EP0410330A2 - Method and apparatus for operating a refrigeration system - Google Patents

Method and apparatus for operating a refrigeration system Download PDF

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Publication number
EP0410330A2
EP0410330A2 EP19900113997 EP90113997A EP0410330A2 EP 0410330 A2 EP0410330 A2 EP 0410330A2 EP 19900113997 EP19900113997 EP 19900113997 EP 90113997 A EP90113997 A EP 90113997A EP 0410330 A2 EP0410330 A2 EP 0410330A2
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EP
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Prior art keywords
cooling
compressors
refrigeration system
cooling point
requirement
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EP19900113997
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German (de)
French (fr)
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EP0410330A3 (en
EP0410330B1 (en
Inventor
Wolfgang Höner
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York Deutschland GmbH
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York International GmbH
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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
    • F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
    • F25B5/02—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in parallel
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/07—Details of compressors or related parts
    • F25B2400/075—Details of compressors or related parts with parallel compressors
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/22—Refrigeration systems for supermarkets
    • 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
    • F25B2600/0251—Compressor control by controlling speed with on-off operation

Definitions

  • the invention relates to a method for operating a refrigeration system, in particular a composite refrigeration system, with at least two compressors connected in parallel, which are operated simultaneously or alternately individually to cover the respective refrigeration requirement of at least one cooling point.
  • the invention further relates to a device for carrying out the method.
  • This device is, in particular, a composite refrigeration system with at least one cooling point provided with sensors, with at least two compressors connected in parallel, which, in cyclically alternating or joint operation, provide the cooling capacity required to cover the cooling requirement.
  • the cooling capacity of a refrigeration system is determined by the cooling requirement of the connected cooling points, which is essentially influenced by the ambient temperature and the atmospheric humidity of the ambient air at the location of the cooling points. As a result, strong fluctuations in the cooling requirement are possible in the course of the season.
  • a refrigeration system must always meet the maximum cooling requirement, i.e. H. If the ambient temperature is high and the ambient air humidity is high, the location of the cooling points should be designed for maximum load of refrigerated goods and temperature as well as for the cooling volume of the cooling points.
  • the previously mentioned fluctuations in the cooling requirement have the consequence that the compressors provided for the cooling supply are operated with different duty cycles, with a known high frequency having a disadvantageous effect on their service life.
  • the switching on of the compressors if there is no common operation due to high cooling demand, the individual compressors are switched on after a predetermined cycle, so that the switching on frequency is as equal as possible for all compressors.
  • the determination of the cooling requirement and the dependent operation of the compressors of the refrigeration system is usually carried out by evaluating the suction pressure in the coolant circuit. For this purpose, the current pressure in the suction line is compared in a control circuit with a lowest value determined by calculation, so that the maximum cooling capacity required to supply the cooling points is provided at maximum cooling requirements.
  • the cooling points are controlled independently of this in a separate control loop that controls the supply of refrigerant to the specified temperature values.
  • the solution to the problem is characterized in that a reference signal for the respective cooling conditions at the cooling point is transmitted to a central unit from each cooling point, that the respective cooling requirement is determined therefrom and that the connected compressors are switched on or off accordingly.
  • the devices originally provided for local temperature control of the cooling points are linked to the capacity control of the compressor network, the reference signal of the cooling point being based on a target specification which includes both the maximum cooling volume and the resulting maximum cooling requirement the location of the cooling point with the prevailing ambient conditions is also taken into account, evaluated in the central unit in order to obtain a measure of the actual cooling requirement and accordingly to put one or more compressors into operation.
  • the refrigerant suction pressure is expediently also evaluated in the central unit as an additional reference variable and is based on the respective switching command to the compressors.
  • the supply of refrigerant to the connected cooling points is opened or closed by the central unit.
  • the cyclical switching or step switching of the compressors is carried out directly by a step switch arranged in the central unit.
  • the deviation of the cooling point temperature from its predetermined target value in conjunction with a stored time factor is a measure of the cooling requirement present, ie. H. a measure of the increase or decrease of the respective evaporation pressure of the refrigerant, taking into account all factors that determine the refrigeration demand.
  • a composite refrigeration system of the type mentioned at the outset for carrying out the method described above is characterized in accordance with the invention in that a central unit is provided which works both with the sensors of each cooling point and with the connected units sealing the refrigeration system is connected that each sensor gives a reference signal to the central unit, which evaluates this to determine the cooling requirement and that the central unit controls the operation of the compressors in accordance with the determined cooling requirement.
  • a sensor is understood to mean a temperature control unit which comprises one or more temperature sensors placed at the cooling point and a thermostat which is operatively connected to them.
  • the thermostat is preferably designed as an electronic temperature controller in order to ensure the most precise possible temperature detection with sufficiently small tolerances.
  • the sensors of each cooling point are connected to a step switch provided for controlling the compressors and apply a reference signal to the latter, and that the step switch controls the operation of the connected compressors in accordance with the reference signals received.
  • the temperature deviation of the cooling points gives a direct connection or return command to the step switch of the compressor control.
  • the signal With a temperature deviation of z. B. 1 to 2 K, the signal is in the neutral zone, ie there is no switching on or off of the compressors. If there is a 1K deviation, the tap changer receives a return signal and if there is a 2K deviation, a step forward signal. Adjustable timers are provided for forward and reverse. With the help of the suction pressure measurement, minimum and maximum values of the suction pressure can be limited.
  • the only figure shows one Circuit diagram of a composite refrigeration system, which works according to the inventive method.
  • the single figure shows a composite refrigeration system 10, with a total of three cooling points 11, which are connected in parallel and which are represented schematically by evaporators 11a.
  • a sensor designed as a temperature control is assigned to each cooling point and is formed from a thermostat 13 and at least one temperature sensor 18.
  • Each thermostat 13 assigned to a cooling point 11 cooperates with the at least one temperature sensor 18 and is connected to a central unit 20 via a signal line 14. Via this signal line 14, the central unit 20 is transmitted a reference signal from each of the thermostats 13 assigned to the cooling points 11 belonging to the refrigeration system, which provides information about the current cooling requirement of the cooling point 11 and thus indirectly about both the temperature of the cooling point 11 and the ambient conditions at the installation site the cooling point 11 there.
  • the signal line 14 is preferably designed as a data bus line, so that signals of different types can be transmitted. In addition, the transmission of control commands with the signal line 14 is also possible.
  • Each cooling point 11 is supplied via an inlet line 19 with the refrigeration unit formed by a compressor 22 with the amount of refrigerant required to cover the respective refrigeration requirement.
  • a remote-controlled shut-off valve 12 is arranged in front of each evaporator 11a in the refrigerant line 19 and interrupts or releases the supply of refrigerant in accordance with the reference signal of the thermostat 13 assigned to this cooling point 11.
  • the shut-off valves are preferably designed such that they assume two end positions, namely “open” and “closed”, without an intermediate position.
  • throttle point 17 in the feed line 19, which is preferably designed as a thermostatic expansion valve in order to ensure the complete evaporation of the refrigerant in the evaporator associated with the cooling point 11, not shown here in any more detail.
  • each cooling point can also be assigned a blower 14, which serves to distribute the cooling power released at the cooling point 11 in the evaporator 11a evenly.
  • the above-mentioned refrigeration unit is formed from three compressors 22, each connected in parallel and driven by an electric motor 23, which has a condenser 25, in which the highly compressed refrigerant is liquefied, giving off heat, and a downstream collector 27, from which the feed line 19 branches. is connected to the evaporators 11a.
  • suction line 24 is designed as a collecting line for the individual lines coming from the individual cooling points and, when the refrigeration unit is reached, is in turn guided in individual lines to the individual compressors 22.
  • this can, as shown in the example, be designed as an air-cooled condenser, and the heat dissipation can be increased by means of a single-stage or multi-stage fan.
  • water cooling can also be provided instead, which serves as a regenerative heat source.
  • the central unit 20 is connected to each thermostat 13 via signal lines 14 and thus receives the current reference values from the connected cooling points 11.
  • control signals can also be transmitted via this signal line 14, which is for the remote actuation of the remotely operated shut-off valves 12 is used.
  • a control line 15 is provided, which establishes the connection between the central unit 20 and the respective drive module of the assigned shut-off valve 12.
  • the additional blower 14, which is used for uniform cooling distribution at the cooling point 11, is also connected via a control line 16 to the associated thermostat 13, the control line 16 being able to be switched through, so that the blower 14 is controlled directly by the central unit 20.
  • each drive motor 23 for the compressors 22 is connected to the central unit 20 via a separate line 28.
  • a pressure sensor 21 is provided, which is used to detect the suction pressure of the refrigerant in the return line 24 and is designed as a measuring transducer and is also connected to the central unit 20.
  • the central unit receives the additional information about the respective refrigerant temperature, which in comparison with the respective cooling point temperature determines the required cooling capacity, i. H. the need for cooling, can be determined.
  • the suction pressure is entered as the setpoint minimum for the maximum cooling capacity.
  • the suction pressure setpoint increase via the thermostats 13 can take place in a preselected range, for example 0-10 K.
  • the deviation from the temperature setpoint of the cooling point can be between 0 and 2 K.
  • a setpoint shift for the suction pressure is 0 K at the maximum deviation of the cooling point temperature. The closer the cooling point temperature approaches its setpoint, the greater the increase in suction pressure setpoint. If there is a 0 K deviation from the cold store temperature setpoint, the largest setpoint increase for the suction pressure of 10 K, for example, comes into play. It is provided that the setpoint shift for the suction pressure takes place step-by-step with the inclusion of a timing element not described here.
  • This increase in the suction pressure setpoint according to the invention increases the operating time of the cooling points 11, which has an advantageous effect on the operation of the throttle valves 17. This prevents short operating times, which lead to inefficient operation of the refrigeration system 10 as a result of insufficient refrigerant filling of the evaporators 11a of the cooling points 11 and which, due to insufficient suction gas overheating, reduce the performance of the compressors 22 and adversely affect their service life.
  • the reference signal of the cooling point 11, which exhibits the greatest deviation of the cooling point temperature from the setpoint value, is decisive for the setpoint shift of the suction pressure of the refrigerant, since compliance with the setpoint for the cooling point must always be given priority.
  • cooling points 11 with a lower setpoint deviation are introduced more quickly to the temperature setpoint due to the higher cold supply compared to the current demand.
  • the method according to the invention is such that when the temperature falls below the cooling point at the cooling point, the supply of refrigerant to this cooling point 11 is interrupted by actuating the remotely operable shut-off valve 12.
  • shut-off valves 12 installed in the feed line 19 have two end positions for "open” and "closed", i. H. without intermediate position.
  • the compressor is switched off with a time delay, but if the suction pressure setpoint is exceeded, a compressor 22 is switched on. If there is a correspondingly high cooling requirement, the entire refrigeration unit, ie. H. all compressors 22 connected in parallel must be switched on.
  • the refrigeration system 10 shown by way of example can also be operated using a second method according to the invention, the temperature deviation at the cooling points 11 being used directly to control the step switch of the compressor control 20.
  • the cooling capacity of the refrigeration system 10 is not adapted to the cooling requirements of the cooling points 11 by shifting the suction pressure setpoint for the refrigerant but by increasing or decreasing the cooling capacity by switching the installed compressors 22 on or off.
  • the detection of the suction pressure of the refrigerant in the return line 24 only serves to limit the suction pressure downwards and upwards, i.e. H. with regard to minimum and maximum pressure.
  • the cooling unit is only switched on again when the temperature of a cooling point has exceeded the specified tolerance range.
  • the compressor is queried and evaluated when the return is requested, and also to initiate the long-term shutdown of the cooling points 11, e.g. B. to defrost iced evaporators.

