EP0410330B1 - Procédé et dispositif de fonctionnement d'une installation frigorifique - Google Patents

Procédé et dispositif de fonctionnement d'une installation frigorifique Download PDF

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Publication number
EP0410330B1
EP0410330B1 EP90113997A EP90113997A EP0410330B1 EP 0410330 B1 EP0410330 B1 EP 0410330B1 EP 90113997 A EP90113997 A EP 90113997A EP 90113997 A EP90113997 A EP 90113997A EP 0410330 B1 EP0410330 B1 EP 0410330B1
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EP
European Patent Office
Prior art keywords
cooling
central unit
cooling point
compressors
refrigeration
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.)
Expired - Lifetime
Application number
EP90113997A
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German (de)
English (en)
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EP0410330A2 (fr
EP0410330A3 (en
Inventor
Wolfgang Höner
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.)
York Deutschland GmbH
Original Assignee
York International GmbH
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Filing date
Publication date
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Application filed by York International GmbH filed Critical York International GmbH
Priority to AT90113997T priority Critical patent/ATE91010T1/de
Publication of EP0410330A2 publication Critical patent/EP0410330A2/fr
Publication of EP0410330A3 publication Critical patent/EP0410330A3/de
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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—Component parts or details not otherwise provided for in this subclass
    • 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—Component parts or details not otherwise provided for in this subclass
    • 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 according to the preamble of claim 1 and an apparatus for performing the method.
  • 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 be designed for the maximum cooling requirement, ie at high ambient temperatures and high atmospheric humidity at the place of installation of the cooling points, for maximum loading of the cooling goods and temperature and 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 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.
  • FR-A-2 505 466 discloses a controller for an air conditioning or refrigeration system with sensors for each cooling point, the measured values of which are fed to a microprocessor for processing as a current or voltage signal in proportion to measured values for temperature, humidity and pressure.
  • the microprocessor switches the compressor stages equipped with different outputs on or off according to the cooling requirement.
  • DE-C-842 351 discloses a controller for a composite refrigeration system, in which solenoid valves of thermostats of the individual cooling points arranged in the coolant line open or close.
  • suction pressure switches are provided, which switch on the compressor stages by means of a corresponding protective control.
  • US-A-4 384 462 shows a system controller for a composite refrigeration system with cooling points which are equipped with sensors for temperature detection, as well as with several compressors which provide the required cooling capacity by joint operation or alternating operation.
  • a reference signal is transmitted from the cooling points to a central unit, where it is evaluated for the purpose of determining the cooling requirement, and the operation of the compressors is thus controlled.
  • the refrigerant suction pressure will be kept practically constant and only the cooling point temperature will be taken as a basis.
  • 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 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 on the evaporators, as a result of incomplete refrigerant exposure to the evaporator and transfer of liquid coolant into the suction line and thus into the compressor are possible in a constant change.
  • the object of the invention is a method for operating a refrigeration system of the type mentioned at the outset, according to which the most uniform possible operation of the refrigeration system is possible and in view of the respective cooling requirement, the most possible uniform utilization of the connected compressors.
  • a refrigeration system working according to the method is to be designed.
  • the solution to the problem is characterized in that the measured values of temperature sensors and the respective refrigerant suction pressure are used as the reference signal, which are evaluated in the central unit, that the minimum suction pressure is specified as the setpoint for the maximum cooling capacity and that a setpoint shift of the Suction pressure control takes place depending on the deviation of the cooling point temperature evaluated in the central unit from its respective setpoint.
  • the devices originally provided for the 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 that includes both the maximum cooling volume and the resulting maximum cooling requirement as well as the location of the cooling point with the prevailing ambient conditions, 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 supply of refrigerant to the connected cooling points is opened or closed by the central unit.
  • 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.
  • a composite refrigeration system with at least one cooling point provided with temperature 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, with a central unit , which is connected both to the temperature sensors of each cooling point and to the connected compressors of the refrigeration system, each temperature sensor giving a reference signal to the central unit, which evaluates the central unit to determine the cooling requirement and controls the operation of the compressors in accordance with the determined cooling requirement, as well as a pressure sensor arranged in the refrigerant suction line, which also gives a reference signal about the current suction pressure for evaluation to the central unit, which reference signal together with de n Reference signals from the temperature sensors are used to determine the setpoint for the minimum suction pressure as a function of the deviation of the cold store temperatures from their respective setpoint.
  • a remotely operable shut-off valve is arranged in the feed line for the refrigerant to each cooling point, said shut-off valve remotely interrupting or releasing the refrigerant feed.
  • the signal lines between the sensors of the cooling points and the central unit can advantageously be designed as bus lines for the transmission of signals and control commands.
  • remotely operated shut-off valves can be controlled via the signal line.
  • a preferred embodiment of the invention provides that the evaporators are assigned at least one cooling point to a fan blower which is connected to the cooling point sensor via a control line.
  • 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 associated with the refrigeration system 11 belonging to the refrigeration system, which provides information about the instantaneous cooling requirement of the refrigeration system 11 and thus indirectly about both the temperature of the refrigeration system 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, as already mentioned, 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 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 form an input signal for the step switch of the compressor controller integrated in the central unit 20, not shown here processed.
  • 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, including 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 demand for cooling, the entire refrigeration unit, ie all compressors 22 connected in parallel, can also be switched on .
  • 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.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
  • Air Conditioning Control Device (AREA)

