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WO2021042654A1 - 全热回收融霜控制方法、控制系统和空气调节装置 - Google Patents

全热回收融霜控制方法、控制系统和空气调节装置 Download PDF

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Publication number
WO2021042654A1
WO2021042654A1 PCT/CN2020/070797 CN2020070797W WO2021042654A1 WO 2021042654 A1 WO2021042654 A1 WO 2021042654A1 CN 2020070797 W CN2020070797 W CN 2020070797W WO 2021042654 A1 WO2021042654 A1 WO 2021042654A1
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WIPO (PCT)
Prior art keywords
demand
hot water
heating
heat recovery
temperature
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Application number
PCT/CN2020/070797
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English (en)
French (fr)
Inventor
冷宇
孙辉
赵雷
李振洪
Original Assignee
青岛海尔空调电子有限公司
海尔智家股份有限公司
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Application filed by 青岛海尔空调电子有限公司, 海尔智家股份有限公司 filed Critical 青岛海尔空调电子有限公司
Priority to EP20860254.0A priority Critical patent/EP4027070B1/en
Publication of WO2021042654A1 publication Critical patent/WO2021042654A1/zh

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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
    • 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 equipment, and in particular relates to a total heat recovery defrosting control method, a total heat recovery defrosting control system and an air conditioning device.
  • the air conditioning device with full heat recovery function is an air conditioning unit that integrates refrigeration, heating, and domestic hot water.
  • this air conditioning device includes a compressor, an outdoor air-side fin heat exchanger that exchanges heat with the air, a water-side heat exchanger, a total heat recovery heat exchanger that recovers heat energy, a four-way valve, and an electronic expansion valve. , Accumulator and multiple solenoid valves, one-way valves and other execution components that are set in the refrigeration cycle system to adjust the flow and direction of the refrigerant to perform different functions.
  • an air conditioning device with full heat recovery function can have multiple functional modes, including heating mode, cooling mode, and hot water Mode and so on.
  • the Chinese patent application (Authorization Announcement No. CN201212721Y) discloses the refrigeration cycle structure and working method of the air-conditioning total heat recovery mechanism.
  • the air-side fin heat exchanger located outdoors may appear frosting.
  • frosting occurs, the heat exchange is caused by the increase of the frost layer.
  • the thermal resistance of the device increases, so that the heat exchange is gradually reduced.
  • the frost layer increases to a certain thickness, the heat exchange rate drops rapidly.
  • corresponding heating and defrosting modes and hot water defrosting modes are configured.
  • the heating and defrosting mode the high-temperature and high-pressure refrigerant is discharged from the compressor and enters the outdoor air-side fin heat exchanger through the four-way valve.
  • the high-temperature and high-pressure refrigerant exchanges heat and defrosts with the air, and at the same time it condenses into a medium-temperature and medium-pressure refrigerant liquid.
  • the medium-temperature and medium-pressure refrigerant liquid passes through the accumulator and is economical.
  • the equipment such as the air conditioner is supercooled, and the low-temperature and low-pressure refrigerant liquid flows into the indoor water-side heat exchanger through the throttling device to exchange heat with the air-conditioning water.
  • the high temperature and high pressure refrigerant is discharged from the compressor, enters the outdoor air-side fin heat exchanger through the four-way valve, and releases heat to the surrounding environment in the outdoor air-side fin heat exchanger. It is condensed into a medium temperature and medium pressure refrigerant liquid. The medium temperature and medium pressure refrigerant is further subcooled through the accumulator, economizer and other equipment, and is reduced in pressure by the throttling mechanism to become a low temperature and low pressure refrigerant liquid. To the heat recovery heat exchanger.
  • the defrost is achieved by sacrificing the heat of the indoor water-side heat exchanger or heat recovery heat exchanger respectively, which will inevitably affect the user's use Comfort.
  • the present invention designs and provides a A total heat recovery defrost control method.
  • a total heat recovery defrosting control method including the following steps: operating in heating mode or hot water mode; judging whether the current operating conditions meet the defrosting operating conditions; if the current operating conditions meet the defrosting operating conditions, then comparing Heating demand and hot water demand; if the heating demand is higher than the hot water demand, the hot water defrosting mode is executed; if the hot water demand is higher than the heating demand, the heating defrosting mode is executed.
  • obtaining the rate of change ⁇ T wi of the inlet water temperature on the heat recovery heat exchanger side during the set sampling period includes the following steps: Obtain the inlet water temperature T wi1 on the heat recovery heat exchanger side at the end of the set sampling period, so The end time of the set sampling period is the current time when it is determined that the defrosting operating conditions are met; the inlet water temperature T wi2 on the heat recovery heat exchanger side at the start time of the set sampling period is obtained, and the heat recovery heat transfer in the set sampling period is calculated The rate of change of the inlet water temperature on the side of the device ⁇ T wi ,
  • obtaining the rate of change ⁇ T h of the outlet water temperature of the heat recovery heat exchanger within a set sampling period includes the following steps: obtaining the outlet water temperature T h1 on the heat recovery heat exchanger side at the end of the set sampling period, and the setting The end time of the sampling period is the current time when it is determined that the defrosting operating conditions are met; the outlet water temperature T h2 on the heat recovery heat exchanger side at the start time of the set sampling period is obtained, and the inlet water temperature on the heat recovery heat exchanger side during the set sampling period is calculated.
  • the rate of change of water temperature ⁇ T h is the rate of change of water temperature ⁇ T h ,
  • the duration of the set sampling period is 30 minutes.
  • the defrosting operating conditions include: the continuous operating time is greater than or equal to a set operating period and the coil temperature of the outdoor heat exchanger is less than or equal to the set defrosting temperature, wherein the set operating period is greater than the set sampling period.
  • a total heat recovery defrosting control system including: a defrosting determination module, which is used to determine whether the current operating conditions meet the defrosting operating conditions in the heating mode or the hot water mode; Module, which is used to compare heating demand and hot water demand; and execution module, which is used to execute the hot water defrost mode when the heating demand is higher than the hot water demand, and when the hot water demand is higher than the heating demand, Perform heating and defrosting mode.
  • a defrosting determination module which is used to determine whether the current operating conditions meet the defrosting operating conditions in the heating mode or the hot water mode
  • Module which is used to compare heating demand and hot water demand
  • execution module which is used to execute the hot water defrost mode when the heating demand is higher than the hot water demand, and when the hot water demand is higher than the heating demand, Perform heating and defrosting mode.
  • the air conditioning device is a total heat recovery unit, which adopts a total heat recovery defrosting control method
  • the total heat recovery defrosting control method includes the following steps: operating in heating mode or In hot water mode; judge whether the current operating conditions meet the defrost operating conditions; if the current operating conditions meet the defrost operating conditions, compare the heating demand with the hot water demand; if the heating demand is higher than the hot water demand, execute Hot water defrost mode; if the hot water demand is higher than the heating demand, the heating defrost mode is executed.