Abstract

Method of operating a refrigeration system, in particular a combination refrigeration system with at least two parallel-connected compressors which are operated simultaneously together or alternately to cover the respective refrigeration requirement of at least one refrigeration point provided with sensors, a reference signal for the current refrigeration conditions at the refrigeration point (11) being transmitted from each refrigeration point (11) to a central unit (20) and the respective refrigeration requirement being determined from this, and the connected compressors (22) correspondingly being switched on or off by the central unit (20). <IMAGE>

Description

Die Erfindung betrifft ein Verfahren zum Betrieb einer Kälteanlage, insbesondere einer Verbund-Kälteanlage, mit wenigstens zwei parallel geschalteten Verdichtern, die zur Deckung des jeweiligen Kältebedarfs wenigstens einer Kühlstelle gleichzeitig gemeinsam oder abwechselnd ein­zeln betrieben werden.The invention relates to a method for operating a refrigeration system, in particular a composite refrigeration system, with at least two compressors connected in parallel, which are operated simultaneously or alternately individually to cover the respective refrigeration requirement of at least one cooling point.

Ferner betrifft die Erfindung eine Vorrichtung zur Durchführung des Verfahrens. Diese Vorrichtung ist ins­besondere eine Verbund-Kälteanlage mit wenigstens einer mit Sensoren versehenen Kühlstelle, mit wenigstens zwei parallel geschalteten Verdichtern, die in zyklisch ab­wechselndem oder gemeinsamem Betrieb die zur Deckung des Kältebedarfs erforderliche Kälteleistung aufbringen.The invention further relates to a device for carrying out the method. This device is, in particular, a composite refrigeration system with at least one cooling point provided with sensors, with at least two compressors connected in parallel, which, in cyclically alternating or joint operation, provide the cooling capacity required to cover the cooling requirement.

Die Kühlleistung einer Kälteanlage wird bestimmt durch den Kältebedarf der angeschlossenen Kühlstellen, der im wesentlichen durch die Umgebungstemperatur und die Luft­feuchtigkeit der Umgebungsluft am Ort der Kühlstellen beeinflußt wird. Hierdurch bedingt sind starke Schwan­kungen des Kältebedarfs im jahreszeitlichen Wechsel mög­lich.The cooling capacity of a refrigeration system is determined by the cooling requirement of the connected cooling points, which is essentially influenced by the ambient temperature and the atmospheric humidity of the ambient air at the location of the cooling points. As a result, strong fluctuations in the cooling requirement are possible in the course of the season.

Unabhängig von solchen Schwankungen muß eine Kälteanlage stets auf den maximalen Kältebedarf, d. h. bei hoher Um­gebungstemperatur und hoher Luftfeuchtigkeit der Umge­bungsluft am Aufstellungsort der Kühlstellen auf maxima­le Kühlgutbeschickung und Kühlguttemperatur sowie auf das Kühlvolumen der Kühlstellen ausgelegt sein. Dabei haben die zuvor erwähnten Schwankungen des Kältebedarfs zur Folge, daß die zur Kälteversorgung vorgesehenen Ver­dichter mit unterschiedlicher Einschaltdauer betrieben werden, wobei bekannterweise sich eine hohe Einschalt­häufigkeit nachteilig auf deren Lebensdauer auswirkt. Um diesem Problem abzuhelfen, ist aus der DE-PS 27 58 153 bekannt, mehrere Verdichter zur Kälteversorgung einer Kälteanlage zusammenzuschalten und bedarfsweise deren Betrieb so vorzusehen, daß ihre Einschaltung abhängig vom aktuellen Kältebedarf erfolgt. Dabei ist insbesonde­re vorgesehen, daß die Einschaltung der Verdichter, so­fern kein gemeinsamer Betrieb aufgrund hohen Kältebe­darfs erfolgt, die einzelnen Verdichter nach einem vor­gegebenen Zyklus eingeschaltet werden, so daß die Ein­schalthäufigkeit für alle Verdichter möglichst gleich ist.Regardless of such fluctuations, a refrigeration system must always meet the maximum cooling requirement, i.e. H. If the ambient temperature is high and the ambient air humidity is high, the location of the cooling points should be designed for maximum load of refrigerated goods and temperature as well as for the cooling volume of the cooling points. The previously mentioned fluctuations in the cooling requirement have the consequence that the compressors provided for the cooling supply are operated with different duty cycles, with a known high frequency having a disadvantageous effect on their service life. In order to remedy this problem, it is known from DE-PS 27 58 153 to interconnect several compressors for the cooling supply of a refrigeration system and, if necessary, to provide their operation in such a way that they are switched on depending on the current cooling requirement. In particular, it is provided that the switching on of the compressors, if there is no common operation due to high cooling demand, the individual compressors are switched on after a predetermined cycle, so that the switching on frequency is as equal as possible for all compressors.

Die Ermittlung des Kältebedarfs und der hiervon abhängi­ge Betrieb der Verdichter der Kälteanlage erfolgt übli­cherweise durch Auswertung des Saugdrucks im Kühlmittel­kreislauf. Hierzu wird in einem Regelkreis der aktuelle Druck in der Saugleitung mit einem durch Berechnung er­mittelten niedrigsten Wert verglichen, so daß bei maxi­malem Kühlbedarf die erforderliche größte Kälteleistung zur Versorgung der Kühlstellen bereitgestellt wird.The determination of the cooling requirement and the dependent operation of the compressors of the refrigeration system is usually carried out by evaluating the suction pressure in the coolant circuit. For this purpose, the current pressure in the suction line is compared in a control circuit with a lowest value determined by calculation, so that the maximum cooling capacity required to supply the cooling points is provided at maximum cooling requirements.

Die Kühlstellen werden hiervon unabhängig in einem eige­nen Regelkreis, der den Zulauf an Kältemittel kontrol­liert, auf die vorgegebenen Temperaturwerte geregelt.The cooling points are controlled independently of this in a separate control loop that controls the supply of refrigerant to the specified temperature values.

Dies hat zur Folge, daß die Kälteübertragung an den Kühlstellen mit der größtmöglichen Temperaturdifferenz erfolgt, obwohl im Teillastbereich eine entsprechend kleinere Temperaturdifferenz ausreichend wäre. Eine sol­che Betriebsweise aber ist unwirtschaftlich und führt zu einer hohen Einschalthäufigkeit. Die hiedurch bedingten kurzen Betriebszeiten können zu Störungen beim Betrieb der Drosselventile, z. B. thermostatische Expansionsven­tile, an den Verdampfern führen, da infolge unvollstän­diger Kältemittelbeaufschlagung der Verdampfer und Über­tragung von flüssigen Kühlmittel in die Saugleitung und damit in den Verdichter in stetem Wechsel möglich sind.The result of this is that the cold transfer takes place at the cooling points with the greatest possible temperature difference, although a correspondingly smaller temperature difference would be sufficient in the part-load range. Such a mode of operation, however, is uneconomical and leads to a high frequency of switching on. The resulting short operating times can lead to malfunctions in the operation of the throttle valves, for. B. thermostatic expansion valves, lead to the evaporators, as a result of incomplete refrigerant exposure to the evaporator and transfer of liquid coolant into the suction line and thus in the compressor in a constant change.

