled by passing through components such as the accumulator and an economizer and changes into low-temperature and low-pressure refrigerant through the throttling device for extracting heat from water for air conditioning in the indoor water-side heat exchanger.
  • a total heat recovery defrosting control method is provided by the present invention.
  • a total heat recovery defrosting control method as defined in claim 1 comprises: operating a total heat recovery unit in a heating mode or in a heated water supply mode; determining whether a current operating condition satisfies a set defrost operating condition; comparing a heating demand with a heated water demand if it is determined that the current operating condition satisfies the set defrost operating condition, performing a heated water defrost mode if the heating demand is higher than the heated water demand; or performing a heating defrost mode if the heated water demand is higher than the heating demand.
  • the process that comparing the heating demand with the heated water demand includes: acquiring a rate of change ⁇ T wi of the inlet water temperature at the heat recovery heat exchanger side within a preset sampling period; acquiring a rate of change ⁇ T h of the outlet water temperature at the heat recovery heat exchanger side within a preset sampling period; it is determined that the heating demand is greater than the heated water demand if ⁇ T wi > ⁇ T h and the heated water defrost mode is executed; or it is determined that the heated water demand is greater than the heating demand if ⁇ T wi ⁇ ⁇ T h and the heating defrost mode is executed.
  • the time duration of the preset sampling period is 30 minutes.
  • set defrost operating condition includes: continuous operating time is greater than or equal to a set operating period and a coil temperature of an outdoor heat exchanger is less than or equal to a preset defrost temperature, wherein the set operating period is greater than the preset sampling period.
  • a total heat recovery defrosting control system including: a defrosting determination module configured to determine whether a current operating condition satisfies a set defrost operating condition; a comparison module configured to compare a heating demand with a heated water demand; and an execution module configured to perform a heated water defrost mode if the heating demand is higher than the heated water demand or to perform a heating defrost mode if the heated water demand is higher than the heating demand.
  • Another aspect of the present invention as defined in claim 10 provides an air conditioning device, which is a total heat recovery unit applying the total heat recovery defrosting control method defined in claims 1-8.
  • the advantages and positive effects of the present invention are: a comparison between the heating demand and the heated water demand is performed to select the heat exchanger with less heat demand to fulfill the defrost function, thereby avoiding a large amount of heat loss of heat exchanger in operating mode, so as to minimize the impact on user experience and further guarantee heating demand or heated water demand by users.
  • Embodiment in the present invention means that specific features, structures or properties described in one embodiment could be included in one or more embodiments.
  • the term in various positions of the specification does not necessarily refer to one same embodiment, nor is it an independent embodiment or an alternative embodiment mutually exclusive with other embodiments. Those skilled in the art could understand that the embodiments described could be combined with other embodiments.
  • the total heat recovery unit could operate in a cooling mode, a heating mode and a heated water supply mode. It is necessary to defrost an outdoor heat exchanger as being operated in the heating mode or in the heated water supply mode.
  • low-temperature and low-pressure refrigerant vapor is compressed by a compressor into high-temperature and high-pressure superheated refrigerant vapor.
  • Corresponding valves in the refrigeration cycle are open to enable the high-temperature and high-pressure superheated refrigerant vapor to flow into a heat recovery heat exchanger to exchange heat with medium on the heat recovery heat exchanger side; usually the medium on the heat recovery heat exchanger side is water in a water tank that is heated to a preset water temperature; while the high-temperature and high-pressure superheated refrigerant vapor is condensed to medium-temperature and high-pressure liquid refrigerant within the heat recovery heat exchanger, and is further guided to flow through an accumulator, a filter and an expansion valve changing to low-temperature and low-pressure liquid.
  • the low-temperature and low-pressure liquid then flows into an outdoor finned-tube heat exchanger through corresponding refrigerant pipeline to exchange heat with outdoor air blown by a switch-on indoor fan.
  • the low-temperature and low-pressure liquid evaporates into low-temperature and low-pressure gaseous refrigerant, and back to the compressor through a four-way valve to complete a refrigerant cycle of the heated water supply mode.