  • the advantages and positive effects of the present invention are: by comparing the total heat recovery unit's heat demand for air-conditioning heating and hot water production, selecting a heat exchanger with a small heat demand for defrosting, avoiding operating mode The heat exchanger loses a lot of heat, thereby reducing the impact on the user experience and ensuring the user’s heating demand or hot water demand.
  • Fig. 1 is a flowchart of an embodiment of the total heat recovery defrost control method disclosed in the present invention
  • Figure 2 is a flowchart of the first alternative method for comparing heating demand and hot water demand
  • Figure 3 is a flowchart of the second alternative method of comparing heating demand and hot water demand
  • Figure 4 is a flowchart of a third alternative method for comparing heating demand and hot water demand
  • Fig. 5 is a schematic block diagram of the structure of an embodiment of the total hot defrost control system disclosed in the present invention.
  • the total heat recovery unit can work in cooling mode, heating mode or hot water mode. It is necessary to defrost the outdoor heat exchanger in heating mode or hot water mode.
  • the low-temperature and low-pressure refrigerant vapor is compressed by the compressor into high-temperature and high-pressure superheated steam, which drives the corresponding valve group in the refrigeration cycle pipeline to open, and the high-temperature and high-pressure superheated steam flows to the heat recovery heat exchanger, and heat recovery Medium heat exchange on the heat exchanger side.
  • the medium on the heat recovery heat exchanger side is usually the water in the water tank, so that the water in the water tank is heated to the set water temperature.
  • the high-temperature and high-pressure superheated steam is condensed into a medium-temperature and high-pressure liquid in the heat recovery heat exchanger, which further guides the refrigerator to flow to the accumulator, then passes through the filter, and then flows through the electronic expansion valve to be converted into a low-temperature and low-pressure liquid.
  • the liquid further flows into the outdoor finned tube heat exchanger through the corresponding refrigerant pipeline, and the outdoor fan is turned on to exchange heat with the outdoor air.
  • the low-temperature and low-pressure liquid evaporates into low-temperature and low-pressure gas, which flows to the compressor through the four-way reversing valve, completing the entire refrigeration cycle of the hot water mode.
  • the low-temperature and low-pressure refrigerant vapor is compressed by the compressor into high-temperature and high-pressure superheated steam, which drives the corresponding valve group to open.
  • the high-temperature and high-pressure superheated steam flows to the indoor water-side heat exchanger through the four-way reversing valve. It exchanges heat with the air-conditioning water to heat the air-conditioning water to the heating set temperature.
  • the high temperature and high pressure superheated steam condenses into a medium temperature and high pressure liquid.
  • the medium-temperature and high-pressure liquid then passes through the refrigerant pipeline, filter, and electronic expansion valve to become a low-temperature and low-pressure liquid.
  • the low-temperature and low-pressure liquid further flows into the outdoor fin-tube heat exchanger through the corresponding refrigerant pipeline, and the outdoor fan is turned on and Outdoor air heat exchange.
  • the low-temperature and low-pressure liquid evaporates into low-temperature and low-pressure gas, which flows to the compressor through the four-way reversing valve, completing the entire refrigeration cycle.
  • step S101 the total heat recovery unit operates in heating mode or hot water mode.
  • the total heat recovery unit works in winter, it can automatically work in heating mode or hot water mode in time sharing, or automatically work in heating mode or hot water mode according to the heat load or hot water demand of the air-conditioned room.
  • step S102 it is judged whether the current operating condition meets the defrosting operating condition.
  • frost When frost is formed, the increase of the frost layer causes the thermal resistance of the outdoor finned tube heat exchanger to increase, which makes the heat exchange gradually decrease.
  • the frost layer increases to a certain thickness, the heat exchange rate drops rapidly, corresponding to the evaporating pressure and evaporating temperature of the unit to begin to drop at an accelerated rate. Therefore, according to the characteristics of the temperature and pressure changes of the coil, the dual factors of temperature and time can be used to determine whether the defrosting operating conditions are met.
  • the defrosting operating condition can be set as: the continuous operating time is greater than or equal to the set operating period, and the coil temperature of the outdoor fin and tube heat exchanger is less than or equal to the set defrosting temperature.
  • the set operating period can be set to 45 minutes, and the set defrost temperature can be set from -8°C to -5°C.
  • the defrosting operating conditions can also be set as the pressure and time dual-factor judgment conditions.
  • the defrost operation conditions can also be set to other defrost determination conditions used in the prior art.
  • step S103 if the current operating conditions meet the defrosting operating conditions, the heating demand and the hot water demand are compared.
  • Heating demand refers to heating the medium, such as air-conditioning water, to the heating set temperature and maintaining the required heat.
  • Hot water demand refers to heating the water in the water tank to the set hot water temperature and maintaining the required heat The heat.
  • step S104-1 if the heating demand is higher than the hot water demand, the hot water defrosting mode is executed, that is, the control target of the heating mode is preferably met and the heat exchange of the heat recovery heat exchanger is used to achieve the defrosting effect.
  • the hot water defrosting mode the four-way valve is used to change the direction, and the high-temperature and high-pressure refrigerant vapor discharged from the compressor enters the outdoor fin-and-tube heat exchanger.
  • high-temperature and high-pressure refrigerant vapor releases heat to the surrounding environment to melt the frost layer.
  • the high-temperature and high-pressure refrigerant vapor releases heat and condenses into a medium-temperature refrigerant liquid, which is further subcooled through refrigerant pipelines, accumulators, economizers, etc., and passes through throttling mechanisms, such as electronic expansion valves, to become low-temperature and low-pressure refrigerants Liquid, low-temperature and low-pressure refrigerant liquid enters the heat recovery heat exchanger, exchanges heat with the water in the water tank, separates gas and liquid, and enters the compressor again for compression, thereby completing a refrigeration cycle in the hot water defrost mode. In this process, the operation of the heating mode with priority guarantee is less affected, and the user experience can be ensured to the greatest extent.
  • step S104-2 if the hot water demand is higher than the heating demand, the heating defrosting mode is executed, that is, the control target of the hot water mode is preferably met and the heat exchange of the indoor water-side heat exchanger is used to achieve the defrosting effect.
  • the heating and defrosting mode the four-way valve is used to change the direction, and the high-temperature and high-pressure refrigerant vapor discharged from the compressor enters the outdoor fin-and-tube heat exchanger. In an outdoor fin-and-tube heat exchanger, high-temperature and high-pressure refrigerant vapor releases heat to the surrounding environment to melt the frost layer.
  • the high-temperature and high-pressure refrigerant vapor releases heat and condenses into a medium-temperature refrigerant liquid, which is further subcooled through refrigerant pipelines, accumulators, economizers, etc., and passes through throttling mechanisms, such as electronic expansion valves, to become low-temperature and low-pressure refrigerants Liquid, low-temperature and low-pressure refrigerant liquid enters the indoor water-side heat exchanger, exchanges heat with air-conditioning water and other media, and then separates gas and liquid, and enters the compressor again for compression, thereby completing a refrigeration cycle in the heating and defrosting mode .
