EP3222939B1 - Gestion du givre d'un évaporateur - Google Patents

Gestion du givre d'un évaporateur Download PDF

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Publication number
EP3222939B1
EP3222939B1 EP16162107.3A EP16162107A EP3222939B1 EP 3222939 B1 EP3222939 B1 EP 3222939B1 EP 16162107 A EP16162107 A EP 16162107A EP 3222939 B1 EP3222939 B1 EP 3222939B1
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EP
European Patent Office
Prior art keywords
heat pump
evaporator
operating
operating temperature
controller
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EP16162107.3A
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German (de)
English (en)
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EP3222939A1 (fr
Inventor
Pavel Trnka
Paul McGahan
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Ademco Cz SRO
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Honeywell sro
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Priority to EP16162107.3A priority Critical patent/EP3222939B1/fr
Priority to CN201710178383.5A priority patent/CN107228513A/zh
Publication of EP3222939A1 publication Critical patent/EP3222939A1/fr
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Classifications

    • 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
    • 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
    • F25B47/022—Defrosting cycles hot gas defrosting
    • F25B47/025—Defrosting cycles hot gas defrosting by reversing the 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
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/005—Arrangement or mounting of control or safety devices of safety devices
    • 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
    • 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
    • F25B2347/00—Details for preventing or removing deposits or corrosion
    • F25B2347/02—Details of defrosting cycles
    • F25B2347/023—Set point defrosting
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/19—Calculation of parameters
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2104—Temperatures of an indoor room or compartment
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2117—Temperatures of an evaporator

Definitions

  • the present disclosure relates to methods, devices, and systems for frost management of an evaporator.
  • Heat can be transported from low temperature reservoirs, such as from ambient outdoor air, to high temperature reservoirs, such as to an indoor building space, by using mechanical and/or electrical energy input to a device such as a heat pump.
  • Heat pumps can use an evaporator to remove heat from air. Operating temperatures of an evaporator of a heat pump evaporator are typically lower than the temperature of the air. If the temperature of the evaporator is below the dew point of the air, moisture in the air can condense on the evaporator surface. Moreover, if the air temperature is below the freezing point, the condensed moisture on the evaporator surface can turn toice.
  • the efficiency of the heat pump can suffer if ice formation on the evaporator surface occurs. That is, as ice forms on the surface of the evaporator of the heat pump, the efficiency of the heat pump can be reduced. When ice formation occurs, it can be necessary to perform defrosting of the evaporator surface to melt the ice that has formed.
  • EP 2320168 A1 discloses a Heat pump device capable of starting defrosting operation at an optimal timing for efficiency.
  • condensation temperature detection means detects a saturation temperature of a condenser
  • evaporation temperature detection means detect the saturation temperature of the evaporator.
  • Operation efficiency is estimated by a value obtained by dividing heating ability estimated from a detection value of the condensation temperature detection means by a difference between a detection value of condensation temperature detection means and that of evaporation temperature detection means or dissipation power estimated by the difference.
  • JP2007225158A discloses a defrosting operation control device having an evaporation temperature sensor, an air suction-side temperature sensor and an air supply-side temperature sensor which respectively measure an evaporation temperature of the refrigerant flowing inside of an evaporator, an air suction-side temperature of the evaporator and an air supply-side temperature of the evaporator.
  • a controller calculates temperature efficiency on the basis of the temperature information.
  • An amount of frost formation on the evaporator is estimated on the basis of changing trend from the start of frosting operation, of the calculated temperature efficiency, and the perfect defrosting start time and termination time are determined on the basis of the mount of frost formation, so that the switching on/off and rotational frequency of a compressor motor is controlled, and a heater is switched on.
  • the present invention provides for a controller for frost management of an evaporator and a corresponding method as claimed in the accompanying claims.
