WO2018100166A1 - Procédé pour faire fonctionner un compresseur frigorifique à vitesse variable - Google Patents

Procédé pour faire fonctionner un compresseur frigorifique à vitesse variable Download PDF

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Publication number
WO2018100166A1
WO2018100166A1 PCT/EP2017/081206 EP2017081206W WO2018100166A1 WO 2018100166 A1 WO2018100166 A1 WO 2018100166A1 EP 2017081206 W EP2017081206 W EP 2017081206W WO 2018100166 A1 WO2018100166 A1 WO 2018100166A1
Authority
WO
WIPO (PCT)
Prior art keywords
refrigerant compressor
speed
control device
electronic control
cooling
Prior art date
Application number
PCT/EP2017/081206
Other languages
German (de)
English (en)
Inventor
Ulrich Gries
Jürgen Ewald Gläser
Allan Haue SLOT
Hans-Erik FOGH
Original Assignee
Nidec Global Appliance Germany Gmbh
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Nidec Global Appliance Germany Gmbh filed Critical Nidec Global Appliance Germany Gmbh
Priority to EP17808456.2A priority Critical patent/EP3548812A1/fr
Priority to US16/465,936 priority patent/US20190310004A1/en
Priority to CN201780074744.XA priority patent/CN110234942A/zh
Publication of WO2018100166A1 publication Critical patent/WO2018100166A1/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
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F25B49/025—Motor control arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F25B49/022—Compressor control arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • 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
    • F25B2600/00—Control issues
    • F25B2600/02—Compressor control
    • F25B2600/025—Compressor control by controlling speed
    • F25B2600/0253—Compressor control by controlling speed with variable speed
    • 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
    • F25B2700/15—Power, e.g. by voltage or current
    • F25B2700/151—Power, e.g. by voltage or current of the compressor motor
    • 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
    • F25B2700/2106—Temperatures of fresh outdoor air
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2115—Temperatures of a compressor or the drive means therefor
    • F25B2700/21153—Temperatures of a compressor or the drive means therefor of electronic components
    • 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
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating

Definitions

  • the invention relates to a method for operating a
  • Variable speed refrigerant compressor for cooling a cooling volume of a refrigeration system, wherein the refrigeration system
  • At least one thermostat for direct or indirect
  • Cooling cycle ends when the refrigerant compressor is put into an OFF state by a further switching signal triggered by the thermostat, wherein an operating cycle in addition to the cooling cycle comprises a rest cycle following the cooling cycle, and wherein the speed behavior of the
  • Refrigerant compressor during a cooling cycle by means of a in an electronic control device of the
  • Controlled refrigerant compressor stored default speed control, and an electronic control device for controlling the cyclical operation of a variable-speed refrigerant compressor. Often the electronic
  • Control device of the refrigerant compressor also as
  • Refrigerant compressor during a cooling cycle by means of a in an electronic control device of the
  • Controlled by the refrigerant compressor stored default speed control based on at least one predefined characteristic by the at least one predefined parameter is monitored for overshoot and / or undershooting by a current characteristic of a current cooling cycle.
  • Variable speed refrigerant compressors are associated with a variety of different refrigeration systems, such as
  • Refrigerated cabinets so for example refrigerators or racks, freezers, air conditioners or heat pumps, can be used. They offer over speed-resistant refrigerant compressors the advantage of being able to work more energy-optimized and the
  • variable speed refrigerant compressor in refrigeration systems with its own electronic control unit and components for monitoring the operating condition of the
  • Refrigeration systems are used. Such refrigeration systems are referred to as intelligent refrigeration systems in the sequence.
  • intelligent refrigeration systems in the electronic control unit of the refrigeration system, which to the electronic control device of the
  • Refrigerant compressor is different, different
  • This control signal may be
  • Refrigerant compressor specifies at what speed the
  • Refrigerant compressor to be operated or whether the electronic control device of the refrigerant compressor to turn this on or off.
  • variable speed refrigerant compressor is in
  • Refrigeration system usually already specifically targeted
  • Refrigeration requirements transmitted to the electronic control device of the refrigerant compressor relates to a different type of refrigeration systems, namely those that have no electronic control unit that can communicate with the electronic control device of the refrigerant compressor and that do not have electronic components for monitoring the operating state of the refrigeration system
  • Such refrigeration systems are therefore referred to as simple refrigeration systems in the sequence. They comprise at least one thermostat, which determines the temperature state of the
  • Temperature state triggers a switching signal, which the
  • Refrigerant compressor placed in the ON state or put in the OFF state.
  • Simple refrigeration systems communicate neither a speed specification to the electronic
  • Control device of the refrigerant compressor other data. They are also unable to others
  • the thermostat either requests or does not request refrigeration power, but does not quantify it, i. E. that the speed control of the refrigerant compressor is thus carried out exclusively by the electronic control device of the refrigerant compressor by programming them.
  • Refrigerant compressor is in terms of parameters to be defined, for example, as far as possible optimized in terms of energy consumption.
  • Refrigeration system receives no information about the operating condition, in particular no speed specification. This disadvantage is compensated in practice by the
  • Refrigerant compressor cause a circulation of a
  • Refrigerant in a sealed refrigerant system Refrigerant in a sealed refrigerant system.