  • the hot water mode operation with priority guarantee has little impact and can ensure the user's use experience to the greatest extent.
  • the above-mentioned total heat recovery defrost control method compares the heat demand of the total heat recovery unit for air-conditioning heating and hot water production, and selects a heat exchanger with a small heat demand for defrosting, avoiding a large amount of heat in the heat exchanger in operation mode Loss, thereby reducing the impact on the user experience and ensuring the user’s heating demand or hot water demand.
  • Step S201 the sampled current set heating water temperature T r and a heat recovery heat exchanger side T wi.
  • the current set heating temperature T r can be set user-set temperature
  • the temperature may be corrected in accordance with the user-set temperature value is corrected by an algorithm stored, the unit may also be made before delivery
  • the written control algorithm is automatically generated according to the environmental parameters.
  • the heating temperature T r may represent the set, air-conditioned room in order to achieve the environmental parameters to achieve the desired air-conditioning target temperature of water in the heating mode. Since the inlet water temperature in the entire total heat recovery unit can be considered the same, and the inlet water temperature T wi on the heat recovery heat exchanger side can be detected by the temperature sensor provided at the water tank inlet, the detection is relatively convenient. Therefore, the inlet water temperature T wi on the side of the heat recovery heat exchanger represents the current actual temperature of the air-conditioning water.
  • Step S203 sampling the current hot water set water temperature Thr and the outlet water temperature Th on the heat recovery heat exchanger side.
  • the current hot water set temperature Thr can also be the set temperature set by the user, or it can be the corrected temperature corrected by the stored algorithm according to the temperature set by the user, or it can be set by the unit.
  • the hot water set water temperature Thr is the target water temperature at which the user needs to use hot water
  • the outlet water temperature Th on the heat recovery heat exchanger side is the available water temperature in the current state.
  • the outlet water temperature Th on the side of the heat recovery heat exchanger can be detected by a temperature sensor arranged at the 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 , that is, the heating load that needs to be adjusted in the heating mode is higher than the heating load that needs to be adjusted in the hot water mode, it is further determined as the heating demand If it is higher than the hot water demand, select the heat exchanger with less impact for defrost operation, that is, execute hot water defrost mode.
  • Step S205-2 if the first temperature difference T d1 is smaller than the second temperature difference T d2 , that is, the heat load that needs to be adjusted in the hot water mode is higher than the heat load that needs to be adjusted in the heating mode, it is further determined as the hot water demand If it is higher than the heating demand, the heat exchanger with low impact is also selected for defrosting operation, that is, the heating and defrosting mode is executed.
  • heating demand and hot water demand can also be compared in the following way.
  • Step S301 Obtain the change rate ⁇ T wi of the inlet water temperature on the heat recovery heat exchanger side in the set sampling period.
  • the rate of change of the inlet water temperature of the water tank on the heat recovery heat exchanger side within the set sampling period represents the temperature change of the water inlet of the water tank on the heat recovery heat exchanger side during a normal operation period.
  • the water circulation in the total heat recovery unit is fast, and the temperature change of the water tank inlet on the side of the heat recovery heat exchanger will also accelerate; the water circulation in the total heat recovery unit is slow, and the heat recovery heat exchanger
  • the temperature change of the water inlet of the water tank on the side will also be slowed down accordingly. Therefore, the temperature change of the water tank inlet on the heat recovery heat exchanger side represents the state of the water circulation in the total heat recovery unit, which is further dynamically reflected in the heating demand during the normal operating time before the defrost operating conditions are met.
  • the unit pre-stores the length of the set sampling period and the inlet water temperature of the heat recovery heat exchanger at each set sampling point, and further obtains the heat recovery heat transfer at the start time of the set sampling period according to the set sampling period time
  • the inlet water temperature T wi2 on the side of the device
  • Step S302 Obtain the change rate ⁇ T h of the outlet water temperature on the heat recovery heat exchanger side within the set sampling period.
  • the change rate of the outlet water temperature of the water tank on the heat recovery heat exchanger side within the set sampling period represents the temperature change of the water outlet of the water tank on the heat recovery heat exchanger side during a normal operation period.
  • the temperature change at the outlet of the water tank on the heat recovery heat exchanger side will also accelerate; if the user uses less water, the temperature change at the outlet of the water tank on the heat recovery heat exchanger side It will also slow down. Therefore, the temperature change of the water tank inlet on the heat recovery heat exchanger side represents the amount of hot water used by the user, which is further dynamically reflected in the hot water demand during the normal operating period before the defrost operating conditions are met.
  • the unit pre-stores the duration of the set sampling period and the outlet water temperature on the heat recovery heat exchanger side of each sampling point, and further obtains the outlet water on the heat recovery heat exchanger side at the beginning of the set sampling period according to the duration of the set sampling period Temperature T h2 ,
  • step S303-1 if ⁇ T wi > ⁇ T h , it is determined that the heating demand is higher than the hot water demand, and the hot water defrosting mode is executed.
  • step S303-2 if ⁇ T wi ⁇ T h , it is determined that the hot water demand is higher than the heating demand, and the heating defrosting mode is executed.
  • the method in Figure 2 provides a way to compare and determine the heating demand and the hot water demand based on static parameters, such as the current heating set temperature and the current hot water set temperature, as shown in Figure 3. It provides a way to compare and determine the heating demand and hot water demand through dynamic parameters, such as the rate of change of the inlet water temperature and the rate of change of the outlet water temperature.
  • a method for judging heating demand and hot water demand is also provided, which combines static and dynamic parameters. Specifically, it includes the following steps:
  • Step S403-1 if the first temperature difference T d1 is greater than the second temperature difference T d2 , obtain the change rate ⁇ T wi of the inlet water temperature on the heat recovery heat exchanger side in the set sampling period and obtain the heat in the set sampling period The rate of change ⁇ T h of the outlet water temperature on the side of the recovery heat exchanger.
  • step S404-1 if ⁇ T wi > ⁇ T h , it is determined that the heating demand is higher than the hot water demand, and the hot water defrosting mode is executed.
  • step S404-2 if ⁇ T wi ⁇ T h , take the user's dynamic usage as the priority, determine that the hot water demand is higher than the heating demand, and execute the heating defrosting mode.
  • Step S403-2 if the first temperature difference T d1 is smaller than the second temperature difference T d2 , obtain the change rate ⁇ T wi of the inlet water temperature on the heat recovery heat exchanger side in the set sampling period and obtain the heat in the set sampling period The rate of change ⁇ T h of the outlet water temperature on the side of the recovery heat exchanger.
  • step S404-3 if ⁇ T wi > ⁇ T h , take the user's dynamic usage as a priority, determine that the heating demand is higher than the hot water demand, and execute the hot water defrosting mode.
  • step S404-4 if ⁇ T wi ⁇ T h , it is determined that the hot water demand is higher than the heating demand, and the heating defrosting mode is executed.