Claims (8)

  1. Procédé d'exploitation d'une installation frigorifique (10), notamment d'une installation frigorifique complexe comportant au moins deux compresseurs raccordés en parallèle, lesquels, pour couvrir le besoin en froid d'au moins un poste frigorifique (11) muni de capteurs (18), fonctionnent soit conjointement, en même temps, soit séparément en alternance, chacun des capteurs (18) transmettant un signal de référence, pour les conditions frigorifiques actuelles régnant au poste frigorifique (11), à une unité centrale (20) qui active ou inactive en conséquence les compresseurs raccordés (22), caractérisé par le fait que l'on utilise comme signal de référence les valeurs de mesure de capteurs de température (18) ainsi que la pression d'aspiration de fluide frigorifique concernée, ces valeurs et cette pression étant interprétées dans l'unité centrale (20), par le fait que l'on fixe à l'avance, comme valeur de consigne pour la puissance frigorifique maximale, le minimum de pression d'aspiration et on déplace la valeur de consigne de la régulation de pression d'aspiration en fonction de l'écart entre les températures des postes frigorifiques et leur valeur de consigne concernée.
  2. Procédé selon revendication 1, caractérisé par le fait que la commande de valves d'isolement sur la conduite d'arrivée de fluide frigorifique de chaque poste frigorifique s'effectue en se basant sur les informations acquises à partir du signal de référence du poste frigorifique et à partir de la comparaison avec la pression d'aspiration de fluide frigorifique.
  3. Procédé selon revendication 1 ou 2, caractérisé par le fait que l'activation ou, selon,le cas, l'inactivation, des compresseurs raccordés s'effectue par un commutateur à gradins intégré dans l'unité centrale.
  4. Installation frigorifique complexe comportant : au moins un poste frigorifique (11) muni de capteurs de température (18); au moins deux compresseurs (22) raccordés en parallèle qui, en fonctionnant en alternance ou simultanément, fournissent la puissance frigorifique nécessaire à la couverture du besoin en froid, une unité centrale (20) qui est reliée aussi bien aux capteurs de température (18) de chaque poste frigorifique (11) qu'aux compresseurs (22) raccordés de l'installation frigorifique (10), chaque capteur de température (18) fournissant à l'unité centrale (20) un signal de référence que l'unité centrale (20) analyse afin de déterminer le besoin en froid, celle-ci commandant le fonctionnement du compresseur (22) en fonction du besoin en froid déterminé, ainsi qu'un capteur de pression (21) disposé sur la conduite d'aspiration de fluide frigorifique (24) et fournissant également à l'unité centrale (20), aux fins d'interprétation, un signal de référence concernant la pression d'aspiration actuelle, ledit signal de référence servant, conjointement avec les signaux de référence des capteurs de température (18), à fixer la valeur de consigne pour le minimum de pression d'aspiration, en fonction de l'écart des températures des postes frigorifiques par rapport à leur valeur de consigne respective.
  5. Installation frigorifique complexe selon revendication 4, caractérisée par le fait qu'une vanne d'arrêt (12) actionnée à distance pour interrompre ou autoriser l'arrivée de fluide frigorifique, est disposée sur la conduite d'arrivée (13) de fluide frigorifique allant à chaque poste frigorifique (11).
  6. Installation frigorifique complexe selon l'une des revendications 4 ou 5, caractérisée par le fait que les lignes de signaux (14) entre les capteurs (13) des postes frigorifiques (11) et l'unité centrale (20) sont réalisées sous forme de lignes-bus pour transmettre des signaux et des ordres de commande.
  7. Installation frigorifique complexe selon revendication 5 ou 6, caractérisée par le fait que les vannes d'arrêt actionnées à distance (12) sont commandées par la ligne de signaux (14, 15).
  8. Installation frigorifique complexe selon l'une des revendications 4 à 7, caractérisée par le fait qu'aux évaporateurs (11a) d'au moins un poste frigorifique (11) est associé un ventilateur (14) qui est relié au capteur (13) du poste frigorifique par l'intermédiaire d'une ligne de commande (16).
EP90113997A 1989-07-28 1990-07-21 Procédé et dispositif de fonctionnement d'une installation frigorifique Expired - Lifetime EP0410330B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT90113997T ATE91010T1 (de) 1989-07-28 1990-07-21 Verfahren und vorrichtung zum betrieb einer kaelteanlage.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3925090A DE3925090A1 (de) 1989-07-28 1989-07-28 Verfahren zum betrieb einer kaelteanlage
DE3925090 1989-07-28