  • one or more embodiments include a memory, and a processor configured to execute executable instructions stored in the memory to receive operating information of a heat pump, determine a first set point of at least one of a number of components of the heat pump and a first operating temperature of an evaporator that correspond to operation of the heat pump at a first operating energy efficiency based on the operating information of the heat pump, receive a second operating temperature of the evaporator that is positively offset from the first operating temperature of the evaporator associated with the operating information of the heat pump, determine a second set point of at least one of the number of components of the heat pump that correspond to an operation of the heat pump at a second operating energy efficiency corresponding to the second operating temperature of the evaporator of the heat pump based on the operating information of the heat pump based on the operating information of the heat pump based on the operating information of the heat pump based on the operating information of the heat pump based on the operating information of the heat pump
  • Performing a defrost interval can remove ice from a surface of an evaporator of a heat pump and restore an efficiency of the heat pump to a level of that prior to ice formation. While a defrost interval may increase the efficiency of the heat pump by removing the ice from the evaporator, the heat pump can consume additional energy to perform the defrost interval, increasing a cost of operation of the heat pump.
  • Overall cost of operation of a heat pump can be characterized by the heating costs and the defrosting costs of the heat pump, as well as the duration of a complete heating interval length and defrost interval length.
  • Frost management of an evaporator in accordance with the present disclosure, can extend a heating interval length of the heat pumpto decrease the length of a defrost interval of the heat pump and/or the number of defrost intervals, thereby decreasing the overall cost of operation of the heat pump.
  • controller 102 as shown in Figure 1 can be controller 302, as shown in Figure 3 .
  • a or "a number of” something can refer to one or more such things.
  • a number of components can refer to one or more components.
  • FIG. 1 illustrates a system for frost management of an evaporator, in accordance with one or more embodiments of the present disclosure.
  • system 100 can include a controller 102, a heat pump 104, and an evaporator 106.
  • Controller 102 can receive operating information of heat pump 104.
  • Operating information of heat pump 104 can include a heat demand of heat pump 104.
  • a heat demand can refer to a request for a change in temperature of a building space (e.g., to be heated) by heat pump 104. That is, an occupant of the building space may set (e.g., via a thermostat) the building space to a desired temperature (e.g., set point), and heat pump 104 can supply the building space with heat based on the heat demand to the set point temperature.
  • Operating information of heat pump 104 can include instantaneous operating conditions of heat pump 104.
  • operating conditions of heat pump 104 can include a current actual temperature of the ambient air (e.g., outdoor air) heat pump 104 can extract heat from.
  • operating conditions of heat pump 104 can include a current actual temperature of a heat transfer fluid that heat pump 104 may sink heat into (e.g., to transfer heat to a refrigerant that can be used to heat a building space).
  • the operating information of heat pump 104 can be transmitted to controller 102 via a network relationship.
  • the operating information of heat pump 104 can be transmitted to controller 102 via a wired or wireless network.
  • the wired or wireless network can be a network relationship that connects heat pump 104 to controller 102.
  • Examples of such a network relationship can include a local area network (LAN), wide area network (WAN), personal area network (PAN), a distributed computing environment (e.g., a cloud computing environment), storage area network (SAN), Metropolitan area network (MAN), a cellular communications network, and/or the Internet, among other types of network relationships.
  • Controller 102 can determine a first set point of at least one of a number of components of heat pump 104 and a first operating temperature of evaporator 106 that correspond to operation of heat pump 104 at a first operating energy efficiency (e.g., the instantaneous operating energy efficiency) based on the operating information of heat pump 104.
  • a first operating temperature of evaporator 106 can be an optimum operating temperature that can correspond to the first operating energy efficiency of the operating information of heat pump 104.
  • the first operating efficiency can be a highest instantaneous energy efficiency of heat pump 104 (e.g., as distinguished from a time averaged value).
  • a set point e.g., the first set point
  • a number of components of heat pump 104 e.g., as will be further described herein
  • a highest possible instantaneous coefficient of performance (COP) of heat pump 104 This highest instantaneous COP can correspond to the optimum operating temperature of evaporator 106.
  • the first (e.g., optimum)operating temperature of evaporator 106 can be associated with an optimum COP of heat pump 104 based on the operating information of heat pump 104.