  • the duration of the sampling period it is preferable to set the duration of the sampling period to 30 minutes. If the time and temperature dual factor is used as the defrosting operating condition, or the time pressure dual factor is used as the defrosting operating condition, the set operating period is preferably set to be greater than the set sampling period to ensure that the rate of change of water temperature can be dynamically determined Complete sampling and an accurate use cycle make the judgment result more accurate.
  • the coil temperature and pressure of the outdoor heat exchanger will rise. When it rises to a certain value, it is determined that the conditions for exiting the defrost mode are met, and the operation in the heating mode or hot water mode is resumed.
  • a total heat recovery defrosting control system is provided. As shown in Fig. 5, the total heat recovery defrost control system 10 includes the following components.
  • the defrost determination module 101 is used to determine whether the current operating conditions meet the defrost operating conditions in the heating mode or the hot water mode.
  • the defrosting operating condition can be set as: the continuous operating time is greater than or equal to the set operating period, and the coil temperature of the outdoor fin and tube heat exchanger is less than or equal to the set defrosting temperature.
  • the set operating period can be set to 45 minutes, and the set defrost temperature can be set from -8°C to -5°C.
  • the defrost operating conditions can also be set as the pressure and time dual-factor judgment conditions.
  • the defrost operation conditions can also be set to other defrost determination conditions used in the prior art.
  • the comparison module 102 is used to compare the heating demand and the hot water demand after the defrost determination module determines that the defrost operation condition is satisfied.
  • the heating demand refers to heating the medium, such as air-conditioning water, to the set heating temperature and maintaining the required heat
  • the hot water demand refers to heating the water in the water tank to the set water temperature and maintaining the required heat The heat.
  • the execution module 103 is configured to execute the hot water defrosting mode when the heating demand is higher than the hot water demand, and execute the heating defrosting mode when the hot water demand is higher than the heating demand.
  • the above-mentioned total heat recovery defrost control method compares the heat demand of the total heat recovery unit for air-conditioning heating and hot water production, and selects a heat exchanger with a small heat demand for defrosting, avoiding a large amount of heat in the heat exchanger in operation mode Loss, thereby reducing the impact on the user experience and ensuring the user’s heating demand or hot water demand.
  • 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 defrost control method.
  • the air conditioning device adopting the total heat recovery defrosting control method can achieve the same technical effect.
  • An embodiment of the present application also provides a computer storage medium, wherein the computer storage medium is stored in a computer program for electronic data exchange, and the computer program causes the air conditioning device to perform part or all of the steps of any method described in the above method embodiment .