  • the refrigerant is thereby absorbed by energy from the
  • Refrigerant compressor called, in a piston-cylinder unit by a in a cylinder housing
  • pumping piston is pumped to a higher pressure level, where the refrigerant emits heat through a condenser and is transported back into the evaporator via a throttle, in which a pressure reduction and the cooling of the refrigerant takes place.
  • the movement of the piston is realized via a crank drive driven by an electric drive unit comprising a crankshaft.
  • Refrigerant compressor is driven during the cooling cycle and one of the electronic control device of the
  • Refrigerant compressor has controlled speed behavior, wherein the electronic control device controls the electric drive unit of the refrigerant compressor.
  • a cooling cycle starts with a from the thermostat
  • Refrigeration system triggered switching signal which the
  • Refrigerant compressor placed in the ON state.
  • the thermostat triggers a switching signal for the ON state of the refrigerant compressor when the
  • Cooling volume temperature or a temperature representative of the cooling volume temperature exceeds a predetermined maximum value.
  • a vapor pressure-based thermostat for the purpose of monitoring the temperature state of the cooling volume of the thermostat, for example, as a vapor pressure-based thermostat, in particular as
  • Bellows thermostat be formed or a bimetallic strip or a NTC (negative temperature coefficient)
  • the refrigerant compressor is driven or
  • the further switching signal can be triggered, for example, when the temperature level or a cooling volume temperature or one for the
  • Cooling volume temperature representative temperature has dropped below a predetermined minimum value due to the cooling cycle taking place in the cooling volume.
  • the electronic control device of the refrigerant compressor operates during the cooling cycles according to a programmed specification, which determines the speed behavior of the
  • Refrigerant compressor during a cooling cycle regulates.
  • This default speed control makes it possible that variable-speed refrigerant compressor even in simple refrigeration systems, which as mentioned above, even no electronic
  • Control unit equipped with the electronic Control device of the refrigerant compressor is able to communicate within the programmed preset
  • the default speed control is set up such that at least one current, from the electronic
  • Control of the refrigerant compressor during a cooling cycle detectable characteristic with at least one, in the
  • Refrigerant compressor is regulated in dependence thereon.
  • the refrigerant compressor is stored by means of the stored in the electronic control device
  • predefined parameter regulated by the at least one predefined parameter in terms of over- and / or
  • the at least one predefined characteristic variable can be a very wide variety of parameters, for example the electrical load of the refrigerant compressor, which electrical load is measured by measuring the electrical current through the refrigerant compressor, in particular by the electric current flowing through the electric drive unit of the refrigerant compressor, during the Cooling cycle is determined.
  • the predefined parameter by the duration of a cooling cycle.
  • the predefined parameter stands for that value of
  • a temperature level in the cooling volume of the refrigeration system should be kept permanently as energy-optimized as possible by the default speed control.
  • the preset speed control causes that when this predetermined duration is exceeded or fallen short of, ie when the time interval between the response of the thermostat
  • Refrigerant compressor is greater or less than that
  • Control device of the refrigerant compressor whose speed changes either immediately or the next cooling cycle, with the aim that subsequent cooling cycles again have a duration that the predefined characteristic (duration)
  • Cooling cycle can be operated as energy-optimized again.
  • Such a preset speed control for operating a variable-speed refrigerant compressor in a simple refrigeration system is known for example from DE 102013114374.
  • the regulation of the rotational speed behavior takes place either during the current cooling cycle, wherein the rotational speed of the refrigerant compressor is increased when a
  • Exceeding the at least one predefined parameter (there duration of a cooling cycle) was detected by the current characteristic. Such an increase may also occur several times during a refrigeration cycle if the current characteristic exceeds a plurality of predefined characteristics, i. If, for example, despite increasing the speed of the thermostat still no switching signal for switching off the
  • Refrigerant compressor triggers because the temperature level or a cooling fluid temperature or one for the
  • Cooling volume temperature representative temperature in the cooling volume is still too high.
  • the increase can for example be progressive, degressive, linear or stepped. Recognizes the electronic control device, for example after several cooling cycles of the refrigerant compressor, that, even multiple, increasing the speed in each refrigeration cycle still does not mean that the predefined characteristic, for example, the predefined duration of a refrigeration cycle can be met, then according to the The technology also be provided that the starting speed of one or more subsequent cooling cycles is already set higher than is provided in the most energy-optimized case.
  • the starting rotational speed of a subsequent cooling cycle is reduced if the at least one predefined parameter is undershot.
  • Refrigerant compressor due to the default speed control is dependent on the individual programming, which is specified by the refrigerant compressor manufacturer at delivery of the refrigerant compressor. It is essential
  • the at least one predefined parameter is selected by the manufacturer of the refrigerant compressor such that previously known operating parameters of the refrigeration system, such as
  • variable-speed refrigerant compressor runs as energy-optimized as possible due to the default speed control during a cooling cycle.
  • Refrigerant compressor is not capable of any
  • Evaporator during a defrosting is heated to form in the area of the evaporator in the cooling volume of the refrigeration system ice or
  • Frost deposits especially when they form a continuous layer, act as an insulating layer and hinder the heat exchange between the cooling volume and the evaporator. During defrosting, it inevitably comes to a heating of the refrigerant in the evaporator.