  • Controller 102 can receive a second operating temperature of evaporator 106 that is positively offset from the first operating temperature of evaporator 106 associated with the operating information of heat pump 104. That is, controller 102 can receive an offset operating temperature of evaporator 106 that is offset (e.g., warmer) from an optimum operating temperature of evaporator 106.
  • COP can be a ratio of heating energy provided by heat pump 104 to electrical energy consumed to provide that heat energy.
  • An optimum COP of heat pump 104 can refer to heat pump 104 operating at a maximum heating energy delivered with the least electrical energy consumed for current operating information of heat pump 104.
  • An evaporator can include a coil that includes refrigerant, wherein the refrigerant flowing from the evaporator carries thermal energy from a low temperature reservoir (e.g., ambient air) to a high temperature reservoir (e.g., a building space).
  • a positively offset operating temperature can be an operating temperature of evaporator 106 that is positively offset by a constant value from a predetermined operating temperature of evaporator 106.
  • Ice formation on the surface of evaporator 106 can act as insulation, reducing the efficiency of evaporator 106 by reducing the heat transfer coefficient of evaporator 106.
  • the speed of ice formation on evaporator 106 can be decreased with a decreasing difference between air temperature (e.g., ambient air temperature) and the operating temperature of evaporator 106. Therefore, the second(e.g., the offset) operating temperature of evaporator 106 can be higher than the first operating temperature of evaporator 106 to slow ice formation.
  • an optimum operating temperature of evaporator 106 can be -13 C, and a positively offset operating temperature of evaporator 106 can be -10 C.
  • An operating temperature of evaporator 106 that is warmer than the optimum operating temperature of evaporator 106 can slow ice formation speed on the surface of evaporator 106.
  • the positively offset operating temperature is described as being three degrees warmer than the optimal operating temperature, embodiments of the present disclosure are not so limited.
  • the positively offset operating temperature can be more than three degrees warmer or less than three degrees warmer than the optimal operating temperature of evaporator 106.
  • the positively offset operating temperature of evaporator 106 can be associated with a COP that is lower than the optimum COP associated with the optimum operating temperature of evaporator 106.
  • the positively offset operating temperature of evaporator 106 can be warmer than the predefined operating temperature of evaporator 106 to extend a heating interval of heat pump 104, but in turn lowering the COP of heat pump 104.
  • the warmer offset operating temperature of evaporator 106 can allow for a longer heating interval length of heat pump 104, lowering the overall cost of operation of heat pump 104, as will be further described herein.
  • Thepositively offset operating temperature of evaporator 106 can be fixed for all operating conditions of heat pump 104.
  • the positively offset operating temperature of evaporator 106 can be three degrees warmer than the optimum operating temperature of evaporator 106 for all operating conditions of heat pump 104, although embodiments of the present disclosure are not so limited to a three degree difference between the positively offset operating temperature and the optimum operating temperature of evaporator 106. That is, even though operating conditions such as fluid and air temperatures (e.g., as will be further described herein) fluctuate during operation of heat pump 104, thepositively offset operating temperature of evaporator 106 can be fixed for changes in operating conditions of heat pump 104.
  • Controller 102 can determine a second set point of at least one of the number of components of heat pump 104 that correspond to an operation of heat pump 104 at a second operating energy efficiency corresponding to the second (e.g., positively offset) operating temperature of evaporator 106, where the positively offset operating temperature of evaporator 106 can be determined or received for different combinations of operating conditions.
  • the second operating temperature can correspond to a second operating energy efficiency.
  • the second operating energy efficiency can be an energy efficiency that is associated with a COP that is lower than the optimum COP associated with the optimum operating temperature of evaporator 106.
  • the first operating energy efficiency can be a highest instantaneous energy efficiency based on the received instantaneous operating information of heat pump 104
  • the second operating energy efficiency can be a highest instantaneous energy efficiency based on the positively offset operating temperature of evaporator 106, where the second operating energy efficiency is lower relative to the first operating energy efficiency.
