EP0152608A2 - Control method for a compound refrigeration plant - Google Patents

Control method for a compound refrigeration plant Download PDF

Info

Publication number
EP0152608A2
EP0152608A2 EP84115860A EP84115860A EP0152608A2 EP 0152608 A2 EP0152608 A2 EP 0152608A2 EP 84115860 A EP84115860 A EP 84115860A EP 84115860 A EP84115860 A EP 84115860A EP 0152608 A2 EP0152608 A2 EP 0152608A2
Authority
EP
European Patent Office
Prior art keywords
fans
volume flow
air volume
temperature
pressure
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP84115860A
Other languages
German (de)
French (fr)
Other versions
EP0152608A3 (en
EP0152608B1 (en
Inventor
Herbert Hansen
Herbert Hartmann
Siegfried Dipl.-Ing. Haaf
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Linde GmbH
Original Assignee
Linde 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
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=6228078&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP0152608(A2) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Linde GmbH filed Critical Linde GmbH
Priority to AT84115860T priority Critical patent/ATE39180T1/en
Publication of EP0152608A2 publication Critical patent/EP0152608A2/en
Publication of EP0152608A3 publication Critical patent/EP0152608A3/en
Application granted granted Critical
Publication of EP0152608B1 publication Critical patent/EP0152608B1/en
Expired legal-status Critical Current

Links

Images

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
    • F25B49/027—Condenser 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2116—Temperatures of a condenser
    • F25B2700/21161—Temperatures of a condenser of the fluid heated by the condenser

Definitions

  • the invention relates to a method for controlling a composite refrigeration system with a plurality of compressors and at least one fan for removing the heat of condensation.
  • a composite refrigeration system essentially consists of several compressors with a common suction line and a common pressure line, a condenser and several evaporators as well as expansion elements which are assigned to the evaporators.
  • the condenser is assigned one or more fans which dissipate the heat generated during the liquefaction of the refrigerant.
  • the operation of the compressors and fans requires a high drive energy. To reduce this, compressors are therefore usually switched off during part-load operation, while the condenser fan or fans continue to be operated at full air output. Although this can achieve a certain reduction in energy consumption, the result of this measure is that the application range of the expansion valves is exceeded. This is because the fans with full air volume flow and switching off individual compressors can cause the condensing pressure to drop too low.
  • the lower limit of the condensing pressure is given by the expansion valves used and the refrigerant.
  • the object of the invention is to optimize the ratio of the cooling capacity of the compressors to the power consumption of the compressors and fans, that is to say to minimize the total power consumption in particular with a predetermined cooling capacity.
  • the area of application of the expansion valves should be maintained compared to the known method and the condensing pressure should be optimized.
  • This object is achieved in that the air volume flow of the fan or fans is controlled depending on the air intake temperature and / or the instantaneous cooling capacity.
  • the invention is based on the idea of switching the optimal number of condensing fans for a predetermined number of compressors in operation. In contrast to the known method, work is no longer carried out with a full air volume flow but with a reduced air volume flow. The saving in energy required to drive the condensing fans is greater than the possible increase in drive energy for the compressors.
  • a predetermined range of the condensing pressure must be maintained in a development of the inventive concept. This range is limited on the one hand by a minimum pressure, which is necessary for the expansion valves to work properly, and on the other hand, by a maximum pressure, which is determined by the application limits of the refrigerant compressors.
  • the range of condensing pressure to be observed also depends on the refrigerant used.
  • the range of common refrigerants such as R22 and R 502 is, for example, between approx. 10 bar and approx. 20 bar.
  • the regulation of the air volume flow according to the invention is particularly provided so that the air volume flow is reduced at a lower air intake temperature.
  • lower air intake temperature i.e. lower outside temperature
  • full air output is first driven in a start-up phase and then the air output is reduced to 2/3 of the original value, for example by reducing the speed of the fans.
  • the energy savings that can be achieved with this are described below.
  • the method according to the invention is applicable to all composite refrigeration systems, e.g. for refrigerated and frozen sales furniture in supermarkets, for slaughterhouses, cold stores or process engineering systems.
  • compressors 1a, 1b, 1c and 1d connected in parallel are connected to a collecting container 7 via a common suction line 4, a plurality of evaporators 5 and expansion valves 6.
  • evaporators 5 and expansion valves 6 For the sake of simplicity, only one evaporator and one expansion valve are shown, but in practice several evaporators and expansion valves are usually connected in parallel.
  • Liquid refrigerant is stored in the collecting container and fed to the evaporators via the expansion valves 6.
  • the refrigerant suction gas in line 4 is then evenly distributed to the individual compressors of the composite system and sucked in by them.
  • Compressed refrigerant vapor is then passed into a common pressure line 8 and led to a condenser 9, in which the vapors are condensed and released in liquid form via line 10 into the collecting container 7.
  • the condenser 9 is equipped with fans 11, 12 which are connected to a control unit 13.
  • the air volume flow circulated by the fans is passed over the condenser and removes the heat of condensation, so that the refrigerant condensation can take place in the condenser.
  • a temperature sensor 14 is connected to the control unit 13 and detects the temperature in the air intake duct of the condenser.
  • the condenser is also assigned a pressure transmitter 20, which is also connected to the control unit 13.
  • a condenser 15 is also provided in line 8, in which the condensation heat can be used for heating domestic water and / or for space heating.
  • Via line 16 for example, water is brought in from the space heating circuit and heated in the condenser 15. If the heat of liquefaction is insufficient, a boiler 17 can also be switched on. The hot water is returned to the heat consumers via a pump 18.
  • a heating controller 19, which is connected to the control unit 13, is assigned to the boiler.
  • Parameters A and B are used to adapt to the respective refrigerant and system-specific conditions.
  • the refrigerating capacity can be adapted to this requirement by raising the evaporating temperature (increasing the evaporating pressure) of the refrigerant. As a result, the pressure difference to be overcome by the compressors is reduced, which leads to a corresponding energy saving.
  • the process according to the invention proceeds somewhat differently with heat recovery.
  • the fans are switched in this case as a function of the heating controller 19, which detects the water supply temperature and whose setpoint is shifted from the outside temperature. If the heat of condensation in the condenser 15 is not sufficient to ensure the necessary heating of the water, the boiler 17 is additionally switched on. If the condensing pressure rises to an adjustable first upper limit value during heat recovery, the boiler 17 continues to be controlled via the heating controller 19. The current air volume flow through the condenser 9 is not changed. However, if the condensing pressure continues to rise and exceeds a second upper limit value, the control of the fans or the air volume flow is taken over directly by the condensing pressure regulator 20. This regulator causes the air volume flow to be increased. If the pressure falls below the first upper pressure limit, the heating regulator takes over ler 19 again the control of the boiler and fans.
  • control device 13 essentially comprises a microcomputer with associated software, data input and data acquisition, data acquisition and conversion and processing, and an output. Furthermore, a 16-digit alphanumeric display and a 10-key data keyboard are arranged on the control device, among other things, for entering setpoints, for querying actual values, outputting messages, and setting a timer.
  • the control unit includes the following options:
  • Each refrigeration consumer is usually assigned a solenoid valve that is switched by a thermostat. If the thermostat of the consumer requests cooling capacity and at least one compressor is in operation, the solenoid valve opens. However, if the pressure on the low pressure side is so low that a pressure switch has responded, all compressors and the solenoid valves are switched off closed and cannot be opened by the thermostats. In this case, it is intended to pulse the solenoid valve, the thermostat of which requires cooling capacity, that is, to switch it on and off alternately. On the one hand, this ensures that the pressure in the suction line rises and, on the other hand, the evaporator is not overfilled with liquid refrigerant, which prevents damage to the compressor due to liquid hammer.