Publications (3)

Publication Number Publication Date
EP0410330A2 EP0410330A2 (fr) 1991-01-30
EP0410330A3 EP0410330A3 (en) 1991-06-26
EP0410330B1 true EP0410330B1 (fr) 1993-06-23

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EP90113997A Expired - Lifetime EP0410330B1 (fr) 1989-07-28 1990-07-21 Procédé et dispositif de fonctionnement d'une installation frigorifique

Country Status (3)

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EP (1) EP0410330B1 (fr)
AT (1) ATE91010T1 (fr)
DE (2) DE3925090A1 (fr)

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US7290398B2 (en) 2003-08-25 2007-11-06 Computer Process Controls, Inc. Refrigeration control system
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US7596959B2 (en) 2005-10-21 2009-10-06 Emerson Retail Services, Inc. Monitoring compressor performance in a refrigeration system
US7644591B2 (en) 2001-05-03 2010-01-12 Emerson Retail Services, Inc. System for remote refrigeration monitoring and diagnostics
US7665315B2 (en) 2005-10-21 2010-02-23 Emerson Retail Services, Inc. Proofing a refrigeration system operating state
US7752854B2 (en) 2005-10-21 2010-07-13 Emerson Retail Services, Inc. Monitoring a condenser in a refrigeration system
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EP1980805B1 (fr) 2005-03-18 2009-09-02 Danfoss A/S Procédé de contrôle d'un système de réfrigération
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US9140728B2 (en) 2007-11-02 2015-09-22 Emerson Climate Technologies, Inc. Compressor sensor module
DE102008041939A1 (de) * 2008-09-10 2010-03-11 Ago Ag Energie + Anlagen Verfahren zum Betreiben einer Wärmepumpe oder Kältemaschine bzw. einer Kraftmaschine sowie Wärmepumpe oder Kältemaschine und Kraftmaschine
MX2011012546A (es) 2009-05-29 2012-10-03 Emerson Retail Services Inc Sistema y metodo para monitorear y evaluar modificaciones de parametros operativos de equipo.
EP2681497A4 (fr) 2011-02-28 2017-05-31 Emerson Electric Co. Solutions de contrôle et de diagnostic d'un système hvac destinées à des habitations
US8964338B2 (en) 2012-01-11 2015-02-24 Emerson Climate Technologies, Inc. System and method for compressor motor protection
US9310439B2 (en) 2012-09-25 2016-04-12 Emerson Climate Technologies, Inc. Compressor having a control and diagnostic module
US9551504B2 (en) 2013-03-15 2017-01-24 Emerson Electric Co. HVAC system remote monitoring and diagnosis
US9803902B2 (en) 2013-03-15 2017-10-31 Emerson Climate Technologies, Inc. System for refrigerant charge verification using two condenser coil temperatures
WO2014144446A1 (fr) 2013-03-15 2014-09-18 Emerson Electric Co. Diagnostic et système de télésurveillance de chauffage, de ventilation et de climatisation
CA2908362C (fr) 2013-04-05 2018-01-16 Fadi M. Alsaleem Systeme de pompe a chaleur a diagnostique de charge de fluide refrigerant
RU2735041C1 (ru) * 2017-05-01 2020-10-27 Данфосс А/С Способ управления давлением всасывания, основанный на охлаждающем объекте под самой большой нагрузкой
DE102021117724A1 (de) * 2021-07-08 2023-01-12 Bitzer Kühlmaschinenbau Gmbh Kältemittelverdichterverbund

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US7644591B2 (en) 2001-05-03 2010-01-12 Emerson Retail Services, Inc. System for remote refrigeration monitoring and diagnostics
US7290398B2 (en) 2003-08-25 2007-11-06 Computer Process Controls, Inc. Refrigeration control system
US7885959B2 (en) 2005-02-21 2011-02-08 Computer Process Controls, Inc. Enterprise controller display method
US7885961B2 (en) 2005-02-21 2011-02-08 Computer Process Controls, Inc. Enterprise control and monitoring system and method
US7594407B2 (en) 2005-10-21 2009-09-29 Emerson Climate Technologies, Inc. Monitoring refrigerant in a refrigeration system
US7596959B2 (en) 2005-10-21 2009-10-06 Emerson Retail Services, Inc. Monitoring compressor performance in a refrigeration system
US7665315B2 (en) 2005-10-21 2010-02-23 Emerson Retail Services, Inc. Proofing a refrigeration system operating state
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

Also Published As

Publication number Publication date
DE3925090A1 (de) 1991-02-07
ATE91010T1 (de) 1993-07-15
EP0410330A2 (fr) 1991-01-30
EP0410330A3 (en) 1991-06-26
DE59001849D1 (de) 1993-07-29

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