  • the positively offset operating temperature of evaporator 106 can be determined by adding a time average cost of defrosting evaporator 106 and a time average cost of heating by heat pump 104.
  • an optimized offset temperature can be determined by the following equation: min ⁇ , ⁇ T E c DEFROST ⁇ D + ⁇ + 1 ⁇ ⁇ 0 ⁇ c E Q ⁇ SP COP ⁇ U t , ⁇ T E dt , s . t .
  • the time average cost of defrosting can be determined using a defrosting cost and a defrosting interval length. For example, min ⁇ , ⁇ T E c DEFROST ⁇ D + ⁇ of Equation 1 can be used to determine the minimum time average cost of defrosting by dividing the defrosting cost of evaporator 106 (e.g., c DEFROST ) by the defrosting interval (e.g., ⁇ D + ⁇ ).
  • the operating information of heat pump 104 can include a heat transfer coefficient of evaporator 106, where the time average cost of heating is determined by a COP of heat pump 104 using the heat transfer coefficient of evaporator 106 and the positively offset operating temperature of evaporator 106.
  • the COP of heat pump 104 is a function of the heat transfer coefficient that changes as a function of time (e.g., U(t)) as well as the positively offset operating temperature that does not change as a function of time (e.g., ⁇ T E ).
  • the heating interval length of heat pump 104 based on the positively offset operating temperature of evaporator 106 can be longer than a heating interval length of heat pump 104 based on the predetermined operating temperature of evaporator 106.
  • a heating interval length of heat pump 104 based on a first (e.g., optimum)operating temperature of evaporator 106 of -13 C can be 80 minutes
  • the heating interval length of heat pump 104 based on the positively offset operating temperature of evaporator 106 of -10 C can be 105 minutes.
  • a heating interval length can be the length of time heat pump 104 operates in a heating mode. For example, if heat pump 104 operates to heat an indoor building space for 60 minutes, the heating interval length of heat pump 104 is 60 minutes.
  • the heating interval length of heat pump 104 based on the first (e.g., optimum) operating temperature of evaporator 106 and the positively offset operating temperature of evaporator 106 are described as being 80 minutes and 105 minutes, respectively, embodiments of the present disclosure are not so limited.
  • the heating interval length of heat pump 104 based on the first (e.g., optimum) operating temperature of evaporator 106 can be longer or shorter than 80 minutes.
  • the heating interval length of heat pump 104 based on the positively offset operating temperature of evaporator 106 can be longer or shorter than 105 minutes.
  • Controller 102 can modify a set point of at least one of a number of components of heat pump 104 based on the operating information such that a heating mode of heat pump 104 is enabled for the heating interval length of heat pump 104. For example, a set point of a component of heat pump 104 can be modified to the determined second set point such that heat pump 104 operates in heating mode for the heating interval length of heat pump 104.
  • the number of components of heat pump 104 can include a compressor.
  • the compressor can pressurize and circulate a heat transfer fluid through heat pump 104.
  • the heat transfer fluid in a gaseous state, can be pressurized and circulated by the compressor.
  • a compressor can be a mechanical device that increases the pressure of a gas (e.g., heat transfer fluid) by reducing its volume.
  • a set point of the compressor, such as compressor speed, can be modified such that the heating mode of heat pump 104 is enabled for the heating interval length of heat pump 104.
  • the number of components of heat pump 104 can include a water pump.
  • the water pump can circulate a working fluid (e.g., water)past a condenser of heat pump 104 so that the condenser can transfer heat to the working fluid, allowing the working fluid to heat a building space.
  • a set point of the water pump such as water pump speed, can be modified such that the heating mode of heat pump 104 is enabled for the heating interval length of heat pump 104.
  • the number of components of heat pump 104 can include a fan.
  • the fan can circulate a working fluid by a condenser of heat pump 104 so that the condenser transfers heat to the working fluid, allowing the working fluid to heat a building space.
  • a set point of the fan, such as fan speed, can be modified such that the heating mode of heat pump 104 is enabled for the heating interval length of heat pump 104.