  • the disclosed device may be implemented in other ways.
  • the device embodiments described above are merely illustrative.
  • the division of the above-mentioned units or modules is only a logical function division.
  • there may be other division methods for example, multiple units or components may be combined or It can be integrated into another system, or some features can be ignored or not implemented.
  • the displayed or discussed mutual coupling or direct coupling or communication connection may be indirect coupling or communication connection through some interfaces, devices or units, and may be in electrical or other forms.
  • the units described above as separate components may or may not be physically separate, and the components displayed as units may or may not be physical units, that is, they may be located in one physical space, or they may be distributed on multiple network units. Some or all of the units may be selected according to actual needs to achieve the objectives of the solutions of the embodiments.
  • the functional units in the various embodiments of the present application may be integrated into one processing unit, or each unit may exist alone physically, or two or more units may be integrated into one unit.
  • the above-mentioned integrated unit can be implemented in the form of hardware or software functional unit.

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Abstract

一种全热回收融霜控制方法、控制系统(10)及空气调节装置，所述方法包括以下步骤：运行在制热模式或热水模式下；判断当前运行工况是否满足融霜运行条件；如果当前运行工况满足融霜运行条件，则比较制热需求和热水需求；如果制热需求高于热水需求，则执行热水融霜模式；如果热水需求高于制热需求，则执行制热融霜模式。所述控制系统(10)，具有融霜判定模块(101)、比较模块(102)和执行模块(103)。通过比较全热回收机组对空调制热和制热水的热量需求，选择热量需求小的换热器进行融霜，避免运行模式下的换热器的热量大量损失，从而降低对用户使用体验的影响，保证用户的制热需求或热水需求

Description

全热回收融霜控制方法、控制系统和空气调节装置 技术领域
本发明属于空气调节设备技术领域，尤其涉及一种全热回收融霜控制方法，一种全热回收融霜控制系统以及一种空气调节装置。
背景技术
具有全热回收功能的空气调节装置是集制冷、供暖、生活热水于一体的空调机组。通常来说，这种空气调节装置包括压缩机，与空气热交换的室外空气侧翅片换热器，水侧换热器，回收热能的全热回收换热器、四通阀、电子膨胀阀、储液器以及设置在制冷循环系统中用于调节制冷剂流量和流向以执行不同功能的多个电磁阀、单向阀等执行部件。由于制冷剂可以有不同的流向并在换热器中与多种介质进行热交换，因此，具有全热回收功能的空气调节装置可以有多种功能模式，包括制热模式、制冷模式、热水模式等等。中国专利申请(授权公告号CN201212721Y)中公开了空调全热回收机构的制冷循环结构以及工作方式。
在制热运行模式或热水模式下，尤其是当环境温度较低时，位于室外的空气侧翅片换热器可能会出现结霜的现象，结霜时，由于霜层的增加，换热器的热阻增加，使换热量逐渐减少。当霜层增加到一定厚度时，换热量便迅速下降。为了避免换热量下降对空气调节装置运行造成的影响，配置了相应的制热融霜模式和热水融霜模式。在制热融霜模式中，高温高压制冷剂从压缩机中排出，经过四通阀进入室外空气侧翅片换热器。在室外空气侧翅片换热器中，高温高压状态的制冷剂和空气热交换放热融霜，同时冷凝为中温中压的制冷剂液体，中温中压的制冷剂液体经过储液器、经济器等设备进行过冷，并经节流装置成为低温低压制冷剂液体流动至室内的水侧换热器中与空调水进行热交换。在热 水融霜模式中，高温高压制冷剂从压缩机中排出，经过四通阀进入室外空气侧翅片换热器，在室外空气侧翅片换热器中向周围环境放热融霜，并冷凝成中温中压的制冷剂液体，中温中压的制冷剂经过储液器、经济器等设备进一步过冷，通过节流机构降压成为低温低压制冷剂液体，低温低压制冷剂液体进一步流动至热回收换热器。不难看出，在制热融霜模式或者热水融霜模式中，分别是通过牺牲室内水侧换热器或者热回收换热器的热量来实现融霜，这不可避免的会影响用户使用的舒适性。
本背景技术所公开的上述信息仅仅用于增加对本申请背景技术的理解，因此，其可能包括不构成本领域普通技术人员已知的现有技术。
发明内容
针对具有全热回收功能的空气调节装置在冬天制冷或制热水时室外换热器容易出现结霜，而融霜操作会消耗系统换热量，降低用户体验的问题，本发明设计并提供一种全热回收融霜控制方法。
为实现上述发明目的，本发明采用下述技术方案予以实现：
一种全热回收融霜控制方法，包括以下步骤：运行在制热模式或热水模式下；判断当前运行工况是否满足融霜运行条件；如果当前运行工况满足融霜运行条件，则比较制热需求和热水需求；如果制热需求高于热水需求，则执行热水融霜模式；如果热水需求高于制热需求，则执行制热融霜模式。
进一步的，比较制热需求和热水需求时执行以下步骤：采样当前制热设定温度T r和热回收换热器侧的进水温度T wi；计算第一温差T d1:T d1＝T r-T wi；采样当前热水设定水温T hr和热回收换热器侧的出水温度T h；计算第二温差T d2:T d2＝T hr-T h；如果所述第一温差T d1大于所述第二温差T d2，则判定为所述制热需求高于热水需求，执行热水融霜模式；如果所述第一温差T d1小于所述第二温差T d2，则判定为所述热水需求高于制热需求，执行制热融霜模式。
作为另一种可选方案，比较制热需求和热水需求时执行以下步骤：获取设定采样周期内热回收换热器侧的进水温度的变化率ΔT wi；获取设定采样周期内 热回收换热器侧的出水温度的变化率ΔT h；如果ΔT wi＞ΔT h，则判定为所述制热需求高于热水需求，执行热水融霜模式；如果ΔT wi＜ΔT h，则判定为所述热水需求高于制热需求，执行制热融霜模式。