Ausgehend vom vorstehend genannten Stand der Technik ist es Aufgabe der Erfindung ein Verfahren zum Betrieb einer Kälteanlage der eingangs genannten Art anzugeben, nach welchem ein möglichst gleichförmiger Betrieb der Kälte­anlage möglich ist und im Hinblick auf den jeweiligen Kältebedarf eine möglichst gleichmäßige Auslastung der angeschlossenen Verdichter erfolgt. Außerdem soll eine nach dem Verfahren arbeitende Kälteanlage konzipiert werden.Starting from the above-mentioned prior art, it is an object of the invention to provide a method for operating a refrigeration system of the type mentioned at the outset, according to which the refrigeration system can be operated as uniformly as possible and with regard to the respective cooling requirement, the connected compressors are utilized as evenly as possible. In addition, a refrigeration system working according to the method is to be designed.

Die Lösung der Aufgabe ist erfindungsgemäß dadurch ge­kennzeichnet, daß von jeder Kühlstelle ein Referenzsi­gnal für die jeweiligen Kühlbedingungen an der Kühlstel­le an eine Zentraleinheit übermittelt wird, daß hieraus der jeweilige Kältebedarf ermittelt wird und daß dement­sprechend die angeschlossenen Verdichter ein- bzw. abge­schaltet werden.The solution to the problem is characterized in that a reference signal for the respective cooling conditions at the cooling point is transmitted to a central unit from each cooling point, that the respective cooling requirement is determined therefrom and that the connected compressors are switched on or off accordingly.

Gemäß der Erfindung ist danach vorgesehen, daß die ur­sprünglich zur örtlichen Temperaturregelung der Kühl­stellen vorgesehenen Einrichtungen mit der Leistungsre­gelung des Verdichter-Verbundes verknüpft werden, dabei wird das Referenzsignal der Kühlstelle unter Zugrundele­gung einer Sollvorgabe, die sowohl das maximale Kühlvo­lumen sowie den hieraus resultierenden maximalen Kälte­bedarf als auch den Aufstellungsort der Kühlstelle mit den vorherrschenden Umgebungsbedingungen berücksichtigt, in der Zentraleinheit ausgewertet, um so ein Maß für den tatsächlichen Kältebedarf zu erhalten und demgemäß einen oder mehrere Verdichter in Betrieb zu nehmen.According to the invention, it is provided that the devices originally provided for local temperature control of the cooling points are linked to the capacity control of the compressor network, the reference signal of the cooling point being based on a target specification which includes both the maximum cooling volume and the resulting maximum cooling requirement the location of the cooling point with the prevailing ambient conditions is also taken into account, evaluated in the central unit in order to obtain a measure of the actual cooling requirement and accordingly to put one or more compressors into operation.

Zweckmäßigerweise wird als zusätzliche Referenzgröße der Kältemittelsaugdruck ebenfalls in der Zentraleinheit ausgewertet und dem jeweiligen Schaltbefehl an die Ver­dichter zugrundegelegt.The refrigerant suction pressure is expediently also evaluated in the central unit as an additional reference variable and is based on the respective switching command to the compressors.

In vorteilhafter Ausgestaltung der Erfindung kann ferner vorgesehen sein, daß der Zulauf an Kältemittel zu den angeschlossenen Kühlstellen von der Zentraleinheit ge­öffnet oder geschlossen wird.In an advantageous embodiment of the invention it can further be provided that the supply of refrigerant to the connected cooling points is opened or closed by the central unit.

Während also bei herkömmlichen Kälteanlagen die Be­triebsweise der Verdichter zur Deckung des aktuellen Kältebedarfs üblicherweise mit festem Kältemittelsaug­druck-Sollwert erfolgt, und lediglich bei z. B. Super­märkten, in denen Verbund-Kälteanlagen ebenfalls zum Einsatz kommen, eine verbesserte Ausführung mit gleiten­dem Saugdruck-Sollwert Verwendung findet, bei der als Führungsgröße für die Sollwertanpassung die separate Temperatur und/oder relative Luftfeuchte des Verkaufs­raumes gewählt wird, ist gemäß der Erfindung vorgesehen, auf derartigen apparativen Aufwand zu verzichten, indem die ebenfalls vorgesehene Sollwertverschiebung der Saug­druck-Regelung mittels der in der Zentraleinheit ausge­werteten Kühlstellentemperaturen erfolgt.So while in conventional refrigeration systems, the operation of the compressors to cover the current refrigeration demand usually takes place with a fixed refrigerant suction pressure setpoint, and only with z. B. supermarkets, in which composite refrigeration systems are also used, an improved version with sliding suction pressure setpoint is used, in which the separate temperature and / or relative humidity of the sales room is selected as a guide variable for the setpoint adjustment, is provided according to the invention to dispense with such expenditure on equipment, in that the setpoint value shift of the suction pressure control, which is also provided, is carried out by means of the cooling point temperatures evaluated in the central unit.

Auf diese Weise werden nicht nur die Temperatur und die relative Feuchte der Umgebungsluft sondern alle den Käl­tebedarf beeinflussenden Faktoren berucksichtigt. Hier­durch ist erstmals auch für Kühlräume die Möglichkeit der energetisch vorteilhaften Kühlung mit gleitendem Saugdruck-Sollwert geschaffen.In this way, not only the temperature and the relative humidity of the ambient air but also all factors influencing the cooling requirement are taken into account. For the first time, this also creates the possibility of energetically advantageous cooling with sliding suction pressure setpoint for cold rooms.

Gemäß einer hierzu äquivalenten Variante zur Lösung der der Erfindung zugrundeliegenden Aufgabe kann ferner vor­gesehen sein, daß die zyklische Umschaltung bzw. Stufen­schaltung der Verdichter von einem in der Zentraleinheit angeordneten Stufenschalter unmittelbar vorgenommen wird. Gemäß der Erfindung ist also die Abweichung der Kühlstellentemperatur von ihrem vorgegebenen Sollwert in Verbindung mit einem gespeicherten Zeitfaktor ein Maß für den vorhandenen Kältebedarf, d. h. ein Maß für die Erhöhung oder die Absenkung des jeweiligen Verdampfungs­druckes des Kältemittels, wobei alle kältebedarfsbestim­menden Faktoren Berücksichtigung finden.According to a variant equivalent to this to achieve the object on which the invention is based, it can further be provided that the cyclical switching or step switching of the compressors is carried out directly by a step switch arranged in the central unit. According to the invention, the deviation of the cooling point temperature from its predetermined target value in conjunction with a stored time factor is a measure of the cooling requirement present, ie. H. a measure of the increase or decrease of the respective evaporation pressure of the refrigerant, taking into account all factors that determine the refrigeration demand.

Mit Hilfe dieser erfindungsgemäßen Verfahrensweise wird erreicht, daß die Verdichter stets mit der höchstmögli­chen und damit wirtschaftlichsten Verdampfungstemperatur betrieben werden können und gleichzeitig die vorge­schriebenen Kühlstellentemperaturen mit Sicherheit ein­gehalten werden. Hierdurch ist einerseits eine hohe Le­bensdauer der Verdichter gewährleistet und damit ande­rerseits ein hohes Maß an Verfügbarkeit, um die vorge­schriebenen Kühlstellen-Temperaturen einzuhalten.With the help of this procedure according to the invention it is achieved that the compressors can always be operated with the highest possible and therefore most economical evaporation temperature and at the same time the prescribed cooling point temperatures are maintained with certainty. This ensures on the one hand a long service life of the compressors and on the other hand a high degree of availability in order to maintain the prescribed cooling point temperatures.

Eine Verbundkälteanlage der eingangs genannten Art zur Durchführung des vorstehend beschriebenen Verfahrens ist erfindungsgemäß dadurch gekennzeichnet, daß eine Zen­traleinheit vorgesehen ist, die sowohl mit den Sensoren jeder Kühlstelle als auch mit den angeschlossenen Ver­ dichtern der Kälteanlage verbunden ist, daß jeder Sensor ein Referenzsignal an die Zentraleinheit gibt, welches diese zur Ermittlung des Kältebedarfs auswertet und daß die Zentraleinheit entsprechend dem ermittelten Kältebe­darf den Betrieb der Verdichter steuert.A composite refrigeration system of the type mentioned at the outset for carrying out the method described above is characterized in accordance with the invention in that a central unit is provided which works both with the sensors of each cooling point and with the connected units sealing the refrigeration system is connected that each sensor gives a reference signal to the central unit, which evaluates this to determine the cooling requirement and that the central unit controls the operation of the compressors in accordance with the determined cooling requirement.