  • the number of components of heat pump 104 can include an expansion valve.
  • a heat transfer fluid after passing through a condenser of heat pump 104, can pass through an expansion valve to lower the pressure of the heat transfer fluid.
  • an expansion valve can be a flow-restricting device that causes a pressure drop of the heat transfer fluid.
  • a set point of the expansion valve, such as valve position, can be modified such that the heating mode of heat pump 104 is enabled for the heating interval length of heat pump 104.
  • the set points associated with the number of components of heat pump 104 can be modified within a predetermined range.
  • the expansion valve positioning may be modified within a process limit of heat pump 104 to ensure the heat transfer fluid does not condense into a liquid, since allowing liquid to enter the compressor of heat pump 104 can catastrophically damage the compressor.
  • Determining a second set point of the number of components of the heat pump using the second operating temperature that is positively offset from the first operating temperature, and modifying a set point of at least one of a number of components of the heat pump to the second set point such that a heating mode of the heat pump is enabled for the heating interval length of the heat pump can allow for a lower cost of operation of the heat pump.
  • a heating interval length of the heat pump can be lengthened, thereby decreasing the number of defrost cycles of the heat pump, and in effect decreasing the overall cost of operation of the heat pump.
  • Figure 2 is a flow chart of a method for frost management of an evaporator, in accordance with one or more embodiments of the present disclosure.
  • Method 208 can be performed by, for example, controllers 102, and 302, described in connection with Figures 1 , and 3 , respectively.
  • the method 208 can include receiving operating information of a heat pump.
  • Operating information of a heat pump e.g., heat pump 104, previously described in connection with Figure 1
  • Operating information of the heat pump can include user demands, such as a heat demand of a space conditioned by the heat pump.
  • Operating information of the heat pump can also include operating conditions of the heat pump.
  • operating conditions of the heat pump can include a temperature of ambient air (e.g., outdoor air) the heat pump can extract heat from, as well as a temperature of a heat transfer fluid the heat pump may be sinking heat into from the ambient air.
  • the method 208 can include determining a first set point of at least one of a number of components of the heat pump and a first operating temperature of an evaporator that correspond to operation of the heat pump at a first operating energy efficiency.
  • the operating information of the heat pump can be used to determine a first set point of a number of components of the heat pump such that the evaporator of the heat pump can realize a first (e.g., optimum) operating temperaturethat corresponds to a first operating energy efficiency of the heat pump.
  • the firstoperating energy efficiency of the heat pump can be a highest instantaneous energy efficiency that can be associated with highest instantaneous coefficient of performance (COP) of the heat pump. That is, the heat pump can have an optimum COP associated with an optimum operating temperature of the evaporator of the heat pump based on the instantaneous operating information of the heat pump and set points of a number of components of the heat pump.
  • COP instantaneous coefficient of performance
  • the method can further include determining a coefficient of performance (COP) of the heat pump based on the positively offset operating temperature and the operating information of the heat pump. For example, the operating information of the heat pump and the positively offset operating temperature can be used to determine a COP of the heat pump while the evaporator is at thepositively offset operating temperature.
  • COP coefficient of performance
  • the COP of the heat pump based on the positively offset operating temperature and the operating information of the heat pump can be lower than the COP of the heat pump based on the optimum operating temperature. That is, the COP of the heat pump using the positively offset operating temperature can be lower such that the positively offset operating temperature of the evaporator is higher in order to slow ice formation on the surface of the evaporator.
  • the method 208 can include determining an offset operating temperature that ispositively offset from an optimum operating temperature of the evaporator associated with the operating information of the heat pump.
  • the optimum operating temperature of the evaporator can be lower (e.g., colder) than thepositively offset operating temperature of the evaporator.
  • the method 208 can include determining a second set point of at least one of a number of components of the heat pump that correspond to an operation of the heat pump at a second operating energy efficiency corresponding to the positively offset operating temperature of the evaporator of the heat pump based on the operating information of the heat pump at the point in time.