作为另一种可选方案，比较制热需求和热水需求时执行以下步骤：采样当前制热设定温度T r和热回收换热器侧的进水温度T wi，计算第一温差T d1:T d1＝T r-T wi；采样当前热水设定水温T hr和热回收换热器的出水温度T h，并计算第二温差T d2:T d2＝T hr-T h；如果所述第一温差T d1大于所述第二温差T d2，则获取设定采样周期内热回收换热器侧的进水温度的变化率ΔT wi并获取设定采样周期内热回收换热器的出水温度的变化率ΔT h；如果ΔT wi＞ΔT h，则判定为所述制热需求高于热水需求，执行热水融霜模式，如果ΔT wi＜ΔT h，则判定为所述热水需求高于制热需求，执行制热融霜模式；如果所述第一温差T d1小于所述第二温差T d2，则获取设定采样周期内热回收换热器侧的进水温度的变化率ΔT wi并获取设定采样周期内热回收换热器的出水温度的变化率ΔT h；如果ΔT wi＞ΔT h，则判定为所述制热需求高于热水需求，执行热水融霜模式，如果ΔT wi＜ΔT h，则判定为所述热水需求高于制热需求，执行制热融霜模式。
更进一步的，获取设定采样周期内热回收换热器侧的进水温度的变化率ΔT wi包括以下步骤：获取设定采样周期终止时刻的热回收换热器侧的进水温度T wi1，所述设定采样周期终止时刻为判定为满足融霜运行条件的当前时刻；获取设定采样周期起始时刻的热回收换热器侧的进水温度T wi2，计算设定采样周期内热回收换热器侧的进水温度的变化率ΔT wi，
Figure PCTCN2020070797-appb-000001
更进一步的，获取设定采样周期内热回收换热器的出水温度的变化率ΔT h包括以下步骤：获取设定采样周期终止时刻的热回收换热器侧的出水温度T h1，所述设定采样周期终止时刻为判定为满足融霜运行条件的当前时刻；获取设定采样周期起始时刻的热回收换热器侧的出水温度T h2，计算设定采样周期内热回收换热器侧的进水温度的变化率ΔT h，
Figure PCTCN2020070797-appb-000002
优选的，所述设定采样周期的时长为30分钟。
进一步的，所述融霜运行条件包括：连续运行时间大于等于设定运行周期且室外换热器的盘管温度小于等于设定融霜温度，其中所述设定运行周期大于设定采样周期。
本发明的另一个方面提供一种全热回收融霜控制系统，包括：融霜判定模块，其用于在制热模式或热水模式下，判断当前运行工况是否满足融霜运行条件；比较模块，其用于比较制热需求和热水需求；和执行模块，其用于在制热需求高于热水需求时，执行热水融霜模式并在热水需求高于制热需求时，执行制热融霜模式。
本发明的另一个方面提供一种空气调节装置，空气调节装置为全热回收机组，其采用全热回收融霜控制方法，全热回收融霜控制方法，包括以下步骤：运行在制热模式或热水模式下；判断当前运行工况是否满足融霜运行条件；如果当前运行工况满足融霜运行条件，则比较制热需求和热水需求；如果制热需求高于热水需求，则执行热水融霜模式；如果热水需求高于制热需求，则执行制热融霜模式。
与现有技术相比，本发明的优点和积极效果是：通过比较全热回收机组对空调制热和制热水的热量需求，选择热量需求小的换热器进行融霜，避免运行模式下的换热器的热量大量损失，从而降低对用户使用体验的影响，保证用户的制热需求或热水需求。
结合附图阅读本发明的具体实施方式后，本发明的其他特点和优点将变得更加清楚。
附图说明
为了更清楚地说明本发明实施例中的技术方案，下面将对实施例中所需要使用的附图作一简单地介绍，显而易见地，下面描述中的附图是本发明的一些实施例，对于本领域普通技术人员来讲，在不付出创造性劳动的前提下，还可以根据这些附图获得其他的附图。
图1为本发明所公开的全热回收融霜控制方法一种实施例的流程图；
图2为比较制热需求和热水需求的第一种可选方式的流程图；
图3为比较制热需求和热水需求的第二种可选方式的流程图；
图4为比较制热需求和热水需求的第三种可选方式的流程图；
图5为本发明所公开的全热融霜控制系统一种实施方式的结构示意框图。
具体实施方式
为了使本发明的目的、技术方案及优点更加清楚明白，以下将结合附图和实施例，对本发明作进一步详细说明。
本发明的说明书和权利要求书及所述附图中的术语“第一”、“第二”、“第三”等是用于区别不同对象，而不是用于描述特定顺序。此外，术语“包括”和“具有”以及它们的任何变形，代表覆盖不排他的包含。例如包含了一系列步骤或单元的过程、方法、系统、产品或设备没有限定于已列出的步骤或单元，而是可选地还包括没有列出的步骤或单元，或可选地还包括对于这些过程、方法、产品或设备固有的其它步骤或单元。
在本发明中“实施例”代表结合实施例描述的特定特征、结构或特性可以包含在本申请的至少一个实施例中。在说明书中，各个位置出现该短语并不一定均是指相同的实施例，也不是与其它实施例互斥的独立的或备选的实施例。本领域技术人员可以理解，本文所描述的实施例可以与其它实施例相结合。
首先对全热回收机组进行介绍。全热回收机组可以工作在制冷模式，制热模式或热水模式。在制热模式或热水模式下需要对室外换热器融霜。
在热水模式下，低温低压的制冷剂蒸汽经压缩机压缩成高温高压的过热蒸汽，驱动制冷循环管路中相应的阀组打开，高温高压的过热蒸汽流向热回收换热器，与热回收换热器侧的介质热交换。热回收换热器侧的介质通常为水箱中的水，从而把水箱中的水加热到设定水温。同时高温高压的过热蒸汽在热回收换热器中冷凝成中温高压的液体，进一步引导制冷器流向储液器，再经过过滤器，然后流过电子膨胀阀转换为低温低压的液体，低温低压的液体再进一步经过相应的制冷剂管路流入室外翅片管式换热器，室外风机打开与室外空气热交 换。低温低压液体蒸发成低温低压气体，经四通换向阀流向压缩机，完成整个热水模式的制冷循环。
在制热模式下，低温低压的制冷剂蒸汽经压缩机压缩成高温高压的过热蒸汽，驱动相应的阀组打开，高温高压的过热蒸汽经四通换向阀流向室内的水侧换热器，与空调水进行热交换，把空调水加热到制热设定温度。同时高温高压的过热蒸汽冷凝成中温高压的液体。中温高压液体再经过制冷剂管路、过滤器、电子膨胀阀变为低温低压的液体，低温低压的液体再进一步经过相应的制冷剂管路流入室外翅片管式换热器，室外风机打开与室外空气热交换。低温低压液体蒸发成低温低压气体，经四通换向阀流向压缩机，完成整个制冷循环。
以下参照附图对全热回收融霜控制方法进行介绍，具体来说，如图1所示，包括以下步骤。
步骤S101，全热回收机组运行在制热模式或热水模式下。全热回收机组在冬季工作时，可以自动分时工作在制热模式或热水模式下，或者根据空调房间的热负荷或热水需求自动工作在制热模式或热水模式下。
步骤S102，判断当前运行工况是否满足融霜运行条件。结霜时，由于霜层的增加，导致室外翅片管式换热器的热阻增加，使得换热量逐渐减少。当霜层增加到一定厚度时，换热量便迅速下降，对应着机组的蒸发压力和蒸发温度都要开始加速下降。因此，根据盘管温度、压力变化的特性，可以采用温度与时间双因子判断是否满足融霜运行条件。举例来说，融霜运行条件可以设定为：连续运行时间大于等于设定运行周期，且室外翅片管式换热器的盘管温度小于等于设定融霜温度。可选的，设定运行周期可以设定为45分钟，设定融霜温度可以设定为-8℃至-5℃。除了温度与时间双因子判断条件外，融霜运行条件还可以设定为压力与时间双因子的判断条件。融霜运行条件还可以设定为现有技术中所采用的其它融霜判定条件。
步骤S103，如果当前运行工况满足融霜运行条件，则比较制热需求和热水需求。制热需求是指将介质，如空调水等加热到制热到制热设定温度并维持所 需要的热量，热水需求是指将水箱中的水加热到热水设定水温并维持所需要的热量。
步骤S104-1，如果制热需求高于热水需求，则执行热水融霜模式，即优选满足制热模式的控制目标而采用热回收换热器的换热实现融霜效果。在热水融霜模式下，通过四通阀实现换向，压缩机排出的高温高压的制冷剂蒸汽进入室外翅片管式换热器中。在室外翅片管式换热器中，高温高压的制冷剂蒸汽向周围环境放热，融化霜层。高温高压的制冷剂蒸汽放热后冷凝成中温的制冷剂液体，进一步通过制冷剂管路、储液器、经济器等过冷，并经过节流机构，如电子膨胀阀等成为低温低压制冷剂液体，低温低压的制冷剂液体进入热回收换热器中，与水箱中的水换热后进行气液分离，并再次进入压缩机进行压缩，从而完成热水融霜模式下的一个制冷循环。在这个过程中，优先保证的制热模式的运行受到的影响小，可以最大程度的确保用户的使用体验。