Abstract

1. A method of controlling a compound refrigerating plant comprising a plurality of compressors and at least one fa for the discharge of the heat of liquefication, wherein the air volume flow of the fan or fans is changed in dependence upon the suction air temperature and the refrigerating capacity, characterised in that the suction air temperature Ta and the liquefication pressure Pc are measured and a theoretica value Pc,s of the liquefication pressure is set, which is dpendent upon the air suction temperature.

Description

Die Erfindung betrifft ein Verfahren zur Steuerung einer Verbundkälteanlage mit mehreren Verdichtern und mindestens einem Ventilator für die Abführung der Verflüssigungswärme.The invention relates to a method for controlling a composite refrigeration system with a plurality of compressors and at least one fan for removing the heat of condensation.

Eine Verbundkälteanlage besteht im wesentlichen aus mehreren Verdichtern mit einer gemeinsamen Saugleitung und einer gemeinsamen Druckleitung, einem Verflüssiger und mehreren Verdampfern sowie Expansionsorganen, die den Verdampfern zugeordnet sind. Dem Verflüssiger sind dabei ein oder mehrere Ventilatoren zugeordnet, die die bei der Verflüssigung des Kältemittels entstehende Wärme abführen. Je nach Kältebedarf ist eine bestimmte Anzahl von Verdichtern sowie eine bestimmte Anzahl von Ventilatoren in Betrieb. Der Betrieb der Verdichter und Ventilatoren erfordert eine hohe Antriebsenergie. Um diese zu senken, werden daher üblicherweise bei Teillastbetrieb Verdichter abgeschaltet, während der oder die Ventilatoren der Verflüssiger weiter bei voller Luftleistung betrieben werden. Damit kann zwar eine gewisse Senkung des Energiebedarfs erreicht werden, doch hat diese Maßnahme zur Folge, daß der Anwendungsbereich der Expansionsventile überschritten wird. Dies rührt daher, daß die Ventilatoren bei vollem Luftvolumenstrom und Abschaltung einzelner Verdichter eine zu tiefe Absenkung des Verflüssigungsdrucks bewirken können. Die untere Begrenzung des Verflüssigungsdruckes ist durch die verwendeten Expansionsventile sowie das Kältemittel gegeben.A composite refrigeration system essentially consists of several compressors with a common suction line and a common pressure line, a condenser and several evaporators as well as expansion elements which are assigned to the evaporators. The condenser is assigned one or more fans which dissipate the heat generated during the liquefaction of the refrigerant. Depending on the cooling requirement, a certain number of compressors and a certain number of fans are in operation. The operation of the compressors and fans requires a high drive energy. To reduce this, compressors are therefore usually switched off during part-load operation, while the condenser fan or fans continue to be operated at full air output. Although this can achieve a certain reduction in energy consumption, the result of this measure is that the application range of the expansion valves is exceeded. This is because the fans with full air volume flow and switching off individual compressors can cause the condensing pressure to drop too low. The lower limit of the condensing pressure is given by the expansion valves used and the refrigerant.

Der Erfindung liegt die Aufgabe zugrunde, das Verhältnis von Kälteleistung der Verdichter zur Leistungsaufnahme der Verdichter und Ventilatoren zu optimieren, also insbesondere bei einer vorgegebenen Kälteleistung eine Minimierung der Gesamtleistungsaufnahme zu erreichen. Dabei soll gleichzeitig der Anwendungsbereich der Expansionsventile gegenüber dem bekannten Verfahren beibehalten und der Verflüssigungsdruck optimiert werden.The object of the invention is to optimize the ratio of the cooling capacity of the compressors to the power consumption of the compressors and fans, that is to say to minimize the total power consumption in particular with a predetermined cooling capacity. At the same time, the area of application of the expansion valves should be maintained compared to the known method and the condensing pressure should be optimized.

Diese Aufgabe wird erfindungsgemäß dadurch gelöst, daß der Luftvolumenstrom des oder der Ventilatoren in Abhängigkeit von der Luftansaugtemperatur und/oder der momentanen Kälteleistung geregelt wird.This object is achieved in that the air volume flow of the fan or fans is controlled depending on the air intake temperature and / or the instantaneous cooling capacity.

Die Erfindung basiert auf dem Gedanken, zu einer vorgegebenen Anzahl von in Betrieb befindlichen Verdichtern die optimale Anzahl von Verflüssigungsventilatoren zu schalten. Im Gegensatz zu dem bekannten Verfahren wird nicht mehr mit vollem Luftvolumenstrom sondern mit reduziertem Luftvolumenstrom gearbeitet. Dabei ist die Einsparung der für den Antrieb der Verflüssigungsventilatoren benötigten Energie größer als der eventuelle Anstieg der Antriebsenergie der Verdichter.The invention is based on the idea of switching the optimal number of condensing fans for a predetermined number of compressors in operation. In contrast to the known method, work is no longer carried out with a full air volume flow but with a reduced air volume flow. The saving in energy required to drive the condensing fans is greater than the possible increase in drive energy for the compressors.