  • the thermostat does not trigger a switching signal during the defrosting process in order to prevent the
  • the thermostat is due to the detected by the heating of the evaporator deviation of the temperature level in the cooling volume or the cooling volume temperature or for the
  • Power interruptions are the order of the day. Depending on the duration of the power interruption, the temperature in the cooling volume increases. As soon as the power supply is restored, the thermostat will switch to the switching signal
  • Cooling cycle triggered in which the speed curve is controlled according to the default speed control. This has the consequence that the speed of the refrigerant compressor is gradually increased, so the available cooling capacity increases slowly, although the cooling requirement of the cooling volume after defrosting or due to the heating due to the
  • Cooling cycle is disproportionately higher than the duration of the previous cooling cycles and from the long duration of the
  • Refrigeration compressor with a simple refrigeration system which does not have its own electronic control unit, which with the electronic control device of
  • Refrigerant compressor can communicate, which is a
  • Adjustment of the speed behavior in response to a previous special operating state allows the refrigerator temperature as fast as possible and possible
  • the invention relates to a method for operating a variable-speed refrigerant compressor as part of a simple refrigeration system, which does not have its own control unit, of the kind mentioned in the introduction.
  • a variable-speed refrigerant compressor as part of a simple refrigeration system, which does not have its own control unit, of the kind mentioned in the introduction.
  • the invention provides that in the electronic
  • Control device of the refrigerant compressor is stored at least one comparison parameter and an over- or
  • Target speed control is aimed solely at a regular operation of the refrigerant compressor and aims for a possible energy-optimized operation of the refrigerant compressor during such a control operation, the monitoring of the comparison parameter for detecting a previous special operating condition of the refrigeration system, in particular one Defrosting or interruption of power supply, designed and therefore provides one of which for the
  • Preset speed control necessary monitoring state separate, second monitoring state.
  • comparison parameter and the parameter are the same measured variable, it is necessary that the specifically defined values or value ranges of the comparison parameter and characteristic variable differ from one another. In particular, it may be provided that it is in the
  • Comparison parameter is a value of the measured variable, which is not assigned to the control mode or in which the control mode is no longer the optimal operating condition
  • the comparison parameter can represent a value of the measured variable that is outside of the means of the
  • the at least one comparison parameter is a variable that the electronic control device of the
  • Refrigerant compressor can detect and monitor itself without giving up additional information from one
  • Control unit of the refrigeration system which is not available in simple refrigeration systems, to be instructed.
  • the duration of operating cycles of the refrigerant compressor, in particular of the refrigeration cycle and rest cycle, as well as the load of the refrigeration cycle are conceivable as at least one comparison parameter
  • Comparison parameters such as load and duration of an operating cycle or load and / or duration of an operating cycle as well as further temperature is conceivable, the at least one comparison parameter being two or three
  • Comparison parameter in order to detect an overshoot or undershoot of the comparison parameter or the value of the comparison parameter can.
  • the current parameter value represents a currently measured value of the measured variable, which can be compared with the comparison parameter.
  • the comparison parameter can either be stored as a predetermined value in the electronic control device, that is already defined during manufacture, or be redefined during operation to allow the detection of defrosting as a deviation from the default speed control, as in more detail in the episode described.
  • the value of the at least one comparison parameter represents a limit value which is set in such a way that when the comparison parameter is exceeded or undershot by the current parameter value, it can be concluded that a previous special operating state, in particular a defrosting process or an interruption of the current supply.
  • the refrigerant compressor is connected to one of the
  • the detection of the special operating state can at any time one
  • Detection may be provided during the rest cycle or at the beginning of the cooling cycle that the special cooling cycle is started instead of a conventional conventional cooling cycle intended.
  • the one triggered by the thermostat triggers
  • the special cooling cycle is usually characterized by a speed behavior with an average speed, which is increased compared to the average speed of the default speed control. Immediately by increasing the middle
  • Arithmetic, geometric or harmonic mean understood over the duration of the cooling cycle.
  • Refrigerant compressor is stored at least one comparison parameter and an overshoot or undershoot the
  • the invention also relates to an electronic
  • Control device for controlling the cyclical operation of a variable-speed refrigerant compressor, wherein the
  • Thermostat for direct or indirect monitoring of a temperature condition of a cooling volume of a refrigeration system triggered switching signal to start a cooling cycle and to end a rest cycle and
  • Control device stored default speed control to regulate.
  • Control device is stored and the electronic
  • Control device is set up
  • Refrigerant compressor is in a start phase of a refrigeration cycle.
  • the load of the Refrigerant compressor is in a start phase of a refrigeration cycle.
  • Refrigerant compressor as operating parameters, since these in simple manner by measuring the electric current through the refrigerant compressor, in particular by the electrical drive unit of the
  • Refrigerant compressor electrical energy flowing during the cooling cycle is detected.
  • the start-up phase of the cooling cycle begins as soon as the refrigerant compressor has been switched to the ON state due to the receipt of the thermostat-triggered switching signal.