  • the positively offset operating temperature and the operating information of the heat pump can be used to determine the second set point of a number of components of the heat pump such that the evaporator of the heat pump can realize an positively offset operating temperature, where the positively offset operating temperature can correspond to a slightly lower COP of the heat pump relative to the optimum operating temperature of the evaporator.
  • the method 208 can include modifying a set point of at least one of a number of components of the heat pump based on the operating information such that a heating mode of the heat pump is enabled for the heating interval length of the heat pump. For example, a set point such as a speed or position of a compressor, a water pump, a fan, and/or an expansion valve of the heat pump can be modified to the determined second set point such that the evaporator of the heat pump can realize an offset operating temperature.
  • a set point such as a speed or position of a compressor, a water pump, a fan, and/or an expansion valve of the heat pump can be modified to the determined second set point such that the evaporator of the heat pump can realize an offset operating temperature.
  • the method can further include enabling a defrost mode of the heat pump after the heating interval length of the heat pump.
  • a defrost mode can be enabled to remove any ice that has formed on the surface of the evaporator of the heat pump.
  • the method can be continuously repeated. For example, as operating information of the heat pump such as operating conditions change with time, the method can be repeated to modify the heating interval length based on the changing operating information of the heat pump. That is, the method can be repeated to lengthen or shorten the heating interval length as necessary to ensure a cost of operation of the heat pump is reduced relative to a cost of operation using a heating interval length associated with an optimum operating temperature of the evaporator.
  • FIG 3 is a schematic block diagram of a controller for crowd comfortable settings, in accordance with one or more embodiments of the present disclosure.
  • Controller 302 can be, for example, controller 102, previously described in connection with Figure 1 .
  • Controller 302 can include a memory 320 and a processor 318 configured for frost management of an evaporator, in accordance with the present disclosure.
  • the memory 320 can be any type of storage medium that can be accessed by the processor 318 to perform various examples of the present disclosure.
  • the memory 320 can be a non-transitory computer readable medium having computer readable instructions (e.g., computer program instructions) stored thereon that are executable by the processor 318 to receive operating information of a heat pump.
  • processor 318 can execute the executable instructions stored in memory 320 to determine a first set point of at least one of a number of components of the heat pump and a first operating temperature of an evaporator that correspond to operation of the heat pump at a first operating energy efficiency at the point in time based on the operating information of the heat pump.
  • processor 318 can execute the executable instructions stored in memory 320 to receive a second operating temperature of the evaporator that is positively offset from the first operating temperature of the evaporator associated with the operating information of the heat pump,and determine a second set point of at least one of the number of components of the heat pump that correspond to an operation of the heat pump at a second operating energy efficiency corresponding to the second operating temperature of the evaporator of the heat pump based on the operating information of the heat pump at the point in time. Further, processor 318 can execute the executable instructions stored in memory 320 to modify a set point of at least one of the number of components of the heat pump to the second set point such that a heating mode of the heat pump is enabled for the heating interval length of the heat pump.
  • the memory 320 can be volatile or nonvolatile memory.
  • the memory 320 can also be removable (e.g., portable) memory, or non-removable (e.g., internal) memory.
  • the memory 320 can be random access memory (RAM) (e.g., dynamic random access memory (DRAM) and/or phase change random access memory (PCRAM)), read-only memory (ROM) (e.g., electrically erasable programmable read-only memory (EEPROM) and/or compact-disc read-only memory (CD-ROM)), flash memory, a laser disc, a digital versatile disc (DVD) or other optical storage, and/or a magnetic medium such as magnetic cassettes, tapes, or disks, among other types of memory.
  • RAM random access memory
  • DRAM dynamic random access memory
  • PCRAM phase change random access memory
  • ROM read-only memory
  • EEPROM electrically erasable programmable read-only memory
  • CD-ROM compact-disc read-only memory
  • flash memory a laser disc
  • memory 320 is illustrated as being located within controller 302, embodiments of the present disclosure are not so limited.
  • memory 320 can also be located internal to another computing resource (e.g., enabling computer readable instructions to be downloaded over the Internet or another wired or wireless connection).