  • low-temperature and low-pressure refrigerant vapor is compressed by the compressor into high-temperature and high-pressure superheated refrigerant vapor.
  • Corresponding valves in the refrigeration cycle are open to enable the high-temperature and high-pressure superheated refrigerant vapor to flow into an indoor water-side heat exchanger through the four-way valve and exchange heat with water for air conditioning and warm the water for air conditioning up to a preset heating temperature; while the high-temperature and high-pressure superheated refrigerant vapor is condensed to medium-temperature and high-pressure liquid refrigerant, and is further guided to flow through refrigerant pipeline, the filter and the expansion valve to changing to low-temperature and low-pressure liquid.
  • the low-temperature and low-pressure liquid then flows into an outdoor finned-tube heat exchanger through corresponding refrigerant pipeline to exchange heat with outdoor air blown by a switch-on indoor fan.
  • the low-temperature and low-pressure liquid evaporates into low-temperature and low-pressure gaseous refrigerant, and back to the compressor through the four-way valve to complete a refrigerant cycle of the heating mode.
  • Fig.1 is a flowchart of a total heat recovery defrosting control method according to the present invention, and the control method includes steps as follows.
  • Step S 101 the total heat recovery unit is operated in the heating mode or in the heated water supply mode.
  • the total recovery unit could automatically work in the heating mode or in the heated water supply mode in different periods of time, or automatically work in the heating mode and the heated water supply mode according to varied heat load of the air-conditioned room or heated water requirements.
  • Step S 102 determining whether a current operating condition satisfies a set defrost operating condition.
  • frost layer will increase thermal resistance of the outdoor finned-tube heat exchanger resulting in a gradual decrease of the amount of heat transferred. But if the frost grows to a certain thickness, the amount of heat transferred will drop significantly, thereby inducing that both of the evaporating pressure and the evaporating temperature of the unit begin to drop at an accelerated rate. Therefore with those features of coil temperature and pressure, dual factors including temperature and time could be used to determine whether a current operating condition satisfies a set defrost operating condition.
  • the set defrost operating condition is satisfied if the continuous operating time is greater than or equal to a set operating period and a coil temperature of the outdoor finned-tube heat exchanger is less than or equal to a preset defrost temperature.
  • the set operating period is optionally 45 minutes and the preset defrost temperature could be in a range from-8°C to -5°C.
  • pressure and time also could be chosen as the dual factors in the set defrost operating condition.
  • Other set defrost operating conditions known by the ordinary skills in the art also could be used as the set defrost operating condition.
  • Step S103 comparing a heating demand with a heated water demand if it is determined that the current operating condition satisfies the set defrost operating condition, in which the heating load refers to the amount of heat required to warm up medium, such as water for air conditioning and the like, to a preset heating temperature and maintain at the preset heating temperature, while the heated water requirement refers to the amount of heat required to warm up water in a water tank to a preset water temperature and maintain at the preset water temperature.
  • the heating load refers to the amount of heat required to warm up medium, such as water for air conditioning and the like
  • Step S 104-1 performing a heated water defrost mode if the heating demand is higher than the heated water demand; more precisely the unit is preferably configured to meet the control target of the heating mode but to realize a defrost function with the heat transferred by the heat recovery heat exchanger.
  • high-temperature and high-pressure refrigerant vapor discharged from the compressor flows into the outdoor air-side finned-tube heat exchanger and release heat to surrounding so that frost is melted while the high-temperature and high-pressure refrigerant vapor is condensed to medium-temperature liquid refrigerant, and then is supercooled as passing through refrigerant pipeline, an accumulator and an economizer, and is turned to low-temperature and low-pressure liquid refrigerant; the low-temperature and low-pressure liquid refrigerant enters into the heat recovery heat exchanger and transfers heat with water in the water tank; after heat exchange enters into a gas-liquid separator to remove droplets from gaseous refrigerant and then back to the compressor again for compression, thereby completing a refrigeration cycle in the heated water defrost mode.