  • a current cooling cycle is interrupted for starting the special cooling cycle, in other words the
  • the electronic control device of the refrigerant compressor has circuits or
  • Control device is adapted to a load of
  • the monitored comparison parameter is the load
  • an average load which is averaged over a defined starting phase of the refrigerant compressor.
  • average load is meant the mean value of the loads, ie the sum of all detected individual loads during the starting phase averaged, for example as
  • Outliers of the load are compensated and a load behavior can be mapped.
  • the previous special operating state can be better monitored by monitoring the average load, since due to the heating of the refrigerant in the refrigerant system, the load of the refrigerant compressor over the start phase of the refrigeration cycle, usually at least over the first 30 s of the refrigeration cycle, is relatively large. Therefore, in a further embodiment of the invention
  • the duration of the starting phase is preferably between 10 s and 90 s, in particular between 30 s and 80 s, more preferably between 40 s and 70 s is monitored ,
  • the duration of the idle cycle is particularly suitable as a comparison parameter, since during normal operation according to the default speed control, the duration of the idle cycle usually does not exceed a maximum value. Therefore, in a further embodiment of the invention
  • the at least one monitored comparison parameter is a duration of the rest cycle.
  • due to the cold losses and / or insulation losses in the cooling volume is a duration
  • the special operating state usually leads to a longer duration of the rest cycle, for example up to 15
  • the comparison parameter is the maximum value of the duration of the rest cycle Are defined. If the actual duration of the current idle cycle exceeds the comparison parameter, then the
  • Thermostat triggered switching signal immediately the
  • Control device is adapted to a duration of the
  • Comparison parameter is a reference temperature ..
  • the detection and transmission of the additional temperature which is independent of the monitored by the thermostat temperature level of the refrigerant compressor, provides an additional
  • Measured temperature measuring device which is part of the electronic control device of the refrigerant compressor or on a housing of the refrigerant compressor
  • Comparison of the currently measured additional temperature as currently measured parameter value and the comparison temperature as a comparison parameter it can be determined, for example, that the refrigerant compressor was not in operation for a long period of time, if the currently measured additional temperature is below the reference temperature. Thus, it can be concluded on the monitoring of the additional temperature to a previously occurred special operating state, ie about a defrost or a
  • Control device is connected to a temperature measuring device for measuring an independent of the temperature cooling volume, further temperature, and that the stored comparison parameter is a comparison temperature and the currently measured parameter value is the further temperature.
  • the temperature measuring device can
  • thermometer for example, be designed as a probe, a resistance thermometer, a thermocouple or a temperature sensor.
  • electronic controllers are capable of detecting a previous power interruption. However, they are unable to determine how long the power supply was interrupted. In the case of a brief interruption, it would not be expedient to trigger a special cooling cycle since only a small additional cooling requirement prevails in the cooling volume. Therefore, a special cooling cycle is triggered only when the electronic control device of Refrigerant compressor has detected an interruption of the power supply and the comparison parameter is exceeded or fallen below by the currently measured parameter value. This ensures that the special cooling cycle is triggered only when an interruption of the power supply has been detected and due to the overshooting or undershooting of the comparison parameter by the currently measured
  • Comparison parameter in the first case also represents a load, in particular a medium load, or represents a comparison temperature in the second case.
  • a load in particular a medium load
  • a comparison temperature in the second case.
  • Refrigerant compressor monitors whether a power supply of the electronic control device has been interrupted
  • the electronic control device is set up to
  • inventive electronic control device is
  • the temperature measuring device is part of the electronic control device of the refrigerant compressor or that the temperature measuring device is arranged on a housing of the refrigerant compressor to a
  • the electronic control device of the refrigerant compressor already has other purposes,
  • Control device provided temperature measuring device as a further measured temperature is that only the programming of the electronic control device of the
  • Refrigerant compressor must be changed and not the structure of the electronic control device itself. This can also be already in use
  • Refrigerant compressor is mounted. There is
  • Refrigerant compressor and electronic control device of the refrigerant compressor usually as an assembly
  • Refrigerant compressor is arranged. This is the
  • Temperature measuring device Part of the delivered module and the functionality of the method is guaranteed regardless of any assembly or connection errors of the manufacturer of the refrigeration system. Particularly preferred is the
  • Temperature measuring device arranged on an outside of the housing, while the components of the
  • Refrigerated compressor deposited to have to resort to predefined stored comparison parameters in the delivery state is in another preferred
  • Refrigerant compressor is stored over at least two operating cycles as a stored parameter value.
  • the development of the stored parameter values indicates a special operating state.
  • the stored parameter values are above 3, 4, 5, 8 or 10
  • the currently measured parameter value is the further temperature, for example, the measured further temperature at the beginning of the cooling cycle and / or the measured further temperature at the end of the cooling cycle
  • stored temperatures are determined at the beginning of a cooling cycle and / or at the end of a cooling cycle, a cooling rate over which an expected further temperature at the beginning of the next cooling cycle is determined, wherein the expected further temperature as the comparison temperature, optionally including a multiplicative deviation factor is defined.