Für die Regelung des Luftvolumenstroms bieten sich insbesondere zwei Möglichkeiten an, nämlich Zu- und/oder Abschalten von Ventilatoren oder Änderung der Drehzahl der Ventilatoren. In der Praxis wird dabei wohl in erster Linie die ! zweitgenannte Möglichkeit wahrgenommen werden, da es sich herausgestellt hat, daß beispielsweise zwei mit halbem Luftvolumenstrom betriebene Ventilatoren weniger Antriebsenergie benötigen als ein mit vollem Luftvolumenstrom betriebener Ventilator.There are two options for regulating the air volume flow, namely switching fans on and / or off or changing the speed of the fans. In practice, this will primarily be the! second possibility to be perceived as it is has shown that, for example, two fans operated at half the air volume flow require less drive energy than one fan operated at full air volume flow.

Überdies besteht auch die Möglichkeit, den Luftvolumenstrom durch Verstellung von Drosselklappen zu verändern.In addition, there is also the possibility of changing the air volume flow by adjusting throttle valves.

Bei der Durchführung des erfindungsgemäßen Verfahrens ist in Weiterbildung des Erfindungsgedankens ein vorgegebener Bereich des Verflüssigungsdruckes einzuhalten. Dieser Bereich ist einerseits durch einen minimalen Druck begrenzt, der für ein einwandfreies Arbeiten der Expansionsventile notwendig ist, und andererseits durch einen maximalen Druck, der durch die Anwendungsgrenzen der Kältemittelverdichter bestimmt wird. Der einzuhaltende Bereich des Verflüssigungsdruckes hängt überdies von dem jeweils verwendeten Kältemittel ab. Bei den gebräuchlichen Kältemitteln wie R22 und R 502 liegt der Bereich beispielsweise zwischen ca. 10 bar und ca. 20 bar.In carrying out the method according to the invention, a predetermined range of the condensing pressure must be maintained in a development of the inventive concept. This range is limited on the one hand by a minimum pressure, which is necessary for the expansion valves to work properly, and on the other hand, by a maximum pressure, which is determined by the application limits of the refrigerant compressors. The range of condensing pressure to be observed also depends on the refrigerant used. The range of common refrigerants such as R22 and R 502 is, for example, between approx. 10 bar and approx. 20 bar.

Die erfindungsgemäße Regelung des Luftvolumenstroms ist insbesondere so vorgesehen, daß bei geringerer Luftansaugtemperatur der Luftvolumenstrom verringert wird. Selbstverständlich beinhaltet dies, daß bei erhöhter Luftansaugtemperatur der Luftvolumenstrom vergrößert wird. Bei z.B. geringerer Luftansaugtemperatur, d.h. geringerer Außentemperatur, wird in einer Anfahrphase zunächst volle Luftleistung gefahren und dann die Luftleistung beispielsweise durch Reduzierung der Drehzahl der Ventilatoren auf 2/3 des ursprünglichen Wertes reduziert. Die damit erzielbaren Einsparungen an Energieaufwand werden weiter unten beschrieben.The regulation of the air volume flow according to the invention is particularly provided so that the air volume flow is reduced at a lower air intake temperature. Of course, this means that the air volume flow is increased when the air intake temperature is increased. With e.g. lower air intake temperature, i.e. lower outside temperature, full air output is first driven in a start-up phase and then the air output is reduced to 2/3 of the original value, for example by reducing the speed of the fans. The energy savings that can be achieved with this are described below.

Bei dem bislang beschriebenen Verfahren findet in Verbindung mit der Verbundkälteanlage keine Wärmerückgewinnung statt. In Weiterbildung des erfindungsgemäßen Verfahrens ist jedoch auch die Steuerung einer Verbundkälteanlage vorgesehen, bei der eine zusätzliche Wärmerückgewinnung für Raumheizung und Brauchwassererwärmung vorgesehen ist. In diesem Falle wird erfindungsgemäß der Luftvolumenstrom zusätzlich in Abhängigkeit von der Warmwasservorlauftemperatur und/oder der Raumtemperatur geregelt.The method described so far takes place in Verbin heat recovery does not take place with the composite refrigeration system. In a further development of the method according to the invention, however, the control of a composite refrigeration system is also provided, in which an additional heat recovery is provided for space heating and domestic water heating. In this case, the air volume flow is additionally regulated according to the hot water flow temperature and / or the room temperature.

Zur Energieeinsparung durch Abwärmenutzung können entsprechend den örtlichen Gegebenheiten und vorhandener Kälteanlage überdies die folgenden Wärmerückgewinnungssysteme installiert werden:

  • - Vorerhitzer in Lüftungsgeräten, die von dem warmen Druckgas durchströmt werden und im Heizbetrieb als Verflüssiger arbeiten.
  • - Den luftgekühlten Verflüssigern vorgeschaltete wassergekühlte Apparate, die ihre Wärme an die Vorheizregister von Lüftungsgeräten abgeben.
  • - Wärmepumpen, die bei Verbundanlagen durch einen Verdampfer-Verflüssiger die Verflüssigungswärme aufnehmen und sie mit einem hohen Temperaturniveau, mittels Wasser als Trägermedium, direkt in den Heizwasserrücklauf der Heizanlage einspeisen (Vorlauftemperatur ca. 60°C) .
To save energy by using waste heat, the following heat recovery systems can also be installed depending on the local conditions and existing cooling system:
  • - Preheater in ventilation units through which the warm compressed gas flows and which work as a condenser in heating mode.
  • - Water-cooled devices connected upstream of the air-cooled condensers, which emit their heat to the preheating register of ventilation units.
  • - Heat pumps that absorb the heat of condensation in composite systems through an evaporator-condenser and feed them directly into the heating water return of the heating system at a high temperature level using water as the carrier medium (flow temperature approx. 60 ° C).

Das erfindungsgemäße Verfahren ist anwendbar auf alle Verbundkälteanlagen, so z.B. für gekühlte und tiefgekühlte Verkaufsmöbel in Supermärkten, für Schlachthöfe, Kühlhäuser oder verfahrenstechnische Anlagen.The method according to the invention is applicable to all composite refrigeration systems, e.g. for refrigerated and frozen sales furniture in supermarkets, for slaughterhouses, cold stores or process engineering systems.