Dabei wird definitionsgemäß hier und im weiteren unter Sensor eine Temperatur-Regeleinheit verstanden, die ei­nen oder mehrere an der Kühlstelle plazierte Temperatur­fühler und einen mit diesen in Wirkverbindung stehenden Thermostaten umfaßt. Vorzugsweise ist der Thermostat als elektronischer Temperaturregler ausgebildet, um eine möglichst präzise Temperaturerfassung mit genügend klei­nen Toleranzen zu gewährleisten.By definition, here and hereinafter, a sensor is understood to mean a temperature control unit which comprises one or more temperature sensors placed at the cooling point and a thermostat which is operatively connected to them. The thermostat is preferably designed as an electronic temperature controller in order to ensure the most precise possible temperature detection with sufficiently small tolerances.

Gemäß einer weiteren erfindungsgemäßen Lösung kann vor­gesehen sein, daß die Sensoren jeder Kühlstelle mit ei­nem zur Steuerung der Verdichter vorgesehenen Stufen­schalter verbunden sind und diesen mit einem Referenzsi­gnal beaufschlagen, und daß der Stufenschalter entspre­chend den erhaltenen Referenzsignalen den Betrieb der angeschlossenen Verdichter steuert.According to a further solution according to the invention, it can be provided that the sensors of each cooling point are connected to a step switch provided for controlling the compressors and apply a reference signal to the latter, and that the step switch controls the operation of the connected compressors in accordance with the reference signals received.

Die Temperaturabweichung der Kühlstellen gibt direkt ei­nen Zuschalt- oder Rücklaufbefehl auf den Stufenschalter der Verdichtersteuerung. Bei einer Temperaturabweichung von z. B. 1 bis 2 K befindet sich das Signal in der neu­tralen Zonde, d. h. es erfolgt weder ein Zu- noch ein Abschalten der Verdichter. Bei einer Abweichung 1K erhält der Stufenschalter ein Rücklaufsignal und bei Ab­weichung 2K einen Impuls für Vorlauf. Für Vorlauf und Rücklauf sind einstellbare Zeitglieder vorgesehen. Mit Hilfe der Saugdruckmessung können Minimum- und Maximum­werte des Saugdruckes begrenzt werden.The temperature deviation of the cooling points gives a direct connection or return command to the step switch of the compressor control. With a temperature deviation of z. B. 1 to 2 K, the signal is in the neutral zone, ie there is no switching on or off of the compressors. If there is a 1K deviation, the tap changer receives a return signal and if there is a 2K deviation, a step forward signal. Adjustable timers are provided for forward and reverse. With the help of the suction pressure measurement, minimum and maximum values of the suction pressure can be limited.

Diese und weitere vorteilhafte Ausgestaltungen der Er­findung sind in den Unteransprüchen angegeben.These and further advantageous refinements of the invention are specified in the subclaims.

Anhand eines in der Zeichnung dargestellten Ausführungs­beispiels sollen die Erfindung, vorteilhafte Ausgestal­tungen sowie Vorteile der Erfindung näher erläutert und beschrieben werden.The invention, advantageous refinements and advantages of the invention are to be explained and described in more detail using an exemplary embodiment shown in the drawing.

Die einzige Figur zeigt ein
Schaltschema einer Verbund-Kälteanlage, welche nach dem erfindungsgemäßen Verfahren arbeitet.The only figure shows one
Circuit diagram of a composite refrigeration system, which works according to the inventive method.

Die einzige Figur zeigt eine Verbund-Kälteanlage 10, mit insgesamt drei Kühlstellen 11, die parallel geschaltet sind und die durch Verdampfer 11a schematisch darge­stellt sind.The single figure shows a composite refrigeration system 10, with a total of three cooling points 11, which are connected in parallel and which are represented schematically by evaporators 11a.

Einer jeden Kühlstelle ist ein als Temperatur-Regelung ausgebildeter Sensor zugeordnet, der aus einem Thermo­stat 13 und wenigstens einem Temperaturfühler 18 gebil­det ist. Jeder einer Kühlstelle 11 zugeordnete Thermo­stat 13 arbeitet mit dem wenigstens einen Temperaturfüh­ler 18 zusammen und ist über eine Signalleitung 14 mit einer Zentraleinheit 20 verbunden. Über diese Signallei­tung 14 wird die Zentraleinheit 20 von jedem der den zur Kälteanlage gehörenden Kühlstellen 11 zugeordneten Ther­mostaten 13 ein Referenzsignal übermittelt, welches Auf­schluß über den momentanen Kältebedarf der Kühlstelle 11 und damit indirekt sowohl über die Temperatur der Kühl­stelle 11 als auch über die Umgebungsbedingungen am Auf­stellungsort der Kühlstelle 11 gibt.A sensor designed as a temperature control is assigned to each cooling point and is formed from a thermostat 13 and at least one temperature sensor 18. Each thermostat 13 assigned to a cooling point 11 cooperates with the at least one temperature sensor 18 and is connected to a central unit 20 via a signal line 14. Via this signal line 14, the central unit 20 is transmitted a reference signal from each of the thermostats 13 assigned to the cooling points 11 belonging to the refrigeration system, which provides information about the current cooling requirement of the cooling point 11 and thus indirectly about both the temperature of the cooling point 11 and the ambient conditions at the installation site the cooling point 11 there.

Vorzugsweise ist die Signalleitung 14 als Datenbuslei­tung ausgebildet, so daß Signale unterschiedlicher Art übertragen werden können. Außerdem ist auch die Übertra­gung von Steuerbefehlen mit der Signalleitung 14 mög­lich.The signal line 14 is preferably designed as a data bus line, so that signals of different types can be transmitted. In addition, the transmission of control commands with the signal line 14 is also possible.

Jede Kühlstelle 11 wird über eine Zulaufleitung 19 mit der von einem aus Verdichtern 22 gebildeten Kälteaggre­gat mit der zur Deckung des jeweiligen Kältebedarfs er­forderlichen Kältemittelmenge versorgt.Each cooling point 11 is supplied via an inlet line 19 with the refrigeration unit formed by a compressor 22 with the amount of refrigerant required to cover the respective refrigeration requirement.

In der Kältemittelleitung 19 ist vor jedem Verdampfer 11a jeweils ein fernbetätigbares Absperrventil 12 ange­ordnet, welches die Zufuhr an Kältemittel entsprechend dem Referenzsignal des dieser Kühlstelle 11 zugeordneten Thermostaten 13 unterbricht oder freigibt. Vorzugsweise sind die Absperrventile so ausgebildet, daß sie zwei Endstellungen, nämlich "offen" und "geschlossen", ohne Zwischenstellung einnehmen.A remote-controlled shut-off valve 12 is arranged in front of each evaporator 11a in the refrigerant line 19 and interrupts or releases the supply of refrigerant in accordance with the reference signal of the thermostat 13 assigned to this cooling point 11. The shut-off valves are preferably designed such that they assume two end positions, namely “open” and “closed”, without an intermediate position.

In Durchflußrichtung hinter dem Absperrventil 12 befin­det sich in der Zulaufleitung 19 eine Drosselstelle 17, die vorzugsweise als thermostatisches Expansionsventil ausgebildet ist, um die völlige Verdampfung des Kälte­mittels in dem der Kühlstelle 11 zugeordneten, hier nicht näher gezeigten Verdampfer zu gewährleisten.In the flow direction behind the shut-off valve 12 there is a throttle point 17 in the feed line 19, which is preferably designed as a thermostatic expansion valve in order to ensure the complete evaporation of the refrigerant in the evaporator associated with the cooling point 11, not shown here in any more detail.

Ergänzend kann jeder Kühlstelle zusätzlich ein Gebläse 14 zugeordnet sein, welches dazu dient, die an der Kühl­stelle 11 im Verdampfer 11a freigesetzte Kälteleistung gleichmäßig zu verteilen.In addition, each cooling point can also be assigned a blower 14, which serves to distribute the cooling power released at the cooling point 11 in the evaporator 11a evenly.

Das bereits erwähnte Kälteaggregat ist aus drei parallel geschalteten jeweils von einem Elektromotor 23 angetrie­benen Verdichtern 22 gebildet, welche über einen Konden­sator 25, in welchem das hochverdichtete Kältemittel verflüssigt wird unter Abgabe von Wärme, und einen nach­geschalteten Sammler 27, von welchem die Zulaufleitung 19 abgeht, mit den Verdampfern 11a verbunden ist.The above-mentioned refrigeration unit is formed from three compressors 22, each connected in parallel and driven by an electric motor 23, which has a condenser 25, in which the highly compressed refrigerant is liquefied, giving off heat, and a downstream collector 27, from which the feed line 19 branches. is connected to the evaporators 11a.

Der Rücklauf des Kältemittels zum Kälteaggregat erfolgt über eine Saugleitung 24, welche als Sammelleitung für die von den einzelnen Kühlstellen kommenden Einzellei­tungen ausgebildet ist und bei Erreichen des Kälteaggre­gats wiederum in Einzelleitungen zu den einzelnen Ver­dichtern 22 geführt ist.The return of the refrigerant to the refrigeration unit takes place via a suction line 24, which is designed as a collecting line for the individual lines coming from the individual cooling points and, when the refrigeration unit is reached, is in turn guided in individual lines to the individual compressors 22.