  • Refrigerant compressor is predefined, but in
  • Deviation factor constantly changed. It is also conceivable that the extreme value of the stored parameter values is determined and is used directly as a comparison parameter. Therefore, in a particularly preferred
  • Embodiment variant of the invention provides that in the electronic control device of the refrigerant compressor, an extreme value of the stored parameter values is selected and the comparison parameter as a function of
  • Extreme value of the stored parameter values is determined, preferably corresponding to the extreme value.
  • the mean value can be calculated, for example, as a geometric, arithmetic or harmonic mean of the stored parameter values. Again, the comparison parameter depending on the mean, for example, under
  • the comparison parameter can take into account possible fluctuations of the operating state by a predefined, in the
  • the comparison parameter is determined by multiplying the extreme value or the mean value with a deviation factor, wherein the
  • Deviation factor at least 1.25, preferably at least 1.50, more preferably 1.75, in particular 2.0.
  • the default speed control can be designed such that, depending on the
  • maximum speed or average speed a new starting speed for the subsequent cooling cycle is set. If no detection of the special operating state takes place and thus no special cooling cycle can be triggered, but a normal cooling cycle follows the special operating state, then the long duration of this cooling cycle and the high speed also have a negative effect on the following operating cycles:
  • the increased cooling demand results solely from the Effects of the special operating state and not on a generally higher cooling requirement of the cooling volume.
  • a starting rotational speed of the refrigerant compressor for the cooling cycle following the special cooling cycle is set to a value stored in the electronic control device.
  • a particularly effective cooling of the cooling volume in response to a special operating state, such as a defrosting operation or the interruption of the energy supply is achieved in a further embodiment of the invention in that the refrigerant compressor is operated during the special cooling cycle such that the cooling volume, a higher average cooling capacity is supplied than at a comparable cooling cycle controlled according to the default speed control.
  • the increased cooling capacity is achieved by an increased speed of the refrigerant compressor.
  • Method provides that the refrigerant compressor is operated during the special cooling cycle such that a
  • defined speed is not exceeded until the end of the special cooling cycle, wherein the defined speed at least 75%, preferably at least 85%, particularly preferably at least 90%, in particular between 95% and 100%, of a maximum speed of the refrigerant compressor is.
  • the refrigerant compressor for example, over a first defined period of time with a first defined speed of 95% of the maximum speed can be operated over a second defined period of time with a second defined speed of 80% of the maximum speed, wherein the cycles repeat alternately until the special cooling cycle ends.
  • the refrigerant compressor for example, over a first defined period of time with a first defined speed of 95% of the maximum speed can be operated over a second defined period of time with a second defined speed of 80% of the maximum speed, wherein the cycles repeat alternately until the special cooling cycle ends.
  • Refrigerant compressor is accelerated to a predefined speed at the beginning of the special cooling cycle, wherein the at least one defined speed at least 70%, preferably more at least 80%, more preferably at least 90%, in particular between 95% and 100%, a maximum speed of
  • Refrigerant compressor is.
  • variable-speed refrigerant compressor with an electric drive unit and a drivable by the electric drive unit piston-cylinder unit for
  • An electronic control device for controlling the cyclical operation of the variable speed
  • Refrigerant compressor according to a method of the invention.
  • Such an assembly can be installed in a simple manner in a refrigeration system without a control unit of the refrigeration system to a control signal or a speed specification the electronic control device of
  • Fig. 1 is a schematic representation of a back of a
  • Fig. 2 is a schematic representation of a
  • Fig. 3 is a schematic representation of the speed behavior of three different cycles of
  • Fig. 4 is a schematic representation of the speed behavior after a defrost according to the
  • FIG. 5 shows a schematic representation of the rotational speed behavior after a defrosting process according to a first embodiment variant of the method according to the invention
  • Fig. 6 is a schematic representation of the speed behavior after a defrost according to a second
  • Fig. 7 is a schematic representation of the speed behavior after a power failure according to a third embodiment of the method according to the invention.
  • Figure 1 shows a simple refrigeration system 1 with a variable-speed refrigerant compressor 2, a
  • Refrigerant line 5 and an evaporator 5a Refrigerant line 5 and an evaporator 5a.
  • Refrigerant compressor 2 refrigerant line 5 and
  • Evaporator 5a form a closed refrigerant system with, in which refrigerant circulates during operation, ie during a cooling cycle C K of the refrigerant compressor 2, refrigerant.
  • the refrigeration system 1 has a
  • Cooling volume 4 which can be withdrawn heat by the evaporator 5a or cooling power can be supplied by the refrigerant evaporates in the evaporator 5a.
  • the individual components of the refrigerant compressor 2 so at least one piston-cylinder unit in which the refrigerant is cyclically compressed and an electric
  • Refrigerant compressor 2 is arranged.
  • the variable-speed refrigerant compressor 2 also has a
  • Refrigerant compressor 2 during the cooling cycles C K according to a programmed default, which regulates the speed behavior C K of the refrigerant compressor 2 during a cooling cycle C K.
  • This default speed control allows the
  • variable speed refrigerant compressor 2 in the simple
  • Refrigeration system 1 can be operated while ensuring the most energy-optimized operation possible.
  • the programmed default is already at the
  • Refrigerant compressor manufacturer assembled as an assembly and sold as a unit to the manufacturer of refrigeration systems.