Die Erfindung sei im folgenden anhand eines in Figur 1 schematisch dargestellten Ausführungsbeispiels näher erläutert.The invention is described below on the basis of one in FIG schematically illustrated embodiment explained in more detail.

In dem Ausführungsbeispiel sind vier parallelgeschaltete Verdichter 1a, 1b, 1c und 1d über eine gemeinsame Saugleitung 4,mehrere Verdampfer 5 sowie Expansionsventile 6 an einem Sammelbehälter 7 angeschlossen. Der Einfachheit halber ist nur ein Verdampfer und ein Expansionsventil dargestellt, doch sind in der Praxis meist mehrere Verdampfer und Expansionsventile parallel geschaltet. In dem Sammelbehälter wird flüssiges Kältemittel eingespeichert und über die Expansionsventile 6 den Verdampfern zugeleitet. Das Kältemittelsauggas in Leitung 4 wird sodann gleichmäßig auf die einzelnen Verdichter der Verbundanlage verteilt und von diesen angesaugt. Verdichteter Kältemitteldampf wird sodann in eine gemeinsame Druckleitung 8 geleitet und zu einem Verflüssiger 9 geführt, in dem die Dämpfe kondensiert und in flüssiger Form über Leitung 10 in den Sammelbehälter 7 abgegeben werden.In the exemplary embodiment, four compressors 1a, 1b, 1c and 1d connected in parallel are connected to a collecting container 7 via a common suction line 4, a plurality of evaporators 5 and expansion valves 6. For the sake of simplicity, only one evaporator and one expansion valve are shown, but in practice several evaporators and expansion valves are usually connected in parallel. Liquid refrigerant is stored in the collecting container and fed to the evaporators via the expansion valves 6. The refrigerant suction gas in line 4 is then evenly distributed to the individual compressors of the composite system and sucked in by them. Compressed refrigerant vapor is then passed into a common pressure line 8 and led to a condenser 9, in which the vapors are condensed and released in liquid form via line 10 into the collecting container 7.

Der Verflüssiger 9 ist mit Ventilatoren 11, 12 ausgestattet, die mit einem Steuergerät 13 verbunden sind. Der von den Ventilatoren umgewälzte Luftvolumenstrom wird über den Verflüssiger geleitet und führt dabei die Verflüssigungswärme ab, so daß in dem Verflüssiger die Kältemittelkondensation stattfinden kann. An das Steuergerät 13 ist ein Temperaturfühler 14 angeschlossen, der die Temperatur im Luftansaugkanal des Verflüssigers erfaßt. Dem Verflüssiger ist außerdem ein Drucktransmitter 20 zugeordnet, der ebenfalls an das Steuergerät 13 angeschlossen ist.The condenser 9 is equipped with fans 11, 12 which are connected to a control unit 13. The air volume flow circulated by the fans is passed over the condenser and removes the heat of condensation, so that the refrigerant condensation can take place in the condenser. A temperature sensor 14 is connected to the control unit 13 and detects the temperature in the air intake duct of the condenser. The condenser is also assigned a pressure transmitter 20, which is also connected to the control unit 13.

Zur Wärmerückgewinnung ist in Leitung 8 überdies ein Verflüssiger 15 vorgesehen, in dem die Verflüssigungswärme zur Brauchwasser-Erwärmung und/oder zur Raumheizung genutzt werden kann. über Leitung 16 wird beispielsweise Wasser aus dem Raumheizungskreislauf herangeführt und im Verflüssiger 15 angewärmt. Reicht die Verflüssigungswärme nicht aus, so kann zusätzlich ein Heizkessel 17 eingeschaltet werden. Über eine Pumpe 18 wird das Warmwasser zu den Wärmeverbrauchern zurückgeführt. Dem Heizkessel ist ein Heizungsregler 19 zugeordnet, der mit dem Steuergerät 13 verbunden ist.For heat recovery, a condenser 15 is also provided in line 8, in which the condensation heat can be used for heating domestic water and / or for space heating. Via line 16, for example, water is brought in from the space heating circuit and heated in the condenser 15. If the heat of liquefaction is insufficient, a boiler 17 can also be switched on. The hot water is returned to the heat consumers via a pump 18. A heating controller 19, which is connected to the control unit 13, is assigned to the boiler.

Die mit dem Verfahren gemäß dem vorstehend geschilderten Ausführungsbeispiel erzielbare Energieeinsparung ist aus den Tabellen Punkt 2a) bis d) der Anlage zu entnehmen. Das Verfahren wird zunächst ohne Wärmerückgewinnung beschrieben, so daß der Verflüssiger 15 mit dem daran angeschlossenen Kreislauf unbeachtet bleibt. Der Temperaturfühler 14 erfaßt die Temperatur der Luft im Ansaugkanal des Verflüssigers und verschiebt den Sollwert p . Die Berechnung der Sollwertverschiebung erfolgt im Steuergerät 13 nach der Formel

Figure imgb0001

  • A = Parameter in bar/°C
  • B = Parameter in bar
  • νA = Außentemperatur in °C
  • p = Verflüssigungstank in bar.
The energy savings which can be achieved with the method according to the exemplary embodiment described above can be seen from the tables in points 2a) to d) of the system. The process is first described without heat recovery, so that the condenser 15 with the circuit connected to it is ignored. The temperature sensor 14 detects the temperature of the air in the intake duct of the condenser and shifts the setpoint p. The setpoint shift is calculated in control unit 13 using the formula
Figure imgb0001
  • A = parameter in bar / ° C
  • B = parameter in bar
  • νA = outside temperature in ° C
  • p = liquefaction tank in bar.

Die Parameter A und B dienen der Anpassung an das jeweilige Kältemittel und an anlagenspezifische Gegebenheiten.Parameters A and B are used to adapt to the respective refrigerant and system-specific conditions.

Bei sinkender Umgebungstemperatur sinkt der Kältebedarf der Kälteverbraucher. Eine Anpassung der Kälteleistung an diesen Bedarf kann durch Anheben der Verdampfungstemperatur (Erhöhen des Verdampfungsdruckes) des Kältemittels geschehen. Dadurch wird die von den Verdichtern zu überwindende Druckdifferenz verringert, was zu einer entsprechenden Energieeinsparung führt.When the ambient temperature drops, the cooling consumers' cooling requirements decrease. The refrigerating capacity can be adapted to this requirement by raising the evaporating temperature (increasing the evaporating pressure) of the refrigerant. As a result, the pressure difference to be overcome by the compressors is reduced, which leads to a corresponding energy saving.