Zur Erhöhung des Wirkungsgrades bei der Verflüssigung des Kältemittels im Kondensator 25 kann dieser, wie im Beispiel gezeigt, als luftgekühlter Kondensator ausge­bildet sein, wobei mittels eines ein- oder mehrstufigen Gebläses die Wärmeabfuhr erhöht werden kann. Selbstver­ständlich kann statt dessen auch eine Wasserkühlung vor­gesehen sein, die als regenerative Wärmequelle dient.To increase the efficiency in the liquefaction of the refrigerant in the condenser 25, this can, as shown in the example, be designed as an air-cooled condenser, and the heat dissipation can be increased by means of a single-stage or multi-stage fan. Of course, water cooling can also be provided instead, which serves as a regenerative heat source.

Die Zentraleinheit 20 ist wie bereits erwähnt über Si­gnalleitungen 14 mit jedem Thermostaten 13 verbunden und erhält so die aktuellen Referenzwerte von den ange­schlossenen Kühlstellen 11. Wie ebenfalls erwähnt, kann über diese Signalleitung 14 auch die Übertragung von Steuerbefehlen erfolgen, was für die Fernbetätigung der fernbetätigbaren Absperrventile 12 genutzt wird. Hierzu ist abgehend von der Signalleitung 14 jeweils eine Steu­erleitung 15 vorgesehen, die die Verbindung zwischen der Zentraleinheit 20 und dem jeweiligen Antriebsmodul des zugeordneten Absperrventils 12 herstellt. In gleicher Weise ist auch das zusätzliche Gebläse 14, das zur gleichmäßigen Kälteverteilung an der Kühlstelle 11 dient, über eine Steuerleitung 16 mit dem zugeordneten Thermostat 13 verbunden, wobei die Steuerleitung 16 durchgeschaltet sein kann, so daß das Gebläse 14 direkt von der Zentraleinheit 20 angesteuert wird.As already mentioned, the central unit 20 is connected to each thermostat 13 via signal lines 14 and thus receives the current reference values from the connected cooling points 11. As also mentioned, control signals can also be transmitted via this signal line 14, which is for the remote actuation of the remotely operated shut-off valves 12 is used. For this purpose, starting from the signal line 14, a control line 15 is provided, which establishes the connection between the central unit 20 and the respective drive module of the assigned shut-off valve 12. In the same The additional blower 14, which is used for uniform cooling distribution at the cooling point 11, is also connected via a control line 16 to the associated thermostat 13, the control line 16 being able to be switched through, so that the blower 14 is controlled directly by the central unit 20.

Andererseits besteht auch die Möglichkeit, daß der zuge­ordnete Thermostat 13 die Ansteuerung des zugeordneten Gebläses 14 sowie des Absperrventils 12 übernimmt.On the other hand, there is also the possibility that the associated thermostat 13 takes over the control of the associated blower 14 and the shut-off valve 12.

Ferner ist erfindungsgemäß vorgesehen, daß jeder An­triebsmotor 23 für die Verdichter 22 jeweils über eine separate Leitung 28 mit der Zentraleinheit 20 verbunden ist.It is further provided according to the invention that each drive motor 23 for the compressors 22 is connected to the central unit 20 via a separate line 28.

Außerdem ist ein Drucksensor 21 vorgesehen, der zur Er­fassung des Saugdruckes des Kältemittels in der Rück­laufleitung 24 dient und als Meßwandler ausgebildet ebenfalls mit der Zentraleinheit 20 verbunden ist. An­hand des von dem Drucksensor 21 übermittelten Referenz­wertes für den aktuellen Saugdruck erhält die Zentral­einheit die zusätzliche Information über die jeweilige Kältemitteltemperatur woraus sich im Vergleich mit der jeweiligen Kühlstellentemperatur die erforderliche Kühl­leistung, d. h. der Kältebedarf, bestimmen läßt.In addition, a pressure sensor 21 is provided, which is used to detect the suction pressure of the refrigerant in the return line 24 and is designed as a measuring transducer and is also connected to the central unit 20. On the basis of the reference value for the current suction pressure transmitted by the pressure sensor 21, the central unit receives the additional information about the respective refrigerant temperature, which in comparison with the respective cooling point temperature determines the required cooling capacity, i. H. the need for cooling, can be determined.

Zur Durchführung des erfindungsgemäßen Verfahrens anhand der Funktion der vorstehend beschriebenen Schaltungsan­ordnung wird folgendes ausgeführt. Unter Zugrundelegung des im Beispiel dargestellten Schaltungsschema werden nach dem erfindungsgemäßen Verfahren die Sollwertabwei­chungen der Kühlstellensensoren 13 an die Zentraleinheit 20 weitergemeldet und dort zusammen mit dem Signal der Saugdrucküberwachung 21 zu einem Eingangssignal für den in der Zentraleinheit 20 integrierten, hier nicht näher gezeigten, Stufenschalter der Verdichtersteuerung verar­beitet.To carry out the method according to the invention using the function of the circuit arrangement described above, the following is carried out. On the basis of the circuit diagram shown in the example, the setpoint deviations of the cooling point sensors 13 are reported to the central unit 20 according to the inventive method and there together with the signal of the suction pressure monitor 21 to an input signal for the integrated step switch of the compressor control, not shown here, in the central unit 20 processed.

Gemäß der Erfindung sind die nachfolgend beschriebenen Möglichkeiten vorgesehen.According to the invention, the options described below are provided.

Der Saugdruck wird als Sollwert-Minimum für die maximale Kälteleistung eingegeben. Die Saugdruck-Sollwerterhöhung über die Thermostaten 13 kann in einem vorgewählten Be­reich, beispielsweise 0 - 10 K, erfolgen. Die Abweichung vom Temperatursollwert der Kühlstelle kann dabei zwi­schen 0 und 2 K betragen.The suction pressure is entered as the setpoint minimum for the maximum cooling capacity. The suction pressure setpoint increase via the thermostats 13 can take place in a preselected range, for example 0-10 K. The deviation from the temperature setpoint of the cooling point can be between 0 and 2 K.

Eine Sollwertverschiebung für den Saugdruck beträgt bei der maximalen Abweichung der Kühlstellentemperatur 0 K. Je weiter sich die Kühlstellentemperatur ihrem Sollwert nähert, desto größer kann die Saugdruck-Sollwerterhöhung sein. Bei 0 K Abweichung vom Kühlstellentemperatursoll­wert kommt die größte Sollwertanhebung für den Saugdruck von beispielsweise 10 K zum Tragen. Dabei ist vorgese­hen, daß die Sollwertverschiebung für den Saugdruck schrittweise unter Einbeziehung eines hier nicht näher beschriebenen Zeitgliedes erfolgt.A setpoint shift for the suction pressure is 0 K at the maximum deviation of the cooling point temperature. The closer the cooling point temperature approaches its setpoint, the greater the increase in suction pressure setpoint. If there is a 0 K deviation from the cold store temperature setpoint, the largest setpoint increase for the suction pressure of 10 K, for example, comes into play. It is provided that the setpoint shift for the suction pressure takes place step-by-step with the inclusion of a timing element not described here.

Durch diese erfindungsgemäße Erhöhung des Saugdruck-­Sollwertes wird die Betriebszeit der Kühlstellen 11 er­höht, was sich vorteilhaft auf die Arbeitsweise der Drosselventile 17 auswirkt. Kurze Betriebszeiten, die zu einem unwirtschaftlichen Betrieb der Kälteanlage 10 in­folge ungenügender Kältemittelfüllung der Verdampfer 11a der Kühlstellen 11 führen und die sich infolge ungenü­gender Sauggasüberhitzung leistungsmindernd auf die Ver­dichter 22 und nachteilig auf deren Lebensdauer auswir­ken, werden so verhindert.This increase in the suction pressure setpoint according to the invention increases the operating time of the cooling points 11, which has an advantageous effect on the operation of the throttle valves 17. This prevents short operating times, which lead to inefficient operation of the refrigeration system 10 as a result of insufficient refrigerant filling of the evaporators 11a of the cooling points 11 and which, due to insufficient suction gas overheating, reduce the performance of the compressors 22 and adversely affect their service life.

Gleichzeitig wird hiermit eine höhere Verdampfungstempe­ratur erreicht, bei der der Verdichter mit größerer Lei­stungszahl arbeitet, was gleichbedeutend ist, mit einer Erhöhung seiner Kälteleistung und einer Reduzierung sei­ner Leistungsaufnahme.At the same time, a higher evaporation temperature is achieved, at which the compressor works with a higher coefficient of performance, which is synonymous with an increase in its cooling capacity and a reduction in its power consumption.

Bestimmend für die Sollwertverschiebung des Saugdruckes des Kältemittels ist jeweils das Referenzsignal der Kühlstelle 11, die die größte Sollwertabweichung der Kühlstellentemperatur aufweist, da der Einhaltung des Kühlstellen-Sollwertes stets Vorrang einzuräumen ist.The reference signal of the cooling point 11, which exhibits the greatest deviation of the cooling point temperature from the setpoint value, is decisive for the setpoint shift of the suction pressure of the refrigerant, since compliance with the setpoint for the cooling point must always be given priority.