  • the operation of the heating mode with a high priority is guaranteed and less affected, so the user experience could be
  • Step S104-2 performing a heating defrost mode if the heated water demand is higher than the heating demand; more precisely the unit is preferably configured to meet the control target of the heated water supply mode but to realize a defrost function with the heat transferred by the indoor water-side heat exchanger.
  • high-temperature and high-pressure refrigerant vapor discharged from the compressor flows into the outdoor air-side finned-tube heat exchanger and release heat to surrounding so that frost is melted while the high-temperature and high-pressure refrigerant vapor is condensed to medium-temperature liquid refrigerant, and then is supercooled as passing through refrigerant pipeline, an accumulator and an economizer, and is turned to low-temperature and low-pressure liquid refrigerant; the low-temperature and low-pressure liquid refrigerant enters into the indoor water-side heat exchanger and transfers heat with medium such as water for air conditioning; after heat exchange enters into a gas-liquid separator to remove droplets from gaseous refrigerant and then back to the compressor again for compression, thereby completing a refrigeration cycle in the heating defrost mode.
  • the operation of the heated water supply mode with a high priority is guaranteed and less affected, so the
  • a comparison between the heating demand and the heated water demand is performed to select the heat exchanger with less heat demand to fulfill the defrost function, thereby avoiding a large amount of heat loss of heat exchanger in operating mode, so as to minimize the impact on user experience and further guarantee heating demand or heated water demand by users.
  • the process to compare the heating demand with the heated water demand includes the following steps.
  • Step S201 collecting a current heating set temperature T r and an inlet water temperature T wi at the heat recovery heat exchanger side, wherein the current heating set temperature T r could be a preset temperature input by user, a corrected temperature corrected by a stored algorithm on the basis of the preset temperature input by user, or a given temperature generated by a control algorithm stored in the unit as manufactured according to environmental parameters.
  • the heating set temperature T r refers to a target temperature of the water for air conditioning which could achieve ideal environmental parameters of the air-conditioned room in the heating mode.
  • the inlet water temperature in the entire total heat recovery unit could be considered consistent and the inlet water temperature T wi on the heat recovery heat exchanger side could be obtained by a temperature sensor set at an inlet of the water tank, which is convenient to realize, the inlet water temperature T wi at the heat recovery heat exchanger side represents a current actual temperature of the water for air conditioning.
  • Step S203 collecting a current set temperature of heated water T hr and an outlet water temperature T h at the heat recovery heat exchanger side, wherein the current set temperature of heated water T hr could be preset temperature input by user, a corrected temperature corrected by a stored algorithm on the basis of the preset temperature input by user, or a given temperature generated by a control algorithm stored in the unit as manufactured according to environmental parameters.
  • the current set temperature of heated water T hr is the target temperature of heated water that the user requires and the outlet water temperature T h at the heat recovery heat exchanger side represents the temperature of heated water could be supplied currently, wherein the outlet water temperature T h at the heat recovery heat exchanger side could be detected by a temperature sensor arranged at an water outlet of the water tank.
  • Step S205-1 if the first temperature difference T d1 is greater than the second temperature difference T d2 , it means that the thermal load that requires to be satisfied by operation in the heating mode is greater than the thermal load that requires to be satisfied by operation in the heated water supply mode, and it could be further determined that the heating demand is higher than the heated water demand, the heat exchanger causing less impact on operation as performing a defrost process is selected, to be specific the heated water defrost mode is executed.
  • Step S205-2 if the first temperature difference T d1 is less than the second temperature difference T d2 , it means that the thermal load that requires to be satisfied by operation in the heated water supply mode is greater than the thermal load that requires to be satisfied by operation in the heating mode and it could be further determined that the heated water demand is higher than the heating demand, the heat exchanger causing less impact on operation as performing a defrost process is selected, to be specific the heating defrost mode is executed.