  • Refrigerant compressor 2 will require in the sequence
  • the refrigeration system 1 itself has no independent
  • Refrigerant compressor 2 switching signals, characteristics and
  • Measurements can provide or transmitted a control signal, which contains a speed specification.
  • the only switching signal which the simple refrigeration system 1 to the
  • Control device 6 of the refrigerant compressor 2 transmitted comes from a thermostat 3, depending on the
  • Thermostat 3 usually has a temperature sensor on,
  • a bimetallic strip for example, a bimetallic strip or a
  • Temperature coefficient element which is arranged in the cooling volume 4, to measure the temperature of the cooling volume 4 directly, or is arranged on the evaporator 5a to the
  • the thermostat 3 is vapor pressure-based
  • the thermostat 3 is designed to trigger a switching signal, which to the
  • Control means 6 of the refrigerant compressor 2 is transmitted or to transmit a switching signal to the control device 6, which switching signal sets the refrigerant compressor 2 in an ON state in which the drive unit is activated and refrigerant is compressed in the piston-cylinder unit.
  • the thermostat 3 is designed to trigger a further switching signal, which to the
  • Control device 6 is transmitted or another
  • Temperature measuring unit 7 is provided, via which an independent of the temperature of the cooling volume 4, another
  • Embodiment variant is the temperature measuring unit 7 as
  • FIG. 2 shows a second embodiment of the invention in which the temperature measuring unit 7 on the housing 8 of
  • the housing 8 of the refrigerant compressor 2 may be, for example, a hermetically encapsulated housing 8, which is a
  • Housing lower part 8a and a housing upper part 8b includes.
  • the housing lower part 8a and a housing upper part 8b includes.
  • Housing lower part 8a whereas the reference numeral 7 ⁇ ⁇ ⁇ denotes a dashed illustrated alternative mounting position on a post of the refrigerant compressor 2.
  • Refrigerant compressor 2 stored, predefined
  • Characteristic K v is controlled and the at least one predefined parameter K v is monitored for overshoot and / or undershooting by a current characteristic K a of a current cooling cycle C Ka .
  • the at least one predefined parameter K v is the duration of a cooling cycle C K.
  • the current running time and the actual duration of the cooling cycle C K are monitored by the electronic control device 6.
  • FIG. 3 three operating cycles C 1, C 2, C 3 are shown by way of example which show different rotational speed characteristics of the engine
  • Operating cycle C is made up of one each
  • Refrigerant compressor 2 during a cooling cycle C K is in operation and forcibly circulated refrigerant for cooling the cooling volume 4 by the refrigerant system.
  • the refrigerant compressor 2 is switched without drive and there is essentially no cooling of the cooling volume 4th
  • the first cooling cycle C K i is initiated at the time ti by the triggered by the thermostat 3 switching signal, wherein the refrigerant compressor 2 of the electronic
  • Control device 6 is set in an ON state.
  • the thermostat 3 triggers the switching signal when a deviation of the temperature level of the cooling volume 4 is detected from a predetermined temperature level, which suggests a cooling demand in the cooling volume 4, so that the cooling volume. 4
  • Refrigeration must be supplied through the refrigerant compressor 2. In the present case, at the time ti exceeding the predetermined temperature level of
  • variable speed refrigerant compressor 2 is set in the ON state, it is operated at a start speed vi.
  • time t 2 which corresponds to the predefined duration of the cooling cycle C K i, the predetermined temperature level in the cooling volume 4 has not yet been reached, and the thermostat 3 has accordingly not triggered a switching signal to the
  • Cooling volume 4 of the electronic control device 6 is not known, the speed v by a predetermined value, for example, 10%, 20%, 30% or 50%, the current
  • Speed vi increased to a first increased speed v 2 . This ensures that the refrigeration demand in the cooling volume 4 can be covered more quickly, or at very high refrigeration demand at all, or the refrigeration cycle C K can be terminated quickly.
  • time t 4 receives the electronic control device 6 triggered by the thermostat 3 further switching signal, which signals that the refrigeration demand in the cooling volume 4 is satisfied and the temperature within the cooling volume 4 is within the necessary for cooling predefined temperature levels. Due to the further switching signal, the electronic control device 6 sets the refrigerant compressor 2 in the OFF state, whereby the second idle cycle C R2 is triggered.
  • the elapsed time between times ti and t 4 time corresponds to the actual duration Ki of the first
  • the electronic control device 6 goes from an increased refrigeration demand in the subsequent cooling cycle C K 2.
  • the latter can be the case in particular if cooling cycles C K already exist before the cooling cycle C K i whose duration was longer than the predefined running time K v .
  • the increased starting speed v 4 can correspond, for example, to the last speed v of the preceding cooling cycle C K i or as the mean value of the speeds vi, v 2 , v 3 of the preceding ones
  • Cooling cycle C K i be calculated.
  • Control device 6 triggered by the thermostat 3 more
  • refrigeration cycle C K 2 is less than the predefined
  • Cooling cycle C3 match, so that the refrigeration needs of Cooling is achieved within the volume 4 predefined duration K v with the speed vi.