  • logic is an alternative or additional processing resource to execute the actions and/or functions, etc., described herein, which includes hardware (e.g., various forms of transistor logic, application specific integrated circuits (ASICs), etc.), as opposed to computer executable instructions (e.g., software, firmware, etc.) stored in memory and executable by a processor. It is presumed that logic similarly executes instructions for purposes of the embodiments of the present disclosure.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Pump Type And Storage Water Heaters (AREA)

Claims (13)

  1. Régulateur (102, 302) pour la gestion du givre d'un évaporateur (106), comportant :
    une mémoire (320) ;
    un processeur (318) configuré pour exécuter des instructions exécutables conservées dans la mémoire (320) afin de :
    recevoir des informations de fonctionnement d'une pompe (104) à chaleur ;
    déterminer un premier point de consigne d'au moins un composant parmi une multiplicité de composants de la pompe (104) à chaleur et une première température de fonctionnement d'un évaporateur (106) qui correspondent au fonctionnement de la pompe (104) à chaleur à un premier rendement énergétique de fonctionnement d'après les informations de fonctionnement de la pompe (104) à chaleur pour faire fonctionner la pompe (104) à chaleur dans un mode de chauffage pendant une première longueur d'intervalle de chauffage à la première température de fonctionnement de telle façon que la pompe (104) à chaleur fonctionne à un coefficient de performance (COP) optimal ;
    recevoir une seconde température de fonctionnement de l'évaporateur (106) qui est décalée positivement par rapport à la première température de fonctionnement de l'évaporateur (106) associée aux informations de fonctionnement de la pompe (104) à chaleur ;
    déterminer un second point de consigne d'au moins un composant parmi la multiplicité de composants de la pompe (104) à chaleur qui correspond à un fonctionnement de la pompe (104) à chaleur à un second rendement énergétique de fonctionnement correspondant à la seconde température de fonctionnement de l'évaporateur (106) de la pompe (104) à chaleur d'après les informations de fonctionnement de la pompe (104) à chaleur pour faire fonctionner la pompe (104) à chaleur dans le mode de chauffage pendant une seconde longueur d'intervalle de chauffage correspondant à la seconde température de fonctionnement de telle façon que la pompe (104) à chaleur fonctionne à un COP qui est inférieur au COP optimal ; et
    modifier un point de consigne d'au moins un composant parmi la multiplicité de composants de la pompe (104) à chaleur pour passer au second point de consigne pour activer le mode de chauffage de la pompe (104) à chaleur pendant la seconde longueur d'intervalle de chauffage de la pompe (104) à chaleur qui est plus longue que la première longueur d'intervalle de chauffage de la pompe (104) à chaleur.
  2. Régulateur selon la revendication 1, la seconde température de fonctionnement étant supérieure à la première température de fonctionnement.
  3. Régulateur selon la revendication 1, les informations de fonctionnement de la pompe (104) à chaleur comprenant une demande de chaleur.
  4. Régulateur selon la revendication 1, les informations de fonctionnement de la pompe (104) à chaleur comprenant des conditions de fonctionnement de la pompe à chaleur.
  5. Régulateur selon la revendication 1, des points de consigne associés à la multiplicité de composants de la pompe (104) à chaleur étant modifiés à l'intérieur d'une plage prédéterminée.
  6. Régulateur selon la revendication 1, la multiplicité de composants comprenant un compresseur de la pompe (104) à chaleur.
  7. Régulateur selon la revendication 1, la multiplicité de composants comprenant une pompe à eau de la pompe (104) à chaleur.
  8. Régulateur selon la revendication 1, la multiplicité de composants comprenant un ventilateur de la pompe (104) à chaleur.
  9. Régulateur selon la revendication 1, la multiplicité de composants comprenant un détendeur de la pompe (104) à chaleur.