Kühlstellen 11 mit geringerer Sollwertabweichung werden in diesem Fall aufgrund des höheren Kälteangebotes ge­genüber dem augenblicklichen Bedarf schneller an den Temperatursollwert herangeführt.In this case, cooling points 11 with a lower setpoint deviation are introduced more quickly to the temperature setpoint due to the higher cold supply compared to the current demand.

Grundsätzlich ist das erfindungsgemäße Verfahren so be­schaffen, daß bei Unterschreiten des Temperatursollwer­tes an der Kühlstelle der Zulauf an Kältemittel zu die­ser Kühlstelle 11 durch Betätigen des fernbetätigbaren Absperrventils 12 unterbrochen wird.Basically, the method according to the invention is such that when the temperature falls below the cooling point at the cooling point, the supply of refrigerant to this cooling point 11 is interrupted by actuating the remotely operable shut-off valve 12.

Die in der Zulaufleitung 19 installierten Absperrventile 12 besitzen zwei Endstellungen für "offen" und "ge­schlossen", d. h. ohne Zwischenstellung.The shut-off valves 12 installed in the feed line 19 have two end positions for "open" and "closed", i. H. without intermediate position.

Wird der nach oben verschobene Saugdruck-Sollwert unter­schritten, so erfolgt zeitverzögert die Abschaltung ei­nes Verdichters, hingegen bei Überschreitung des Saug­druck-Sollwertes das Zuschalten eines Verdichters 22. Bei entsprechend hohem Kältebedarf kann auch das gesamte Kälteaggregat, d. h. sämtliche parallel geschalteten Verdichter 22, eingeschaltet sein.If the suction pressure setpoint shifted upwards is undershot, the compressor is switched off with a time delay, but if the suction pressure setpoint is exceeded, a compressor 22 is switched on. If there is a correspondingly high cooling requirement, the entire refrigeration unit, ie. H. all compressors 22 connected in parallel must be switched on.

Wie bereits erwähnt, kann der Betrieb der beispielhaft gezeigten Kälteanlage 10 auch nach einem zweiten erfin­dungsgemäßen Verfahren erfolgen, wobei die Temperaturab­weichung an den Kühlstellen 11 unmittelbar zur Ansteue­rung des Stufenschalters der Verdichtersteuerung 20 dient.As already mentioned, the refrigeration system 10 shown by way of example can also be operated using a second method according to the invention, the temperature deviation at the cooling points 11 being used directly to control the step switch of the compressor control 20.

Hierbei ist vorgesehen, daß die Anpassung der Kältelei­stung der Kälteanlage 10 an den Kältebedarf der Kühl­stellen 11 nicht über eine Verschiebung des Saugdruck-­Sollwertes für das Kältemittel erfolgt sondern durch Er­höhung bzw. Minderung der Kühlleistung mittels Zu- bzw. Abschaltung der installierten Verdichter 22.It is provided here that the cooling capacity of the refrigeration system 10 is not adapted to the cooling requirements of the cooling points 11 by shifting the suction pressure setpoint for the refrigerant but by increasing or decreasing the cooling capacity by switching the installed compressors 22 on or off.

Die Erfassung des Saugdrucks des Kältemittels in der Rücklaufleitung 24 dient hierbei lediglich zur Begren­zung des Saugdruckes nach unten und oben, d. h. hin­sichtlich Minimal- und Maximaldruck.The detection of the suction pressure of the refrigerant in the return line 24 only serves to limit the suction pressure downwards and upwards, i.e. H. with regard to minimum and maximum pressure.

Ergänzend ist darauf hinzuweisen, daß gemäß beiden Va­rianten vorgesehen ist, daß bei Betrieb mit abfallendem Saugdruck - gleichbedeutend mit sinkender Kühlstellen­temperatur - eine Auswertung der Kühlstellentemperaturen jener Kühlstellen 11 erfolgt, die sich innerhalb ihrer Schalthysterese befinden, wobei entsprechend ihrem Ab­stand zum Temperatursollwert der Zulauf an Kältemittel freigegeben wird, bis die Kühlstellentemperatur-Sollwer­te erreicht sind.In addition, it should be pointed out that according to both variants it is provided that, when operating with a decreasing suction pressure - synonymous with falling cooling point temperature - an evaluation of the cooling point temperatures of those cooling points 11 that are within their switching hysteresis takes place, with the supply of refrigerant corresponding to their distance from the temperature setpoint is released until the cooling point temperature setpoints are reached.

Erst wenn kein Zuschalten von Kühlstellen mehr möglich ist, d. h. die Kühlstellentemperatur-Sollwerte erreicht sind und der Saugdruck-Sollwert unterschritten wird, er­folgt die Abschaltung des letzten im Betrieb befindli­chen Verdichters 22.Only when it is no longer possible to switch on cooling points, i.e. H. the cooling point temperature setpoints have been reached and the suction pressure setpoint is not reached, the last compressor 22 in operation is switched off.

Die Wiedereinschaltung des Kälteaggregats erfolgt erst dann, wenn die Temperatur einer Kühlstelle den vorgege­benen Toleranzbereich überschritten hat. Hierbei kann es zweckmäßig sein, den Kühlstellen unterschiedliche Prio­ritäten zuzuordnen, denen zufolge eine Vorrangschaltung resultiert. Hierbei kann unterschieden werden zwischen Kühlstellen mit großem Kältebedarf bzw. mit großer Tem­peraturgenauigkeit und in solche mit geringerem Kältebe­darf oder größerer zulässiger Temperaturabweichung.The cooling unit is only switched on again when the temperature of a cooling point has exceeded the specified tolerance range. In this case, it may be expedient to assign different priorities to the cooling points, according to which a priority switching results. A distinction can be made between cooling points with high cooling requirements or with high temperature accuracy and those with lower cooling requirements or larger permissible temperature deviations.

Ergibt sich im Betrieb die Notwendigkeit der Zuschaltung eines weiteren Verdichters, so wird erfindungsgemäß zu­nächst geprüft, ob sich die Kühlstellentemperaturen be­reits in Sollwertnähe befinden. Ist dies der Fall, so werden diese Kühlstellen sukzessive vorzeitig abgeschal­tet.If, during operation, there is a need to connect a further compressor, it is first checked according to the invention whether the cooling point temperatures are already close to the setpoint. If this is the case, these cooling points are gradually switched off prematurely.

In entgegengesetzter Weise erfolgt eine Abfrage und Aus­wertung bei Rücklaufforderung der Verdichter, ebenso auch zur Einleitung der längerfristigen Abschaltung der Kühlstellen 11, z. B. um vereiste Verdampfer abzutauen.In the opposite manner, the compressor is queried and evaluated when the return is requested, and also to initiate the long-term shutdown of the cooling points 11, e.g. B. to defrost iced evaporators.

Durch diese Maßnahme erfolgt jeweils die volle Ausla­stung der einzelnen Verdichter und es kann auf eine ex­trem feinstufige Unterteilung der Verdichter, z. B. mit­tels Zylinderabschaltung, verzichtet werden. Ein schäd­licher Kurzzeitbetrieb wird verhindert, und die Verdich­ter werden mit höchstmöglicher Verdampfungstemperatur äußert wirtschaftlich betrieben.This measure ensures that the individual compressors are fully utilized and that the compressors can be divided extremely finely, e.g. B. by means of cylinder deactivation. Harmful short-term operation is prevented and the compressors are operated extremely economically with the highest possible evaporation temperature.

Claims (10)