  • the third cooling cycle C K 3 a particularly energy-saving operation of
  • Refrigerant compressor 2 reached.
  • Control device 6 corresponds to the preset speed control, which is designed to allow over the entire operating time of the refrigerant compressor 2 as energy-optimized operation.
  • the refrigeration system 1 undergoes a defrosting in predetermined, usually periodic, intervals.
  • the evaporator 5a for example, over it provided
  • Heating elements heated to remove formed in the cooling volume 4 in the region of the evaporator 5a frost or ice layers.
  • at least the refrigerant in the evaporator 5a is also heated.
  • the defrost is triggered in a rest cycle C R , so that the
  • Refrigerant compressor 2 is in the OFF state during defrosting. During defrosting is no
  • Refrigerant compressor 2 is set in the ON state. Only after the end of the defrosting the thermostat triggers the 3
  • the disadvantages of the prior art will be explained with reference to the speed behavior depicted in FIG.
  • the first two cooling cycles C K i, C K 2 run, as previously described, after the default speed control.
  • the two cooling cycles C K i, C K 2 are shown as such operating cycles in which the predefined duration K v of the actual duration Ki, K 2 corresponds and the refrigerant compressor 2 with the
  • Cooling cycle C K 2 following third rest cycle C R 3 is a Defrosting process, marked as DEFROST in the figure, triggered.
  • the thermostat 3 After the end of the defrosting operation, the thermostat 3 triggers the switching signal and the refrigerant compressor 2 is set in the ON state. Since the electronic control device 6 of the refrigerant compressor 2 of the simple refrigeration system 1 does not receive any control signal, which on a
  • Controlled default speed control and a third cooling cycle C K 3 started. This starts with the start speed vi. As soon as the current time exceeds the predefined duration K v , the speed v of the refrigerant compressor 2 is increased to the first increased speed v 2 . Because the actual duration of the third
  • Cooling cycle C K 3 also exceeds the limits of the predefined duration K v i / K v2 , K v3 , the speed v increases stepwise to the increased speeds v 3 , v 4 and finally to a maximum speed v max . Only after crossing the third
  • Refrigerant compressor 2 pulled to a lower temperature level.
  • Cooling cycle C K 4 in the third cooling cycle C K3 is the same as the cooling cycle C K 4 .
  • Refrigerant compressor 2 operated in the previously described case with a too high for the cooling demand of the cooling volume 4 speed.
  • Control device 6 of the refrigerant compressor 2 at least one comparison parameter P v stored and overshoot or undershooting of the comparison parameter P v is monitored by a current parameter value P a to detect a previous defrosting.
  • the comparison parameter is a comparison duration P v of FIG. 5
  • Refrigerated compressor 2 stored variables is controlled, it is possible the refrigerant compressor 2 immediately after the end of defrosting at a high speed v, in the present case already with the maximum speed v max to operate.
  • a high cooling capacity in particular a maximum
  • Cooling capacity available from the refrigerant compressor
  • Speed v 4 is driven before the refrigerant compressor 2 has been accelerated to the maximum speed v max.
  • v max There are basically any progressive, degressive or
  • the starting speed v s of the subsequent third cooling cycle C K 3 is not by the
  • Figure 6 shows a second embodiment of the
  • the load L of the refrigerant compressor 2 by measuring the
  • a cooling cycle C K controlled by means of the preset speed control starts.
  • the current load L is measured continuously and a current average load L m calculated over the duration of the start phase of the cooling cycle C K , This current average load L m is then measured as currently measured parameter value P a with that in the electronic control device 6 of
  • Refrigerant compressor 2 stored comparison parameter P v compared. Since due to the heating of the refrigerant in the evaporator 5a during the defrosting process and / or due to the high refrigeration demand of the cooling volume 4, the currently measured average load L m exceeds the stored comparison parameter P v and the electronic control device 6 so concludes that a defrosting operation has taken place
  • Cooling cycle C K interrupted after the end of the start phase and the special refrigeration cycle C D started. Since the load L is only measurable during the cooling cycle C K , the
  • Thermostat 3 triggered switching signal can be started, but only after the end of the start phase of the cooling cycle C K.
  • Cooling capacity provides, and therefore the
  • FIG. 7 shows another aspect of the invention in which, due to the monitoring of the comparison parameter P v , the electronic control device 6 of FIG. 7
  • Refrigerant compressor 2 on a previous interruption of the power supply (as POWER BREAK in the drawing
  • the electronic control device 6 monitors the
  • Control device 6 is no information about the duration of the interruption of the power supply. In the event of a brief power failure, the triggering of the special cooling cycle C D does not make sense, since the cold room temperature only rises slightly during the interruption. However, if the power interruption lasts longer, the cooling volume 4 heats up and should be cooled down quickly by means of the special cooling cycle C D.
  • the further temperature T w is used as currently measured parameter value P a
  • the further temperature T w is measured by a temperature measuring device 7, either integral part of the electronic
  • Control device 6 of the refrigerant compressor 2 is or is arranged on the housing 8 of the refrigerant compressor 2.
  • the comparison parameter P v is this
  • Embodiment by a comparison temperature T v with which the currently measured additional temperature T w is compared.