Mit Wärmerückgewinnung verläuft das erfindungsgemäße Verfahren etwas anders. Die Schaltung der Ventilatoren erfolgt in diesem Falle in Abhängigkeit des Heizungsreglers 19, der die Wasservorlauftemperatur erfaßt und dessen Sollwert von der Außentemperatur geschoben wird. Reicht dabei die Verflüssigungswärme im Verflüssiger 15 nicht aus, um die erforderliche Anwärmung des Wassers zu gewährleisten, so wird zusätzlich der.Heizkessel 17 eingeschaltet. Steigt während der Wärmerückgewinnung der Verflüssigungsdruck auf einen einstellbaren ersten oberen Grenzwert an, wird der Heizkessel 17 weiterhin über den Heizungsregler 19 gesteuert. Dabei wird der momentane Luftvolumenstrom durch den Verflüssiger 9 nicht verändert. Steigt der Verflüssigungsdruck aber weiter an und überschreitet einen zweiten oberen Grenzwert, so wird die Steuerung der Ventilatoren bzw. des Luftvolumenstroms direkt von dem Verflüssigungsdruckregler 20 übernommen. Dieser Regler veranlaßt, daß der Luftvolumenstrom erhöht wird. Beim Unterschreiten des ersten oberen Druckgrenzwertes übernimmt der Heizungsregler 19 wieder die Steuerung des Heizkessels und der Ventilatoren.The process according to the invention proceeds somewhat differently with heat recovery. The fans are switched in this case as a function of the heating controller 19, which detects the water supply temperature and whose setpoint is shifted from the outside temperature. If the heat of condensation in the condenser 15 is not sufficient to ensure the necessary heating of the water, the boiler 17 is additionally switched on. If the condensing pressure rises to an adjustable first upper limit value during heat recovery, the boiler 17 continues to be controlled via the heating controller 19. The current air volume flow through the condenser 9 is not changed. However, if the condensing pressure continues to rise and exceeds a second upper limit value, the control of the fans or the air volume flow is taken over directly by the condensing pressure regulator 20. This regulator causes the air volume flow to be increased. If the pressure falls below the first upper pressure limit, the heating regulator takes over ler 19 again the control of the boiler and fans.

Das Steuergerät 13 umfaßt zur Durchführung des erfindungsgemäßen Verfahrens im wesentlichen einen Mikrocomputer mit zugehöriger Software, eine Dateneingabe und -erfassung, Meßwerterfassung und -umwandlung sowie -verarbeitung und eine Ausgabe. Ferner sind auf dem Steuergerät eine bevorzugt 16-stellige alphanumerische Anzeige sowie eine 10er Datentastatur unter anderem zur Eingabe von Sollwerten, zur Abfrage von Istwerten, Ausgabe von Meldungen, Einstellen einer Zeituhr angeordnet.To carry out the method according to the invention, the control device 13 essentially comprises a microcomputer with associated software, data input and data acquisition, data acquisition and conversion and processing, and an output. Furthermore, a 16-digit alphanumeric display and a 10-key data keyboard are arranged on the control device, among other things, for entering setpoints, for querying actual values, outputting messages, and setting a timer.

Mit diesem Steuergerät ist eine optimale Anpassung der erzeugten Kälteleistung an den jeweiligen Kältebedarf der Verbraucher möglich, wobei es prinzipielles Ziel ist, den Verflüssigungsdruck so niedrig wie möglich zu halten, um den Energiebedarf zu minimieren. Dieses trifft sowohl für eine Verbundkälteanlage mit als auch ohne Wärmerückgewinnung zu.With this control unit, an optimal adaptation of the generated cooling capacity to the respective cooling requirement of the consumer is possible, whereby the basic goal is to keep the condensing pressure as low as possible in order to minimize the energy requirement. This applies both to a composite refrigeration system with and without heat recovery.

Das Steuergerät beinhaltet die folgenden Möglichkeiten:The control unit includes the following options:

  • 1. Integrierende Analog-Meßwerterfassung1. Integrating analog measured value acquisition
  • 2. Quarzgesteuerte Kalenderuhr2. Quartz controlled calendar clock
  • 3. Datensicherung bei Netzausfall bis zu 14 Tagen3. Data backup in the event of a power failure for up to 14 days
  • 4. Ausgaben der aktualisierten Istwerte während des Betriebes auf der alphanumerischen Anzeige.4. Output of the updated actual values during operation on the alphanumeric display.
  • 5. Meßwertüberwachung5. Measured value monitoring
  • 6. Eingang für Heizungsregler6. Input for heating controller
  • 7. Autmomatische Umschaltung von Kühl- in den Wärmerückgewinnungsbetrieb und umgekehrt.7. Automatic switchover from cooling to heat recovery mode and vice versa.
  • 8. Steuerung von Kältemittelverdichtern und zusätzlich eine Leistungsstufe pro Verdichter in Abhängigkeit vom Niederdruck.8. Control of refrigerant compressors and an additional power level per compressor depending on the low pressure.
  • 9. Anzahl der Kältemittelverdichter und Leistungsstufen wählbar.9. Number of refrigerant compressors and power levels selectable.
  • 10. Regelung und Überwachung der öltemperatur10. Regulation and monitoring of the oil temperature
  • 11. Steuerung der Kältemittelverdichterzusatzventilatoren in Abhängigkeit der Druckrohrtemperatur.11. Control of the additional refrigerant compressor fans depending on the pressure pipe temperature.
  • 12. Überwachung der Temperatur in der Druckleitung.12. Monitoring the temperature in the pressure line.
  • 13. Überwachung der Wicklungstemperatur der Antriebsmotoren der Kältemittelverdichter.13. Monitoring the winding temperature of the drive motors of the refrigerant compressors.
  • 14. öldrucküberwachung der Kältemittelverdichter14. Oil pressure monitoring of the refrigerant compressors
  • 15. Steuerung der Verflüssigerventilatoren im Kühlbetrieb sowie eine zusätzliche Schaltstufe für einen weiteren Wärmeerzeuger bei der Wärmerückgewinnung.15. Control of the condenser fans in cooling mode and an additional switching stage for a further heat generator in the heat recovery.
  • 16. Anzahl der Stufen der Verflüssigerventilatoren ist wählbar.16. The number of stages of the condenser fans can be selected.
  • 17.Keilrianenüberwachung bei Betrieb der Verflüssigervenilatoren mit Keilriemen.17. V-belt monitoring when operating the condenser fans with V-belts.
  • 18. Drucküberwachung in der Anlage18. Pressure monitoring in the system
  • 19. Sollwertschiebung von Verflüssigungs-'und Verdampfungsdruck.19. Setpoint shift of condensing and evaporation pressure.
  • 20. Zwei Eingänge für Lastabwurf.20. Two inputs for load shedding.
  • 21. Störungen werden mit Datum und Uhrzeit gespeichert.21. Faults are saved with the date and time.
  • 22. Automatische Grundlastumschaltung mit wählbarer Umschaltzeit.22. Automatic base load switchover with selectable switchover time.
  • 23. Alle Daten können auf einem Drucker ausgegeben werden (immer mit Datum und Uhrzeit versehen)23. All data can be output on a printer (always provided with the date and time)
  • 24. Saugdruckanhebung24. Suction pressure increase
  • 25. Pulsen25. Pulse