  10. Procédé mis en œuvre par ordinateur pour la gestion du givre d'un évaporateur (106), comportant :
    la réception, par un régulateur, d'informations de fonctionnement d'une pompe à chaleur ;
    la détermination, par le régulateur, d'un premier point de consigne d'au moins un composant parmi une multiplicité de composants de la pompe (104) à chaleur et d'une première température de fonctionnement d'un évaporateur (106) qui correspondent au fonctionnement de la pompe (104) à chaleur à un premier rendement énergétique de fonctionnement pour faire fonctionner la pompe (104) à chaleur dans un mode de chauffage pendant une première longueur d'intervalle de chauffage à la première température de fonctionnement de telle façon que la pompe (104) à chaleur fonctionne à un coefficient de performance (COP) optimal ;
    la détermination, par le régulateur, d'une température décalée de fonctionnement qui est décalée positivement par rapport à une température de fonctionnement optimale de l'évaporateur (106) associée aux informations de fonctionnement de la pompe à chaleur ;
    la détermination, par le régulateur, d'un second point de consigne d'au moins un composant parmi une multiplicité de composants de la pompe (104) à chaleur qui correspond à un fonctionnement de la pompe (104) à chaleur à un second rendement énergétique de fonctionnement correspondant à la température de fonctionnement décalée positivement de l'évaporateur (106) de la pompe (104) à chaleur d'après les informations de fonctionnement de la pompe à chaleur pour faire fonctionner la pompe (104) à chaleur dans le mode de chauffage pendant une seconde longueur d'intervalle de chauffage correspondant à la température de fonctionnement décalée positivement de telle façon que la pompe (104) à chaleur fonctionne à un COP qui est inférieur au COP optimal ; et
    la modification, par le régulateur, d'un point de consigne d'au moins un composant parmi la multiplicité de composants de la pompe (104) à chaleur pour passer au second point de consigne afin d'activer le mode de chauffage de la pompe (104) à chaleur pendant la seconde longueur d'intervalle de chauffage de la pompe (104) à chaleur qui est plus longue que le premier intervalle de chauffage de la pompe (104) à chaleur.
  11. Procédé selon la revendication 10, la réception d'informations de fonctionnement de la pompe (104) à chaleur comprenant la réception d'une demande de chaleur de la pompe (104) à chaleur.
  12. Procédé selon la revendication 10, le procédé comprenant en outre la détermination du coefficient de performance (COP) de la pompe (104) à chaleur d'après la température décalée de fonctionnement et les informations de fonctionnement de la pompe à chaleur.
  13. Procédé selon la revendication 10, le procédé comprenant en outre l'activation d'un mode de dégivrage de la pompe (104) à chaleur après la longueur d'intervalle de chauffage de la pompe (104) à chaleur.
EP16162107.3A 2016-03-23 2016-03-23 Gestion du givre d'un évaporateur Active EP3222939B1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP16162107.3A EP3222939B1 (fr) 2016-03-23 2016-03-23 Gestion du givre d'un évaporateur
CN201710178383.5A CN107228513A (zh) 2016-03-23 2017-03-23 蒸发器的霜管理

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP16162107.3A EP3222939B1 (fr) 2016-03-23 2016-03-23 Gestion du givre d'un évaporateur

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EP3222939B1 true EP3222939B1 (fr) 2020-08-19

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Publication number Priority date Publication date Assignee Title
JP2007225158A (ja) * 2006-02-21 2007-09-06 Mitsubishi Electric Corp 除霜運転制御装置および除霜運転制御方法
JP4642100B2 (ja) * 2008-09-01 2011-03-02 三菱電機株式会社 ヒートポンプ装置
CN201429276Y (zh) * 2009-06-10 2010-03-24 易达热泵(深圳)有限公司 带蒸发器稳定运行功能的多功能热泵
GB2528213B (en) * 2013-04-18 2020-01-15 Mitsubishi Electric Corp Heat pump apparatus and air conditioning system
CN105387665B (zh) * 2015-11-25 2018-08-10 东南大学 一种以空气源热泵综合性能最佳为目标的除霜控制方法

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CN107228513A (zh) 2017-10-03

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