  • a comparison temperature T v with which the currently measured additional temperature T w is compared.
  • Temperature T w with the reference temperature T v can be checked how far the electronic control device 6 and the housing 8 of the refrigerant compressor 2 have cooled.
  • Refrigerant compressor 2 triggered because it can be concluded on a long-lasting interruption of the power supply.
  • Special cooling cycle C D is triggered without a power failure was detected at the same time, so in other words can be concluded by monitoring the further temperature T w on a previous defrosting and the corresponding special cooling cycle C D are triggered.
  • Parameter P a is not around the further temperature is T w and a previous power failure from the electronic
  • Control device 6 of the refrigerant compressor 2 has been detected. For example, it is also possible to deduce a longer interruption of the power supply if the currently measured parameter value P a is the currently measured load L or the currently determined average load L m and an overshoot or undershoot of the comparison parameter P v has been detected ,
  • Refrigerant compressor 2 is not constantly operated at the maximum speed v max during the special cooling cycle C D , but with a percentage of it, for example, 85% of the maximum speed v max . Furthermore, it may be advantageous if the refrigerant compressor 2 during the
  • Special cooling cycle C D does not fall below a predefined speed v D , wherein the predefined speed v D is again defined as a percentage of the maximum speed v max , for example 75%. It is also advantageous if the refrigerant compressor 2 is operated immediately after the triggering of the special cooling cycle C D with a high predefined speed v D , wherein the predefined speed v D
  • the currently measured parameter values P a are stored in the electronic control device 6 of the refrigerant compressor 2 over several operating cycles C. This is particularly advantageous if the value of the comparison parameter P v is adapted on the basis of the stored parameter values P s .
  • the comparison parameter P v for example, depending on an extreme value P E , ie a minimum or maximum, the stored parameter values P s are varied or
  • Comparison parameter P v can either directly the
  • Comparison parameter P v is taken into account, ie the

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  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)

Abstract

L'invention concerne un procédé pour faire fonctionner un compresseur frigorifique (2) à vitesse variable destiné au refroidissement d'un volume à refroidir (4) d'une installation frigorifique (1) qui ne dispose par d'une unité de commande individuelle, l'installation frigorifique (1) comprenant au moins un thermostat (3) pour la surveillance directe ou indirecte d'un niveau de température du volume à refroidir (4), la vitesse du compresseur frigorifique (2) étant régulée, au cours d'un cycle de refroidissement, par une régulation de vitesse spécifiée stockée dans une unité de commande électronique (6) du compresseur frigorifique (2). L'invention vise à permettre l'adaptation de la caractéristique de vitesse de rotation en réponse à un état de fonctionnement spécial préalable, et le refroidissement aussi rapide et optimisé du point de vue énergétique du volume à refroidir (4). À cette fin, - au moins un paramètre de référence est stocké dans l'unité de commande électronique (6) du compresseur frigorifique (2), et un écart vers le haut ou vers le bas d'une valeur instantanée du paramètre par rapport au paramètre de comparaison est détecté, - un cycle de refroidissement spécial, différent de la régulation de vitesse spécifiée, est lancé lorsque la valeur instantanée mesurée du paramètre est supérieure ou inférieur au paramètre de référence, - le cas échéant, un cycle de refroidissement courant régulé par la régulation de vitesse spécifiée est interrompu par le cycle de refroidissement spécial.
PCT/EP2017/081206 2016-12-01 2017-12-01 Procédé pour faire fonctionner un compresseur frigorifique à vitesse variable WO2018100166A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP17808456.2A EP3548812A1 (fr) 2016-12-01 2017-12-01 Procédé pour faire fonctionner un compresseur frigorifique à vitesse variable
US16/465,936 US20190310004A1 (en) 2016-12-01 2017-12-01 Method for operating a rotational-speed-variable refrigerant compressor
CN201780074744.XA CN110234942A (zh) 2016-12-01 2017-12-01 用于运行转速可变的冷却剂压缩机的方法

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ATGM50255/2016U AT15779U1 (de) 2016-12-01 2016-12-01 Verfahren zum betrieb eines drehzahlvariablen kältemittelverdichters
ATGM50255/2016 2016-12-01

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WO2020078671A1 (fr) * 2018-10-16 2020-04-23 Arcelik Anonim Sirketi Unité de commande ayant un algorithme de commande de compresseur amélioré
CN113330262A (zh) * 2018-12-10 2021-08-31 Bsh家用电器有限公司 制冷器具和用于初始化制冷器具中的除霜过程的方法
EP3899383A4 (fr) * 2018-12-18 2022-10-05 Arçelik Anonim Sirketi Dispositif de refroidissement doté de compresseur à vitesse variable

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2020078671A1 (fr) * 2018-10-16 2020-04-23 Arcelik Anonim Sirketi Unité de commande ayant un algorithme de commande de compresseur amélioré
CN113330262A (zh) * 2018-12-10 2021-08-31 Bsh家用电器有限公司 制冷器具和用于初始化制冷器具中的除霜过程的方法
EP3899383A4 (fr) * 2018-12-18 2022-10-05 Arçelik Anonim Sirketi Dispositif de refroidissement doté de compresseur à vitesse variable

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