步骤S104-2，如果热水需求高于制热需求，则执行制热融霜模式，即优选满足热水模式的控制目标而采用室内的水侧换热器的换热实现融霜效果。在制热融霜模式下，通过四通阀实现换向，压缩机排出的高温高压的制冷剂蒸汽进入室外翅片管式换热器中。在室外翅片管式换热器中，高温高压的制冷剂蒸汽向周围环境放热，融化霜层。高温高压的制冷剂蒸汽放热后冷凝成中温的制冷剂液体，进一步通过制冷剂管路、储液器、经济器等过冷，并经过节流机构，如电子膨胀阀等成为低温低压制冷剂液体，低温低压的制冷剂液体进入室内水侧换热器中，与空调水等介质换热后进行气液分离，并再次进入压缩机进行压缩，从而完成制热融霜模式下的一个制冷循环。在这个过程中，优先保证的热水模式运行收到的影响小，可以最大程度的确保用户的使用体验。
上述全热回收融霜控制方法，通过比较全热回收机组对空调制热和制热水的热量需求，选择热量需求小的换热器进行融霜，避免运行模式下的换热器的热量大量损失，从而降低对用户使用体验的影响，保证用户的制热需求或热水需求。
结合全热回收机组的结构特点，参考图2所示，制热需求和热水需求可以采用以下的方式进行比较。
步骤S201，采样当前制热设定温度T r和热回收换热器侧的进水温度T wi。其中，当前制热设定温度T r可以是用户自行设定的设定温度，也可以是根据用户自行设定的温度值由存储的算法进行修正后的修正温度，还可以是由机组出厂前写入的控制算法根据环境参数自动生成的。具体来说，制热设定温度T r可以代表制热模式下的，为达到理想的空调房间的环境参数所要达到的空调水的目标温度。由于整个全热回收机组中的进水温度可以认为是相同的，而热回收换热器侧的进水温度T wi可以通过设置在水箱进水口的温度传感器检测得到，检测相对方便。因此，热回收换热器侧的进水温度T wi代表当前的空调水的实际温度。
步骤S202，计算第一温差T d1:T d1＝T r-T wi。通过第一温差即可以得到制热模式下，实时温度与目标温度之间的差值，即制热模式需要调节的热负荷。
步骤S203，采样当前热水设定水温T hr和热回收换热器侧的出水温度T h。类似的，当前热水设定水温T hr也可以是用户自行设定的设定温度，也可以是根据用户自行设定的温度值由存储的算法进行修正后的修正温度，还可以是由机组出厂前写入的控制算法根据环境参数生成的温度。具体来说，热水设定水温T hr是用户需要使用热水的目标水温，而热回收换热器侧的出水温度T h则是当前状态下可使用的水的水温。热回收换热器侧的出水温度T h可以通过设置在水箱出水口的温度传感器检测得到。
步骤S204,计算第二温差T d2:T d2＝T hr-T h。通过第二温差即可以得到热水模式下，实时水温与目标水温之间的差值，即热水模式需要调节的热负荷。
步骤S205-1，如果所述第一温差T d1大于所述第二温差T d2，即制热模式需要调节的热负荷高于热水模式需要调节的热负荷，进一步判定为所述制热需求高于热水需求，选择影响小的换热器进行融霜运行，即执行热水融霜模式。
步骤S205-2，如果所述第一温差T d1小于所述第二温差T d2，即热水模式需 要调节的热负荷高于制热模式需要调节的热负荷，进一步判定为所述热水需求高于制热需求，同样选择影响小的换热器进行融霜运行，即执行制热融霜模式。
参考图3所示，制热需求和热水需求还可以采用以下的方式进行比较。
步骤S301，获取设定采样周期内热回收换热器侧的进水温度的变化率ΔT wi。
具体来说，设定采样周期内热回收换热器侧的水箱的进水温度的变化率代表一段正常的运行时间内热回收换热器侧的水箱的进水口的温度变化。在实际运行过程中，全热回收机组中的水循环流动快，热回收换热器侧的水箱进水口的温度变化也会随之加快；全热回收机组中的水循环流动慢，热回收换热器侧的水箱进水口的温度变化也会随之减慢。因此，热回收换热器侧的水箱进水口的温度变化代表全热回收机组中水循环的状态，进一步动态体现在满足融霜运行条件前一段正常运行时间内的制热需求。
获取设定采样周期内热回收换热器侧的进水温度的变化率ΔT wi可以通过以下步骤实现：
获取设定采样周期终止时刻的热回收换热器侧的进水温度T wi1，设定采样周期终止时刻为判定满足融霜运行条件的当前时刻。
机组中预先存储有设定采样周期的时长以及各个设定采样点的热回收换热器侧的进水温度，进一步根据设定采样周期的时长获取设定采样周期起始时刻的热回收换热器侧的进水温度T wi2，
计算设定采样周期内热回收换热器侧的进水温度的变化率ΔT wi，
Figure PCTCN2020070797-appb-000003
步骤S302，获取设定采样周期内热回收换热器侧的出水温度的变化率ΔT h。
具体来说，设定采样周期内热回收换热器侧的水箱的出水温度的变化率代表一段正常的运行时间内热回收换热器侧的水箱的出水口的温度变化。在实际运行过程中，用户使用热水多，热回收换热器侧的水箱出水口的温度变化也会随之加快；用户使用的水少，热回收换热器侧的水箱出水口的温度变化也会随之减慢。因此，热回收换热器侧的水箱进水口的温度变化代表用户使用热水的 水量，进一步动态体现在满足融霜运行条件前一段正常运行时间内的热水需求。
获取设定采样周期内热回收换热器侧的出水温度的变化率ΔT h可以通过以下步骤实现：
获取设定采样周期终止时刻的热回收换热器侧的出水温度T h1，设定采样周期终止时刻为判定满足融霜运行条件的当前时刻；
机组中预先存储设定采样周期的时长以及各个采样点的热回收换热器侧的出水温度，进一步根据设定采样周期的时长获取设定采样周期起始时刻的热回收换热器侧的出水温度T h2，
计算设定采样周期内热回收换热器侧的出水温度的变化率ΔT h，
Figure PCTCN2020070797-appb-000004
步骤S303-1，如果ΔT wi＞ΔT h，则判定为所述制热需求高于热水需求，执行热水融霜模式。
步骤S303-2，如果ΔT wi＜ΔT h，则判定为所述热水需求高于制热需求，执行制热融霜模式。
在上述两个实施例中，图2的方式提供了一种根据静态参数，如当前制热设定温度、当前热水设定温度，比较并判定制热需求和热水需求的方式，图3则提供了一种通过动态参数，如进水温度的变化率、出水温度的变化率，比较并判定制热需求和热水需求的方式。为提高判定的准确率，如图4所示还提供了一种判断制热需求和热水需求的方式，其中融合了静态参数和动态参数，具体来说，包括以下步骤：
步骤S401，采样当前制热设定温度T r和热回收换热器侧水箱的进水温度T wi，并计算第一温差计算第一温差T d1:T d1＝T r-T wi；
步骤S402，采样当前热水设定水温T hr和热回收换热器侧的出水温度T h，并计算第二温差T d2:T d2＝T hr-T h；
步骤S403-1，如果所述第一温差T d1大于所述第二温差T d2，则获取设定采样周期内热回收换热器侧的进水温度的变化率ΔT wi并获取设定采样周期内热回 收换热器侧的出水温度的变化率ΔT h。
步骤S404-1，如果ΔT wi＞ΔT h，则判定为所述制热需求高于热水需求，执行热水融霜模式。
步骤S404-2，如果ΔT wi＜ΔT h，则以用户的动态使用情况为优先级，判定为所述热水需求高于制热需求，执行制热融霜模式。
步骤S403-2，如果所述第一温差T d1小于所述第二温差T d2，则获取设定采样周期内热回收换热器侧的进水温度的变化率ΔT wi并获取设定采样周期内热回收换热器侧的出水温度的变化率ΔT h。
步骤S404-3，如果ΔT wi＞ΔT h，则以用户的动态使用情况为优先级，判定为所述制热需求高于热水需求，执行热水融霜模式。
步骤S404-4，如果ΔT wi＜ΔT h，则判定为所述热水需求高于制热需求，执行制热融霜模式。
在上述的三种判断方式中，优选将设定采样周期的时长设定为30分钟。如果是采用时间温度双因子作为融霜运行条件，或者是采用时间压力双因子作为融霜运行条件，设定运行周期优选设置为大于设定采样周期，以确保在动态判定水温的变化率时可以完整的采样一个准确的使用周期，使得判定结果更为准确。
在融霜完成后，室外换热器的盘管温度和压力会上升，当上升到一定值时，则判定为满足退出融霜模式条件，恢复按照制热模式或热水模式运行。
参照图5所示，提供了一种全热回收融霜控制系统。如图5所示，全热回收融霜控制系统10包括以下组成部分。
融霜判定模块101，其用于在制热模式或热水模式下，判断当前运行工况是否满足融霜运行条件。