Jedem Kälteverbraucher ist üblicherweise ein Magnetventil zugeordnet, das von einem Thermostaten geschaltet wird. Falls der Thermostat des Verbrauchers Kälteleistung anfordert, und mindestens ein Verdichter in Betrieb ist, öffnet das Magnetventil. Ist nun aber der Druck auf der Niederdruckseite so tief, daß ein Druckwächter angesprochen hat, sind alle Verdichter weggeschaltet und die Magnetventile geschlossen und durch die Thermostate nicht zu öffnen. Für diesen Fall ist vorgesehen, das Magnetventil, dessen Thermostat Kälteleistung anfordert, zu pulsen, also im Wechsel ein- und auszuschalten. Damit wird einerseits erreicht, daß der Druck in der Saugleitung ansteigt und andererseits wird eine überfüllung der Verdampfer mit flüssigem Kältemittel verhindert, wodurch Verdichterschäden durch Flüssigkeitsschläge vermieden werden.Each refrigeration consumer is usually assigned a solenoid valve that is switched by a thermostat. If the thermostat of the consumer requests cooling capacity and at least one compressor is in operation, the solenoid valve opens. However, if the pressure on the low pressure side is so low that a pressure switch has responded, all compressors and the solenoid valves are switched off closed and cannot be opened by the thermostats. In this case, it is intended to pulse the solenoid valve, the thermostat of which requires cooling capacity, that is, to switch it on and off alternately. On the one hand, this ensures that the pressure in the suction line rises and, on the other hand, the evaporator is not overfilled with liquid refrigerant, which prevents damage to the compressor due to liquid hammer.

Leistungsbedarfswerte von Verbundkälteanlagen mit 4 KältemittelverdichternPerformance requirements of composite refrigeration systems with 4 refrigerant compressors I. Lufteintrittstemperatur in Verflüssiger entsprechend Auslegungsbedingungen.I. Air inlet temperature in the condenser according to the design conditions.

  • a) Die Leistungswerte einer typischen Verbundkälteanlage für Supermärkte bei Auslegungsbedingungen ergeben sich wie folgt (ohne Kälteverbraucher wie Kühlmöbel, Kühlräume etc).:
    Figure imgb0002
    a) The performance values of a typical composite refrigeration system for supermarkets with design conditions are as follows (without cold consumers such as refrigeration units, cold rooms, etc.):
    Figure imgb0002
  • b) Die Leistungswerte dieser Verbundkälteanlage bei ca. 50% Kältebedarf (2 Kältemittelverdichter in Betrieb) und voller Leistung der Verflüssigungsventilatoren betragen:
    Figure imgb0003
    b) The performance values of this composite refrigeration system with approx. 50% cooling requirement (2 refrigerant compressors in operation) and full performance of the condensing fans are:
    Figure imgb0003
  • c) Bei gleichen Bedingungen wie Punkt 1b) aber Reduzierung der Drehzahl der Verflüssigerventilatoren auf 2/3 der Nenndrehzahl (Reduzierung des Luftvolumenstromes auf ca. 2/3) ergeben sich nachstehende Werte:
    Figure imgb0004
    c) Under the same conditions as point 1b) but reducing the speed of the condenser fans to 2/3 of the nominal speed (reducing the air volume flow to approx. 2/3), the following values result:
    Figure imgb0004

2. Lufteintrittstemperatur in Verflüssiger um 10 K abgesenkt.2. Air inlet temperature in condenser reduced by 10 K.

  • ) a) Bei den sonstigen Bedingungen wie Punkt 1a ergeben sich folgende Werte:
    Figure imgb0005
    ) a) With the other conditions like point 1a the following values result:
    Figure imgb0005
  • b) Bei den sonstigen Bedingungen wie Punkt 2a) aber Reduzierung der Drehzahl der Verflüssigerventilatoren auf 2/3 der Nenndrehzahl ergeben sich für
    Figure imgb0006
    b) With the other conditions like point 2a) but reduction of the speed of the condenser fans to 2/3 of the nominal speed result for
    Figure imgb0006
  • c) Bedingungen wie Punkt 2a) jedoch mit 50% Kältebedarf (2 Kältemittelverdichter in Betrieb) und volle Drehzahl der Verflüssigerventilatoren.
    Figure imgb0007
    c) Conditions as point 2a) but with 50% cooling requirement (2 refrigerant compressors in operation) and full speed of the condenser fans.
    Figure imgb0007
  • d) Bedingungen wie Punkt 2c) jedoch mit Reduzierung der Verflüssigerventilatoren auf 2/3 ihrer Nenndrehzahl.
    Figure imgb0008
    d) Conditions like point 2c) but with reduction of the condenser fans to 2/3 of their nominal speed.
    Figure imgb0008

Claims (6)