  • the process to compare the heating demand with the heated water demand could include the following steps.
  • Step S301 acquiring a rate of change ⁇ T wi of the inlet water temperature at the heat recovery heat exchanger side within a preset sampling period.
  • the rate of change of the inlet water temperature at the heat recovery heat exchanger side within the preset sampling period that represents how the temperature at the inlet of the water tank at the heat recovery heat exchanger side changes during a preset period when the unit being normally operated.
  • the temperature change at the inlet of the water tank at the heat recovery heat exchanger side accelerates as water circulation in the total heat recovery unit is fast while the temperature change at the inlet of the water tank on the heat exchanger side slows down as water circulation in the total heat recovery unit is slow.
  • the temperature change at the inlet of the water tank at the heat recovery heat exchanger side represents water circulation state in the total heat recovery unit, which also could dynamically reflect a heating demand in a period as the unit being normally operated just before the set defrost operating condition is met.
  • the acquisition of the rate of change ⁇ T wi of the inlet water temperature at the heat recovery heat exchanger side within a preset sampling period could be realized by the following steps.
  • a group of inlet water temperatures at the heat recovery heat exchanger side collected at each set sampling point and a time duration of the preset sampling period are stored in the unit, so further an inlet water temperatureT wi2 at the heat recovery heat exchanger side at a time point when the preset sampling period starts could be retrieved according to the time duration of the set sampling period.
  • Step S302 acquiring a rate of change ⁇ T h of the outlet water temperature at the heat recovery heat exchanger side within the preset sampling period.
  • the rate of change of the outlet water temperature at the heat recovery heat exchanger side within the preset sampling period that represents how the temperature at the outlet of the water tank at the heat recovery heat exchanger side changes during a preset period when the unit being normally operated.
  • the temperature change at the outlet of the water tank at the heat recovery heat exchanger side accelerates while the less heated water used by users, the temperature change at the outlet of the water tank at the heat recovery heat exchanger side slows down.
  • the temperature change at the outlet of the water tank at the heat recovery heat exchanger side represents how much heated water used by users, which also could dynamically reflect a heated water demand in a period as the unit being normally operated just before the set defrost operating condition is met.
  • the acquisition of the rate of change ⁇ T h of the outlet water temperature at the heat recovery heat exchanger side within the preset sampling period could be realized by the following steps.
  • a group of outlet water temperatures at the heat recovery heat exchanger side collected at each set sampling point and a time duration of the preset sampling period are stored in the unit, so further an outlet water temperature T h2 at the heat recovery heat exchanger side at a time point when the preset sampling period starts could be retrieved according to the time duration of the set sampling period.
  • Step S303-1 it is determined that the heating demand is greater than the heated water demand if ⁇ T wi > ⁇ T h and the heated water defrost mode is executed.
  • Step S303-2 it is determined that the heated water demand is greater than the heating demand if ⁇ T wi ⁇ ⁇ T h and the heating defrost mode is executed.
  • the method disclosed in Fig.2 provides an approach to compare and evaluate the heating demand and the heated water demand on the basis of static parameters, such as the current heating set temperature and the current set temperature of heated water; while the method disclosed in Fig.3 provides another approach to compare and evaluate the heating demand and the heated water demand based on dynamic parameters, such as the rate of change of the inlet water temperature and the rate of change of the outlet water temperature.
  • static parameters and the dynamic parameters are combined including the following steps.
  • Step S404-1 it is determined that the heating demand is higher than the heated water demand if ⁇ T wi > ⁇ T h and the heated water defrost mode is executed.
  • Step S404-2 it is determined that the heated water demand is higher the heating demand if ⁇ T wi ⁇ ⁇ T h as the user's dynamic usage being regarded as priority and the heating defrost mode is executed.
  • Step S403-2 acquiring the rate of change ⁇ T wi of the inlet water temperature at the heat recovery heat exchanger side within the preset sampling period and the rate of change ⁇ T h of the outlet water temperature at the heat recovery heat exchanger side within the preset sampling period if the first temperature differenceT d1 is less than the second temperature difference T d2 .