举例来说，融霜运行条件可以设定为：连续运行时间大于等于设定运行周期，且室外翅片管式换热器的盘管温度小于等于设定融霜温度。可选的，设定运行周期可以设定为45分钟，设定融霜温度可以设定为-8℃至-5℃。除了温度 与时间双因子判断条件外，融霜运行条件还可以设定为压力与时间双因子的判断条件。融霜运行条件还可以设定为现有技术中所采用的其它融霜判定条件。
比较模块102，比较模块用于在融霜判定模块判定满足融霜运行条件后比较制热需求和热水需求。其中，制热需求是指将介质，如空调水等加热到制热到设定制热温度并维持所需要的热量，热水需求是指将水箱中的水加热到设定水温并维持所需要的热量。
执行模块103，执行模块用于在制热需求高于热水需求时，执行热水融霜模式，并在热水需求高于制热需求时，执行制热融霜模式。
上述全热回收融霜控制方法，通过比较全热回收机组对空调制热和制热水的热量需求，选择热量需求小的换热器进行融霜，避免运行模式下的换热器的热量大量损失，从而降低对用户使用体验的影响，保证用户的制热需求或热水需求。
本发明同时还提供了一种空气调节装置。空气调节装置为全热回收机组。全热回收机组采用全热回收融霜控制方法。全热回收融霜控制方法的具体步骤请参见上述任一实施例的详细描述，在此不再赘述。采用全热回收融霜控制方法的空气调节装置可以实现同样的技术效果。
本申请实施例还提供一种计算机存储介质，其中，该计算机存储介质存储于电子数据交换的计算机程序，该计算机程序使得空气调节装置执行如上方法实施例中记载的任一方法的部分或全部步骤。
在上述实施例中，对各个实施例的描述均各有侧重，某个实施例中没有详述的部分，可以参见其它实施例的相关描述。
在本申请所提供的几个实施例中，应该理解到，所揭露的装置，可通过其它的方式实现。例如，以上所描述的装置实施例仅仅是示意性的，例如上述单元或模块的划分，仅仅为一种逻辑功能划分，实际实现时可以有另外的划分方式，例如多个单元或组件可以结合或者可以集成到另一个系统，或一些特征可以忽略，或不执行。另一点，所显示或讨论的相互之间的耦合或直接耦合或通 信连接可以是通过一些接口、装置或单元的间接耦合或通信连接，可以是电性或其它的形式。
上述作为分离部件说明的单元可以是或者也可以不是物理上分开的，作为单元显示的部件可以是或者也可以不是物理单元，即可以位于一个物理空间，或者也可以分布到多个网络单元上，可以根据实际需要选择其中的部分或者全部单元来实现本实施例方案的目的。
另外，在本申请各个实施例中的各功能单元可以集成在一个处理单元中，也可以是各个单元单独物理存在，也可以两个或两个以上单元集成在一个单元中。上述集成的单元既可以采用硬件的形式实现，也可以采用软件功能单元的形式实现。
以上实施例仅用以说明本发明的技术方案，而非对其进行限制；尽管参照前述实施例对本发明进行了详细的说明，对于本领域的普通技术人员来说，依然可以对前述实施例所记载的技术方案进行修改，或者对其中部分技术特征进行等同替换；而这些修改或替换，并不使相应技术方案的本质脱离本发明所要求保护的技术方案的精神和范围。

Claims (10)

  1. 全热回收融霜控制方法，其特征在于，包括以下步骤：
    运行在制热模式或热水模式下；
    判断当前运行工况是否满足融霜运行条件；
    如果当前运行工况满足融霜运行条件，则比较制热需求和热水需求；
    如果制热需求高于热水需求，则执行热水融霜模式；如果热水需求高于制热需求，则执行制热融霜模式。
  2. 根据权利要求1所述的全热回收融霜控制方法，其特征在于，
    比较制热需求和热水需求时执行以下步骤：
    采样当前制热设定温度T r和热回收换热器侧的进水温度T wi；
    计算第一温差T d1:T d1＝T r-T wi；
    采样当前热水设定水温T hr和热回收换热器侧的出水温度T h；
    计算第二温差T d2:T d2＝T hr-T h；
    如果所述第一温差T d1大于所述第二温差T d2，则判定为所述制热需求高于热水需求，执行热水融霜模式；
    如果所述第一温差T d1小于所述第二温差T d2，则判定为所述热水需求高于制热需求，执行制热融霜模式。
  3. 根据权利要求1所述的全热回收融霜控制方法，其特征在于，
    比较制热需求和热水需求时执行以下步骤：
    获取设定采样周期内热回收换热器侧的进水温度的变化率ΔT wi；
    获取设定采样周期内热回收换热器侧的出水温度的变化率ΔT h；
    如果ΔT wi＞ΔT h，则判定为所述制热需求高于热水需求，执行热水融霜模式；
    如果ΔT wi＜ΔT h，则判定为所述热水需求高于制热需求，执行制热融霜模式。
  4. 根据权利要求1所述的全热回收融霜控制方法，其特征在于，
    比较制热需求和热水需求时执行以下步骤：
    采样当前制热设定温度T r和热回收换热器侧的进水温度T wi，计算第一温差T d1:T d1＝T r-T wi；
    采样当前热水设定水温T hr和热回收换热器的出水温度T h，并计算第二温差T d2:T d2＝T hr-T h；
    如果所述第一温差T d1大于所述第二温差T d2，则获取设定采样周期内热回收换热器侧的进水温度的变化率ΔT wi并获取设定采样周期内热回收换热器的出水温度的变化率ΔT h；如果ΔT wi＞ΔT h，则判定为所述制热需求高于热水需求，执行热水融霜模式，如果ΔT wi＜ΔT h，则判定为所述热水需求高于制热需求，执行制热融霜模式；
    如果所述第一温差T d1小于所述第二温差T d2，则获取设定采样周期内热回收换热器侧的进水温度的变化率ΔT wi并获取设定采样周期内热回收换热器的出水温度的变化率ΔT h；如果ΔT wi＞ΔT h，则判定为所述制热需求高于热水需求，执行热水融霜模式，如果ΔT wi＜ΔT h，则判定为所述热水需求高于制热需求，执行制热融霜模式。
  5. 根据权利要求3或4所述的全热回收融霜控制方法，其特征在于，
    获取设定采样周期内热回收换热器侧的进水温度的变化率ΔT wi包括以下步骤：
    获取设定采样周期终止时刻的热回收换热器侧的进水温度T wi1，所述设定采样周期终止时刻为判定为满足融霜运行条件的当前时刻；
    获取设定采样周期起始时刻的热回收换热器侧的进水温度T wi2，
    计算设定采样周期内热回收换热器侧的进水温度的变化率ΔT wi，
    Figure PCTCN2020070797-appb-100001
  6. 根据权利要求5所述的全热回收融霜控制方法，其特征在于，
    获取设定采样周期内热回收换热器的出水温度的变化率ΔT h包括以下步骤：
    获取设定采样周期终止时刻的热回收换热器侧的出水温度T h1，所述设定采样周期终止时刻为判定为满足融霜运行条件的当前时刻；
    获取设定采样周期起始时刻的热回收换热器侧的出水温度T h2，
    计算设定采样周期内热回收换热器侧的进水温度的变化率ΔT h，
    Figure PCTCN2020070797-appb-100002
  7. 根据权利要求6所述的全热回收融霜控制方法，其特征在于，
    所述设定采样周期的时长为30分钟。
  8. 根据权利要求6所述的全热回收融霜控制方法，其特征在于，
    所述融霜运行条件包括：
    连续运行时间大于等于设定运行周期且室外换热器的盘管温度小于等于设定融霜温度，其中所述设定运行周期大于设定采样周期。
  9. 全热回收融霜控制系统，其特征在于，包括：
    融霜判定模块，其用于在制热模式或热水模式下，判断当前运行工况是否满足融霜运行条件；
    比较模块，其用于比较制热需求和热水需求；和
    执行模块，其用于在制热需求高于热水需求时，执行热水融霜模式并在热水需求高于制热需求时，执行制热融霜模式。
  10. 一种空气调节装置，其为全热回收机组，其特征在于，采用如权利要求1至9任一项所述的全热回收融霜控制方法
PCT/CN2020/070797 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 WO2021042654A1 (zh)

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