1. Verfahren zur Steuerung einer Verbundkälteanlage mit mehreren Verdichtern und mindestens einem Ventilator für die Abführung der Verflüssigungswärme, dadurch gekennzeichnet, daß der Luftvolumenstrom des oder der Ventilatoren in Abhängigkeit von der Luftansaugtemperatur und/oder der momentanen Kälteleistung geregelt wird.1. A method for controlling a composite refrigeration system with several compressors and at least one fan for the dissipation of the condensing heat, characterized in that the air volume flow of the fan or fans is regulated depending on the air intake temperature and / or the instantaneous cooling capacity. 2. Verfahren nach Anspruch 1, dadurch gekennzeichnet, daß der Luftvolumenstrom durch Zu- und/oder Abschalten von Ventilatoren geregelt wird.2. The method according to claim 1, characterized in that the air volume flow is regulated by switching fans on and / or off. 3. Verfahren nach Anspruch 1, dadurch gekennzeichnet, daß der Luftvolumenstrom durch Änderung der Drehzahl der Ventilatoren geregelt wird.3. The method according to claim 1, characterized in that the air volume flow is regulated by changing the speed of the fans. 4. Verfahren nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, daß ein vorgegebener Bereich des Verflüssigungsdruckes eingehalten wird.4. The method according to any one of claims 1 to 3, characterized in that a predetermined range of the condensing pressure is maintained. 5. Verfahren nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, daß bei geringerer Luftansaugtemperatur der Luftvolumenstrom verringert wird.5. The method according to any one of claims 1 to 4, characterized in that at a lower air intake temperature the air volume flow is reduced. 6. Verfahren zur Steuerung einer Verbundkälteanlage nach Anspruch 1, bei der zusätzlich eine Wärmerückgewinnung für Raumheizung und Brauchwasser-Erwärmung vorgesehen ist, dadurch gekennzeichnet, daß der Luftvolumenstrom zusätzlich in Abhängigkeit von der Warmwasservorlauftemperatur und/oder der Raumtemperatur geregelt wird.6. A method of controlling a composite refrigeration system according to claim 1, in which heat recovery for space heating and hot water heating is additionally provided, characterized in that the air volume flow is additionally controlled as a function of the hot water supply temperature and / or the room temperature.
EP84115860A 1984-02-17 1984-12-19 Control method for a compound refrigeration plant Expired EP0152608B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT84115860T ATE39180T1 (en) 1984-02-17 1984-12-19 PROCEDURE FOR CONTROLLING A COMPOUND REFRIGERATION SYSTEM.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19843405810 DE3405810A1 (en) 1984-02-17 1984-02-17 METHOD FOR CONTROLLING A COMPONENT REFRIGERATION SYSTEM
DE3405810 1984-02-17

Publications (3)

Publication Number Publication Date
EP0152608A2 true EP0152608A2 (en) 1985-08-28
EP0152608A3 EP0152608A3 (en) 1986-04-09
EP0152608B1 EP0152608B1 (en) 1988-12-07

Family

ID=6228078

Family Applications (1)

Application Number Title Priority Date Filing Date
EP84115860A Expired EP0152608B1 (en) 1984-02-17 1984-12-19 Control method for a compound refrigeration plant

Country Status (3)

Country Link
EP (1) EP0152608B1 (en)
AT (1) ATE39180T1 (en)
DE (2) DE3405810A1 (en)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0239837A2 (en) * 1986-03-20 1987-10-07 BROWN, BOVERI - YORK Kälte- und Klimatechnik Method of recuperating the condensation heat of a refrigeration system, and refrigeration system for carrying out the method
EP0355180A2 (en) * 1988-08-17 1990-02-28 Nippon Telegraph And Telephone Corporation Cooling apparatus and control method
FR2636723A1 (en) * 1988-09-22 1990-03-23 Danfoss As
DE4008877A1 (en) * 1988-09-22 1991-10-02 Danfoss As Refrigerator with expansion value and evaporator - are connected in series circuit and with expansion value control unit for maintaining desired temp. in work space
FR2748799A1 (en) * 1996-05-17 1997-11-21 Mc International Regulation of refrigeration condenser for energy economy
WO2002086396A1 (en) * 2001-04-20 2002-10-31 York International Corporation Method and apparatus for controlling the removal of heat from the condenser in a refrigeration system
CN107356007A (en) * 2016-06-13 2017-11-17 北京库蓝科技有限公司 A kind of three warm varying capacity of Auto-cascade cycle exports refrigeration system

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10021610A1 (en) * 2000-05-04 2001-11-08 Linde Ag Method for operating a (composite) refrigeration system
DE102010003915B4 (en) * 2010-04-13 2015-11-19 WESKA Kälteanlagen GmbH Refrigeration system with heat recovery and method for operating the refrigeration system

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3138941A (en) * 1963-06-05 1964-06-30 Westinghouse Electric Corp Controls for refrigeration systems having air cooled condensers
US3390538A (en) * 1967-06-23 1968-07-02 Trane Co Refrigeration system
US3460354A (en) * 1968-03-07 1969-08-12 Dunham Bush Inc Refrigeration system and method
US3739596A (en) * 1971-11-10 1973-06-19 Gen Electric Refrigeration system including head pressure control means
US4134274A (en) * 1978-01-26 1979-01-16 The Trane Company System for producing refrigeration and a heated liquid and control therefor
DE2748252A1 (en) * 1977-10-27 1979-05-03 Siemens Ag Heat pump condensation pressure regulation system - is changed to dependence on washing water temp. as necessary
DE3025439A1 (en) * 1979-07-13 1981-05-27 Tyler Refrigeration Corp., Niles, Mich. ENERGY-SAVING COOLING SYSTEM
GB2067275A (en) * 1979-11-22 1981-07-22 Trendpam Eng Ltd Combined refrigeration and heating system

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3138941A (en) * 1963-06-05 1964-06-30 Westinghouse Electric Corp Controls for refrigeration systems having air cooled condensers
US3390538A (en) * 1967-06-23 1968-07-02 Trane Co Refrigeration system
US3460354A (en) * 1968-03-07 1969-08-12 Dunham Bush Inc Refrigeration system and method
US3739596A (en) * 1971-11-10 1973-06-19 Gen Electric Refrigeration system including head pressure control means
DE2748252A1 (en) * 1977-10-27 1979-05-03 Siemens Ag Heat pump condensation pressure regulation system - is changed to dependence on washing water temp. as necessary
US4134274A (en) * 1978-01-26 1979-01-16 The Trane Company System for producing refrigeration and a heated liquid and control therefor
DE3025439A1 (en) * 1979-07-13 1981-05-27 Tyler Refrigeration Corp., Niles, Mich. ENERGY-SAVING COOLING SYSTEM
GB2067275A (en) * 1979-11-22 1981-07-22 Trendpam Eng Ltd Combined refrigeration and heating system