  • Step S404-3 it is determined that the heating demand is higher than the heated water demand if ⁇ T wi > ⁇ T h as the user's dynamic usage being regarded as priority and the heated water defrost mode is executed.
  • Step S404-4 it is determined that the heated water demand is higher the heating demand if ⁇ T wi ⁇ ⁇ T h and the heating defrost mode is executed.
  • the time duration of the preset sampling period is set as 30 minutes.
  • time and temperature is configured as the set defrost operating condition, it is preferable to establish the set operating period longer than the preset sampling period so as to ensure a complete and accurate usage cycle could be sampled for further acquiring the rate of change of water temperature and make the evaluation result more precise.
  • Fig.5 discloses a total heat recovery defrosting control system including components as follows.
  • a defrosting determination module 101 is configured to determine whether a current operating condition satisfies a set defrost operating condition.
  • the set defrost operating condition is satisfied if the continuous operating time is greater than or equal to a set operating period and a coil temperature of the outdoor finned-tube heat exchanger is less than or equal to a preset defrost temperature.
  • the set operating period is optionally 45 minutes and the preset defrost temperature could be in a range from-8°C to -5°C.
  • pressure and time also could be chosen as the dual factors in the set defrost operating condition.
  • Other set defrost operating conditions known by the ordinary skills in the art also could be used as the set defrost operating condition. According to the invention however, only temperature and time are selected as the dual factors.
  • a comparison module 102 is configured to compare a heating demand with a heated water demand if it is determined that the current operating condition satisfies the set defrost operating condition, in which the heating load refers to the amount of heat required to warm up medium, such as water for air conditioning and the like, to a preset heating temperature and maintain at the preset heating temperature, while the heated water requirement refers to the amount of heat required to warm up water in a water tank to a preset water temperature and maintain at the preset water temperature.
  • An execution module 103 is configured to perform a heated water defrost mode if the heating demand is higher than the heated water demand or to perform a heating defrost mode if the heated water demand is higher than the heating demand.
  • a comparison between the heating demand and the heated water demand is performed to select the heat exchanger with less heat demand to fulfill the defrost function, thereby avoiding a large amount of heat loss of heat exchanger in operating mode, so as to minimize the impact on user experience and further guarantee heating demand or heated water demand by users.
  • the invention also provides an air conditioning device.
  • the air conditioning device is a total heat recovery unit.
  • the total heat recovery unit adopts the total heat recovery defrosting control method.
  • the air conditioning device adopting the total heat recovery defrosting control method can achieve the same technical effect.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Signal Processing (AREA)
  • Physics & Mathematics (AREA)
  • Fuzzy Systems (AREA)
  • Mathematical Physics (AREA)
  • Thermal Sciences (AREA)
  • Air Conditioning Control Device (AREA)
  • Heat-Pump Type And Storage Water Heaters (AREA)
EP20860254.0A 2019-09-05 2020-01-08 Total heat recovery defrosting control method and control device, and air conditioning apparatus Active EP4027070B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN201910837881.5A CN112443934B (zh) 2019-09-05 2019-09-05 全热回收融霜控制方法、控制系统和空气调节装置
PCT/CN2020/070797 WO2021042654A1 (zh) 2019-09-05 2020-01-08 全热回收融霜控制方法、控制系统和空气调节装置

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EP4027070A1 EP4027070A1 (en) 2022-07-13
EP4027070A4 EP4027070A4 (en) 2022-10-26
EP4027070C0 EP4027070C0 (en) 2023-09-13
EP4027070B1 true EP4027070B1 (en) 2023-09-13

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CN113108433A (zh) * 2021-03-23 2021-07-13 珠海格力电器股份有限公司 一种多联机空调系统的控制方法
CN113432352B (zh) * 2021-06-22 2023-02-21 山东和同信息科技股份有限公司 一种基于5g物联网技术的空气源热泵除霜调控方法和系统
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