1. Verfahren zum Betrieb einer Kälteanlage, insbe­sondere einer Verbund-Kälteanlage mit wenigstens zwei parallel geschalteten Verdichtern, die zur Deckung des jeweiligen Kältebedarfs von wenigstens einer mit Senso­ren versehenen Kühlstelle gleichzeitig gemeinsam oder abwechselnd nacheinander einzeln betrieben werden, da­durch gekennzeichnet, daß von jeder Kühlstelle (11) ein Referenzsignal für die aktuellen Kühlbedingungen an der Kühlstelle (11) zu einer Zentraleinheit (20) übermittelt wird, daß hieraus der jeweilige Kältebedarf ermittelt wird und daß dementsprechend die angeschlossenen Ver­dichter (22) von der Zentraleinheit (20) ein- bzw. abge­schaltet werden.1. A method of operating a refrigeration system, in particular a composite refrigeration system with at least two compressors connected in parallel, which are operated simultaneously or alternately one after the other to cover the respective refrigeration requirement of at least one cooling point provided with sensors, characterized in that each cooling point ( 11) a reference signal for the current cooling conditions at the cooling point (11) is transmitted to a central unit (20), that the respective cooling requirement is determined therefrom and that the connected compressors (22) are accordingly switched on or off by the central unit (20) will. 2. Verfahren zum Betrieb einer Kälteanlage, insbe­sondere einer Verbund-Kälteanlage, mit wenigstens zwei parallel geschalteten Verdichtern, die zur Deckung des jeweiligen Kältebedarfs von wenigstens einer mit einem Sensor versehenen Kühlstelle gleichzeitig gemeinsam oder abwechselnd nacheinander einzeln betrieben werden, da­durch gekennzeichnet, daß von jeder Kühlstelle ein Refe­renzwert für den jeweiligen Kältebedarf der Kühlstelle (11) an einen Stufenschalter (20) zur Ansteuerung der zur Kälteanlage (10) gehörenden Verdichtern (22) über­mittelt wird und daß der Stufenschalter (20) dementspre­chend die Ein- und Abschaltung der angeschlossenen Ver­dichter (22) vornimmt.2. A method of operating a refrigeration system, in particular a composite refrigeration system, with at least two compressors connected in parallel, which are operated simultaneously or alternately in succession to cover the respective refrigeration requirement of at least one cooling point provided with a sensor, characterized in that each of them A reference value for the respective cooling requirement of the cooling point (11) is transmitted to a step switch (20) for controlling the compressors (22) belonging to the cooling system (10) and that the step switch (20) accordingly switches the connected compressors on and off ( 22). 3. Verfahren nach einem der Ansprüche 1 oder 2, da­durch gekennzeichnet, daß als Referenzsignal der Meßwert eines Temperaturfühlers verwendet und mit dem jeweiligen Kältemittel-Saugdruck verglichen wird.3. The method according to any one of claims 1 or 2, characterized in that the measured value of a temperature sensor is used as a reference signal and is compared with the respective refrigerant suction pressure. 4. Verfahren nach einem der Ansprüche 1 bis 3, da­durch gekennzeichnet, daß unter Zugrundelegung der aus dem Referenzsignal der Kühlstelle (11) und aus dem Ver­gleich mit dem Kältemittel-Saugdruck gewonnenen Informa­tion die Ansteuerung von Abschaltventilen (12) in der Zulaufleitung (13) für die Kältemittelversorgung jeder Kühlstelle (11) erfolgt.4. The method according to any one of claims 1 to 3, characterized in that based on the information obtained from the reference signal of the cooling point (11) and from the comparison with the refrigerant suction pressure, the activation of shut-off valves (12) in the feed line (13) for the refrigerant supply to each cooling point (11). 5. Verbund-Kälteanlage mit wenigstens einer mit Sensoren versehenen Kühlstelle, mit wenigstens zwei pa­rallel geschalteten Verdichtern, die zur Deckung des Kältebedarfs in zyklisch abwechselndem oder gemeinsamem Betrieb die zur Deckung des Kältebedarfs erforderliche Kälteleistung bereitstellen, dadurch gekennzeichnet, daß eine Zentraleinheit (20) vorgesehen ist, die sowohl mit den Sensoren (13) jeder Kühlstelle (11) als auch mit den angeschlossenen Verdichtern (22) der Kälteanlage (10) verbunden ist, daß jeder Sensor (13) ein Referenzsignal an die Zentraleinheit (20) gibt, welches die Zentralein­heit (20) zur Ermittlung des Kältebedarfs auswertet und entsprechend dem ermittelten Kältebedarf dem Betrieb der Verdichter (22) steuert.5. Compound refrigeration system with at least one cooling point provided with sensors, with at least two compressors connected in parallel, which provide the cooling capacity required to cover the cooling requirement in cyclically alternating or joint operation, characterized in that a central unit (20) is provided is, which is connected to both the sensors (13) of each cooling point (11) and the connected compressors (22) of the refrigeration system (10), that each sensor (13) gives a reference signal to the central unit (20), which the Central unit (20) evaluates the cooling requirement and controls the operation of the compressors (22) according to the determined cooling requirement. 6. Verbund-Kälteanlage zur Durchführung des Verfah­rens nach einem der Ansprüche 2 bis 4, mit wenigstens einer mit Sensoren versehenen Kühlstelle, mit wenigstens zwei parallel geschalteten Verdichtern, die in zyklisch abwechselndem oder gemeinsamem Betrieb die zur Deckung des Kältebedarfs erforderliche Kälteleistung bereitstel­ len, dadurch gekennzeichnet, daß ein Stufenschalter (20) vorgesehen ist, der sowohl mit den Sensoren (13) jeder Kühlstelle (11) als auch mit den angeschlossenen von Mo­toren (23) angetriebenen Verdichtern (22) der Kälteanla­ge (10) verbunden ist, daß jeder Sensor (13) ein Refe­renzsignal an den Stufenschalter (20) gibt, welches dem jeweiligen Kältebedarf entspricht, und daß der Stufen­schalter dementsprechend die Motoren (23) der Verdichter (22) ein- bzw. ausschaltet.6. Composite refrigeration system for performing the method according to one of claims 2 to 4, with at least one cooling point provided with sensors, with at least two compressors connected in parallel, which provide the cooling capacity required to cover the cooling demand in cyclically alternating or joint operation len, characterized in that a step switch (20) is provided which is connected both to the sensors (13) of each cooling point (11) and to the connected compressors (22) of the refrigeration system (10) driven by motors (23), that each sensor (13) gives a reference signal to the tap changer (20) which corresponds to the respective cooling requirement, and that the tap changer accordingly switches the motors (23) of the compressors (22) on or off. 7. Verbund-Kälteanlage nach Anspruch 5 oder 6, da­durch gekennzeichnet, daß in der Zulaufleitung (13) für das Kältemittel zu jeder Kühlstelle (11) ein fernbetä­tigbares Absperrventil (12) angeordnet ist, welches ferngesteuert den Kältemittelzulauf unterbricht oder freigibt.7. Composite refrigeration system according to claim 5 or 6, characterized in that in the feed line (13) for the refrigerant to each cooling point (11) a remotely operable shut-off valve (12) is arranged, which interrupts or releases the refrigerant supply remotely. 8. Verbund-Kälteanlage nach einem der Ansprüche 5 bis 7, dadurch gekennzeichnet, daß die Signalleitungen (14) zwischen den Sensoren (13) der Kühlstellen (11) und der Zentraleinheit bzw. dem Stufenschalter (20) als Bus­leitungen zur Übertragung von Signalen und Steuerbefeh­len ausgebildet sind.8. Composite refrigeration system according to one of claims 5 to 7, characterized in that the signal lines (14) between the sensors (13) of the cooling points (11) and the central unit or the step switch (20) as bus lines for the transmission of signals and Control commands are formed. 9. Verbund-Kälteanlage nach einem der Ansprüche 5 bis 8, dadurch gekennzeichnet, daß die fernbetätigbaren Absperrventile (12) über die Signalleitung (14, 15) an­steuerbar sind.9. Composite refrigeration system according to one of claims 5 to 8, characterized in that the remotely operated shut-off valves (12) can be controlled via the signal line (14, 15). 10. Verbund-Kälteanlage nach einem der Ansprüche 5 bis 7, dadurch gekennzeichnet, daß den Verdampfern (11a) wenigstens einer Kühlstelle (11) ein Lüftergebläse (14) zugeordnet ist, das über eine Steuerleitung (16) mit dem Kühlstellensensor (13) verbunden ist.10. Composite refrigeration system according to one of claims 5 to 7, characterized in that the evaporators (11a) at least one cooling point (11) is assigned a fan blower (14) which is connected to the cooling point sensor (13) via a control line (16) is.
EP90113997A 1989-07-28 1990-07-21 Method and apparatus for operating a refrigeration system Expired - Lifetime EP0410330B1 (en)

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DE3925090A DE3925090A1 (en) 1989-07-28 1989-07-28 METHOD FOR OPERATING A REFRIGERATION SYSTEM

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Cited By (29)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0543622A2 (en) * 1991-11-18 1993-05-26 Sanyo Electric Co., Limited. Air conditioner and control apparatus therefor
EP0552127A1 (en) * 1992-01-17 1993-07-21 Carrier Corporation Automatic chiller stopping sequence
EP0604359A1 (en) * 1992-12-21 1994-06-29 Carrier Corporation System for controlling heating or cooling capacity in heating or air conditioning systems
EP0660213A2 (en) * 1993-12-22 1995-06-28 Novar Electronics Corporation Method of refrigeration case synchronization for compressor optimization
WO1997032170A1 (en) * 1996-02-28 1997-09-04 Danfoss A/S Refrigeration system
FR2783309A1 (en) * 1998-09-16 2000-03-17 Mc International Procedure for the regulation of the compression rate of refrigerant fluid and the augmentation of evaporation pressure within a refrigeration installation
WO2001035520A1 (en) * 1999-11-12 2001-05-17 Lg Electronics Inc. Device and method for controlling supply of current and static capacitance to compressor
EP1398584A1 (en) * 2002-09-13 2004-03-17 Whirlpool Corporation Method for controlling a multiple cooling compartment refrigerator, and refrigerator using such method
WO2010029027A1 (en) * 2008-09-10 2010-03-18 Ago Ag Energie + Anlagen Heat pump or refrigeration device and method for operating a heat pump or refrigeration device
US8065886B2 (en) 2001-05-03 2011-11-29 Emerson Retail Services, Inc. Refrigeration system energy monitoring and diagnostics
US8302415B2 (en) 2005-03-18 2012-11-06 Danfoss A/S Method for controlling a refrigeration system
US8473106B2 (en) 2009-05-29 2013-06-25 Emerson Climate Technologies Retail Solutions, Inc. System and method for monitoring and evaluating equipment operating parameter modifications
US8495886B2 (en) 2001-05-03 2013-07-30 Emerson Climate Technologies Retail Solutions, Inc. Model-based alarming
US8700444B2 (en) 2002-10-31 2014-04-15 Emerson Retail Services Inc. System for monitoring optimal equipment operating parameters
US8964338B2 (en) 2012-01-11 2015-02-24 Emerson Climate Technologies, Inc. System and method for compressor motor protection
US8974573B2 (en) 2004-08-11 2015-03-10 Emerson Climate Technologies, Inc. Method and apparatus for monitoring a refrigeration-cycle system
US9121407B2 (en) 2004-04-27 2015-09-01 Emerson Climate Technologies, Inc. Compressor diagnostic and protection system and method
US9140728B2 (en) 2007-11-02 2015-09-22 Emerson Climate Technologies, Inc. Compressor sensor module
US9285802B2 (en) 2011-02-28 2016-03-15 Emerson Electric Co. Residential solutions HVAC monitoring and diagnosis
US9310439B2 (en) 2012-09-25 2016-04-12 Emerson Climate Technologies, Inc. Compressor having a control and diagnostic module
US9310094B2 (en) 2007-07-30 2016-04-12 Emerson Climate Technologies, Inc. Portable method and apparatus for monitoring refrigerant-cycle systems
US9551504B2 (en) 2013-03-15 2017-01-24 Emerson Electric Co. HVAC system remote monitoring and diagnosis
US9638436B2 (en) 2013-03-15 2017-05-02 Emerson Electric Co. HVAC system remote monitoring and diagnosis
US9765979B2 (en) 2013-04-05 2017-09-19 Emerson Climate Technologies, Inc. Heat-pump system with refrigerant charge diagnostics
US9803902B2 (en) 2013-03-15 2017-10-31 Emerson Climate Technologies, Inc. System for refrigerant charge verification using two condenser coil temperatures
US9823632B2 (en) 2006-09-07 2017-11-21 Emerson Climate Technologies, Inc. Compressor data module
US9885507B2 (en) 2006-07-19 2018-02-06 Emerson Climate Technologies, Inc. Protection and diagnostic module for a refrigeration system
US10041713B1 (en) 1999-08-20 2018-08-07 Hudson Technologies, Inc. Method and apparatus for measuring and improving efficiency in refrigeration systems
WO2018202496A1 (en) * 2017-05-01 2018-11-08 Danfoss A/S A method for controlling suction pressure based on a most loaded cooling entity

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10118444A1 (en) * 2001-04-12 2002-10-17 Linde Ag Compressor set and method for regulating a compressor set
DE102005009173A1 (en) * 2005-02-17 2006-08-24 Bitzer Kühlmaschinenbau Gmbh refrigeration plant
EP1851959B1 (en) 2005-02-21 2012-04-11 Computer Process Controls, Inc. Enterprise control and monitoring system
US7752854B2 (en) 2005-10-21 2010-07-13 Emerson Retail Services, Inc. Monitoring a condenser in a refrigeration system
US7752853B2 (en) 2005-10-21 2010-07-13 Emerson Retail Services, Inc. Monitoring refrigerant in a refrigeration system
US7665315B2 (en) 2005-10-21 2010-02-23 Emerson Retail Services, Inc. Proofing a refrigeration system operating state

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2274336A (en) * 1936-04-18 1942-02-24 Westinghouse Electric & Mfg Co Control system for refrigerating apparatus
DE842351C (en) * 1948-02-02 1952-06-26 Escher Wyss Maschinenfabrik G System with several compressors
FR2505466A1 (en) * 1981-05-08 1982-11-12 Quiri Cie Sa Usines Refrigeration or air conditioning system - computer controlling use of individual cooling units and compressors
US4384462A (en) * 1980-11-20 1983-05-24 Friedrich Air Conditioning & Refrigeration Co. Multiple compressor refrigeration system and controller thereof
US4487028A (en) * 1983-09-22 1984-12-11 The Trane Company Control for a variable capacity temperature conditioning system

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4231229A (en) * 1979-03-21 1980-11-04 Emhart Industries, Inc. Energy conservation system having improved means for controlling receiver pressure
US4325223A (en) * 1981-03-16 1982-04-20 Cantley Robert J Energy management system for refrigeration systems
DE3220420A1 (en) * 1982-05-29 1983-12-15 Vereinigte Elektrizitätswerke Westfalen AG, 4600 Dortmund Process for the regulation of an electrically controllable expansion valve
US4621505A (en) * 1985-08-01 1986-11-11 Hussmann Corporation Flow-through surge receiver
DE253928T1 (en) * 1986-07-22 1988-10-13 Margaux Controls Inc., San Jose, Calif., Us CONTROL SYSTEM FOR COMPRESSORS OF COOLING SYSTEMS.

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2274336A (en) * 1936-04-18 1942-02-24 Westinghouse Electric & Mfg Co Control system for refrigerating apparatus
DE842351C (en) * 1948-02-02 1952-06-26 Escher Wyss Maschinenfabrik G System with several compressors
US4384462A (en) * 1980-11-20 1983-05-24 Friedrich Air Conditioning & Refrigeration Co. Multiple compressor refrigeration system and controller thereof
FR2505466A1 (en) * 1981-05-08 1982-11-12 Quiri Cie Sa Usines Refrigeration or air conditioning system - computer controlling use of individual cooling units and compressors
US4487028A (en) * 1983-09-22 1984-12-11 The Trane Company Control for a variable capacity temperature conditioning system

Cited By (63)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0543622A2 (en) * 1991-11-18 1993-05-26 Sanyo Electric Co., Limited. Air conditioner and control apparatus therefor
EP0543622A3 (en) * 1991-11-18 1993-11-18 Sanyo Electric Co Air conditioner and control apparatus therefor
EP0552127A1 (en) * 1992-01-17 1993-07-21 Carrier Corporation Automatic chiller stopping sequence
EP0604359A1 (en) * 1992-12-21 1994-06-29 Carrier Corporation System for controlling heating or cooling capacity in heating or air conditioning systems
EP0660213A2 (en) * 1993-12-22 1995-06-28 Novar Electronics Corporation Method of refrigeration case synchronization for compressor optimization
EP0660213A3 (en) * 1993-12-22 1997-06-04 Novar Electronics Corp Method of refrigeration case synchronization for compressor optimization.
WO1997032170A1 (en) * 1996-02-28 1997-09-04 Danfoss A/S Refrigeration system
DE19607474C1 (en) * 1996-02-28 1997-10-30 Danfoss As Refrigeration system
FR2783309A1 (en) * 1998-09-16 2000-03-17 Mc International Procedure for the regulation of the compression rate of refrigerant fluid and the augmentation of evaporation pressure within a refrigeration installation
US10041713B1 (en) 1999-08-20 2018-08-07 Hudson Technologies, Inc. Method and apparatus for measuring and improving efficiency in refrigeration systems
WO2001035520A1 (en) * 1999-11-12 2001-05-17 Lg Electronics Inc. Device and method for controlling supply of current and static capacitance to compressor
US6844698B1 (en) 1999-11-12 2005-01-18 Lg Electronics Inc. Device and method for controlling supply of current and static capacitance to compressor
US8316658B2 (en) 2001-05-03 2012-11-27 Emerson Climate Technologies Retail Solutions, Inc. Refrigeration system energy monitoring and diagnostics
US8065886B2 (en) 2001-05-03 2011-11-29 Emerson Retail Services, Inc. Refrigeration system energy monitoring and diagnostics
US8495886B2 (en) 2001-05-03 2013-07-30 Emerson Climate Technologies Retail Solutions, Inc. Model-based alarming
EP1398584A1 (en) * 2002-09-13 2004-03-17 Whirlpool Corporation Method for controlling a multiple cooling compartment refrigerator, and refrigerator using such method
US8700444B2 (en) 2002-10-31 2014-04-15 Emerson Retail Services Inc. System for monitoring optimal equipment operating parameters
US9121407B2 (en) 2004-04-27 2015-09-01 Emerson Climate Technologies, Inc. Compressor diagnostic and protection system and method
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US9023136B2 (en) 2004-08-11 2015-05-05 Emerson Climate Technologies, Inc. Method and apparatus for monitoring a refrigeration-cycle system
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US8974573B2 (en) 2004-08-11 2015-03-10 Emerson Climate Technologies, Inc. Method and apparatus for monitoring a refrigeration-cycle system
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US10352602B2 (en) 2007-07-30 2019-07-16 Emerson Climate Technologies, Inc. Portable method and apparatus for monitoring refrigerant-cycle systems
US9310094B2 (en) 2007-07-30 2016-04-12 Emerson Climate Technologies, Inc. Portable method and apparatus for monitoring refrigerant-cycle systems
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WO2018202496A1 (en) * 2017-05-01 2018-11-08 Danfoss A/S A method for controlling suction pressure based on a most loaded cooling entity
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ATE91010T1 (en) 1993-07-15
DE3925090A1 (en) 1991-02-07
EP0410330B1 (en) 1993-06-23
DE59001849D1 (en) 1993-07-29

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