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0239837A2 (en) * 1986-03-20 1987-10-07 BROWN, BOVERI - YORK Kälte- und Klimatechnik Method of recuperating the condensation heat of a refrigeration system, and refrigeration system for carrying out the method
EP0239837A3 (en) * 1986-03-20 1990-03-28 BROWN, BOVERI - YORK Kälte- und Klimatechnik Method of recuperating the condensation heat of a refrigeration system, and refrigeration system for carrying out the method
EP0355180A2 (en) * 1988-08-17 1990-02-28 Nippon Telegraph And Telephone Corporation Cooling apparatus and control method
EP0355180A3 (en) * 1988-08-17 1990-03-28 Nippon Telegraph And Telephone Corporation Cooling apparatus and control method
FR2636723A1 (en) * 1988-09-22 1990-03-23 Danfoss As
DE4008877A1 (en) * 1988-09-22 1991-10-02 Danfoss As Refrigerator with expansion value and evaporator - are connected in series circuit and with expansion value control unit for maintaining desired temp. in work space
FR2748799A1 (en) * 1996-05-17 1997-11-21 Mc International Regulation of refrigeration condenser for energy economy
WO2002086396A1 (en) * 2001-04-20 2002-10-31 York International Corporation Method and apparatus for controlling the removal of heat from the condenser in a refrigeration system
US6530236B2 (en) 2001-04-20 2003-03-11 York International Corporation Method and apparatus for controlling the removal of heat from the condenser in a refrigeration system
EP1811249A1 (en) * 2001-04-20 2007-07-25 York International Corporation Method and apparatus for controlling the removal of heat from the condenser in a refrigeration system
CN107356007A (en) * 2016-06-13 2017-11-17 北京库蓝科技有限公司 A kind of three warm varying capacity of Auto-cascade cycle exports refrigeration system
CN107356007B (en) * 2016-06-13 2024-04-09 北京库蓝科技有限公司 Self-overlapping three-temperature variable capacity output refrigerating system

Also Published As

Publication number Publication date
ATE39180T1 (en) 1988-12-15
DE3475564D1 (en) 1989-01-12
DE3405810A1 (en) 1985-08-22
EP0152608A3 (en) 1986-04-09
EP0152608B1 (en) 1988-12-07

Similar Documents

Publication Publication Date Title
DE60123719T2 (en) Method for controlling a variable speed drive for multiple cooling units
DE60222720T2 (en) Cooling system with variable speed drive
DE3517222C2 (en)
DE10231877B4 (en) Konstanttemperaturflüssigkeitszirkuliervorrichtung
DE69832745T2 (en) Refrigerant pressure control for heat pump operating in heating mode
DE3517221C2 (en)
DE3517216A1 (en) METHOD FOR OPERATING A STEAM COMPRESSION REFRIGERATION SYSTEM AND ARRANGEMENT FOR CONTROLLING THE SAME
DE3716393A1 (en) REFRIGERATION PLANT
EP0410330A2 (en) Method and apparatus for operating a refrigeration system
DE3517217A1 (en) OPERATING METHOD AND CONTROL ARRANGEMENT FOR A REFRIGERATION SYSTEM
DE3517218A1 (en) METHOD FOR OPERATING A STEAM COMPRESSION REFRIGERATION SYSTEM AND ARRANGEMENT FOR CONTROLLING THE SAME
CH678453A5 (en)
EP2199706B1 (en) A switching device air conditioner and operation method thereof
DE60123321T2 (en) Compressor system with a controlled cooling fan
DE102013114374B4 (en) Method for controlling the speed of a variable speed compressor
DE3907859C2 (en) Air-cooled refrigeration unit with a coolant circuit
DE3517219A1 (en) OPERATING METHOD AND CONTROL ARRANGEMENT FOR A REFRIGERATION SYSTEM
DE3500800A1 (en) TWO-STAGE REFRIGERANT SYSTEM
EP0152608B1 (en) Control method for a compound refrigeration plant
DE19937949C2 (en) Device and method for heating and / or cooling a vehicle interior
EP3564601A1 (en) Predictive control of a heat pump
DE4119557A1 (en) DEVICE WITH COOLING CIRCUIT
DE3823559C1 (en)
DE3415000C2 (en)
DE102019119751B3 (en) Method for operating a refrigeration cycle of a motor vehicle and refrigeration cycle

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Designated state(s): AT BE CH DE FR GB IT LI LU NL SE

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Kind code of ref document: A3

Designated state(s): AT BE CH DE FR GB IT LI LU NL SE

17P Request for examination filed

Effective date: 19860326

17Q First examination report despatched

Effective date: 19870313

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT BE CH DE FR GB IT LI LU NL SE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Effective date: 19881207

Ref country code: NL

Effective date: 19881207

Ref country code: IT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT;WARNING: LAPSES OF ITALIAN PATENTS WITH EFFECTIVE DATE BEFORE 2007 MAY HAVE OCCURRED AT ANY TIME BEFORE 2007. THE CORRECT EFFECTIVE DATE MAY BE DIFFERENT FROM THE ONE RECORDED.

Effective date: 19881207

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 19881207

Ref country code: BE

Effective date: 19881207

REF Corresponds to:

Ref document number: 39180

Country of ref document: AT

Date of ref document: 19881215

Kind code of ref document: T

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AT

Effective date: 19881219

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 19881231

Ref country code: LI

Effective date: 19881231

Ref country code: CH

Effective date: 19881231

REF Corresponds to:

Ref document number: 3475564

Country of ref document: DE

Date of ref document: 19890112

ET Fr: translation filed
NLV1 Nl: lapsed or annulled due to failure to fulfill the requirements of art. 29p and 29m of the patents act
GBV Gb: ep patent (uk) treated as always having been void in accordance with gb section 77(7)/1977 [no translation filed]
PLBI Opposition filed

Free format text: ORIGINAL CODE: 0009260

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

26 Opposition filed

Opponent name: DANFOSS A/S

Effective date: 19890811

PLBN Opposition rejected

Free format text: ORIGINAL CODE: 0009273

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: OPPOSITION REJECTED

27O Opposition rejected

Effective date: 19901007

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 19950105

Year of fee payment: 11

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 19951212

Year of fee payment: 12

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Effective date: 19960903

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Effective date: 19970829

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST