EP1570215B1 - Evaporation process control for use in refrigeration technology - Google Patents

Evaporation process control for use in refrigeration technology Download PDF

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Publication number
EP1570215B1
EP1570215B1 EP02782599A EP02782599A EP1570215B1 EP 1570215 B1 EP1570215 B1 EP 1570215B1 EP 02782599 A EP02782599 A EP 02782599A EP 02782599 A EP02782599 A EP 02782599A EP 1570215 B1 EP1570215 B1 EP 1570215B1
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EP
European Patent Office
Prior art keywords
condenser
evaporator
temperature
refrigerant
iwt
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EP02782599A
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German (de)
French (fr)
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EP1570215A1 (en
Inventor
Remo Meister
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BMS Energietechnik AG
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BMS Energietechnik AG
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    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/31—Expansion valves
    • 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
    • F25B2341/00—Details of ejectors not being used as compression device; Details of flow restrictors or expansion valves
    • F25B2341/06—Details of flow restrictors or expansion valves
    • F25B2341/063—Feed forward expansion valves
    • 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
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2513—Expansion valves
    • 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
    • F25B2700/19—Pressures
    • F25B2700/193—Pressures of the compressor
    • F25B2700/1933—Suction pressures
    • 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
    • F25B2700/19—Pressures
    • F25B2700/197—Pressures of the evaporator
    • 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
    • F25B2700/2103—Temperatures near a heat exchanger
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2115—Temperatures of a compressor or the drive means therefor
    • F25B2700/21151—Temperatures of a compressor or the drive means therefor at the suction side of the compressor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2115—Temperatures of a compressor or the drive means therefor
    • F25B2700/21152—Temperatures of a compressor or the drive means therefor at the discharge side of the compressor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2115—Temperatures of a compressor or the drive means therefor
    • F25B2700/21155—Temperatures of a compressor or the drive means therefor of the oil
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2117—Temperatures of an evaporator
    • F25B2700/21174—Temperatures of an evaporator of the refrigerant at the inlet of the evaporator
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2117—Temperatures of an evaporator
    • F25B2700/21175—Temperatures of an evaporator of the refrigerant at the outlet of the evaporator
    • 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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • 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

Definitions

  • the evaporator In order to optimally operate an evaporator in refrigeration, the evaporator is so far supplied with wet steam that a control valve (expansion valve) (3) to a minimum stable signal, usually after the evaporator outlet pressure (12) and the associated evaporator outlet temperature (13) of the refrigerant regulated is (drawing Fig. 1, 2 and 3).
  • the difference of the evaporator pressure, converted into the associated evaporation temperature and the evaporation temperature actually measured as the temperature, serves as a measured variable for the control valve.
  • Stable control behavior with the smallest possible temperature difference, is sought. The smallest possible temperature difference results in a higher evaporator output. If the difference is too small or the signal is unstable, there will be liquid hammer or power reduction on the compressor (1). If the difference is too large, the evaporator performance is reduced (4).
  • IWT internal heat exchangers
  • FIGS. 4, 5, 6 Some of the evaporators are already equipped with internal heat exchangers (IWT) (5) (FIGS. 4, 5, 6). However, these are designed as "thermally short" apparatus and not involved in the evaporator control by inlet steam content. The refrigerant liquid is not cooled down much and the suction vapors are not overheated. Overheating of the suction steam is limited to approx. 5-10K. Today's conventional injectors are not designed for maximum overheating, and the adjustable superheat is a maximum of about 20-25K.
  • the aim of the invention is to achieve the following in refrigerating / freezing plants, refrigerating machines for cooling and heating operation, refrigeration systems, refrigeration sets, heat pumps, air conditioning systems and all other systems with the use of refrigerant for evaporation:
  • the refrigeration system consisting essentially of compressor (1), condenser (2), injection valve (3) and evaporator (4) with an additional internal heat exchanger (5) hereinafter referred to as IWT provided (Fig. 7, 8 , 9, 10, 11).
  • This IWT (5) is installed between evaporator (4) and compressor (1) on the one hand and between condenser (2) and injection valve (3) on the other hand (drawing Fig. 8, 9, 10).
  • the actual evaporation (first stage) (4) takes place partially or completely in the evaporator (4).
  • liquid refrigerant is admitted at the evaporator outlet.
  • the regulation registered here for the first time assumes for the first time the measured variables of the liquid temperature of the refrigerant before the injection valve (3) and the evaporator pressure (FIGS. 7, 8, 9, 10, 11, points 9, 10, 11, 12).
  • the evaporator pressure is removed at the inlet of the evaporator (12) (beginning of evaporation) ( Figures 7, 8, 9, 10, 11, point 12).
  • the outlet pressure or any value derived from both pressure readings can also be used as the measured value (FIGS. 7, 23).
  • the evaporation process is started as close as possible to the left limit curve of the 1g p, h diagram.
  • the beginning of the evaporation process is defined by the liquid temperature before the injection valve (11, 9) and the evaporation pressure (12, 10) (FIGS. 7, 8, 9, 10, 11, points 11, 12, 9, 10).
  • the definition of the controlled variable can be made from the evaporation pressure and a fixed (temperature) difference (adjustable) or from a stored curve calculation per refrigerant.
  • the injection valve (3) lowers the temperature of the refrigerant liquid (11) before the injection valve (3) by opening the valve (3) and increases the refrigerant liquid temperature by closing the valve (3), thus trying the desired setpoint at a corresponding evaporation pressure ( 12).
  • the degree of flooding or overheating (19, 13) of the evaporator or evaporators (4) thus determines the subcooling temperature of the liquid refrigerant (11) at a corresponding evaporation pressure (12) and the suction steam temperature (13) at the compressor inlet (14).
  • the measured value for this safety and optimization function is the suction steam temperature at the outlet IWT (5) (13), the suction steam temperature at the inlet compressor (1) (14), the hot gas temperature (outlet compressor) (15), Oil temperature of the compressor (1) (16) or another corresponding temperature is used (Fig. 8, 9, 10, 11 points 13, 14, 15, 16).
  • optimally maximum subcooling (11) of the refrigerant liquid and optimally maximum suction steam superheating (14), depending on the corresponding compressor, are sought (FIGS. 7, 9, 10, 11, points 11, 14).
  • the refrigeration system consists of one or more evaporators (4), one or more IWTs (5), one or more compressors (1) or one or more injection valves (3), and whether these are grouped together or not. It also does not matter whether or not one or more evaporators (4) are grouped together with only one or more IWTs (5) (FIGS. 10-18, points 9, 10, 13, 14, 15, 16). , Any combination between injectors (3), evaporators (4), IWT's (5) and compressors (1) is therefore possible.
  • the injectors (3) are mechanical, thermal, electronic or otherwise, and whether they are timed, continuous or otherwise. Relevant is the process and control loop with the listed dependencies between evaporation start 11, 12), evaporation end (13, 19) depending on the refrigerant liquid inlet temperature (21) in the IWT (5), the Saugdampfaustrittstemperatur (13) from the IWT (5) Condition of the refrigerant (wet steam (19) or superheated suction steam (13)) when leaving the evaporator (19) resp.
  • the advantage of this evaporator control consists of the fact that the evaporator (4) is optimally flooded and utilized (drawing FIGS. 7, 9, 10, 11 points 17, 19) that the pressure drop on the refrigerant side via the evaporator (4) is smaller in that thereby the evaporation temperature (23) is increased, thereby smaller evaporators (4) can be used, thereby reducing the refrigerant mass flow for a required cooling capacity, thereby causing the compressors (1) to become smaller (cooling), thereby resulting in less energy for cooling is required that thereby the degrees of delivery and lubrication and thus the life of the compressor (1) is increased.
  • the control is set so that the maximum power always comes to the evaporator (4) ( Figure 7, 8, 9 points 17) and not to the IWT (5) (18) (largest possible enthalpy distance at point 17).
  • New to our invention is that the refrigerant enters as a liquid / gas mixture with a high gas content in a second evaporation stage (5, 18, 20) (dry evaporator), in which a residual evaporation followed by high superheating of the refrigerant (13) and a simultaneous Supercooling of the liquid refrigerant takes place on the second side of the IWT (5) (11).
  • a second evaporation stage (5, 18, 20) (dry evaporator)
  • a residual evaporation followed by high superheating of the refrigerant (13) and a simultaneous Supercooling of the liquid refrigerant takes place on the second side of the IWT (5) (11).
  • New to our invention is that the suction steam superheating (13) is chosen as large as possible.
  • a refrigeration system consisting essentially of one or more:
  • a refrigeration system additionally comprises one or more of the aforementioned components and additionally desupers (24), one or more waste heat utilization exchangers, further subcoolers (25), sight glasses (7), dryers (6), filters, valves (8), safety apparatuses , Absperrapparaturen, collectors, oil pumps, distribution systems, electrical and control parts, refrigeration aids, etc. on.
  • the measured value for Saugdampfbegrenzung on the suction line to the refrigerant compressor (1) is removed.
  • the measured values of the refrigerant liquid temperature (11) and the evaporator inlet pressure (12) are used.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Air Conditioning Control Device (AREA)
  • Sorption Type Refrigeration Machines (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
  • Peptides Or Proteins (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Organic Low-Molecular-Weight Compounds And Preparation Thereof (AREA)

Abstract

The invention relates to an evaporator control by use of an expansion valve and an internal heat exchanger IHE. The evaporator control is controlled after the start of the evaporation process and the temperature of the compressor suction vapor, oil and hot gas as well as coolant liquid is controlled and regulated upstream of the expansion valve.

Description

Verdampfen von Kältemittel in Kühl- und Tiefkühlanlagen, Kältetechnik, Kältemaschine für Kühl- und Heizbetrieb, Kälteanlagen, Kältesätze, Wärmepumpen, Klimaanlagen und weitere.Evaporation of refrigerant in refrigeration and freezing systems, refrigeration, chiller for cooling and heating, refrigeration, refrigeration, heat pumps, air conditioning and more.

Stand der Technik:State of the art:

Verdampferregelung mit Trockenexpansion nach dem minimalsten stabilen Signal (MMS) (Fig. 1, 2 und 3).Evaporator control with dry expansion after the minimum stable signal (MMS) (Figures 1, 2 and 3).

Um einen Verdampfer in der Kältetechnik optimal zu betreiben, wird der Verdampfer soweit mit Nassdampf beaufschlagt, dass ein Regelventil (Expansionsventil) (3) auf ein minimalstes stabiles Signal, normalerweise nach dem Verdampferaustrittsdruck (12) und der dazugehörenden Verdampferaustrittstemperatur (13) des Kältemittels geregelt wird (Zeichnung Fig. 1, 2 und 3). Die Differenz des Verdampferdrucks, umgerechnet in die dazugehörende Verdampfungstemperatur und der tatsächlich als Temperatur gemessenen Verdampfungstemperatur dient dem Regelventil als Messgrösse. Dabei werden stabile Regelverhalten, bei einer möglichst kleinen Temperaturdifferenz, gesucht. Eine möglichst kleine Temperaturdifferenz hat eine höhere Verdampferleistung zur Folge. Ist die Differenz zu klein oder das Signal nicht stabil, kommt es zu Flüssigkeitsschlägen oder Leistungsverminderung am Verdichter (1). Ist die Differenz zu gross, kommt es zu einer Verminderung der Verdampferleistung (4).In order to optimally operate an evaporator in refrigeration, the evaporator is so far supplied with wet steam that a control valve (expansion valve) (3) to a minimum stable signal, usually after the evaporator outlet pressure (12) and the associated evaporator outlet temperature (13) of the refrigerant regulated is (drawing Fig. 1, 2 and 3). The difference of the evaporator pressure, converted into the associated evaporation temperature and the evaporation temperature actually measured as the temperature, serves as a measured variable for the control valve. Stable control behavior, with the smallest possible temperature difference, is sought. The smallest possible temperature difference results in a higher evaporator output. If the difference is too small or the signal is unstable, there will be liquid hammer or power reduction on the compressor (1). If the difference is too large, the evaporator performance is reduced (4).

Nach dem selben Prinzip (überhitzter Kältemitteldampf am Ende des Verdampfungsprozesses) werden auch automatische Ventile, Kapillarrohre oder andere Apparaturen bemessen und eingesetzt.According to the same principle (superheated refrigerant vapor at the end of the evaporation process) also automatic valves, capillary tubes or other equipment are sized and used.

Dem Verdampfer werden zum Teil heute schon interne Wärmeaustauscher (IWT) (5) (Fig 4, 5, 6) nachgeschaltet. Allerdings werden diese als "thermisch kurze" Apparate ausgelegt und nicht in die Verdampferregelung nach Eintrittsdampfgehalt eingebunden. Die Kältemittelflüssigkeit wird nicht stark herunter gekühlt und die Saugdämpfe werden nicht stark überhitzt. Die Überhitzung des Saugdampfes ist auf ca. 5-10K begrenzt. Heute übliche Einspritzventile sind auch nicht auf maximale Überhitzungen konzipiert, und die einstellbare Überhitzung liegt bei maximal ca. 20-25K.Some of the evaporators are already equipped with internal heat exchangers (IWT) (5) (FIGS. 4, 5, 6). However, these are designed as "thermally short" apparatus and not involved in the evaporator control by inlet steam content. The refrigerant liquid is not cooled down much and the suction vapors are not overheated. Overheating of the suction steam is limited to approx. 5-10K. Today's conventional injectors are not designed for maximum overheating, and the adjustable superheat is a maximum of about 20-25K.

Aus der Druckschrift EP-A1-1 014 013 ist ein mit CO2 arbeitender Kälteerzeugungs-Kreisprozess vom Dampf-Verdichtungs-Typ bekannt, der mit einem Verdampfer und einem internen Wärmetauscher arbeitet. Zwischen dem Verdampfer und dem internen Wärmetauscher ist ein Überhitzungs-Regelventil angeordnet, welches den Massenstrom des Anteils der flüssigen Phase in Abhängigkeit von einem Steuersignal steuert, um einen Grad der Überhitzung des Gasphasenanteils zu halten. Als Steuersignale werden insbesondere Temperatursignale verwendet, die von Temperatursensoren an den Ausgängen des Verdampfers und des internen Wärmetauschers aufgenommen werden.From the publication EP-A1-1 014 013 For example, there is known a CO2-type vapor compression type refrigeration cycle process which uses an evaporator and an internal heat exchanger. Disposed between the evaporator and the internal heat exchanger is an overheat control valve which controls the mass flow of the portion of the liquid phase in response to a control signal to maintain a degree of overheating of the gas phase portion. As control signals in particular temperature signals are used, which are recorded by temperature sensors at the outputs of the evaporator and the internal heat exchanger.

Detaillierte Darstellung der Erfindung:Detailed description of the invention:

Ziel der Erfindung ist es, bei Kühl-/Tiefkühlanlagen, Kältemaschinen für Kühl- und Heizbetrieb, Kälteanlagen, Kältesätzen, Wärmepumpen, Klimaanlagen und allen anderen Anlagen mit Einsatz von Kältemittel zur Verdampfung Folgendes zu erreichen:The aim of the invention is to achieve the following in refrigerating / freezing plants, refrigerating machines for cooling and heating operation, refrigeration systems, refrigeration sets, heat pumps, air conditioning systems and all other systems with the use of refrigerant for evaporation:

Die Saugdampfüberhitzung im Verdampfer (4) klein zu halten oder den Verdampfer (4) mit Nassdampf zu verlassen und dabei die Saugdampfüberhitzung vor dem Verdichter (1) möglichst hoch zu halten (soweit die Einsatzgrenzen des Verdichters, des Öls oder des Kältemittels und / oder die verschiedenen Temperaturverhältnisse dies zulassen).To keep the suction steam superheat in the evaporator (4) small or to leave the evaporator (4) with wet steam while keeping the Saugdampfüberhitzung before the compressor (1) as high as possible (as far as the application limits of the compressor, the oil or the refrigerant and / or the different temperature conditions allow this).

Zu diesem Zweck wird die Kälteanlage bestehend zur Hauptsache aus Verdichter (1), Kondensator (2), Einspritzventil (3) und Verdampfer (4) mit einem zusätzlichen internen Wärmeaustauscher (5) im Folgenden mit IWT bezeichnet, versehen (Fig. 7, 8, 9, 10, 11).For this purpose, the refrigeration system consisting essentially of compressor (1), condenser (2), injection valve (3) and evaporator (4) with an additional internal heat exchanger (5) hereinafter referred to as IWT provided (Fig. 7, 8 , 9, 10, 11).

Dieser IWT (5) wird zwischen Verdampfer (4) und Verdichter (1) einerseits und zwischen Kondensator (2) und Einspritzventil (3) andererseits eingebaut (Zeichnung Fig. 8, 9, 10).This IWT (5) is installed between evaporator (4) and compressor (1) on the one hand and between condenser (2) and injection valve (3) on the other hand (drawing Fig. 8, 9, 10).

Auf der einen Seite wird der IWT (5) mit flüssigem Kältemittel (Flüssigkeitsseite) und auf der anderen Seite mit überhitztem dampfförmigen Kältemittel oder mit Nassdampf durchströmt.On one side of the IWT (5) with liquid refrigerant (liquid side) and on the other side with superheated vapor refrigerant or wet steam flows through.

Wird der IWT mit reinen Medien (flüssiges Kältemittel und überhitzem Saugdampf) durchströmt, sprechen wir von einem Wärmeaustausch (Fig. 4, 5, 6). Wird der IWT mit einem flüssigen Kältemittel und Nassdampf mit anschliessender Saugdampfüberhitzung betrieben, sprechen wir von einer zweiten Verdampfungsstufe mit integrierter Flüssigkeitsunterkühlung und Saugdampfüberhitzung (Fig. 7, 8, 9, 10). Im Folgenden sind immer beide Möglichkeiten gemeint.If the IWT flows through pure media (liquid refrigerant and superheated suction steam), we speak of a heat exchange (Fig. 4, 5, 6). If the IWT is operated with a liquid refrigerant and wet steam with subsequent suction steam overheating, we speak of a second evaporation stage with integrated liquid subcooling and suction steam superheating (FIGS. 7, 8, 9, 10). In the following, both options are always meant.

Die eigentliche Verdampfung (erste Stufe) (4) findet teilweise oder ganz im Verdampfer (4) statt. Um diesen Verdampfer (4) optimal betreiben zu können, wird am Verdampferaustritt flüssiges Kältemittel zugelassen.The actual evaporation (first stage) (4) takes place partially or completely in the evaporator (4). In order to be able to operate this evaporator (4) optimally, liquid refrigerant is admitted at the evaporator outlet.

Da am Verdampferaustritt flüssiges Kältemittel zugelassen wird, fehlt zur Regelung des Verdampfers (4) eine Messgrösse zur Bestimmung der Überhitzung, und das Expansionsventil (3) kann die Kältemittelbefüllung des Verdampfers (4) nicht mehr regeln.Since liquid refrigerant is admitted at the evaporator outlet, a measured variable for determining the overheating is missing for controlling the evaporator (4), and the expansion valve (3) can no longer control the refrigerant filling of the evaporator (4).

Die hier zum Patent angemeldete Regelung übernimmt als Neuheit erstmals die Messgrössen der Flüssigkeitstemperatur des Kältemittels vor dem Einspritzventil (3) und den Verdampferdruck (Fig. 7, 8, 9, 10, 11, Punkte 9, 10, 11, 12).As a novelty, the regulation registered here for the first time assumes for the first time the measured variables of the liquid temperature of the refrigerant before the injection valve (3) and the evaporator pressure (FIGS. 7, 8, 9, 10, 11, points 9, 10, 11, 12).

Es ist dabei egal, um was für Verdampfertypen oder Verdampferbauarten und um was für Kältemittel und Einsatzgebiete es sich dabei handelt.It does not matter what types of evaporators or evaporator types and what kind of refrigerant and applications it is.

Der Verdampferdruck wird am Eintritt des Verdampfers (12) (Beginn der Verdampfung) abgenommen (Fig. 7, 8, 9, 10, 11, Punkt 12). In speziellen Fällen kann auch der Ausrittsdruck oder ein beliebiger Wert, hergeleitet aus beiden Druckmesswerten (Kältemittelglide), als Messwert verwendet werden (Fig. 7, 23).The evaporator pressure is removed at the inlet of the evaporator (12) (beginning of evaporation) (Figures 7, 8, 9, 10, 11, point 12). In special cases, the outlet pressure or any value derived from both pressure readings (refrigerant glide) can also be used as the measured value (FIGS. 7, 23).

Mit dieser Regelung wird der Beginn des Verdampfungsprozesses geregelt (Fig. 7, Punkte 11, 12) und nicht wie bisher das Ende der Verdampfung (Fig. 3, Punkte 12 und 13).This control regulates the beginning of the evaporation process (Figure 7, points 11, 12) and not the end of evaporation as before (Figure 3, points 12 and 13).

Es ist dabei egal, ob genau nach der linken Grenzkurve zwischen Kältemittelflüssig- zu Kältemittelnassdampf im lg p, h-Diagramm des Kältemittels oder nach einem Wert (links) oder rechts dieser Grenzkurve geregelt wird.It does not matter whether exactly according to the left limit curve between refrigerant liquid to Kältemittelnassdampf in lg p, h-diagram of the refrigerant or to a value (left) or right of this limit curve is regulated.

Bei "optimierten" Verdampferbauarten wird möglichst nahe der linken Grenzkurve des 1g p, h-Diagramms der Verdampfungsprozess gestartet. Bei nichtoptimierten Verdampfern kann es von Vorteil sein, einen bestimmten Gasanteil zu Beginn des Verdampfungsprozesses zuzulassen. Dabei wird nach dem Optimum für den jeweiligen Verdampfer rechts dieser Grenzkurve der Verdampfungsprozess gestartet.In "optimized" evaporator types, the evaporation process is started as close as possible to the left limit curve of the 1g p, h diagram. For non-optimized evaporators, it may be advantageous to allow a certain proportion of gas at the beginning of the evaporation process. In this case, the evaporation process is started after the optimum for the respective evaporator right of this limit curve.

Der Beginn des Verdampfungsprozesses definiert sich aus der Flüssigkeitstemperatur vor dem Einspritzventil (11, 9) und dem Verdampfungsdruck (12, 10) (Fig. 7, 8, 9, 10, 11, Punkte 11, 12, 9, 10).The beginning of the evaporation process is defined by the liquid temperature before the injection valve (11, 9) and the evaporation pressure (12, 10) (FIGS. 7, 8, 9, 10, 11, points 11, 12, 9, 10).

Die Definition der Regelgrösse kann, wie die Überhitzungsregelung, aus dem Verdampfungsdruck und einer festen (Temperatur-) Differenz (einstellbar) oder aus einer hinterlegten Kurvenberechnung je Kältemittel erfolgen.
Das Einspritzventil (3) senkt dabei die Temperatur der Kältemittelflüssigkeit (11) vor dem Einspritzventil (3) durch Öffnen des Ventils (3) und erhöht die Kältemittelflüssigkeitstemperatur durch Schliessen des Ventils (3) und versucht so, den gewünschten Sollwert bei einem entsprechenden Verdampfungsdruck (12) zu erhalten.The definition of the controlled variable, like the overheating control, can be made from the evaporation pressure and a fixed (temperature) difference (adjustable) or from a stored curve calculation per refrigerant.
The injection valve (3) lowers the temperature of the refrigerant liquid (11) before the injection valve (3) by opening the valve (3) and increases the refrigerant liquid temperature by closing the valve (3), thus trying the desired setpoint at a corresponding evaporation pressure ( 12).

Der Überflutungs- oder Überhitzungsgrad (19, 13) des oder der Verdampfer (4) bestimmen somit die Unterkühlungstemperatur des flüssigen Kältemittels (11) bei entsprechendem Verdampfungsdruck (12) und die Saugdampftemperatur (13) am Verdichtereintritt (14).The degree of flooding or overheating (19, 13) of the evaporator or evaporators (4) thus determines the subcooling temperature of the liquid refrigerant (11) at a corresponding evaporation pressure (12) and the suction steam temperature (13) at the compressor inlet (14).

Beim Erreichen von Grenzwerten, wie zum Beispiel der höchsten maximal zulässige Temperatur für den Verdichter (13, 14, 15, 16), übernimmt ein weiterer Temperaturmessfühler (optional) und übersteuert die Regelung der Kältemittelflüssigkeitseintrittstemperatur ins Einspritzventil (11) nach Verdampferdruck (12) (Fig. 7, 9, 11 Punkte 11, 12 und 13 (14, 15, 16)).Upon reaching limit values, such as the highest maximum permissible temperature for the compressor (13, 14, 15, 16), another temperature sensor (optional) and overrides the control of the refrigerant liquid inlet temperature in the injection valve (11) by evaporator pressure (12) ( Fig. 7, 9, 11 points 11, 12 and 13 (14, 15, 16)).

Es spielt dabei keine Rolle, ob als Messgrösse für diese Sicherheits- und Optimierungsfunktion die Saugdampftemperatur am Austritt IWT (5) (13), die Saugdampftemperatur am Eintritt Verdichter (1) (14), die Heissgastemperatur (Austritt Verdichter) (15), die Öltemperatur des Verdichters (1) (16) oder eine andere entsprechende Temperatur verwendet wird (Fig. 8, 9, 10, 11 Punkte 13, 14, 15, 16).It does not matter whether the measured value for this safety and optimization function is the suction steam temperature at the outlet IWT (5) (13), the suction steam temperature at the inlet compressor (1) (14), the hot gas temperature (outlet compressor) (15), Oil temperature of the compressor (1) (16) or another corresponding temperature is used (Fig. 8, 9, 10, 11 points 13, 14, 15, 16).

In jedem Fall wird entsprechend des Verdampfertyps immer eine optimal-maximale Unterkühlung (11) der Kältemittelflüssigkeit und eine je nach dem entsprechenden Verdichter optimal-maximale Saugdampfüberhitzung (14) angestrebt (Fig. 7, 9, 10, 11 Punkte 11, 14).In any case, according to the type of evaporator, optimally maximum subcooling (11) of the refrigerant liquid and optimally maximum suction steam superheating (14), depending on the corresponding compressor, are sought (FIGS. 7, 9, 10, 11, points 11, 14).

Es spielt dabei keine Rolle, ob das Kältesystem aus einem oder mehreren Verdampfern (4), einem oder mehreren IWT's (5), einem oder mehreren Verdichtern (1) oder einem oder mehreren Einspritzventilen (3) besteht, und ob diese zu Gruppen zusammengefasst sind oder nicht. Es spielt dabei auch keine Rolle, ob ein oder mehrere Verdampfer (4) mit nur einem oder mehreren IWT's (5) zu Gruppen zusammengefasst sind oder nicht (Fig. 10-18, Punkte 9, 10, 13, 14, 15, 16). Jegliche Kombinationen zwischen Einspritzventilen (3), Verdampfern (4), IWT's (5) und Verdichtern (1) ist also möglich.It does not matter whether the refrigeration system consists of one or more evaporators (4), one or more IWTs (5), one or more compressors (1) or one or more injection valves (3), and whether these are grouped together or not. It also does not matter whether or not one or more evaporators (4) are grouped together with only one or more IWTs (5) (FIGS. 10-18, points 9, 10, 13, 14, 15, 16). , Any combination between injectors (3), evaporators (4), IWT's (5) and compressors (1) is therefore possible.

Es spielt keine Rolle, ob die Einspritzventile (3) mechanischer, thermischer, elektronischer oder anderer Bauart sind, und ob diese getaktet, stetig oder anders regeln. Massgeblich ist der Prozess und Regelkreis mit den aufgeführten Abhängigkeiten zwischen Verdampfungsbeginn 11, 12), Verdampfungsende (13, 19) in Abhängigkeit der Kältemittelflüssigkeitseintrittstemperatur (21) in den IWT (5), der Saugdampfaustrittstemperatur (13) aus dem IWT (5), dem Zustand des Kältemittels (Nassdampf (19) oder überhitzter Saugdampf (13)) beim Verlassen des Verdampfers (19) resp. dem Eintreten (20) in den IWT (5), welcher einmal als zweite Verdampferstufe mit anschliessender hoher Saugdampfüberhitzung (13) und ein anderes Mal bei der gleichen Anlage als reiner Wärmetauscher zum Überhitzen des Saugdampfes (13) betrieben wird. Es spielt dabei auch keine Rolle, ob eine dem IWT (5) vorgeschaltete externe Unterkühlerstufe (25) dem Prozess einmal zu- und einmal weggeschaltet wird.It does not matter if the injectors (3) are mechanical, thermal, electronic or otherwise, and whether they are timed, continuous or otherwise. Relevant is the process and control loop with the listed dependencies between evaporation start 11, 12), evaporation end (13, 19) depending on the refrigerant liquid inlet temperature (21) in the IWT (5), the Saugdampfaustrittstemperatur (13) from the IWT (5) Condition of the refrigerant (wet steam (19) or superheated suction steam (13)) when leaving the evaporator (19) resp. the entry (20) in the IWT (5), which is operated once as a second evaporator stage with subsequent high Saugdampfüberhitzung (13) and another time in the same system as a pure heat exchanger for superheating the suction steam (13). It also does not matter if an external subcooler stage (25) connected upstream of the IWT (5) is switched on and off once.

Der Vorteil dieser Verdampferregelung besteht aus der Tatsache, dass so der Verdampfer (4) optimal überflutet und ausgenutzt wird (Zeichnung Fig. 7, 9, 10, 11 Punkte 17, 19), dass der Druckabfall kältemittelseitig über den Verdampfer (4) kleiner wird, dass dadurch die Verdampfungstemperatur (23) erhöht wird, dass dadurch kleinere Verdampfer (4) eingesetzt werden können, dass dadurch der Kältemittelmassenstrom für eine geforderte Kälteleistung kleiner wird, dass dadurch die Verdichter (1) kleiner werden (Kälteerzeugung), dass dadurch weniger Energie zur Kälteerzeugung benötigt wird, dass dadurch die Liefergrade und die Schmierung und somit die Lebensdauer der Verdichter (1) erhöht wird.The advantage of this evaporator control consists of the fact that the evaporator (4) is optimally flooded and utilized (drawing FIGS. 7, 9, 10, 11 points 17, 19) that the pressure drop on the refrigerant side via the evaporator (4) is smaller in that thereby the evaporation temperature (23) is increased, thereby smaller evaporators (4) can be used, thereby reducing the refrigerant mass flow for a required cooling capacity, thereby causing the compressors (1) to become smaller (cooling), thereby resulting in less energy for cooling is required that thereby the degrees of delivery and lubrication and thus the life of the compressor (1) is increased.

Die Regelung wird so eingestellt, dass das Leistungsmaximum immer dem Verdampfer (4) (Fig. 7, 8, 9 Punkte 17) und nicht dem IWT (5) (18) zukommt (grösste mögliche Enthalpiestrecke bei Punkt 17).The control is set so that the maximum power always comes to the evaporator (4) (Figure 7, 8, 9 points 17) and not to the IWT (5) (18) (largest possible enthalpy distance at point 17).

Neu:New:

Neu an unserer Erfindung ist, dass ein Verdampfungssystem mit Trockenexpansion als überfluteter Verdampfer (4) eingesetzt wird, bei dem das Kältemittel den Verdampfer (4) in der ersten Stufe mit Flüssigkeitsanteilen verlässt (17, 19).What is new about our invention is that a dry expansion evaporation system is used as a flooded evaporator (4) in which the refrigerant leaves the evaporator (4) in the first stage with liquid fractions (17, 19).

Neu an unserer Erfindung ist, dass das Kältemittel als Flüssigkeits-/Gasgemisch mit hohem Gasanteil in eine zweite Verdampfungsstufe (5, 18, 20) eintritt (trockener Verdampfer), bei der eine Restverdampfung mit anschliessend hoher Überhitzung des Kältemittels (13) und einer gleichzeitigen Unterkühlung des flüssigen Kältemittels auf der zweiten Seite des IWT's (5) stattfindet (11).New to our invention is that the refrigerant enters as a liquid / gas mixture with a high gas content in a second evaporation stage (5, 18, 20) (dry evaporator), in which a residual evaporation followed by high superheating of the refrigerant (13) and a simultaneous Supercooling of the liquid refrigerant takes place on the second side of the IWT (5) (11).

Neu an unserer Erfindung ist, dass nach dem Verdampfungsbeginn (12) des Verdampfungsprozesses und nicht nach dem Verdampfungsende (13) geregelt wird.What is new about our invention is that it is regulated after the start of evaporation (12) of the evaporation process and not after the end of evaporation (13).

Neu an unserer Erfindung ist, dass durch diese Regelung mit unterschiedlichen Saugdampfüberhitzungen (13), je nach Flüssigkeitseintrittstemperatur (21) in den IWT (5), auf den Verdichter (1) gefahren wird.What is new about our invention is that this regulation with different suction steam superheating (13), depending on the liquid inlet temperature (21) in the IWT (5), on the compressor (1) is driven.

Neu an unserer Erfindung ist, dass die Saugdampfüberhitzung (13) möglichst gross gewählt wird.New to our invention is that the suction steam superheating (13) is chosen as large as possible.

Neu an unserer Erfindung ist, dass das verwendete, ausserhalb oder innerhalb des Verdampfers eingebaute Expansionsventil (3) die Kältemittelflüssigkeitstemperatur (11) vor dem Eintritt in das Einspritzventil (3) regelt.What is new about our invention is that the expansion valve (3) used outside or inside the evaporator regulates the refrigerant liquid temperature (11) before it enters the injection valve (3).

Neu an unserer Erfindung ist, dass das verwendete, ausserhalb oder innerhalb des Verdampfers (4) eingebaute Expansionsventil (3) die Saugdampftemperatur am Eintritt des Kältemittelverdichters (14) beschränkt und zugleich die Leistung der internen Unterkühlung (18) in Abhängigkeit der zur Verfügung stehenden Verdampferleistung (17) der ersten Stufe (4) regelt.What is new about our invention is that the expansion valve (3) used outside or inside the evaporator (4) restricts the suction steam temperature at the inlet of the refrigerant compressor (14) and at the same time limits the performance of the internal subcooling (18) as a function of the available evaporator capacity (17) of the first stage (4).

Aufzählung der Zeichnungen:List of drawings:

  • Fig. 1: Kältemittelkreislauf im lg p, h-Diagramm "Stand der Technik"1: refrigerant circuit in the lg p, h diagram "prior art"
  • Fig. 2: Kältemittelkreislauf "Stand der Technik"2: refrigerant circuit "prior art"
  • Fig. 3: Kältemittelkreislauf im lg p, h-Diagramm mit integrierten ApparatenFig. 3: Refrigerant circuit in lg p, h diagram with integrated apparatus
  • Fig. 4: Kältemittelkreislauf im 1g p, h-Diagramm mit IWT "Stand der Technik"4: Refrigerant circuit in 1g p, h diagram with IWT "prior art"
  • Fig. 5: Kältemittelkreislauf mit IWT "Stand der Technik"5: refrigerant circuit with IWT "state of the art"
  • Fig. 6: Kältemittelkreislauf mit IWT "Stand der Technik" im 1g p, h-Diagramm mit integrierten ApparatenFig. 6: refrigerant circuit with IWT "prior art" in 1g p, h diagram with integrated apparatus
  • Fig. 7: Kältemittelkreislauf im 1g p, h-Diagramm mit Zweistufenverdampfer "Patent"7: Refrigerant circuit in 1 g p, h diagram with two-stage evaporator "patent"
  • Fig. 8: Kältemittelkreislauf mit Zweistufenverdampfer "Patent"Fig. 8: Refrigerant circuit with two-stage evaporator "Patent"
  • Fig. 9: Kältemittelkreislauf im 1g p, h-Diagramm mit Zweistufenverdampfer "Patent" mit integrierten ApparatenFig. 9: Refrigerant circuit in 1g p, h diagram with two-stage evaporator "patent" with integrated apparatus
  • Fig. 10:Kältemittelkreislauf im 1g p, h-Diagramm mit Zweistufenverdampfer "Patent" mit integrierten Apparaten und Zweistufenunterkühlung (und Enthitzer)10: Refrigerant circuit in 1 g p, h diagram with two-stage evaporator "Patent" with integrated apparatus and two-stage subcooling (and desuperheater)
  • Fig. 11:Kältemittelkreislauf mit Verdampfer- und Messwertkombinationen (Beispiel)Fig. 11: Refrigerant circuit with evaporator and measured value combinations (example)
  • Fig. 12:Legende der Punkte aus den ZeichnungenFig. 12: Legend of the points from the drawings
Ausführung der Erfindung:Embodiment of the invention:

Ein Kältesystem bestehend im Wesentlichen aus einem oder mehreren:A refrigeration system consisting essentially of one or more:

Verflüssigern (2), Verdampfern (4), IWT' (5), Kältemittelverdichtern (1), Einspritzventilen (3), Kältemittel, kältetechnischen Hilfsstoffen und Öl.Condensers (2), evaporators (4), IWT '(5), refrigerant compressors (1), injectors (3), refrigerants, refrigerants and oils.

Optional weist ein Kältesystem je nach Anwendung zusätzlich einen oder mehrere der vorgenannten Komponenten und zusätzlich Enthitzer (24), einen oder mehrere Abwärmenutzungstauscher, weitere Unterkühler (25), Schaugläser (7), Trockner (6), Filter, Ventile (8), Sicherheitsapparaturen, Absperrapparaturen, Sammler, Ölpumpen, Verteilsysteme, Elektro-, Steuer- und Regelteile, kältetechnische Hilfsstoffe, etc. auf.Optionally, depending on the application, a refrigeration system additionally comprises one or more of the aforementioned components and additionally desupers (24), one or more waste heat utilization exchangers, further subcoolers (25), sight glasses (7), dryers (6), filters, valves (8), safety apparatuses , Absperrapparaturen, collectors, oil pumps, distribution systems, electrical and control parts, refrigeration aids, etc. on.

Bei der Montage des Einspritzventils (3) vor dem Verdampfer (4) wird der Messwert zur Saugdampfbegrenzung an der Saugleitung zum Kältemittelverdichter (1) abgenommen. Zur Regelung der Verdampfung (17, 19) werden die Messwerte der Kältemittelflüssigkeitstemperatur (11) und des Verdampfereintrittsdrucks (12) verwendet.When mounting the injection valve (3) before the evaporator (4), the measured value for Saugdampfbegrenzung on the suction line to the refrigerant compressor (1) is removed. For controlling the evaporation (17, 19), the measured values of the refrigerant liquid temperature (11) and the evaporator inlet pressure (12) are used.

Claims (9)

  1. A method for the regulation (closed-loop control) of evaporators (4, 12) in refrigeration systems, with which the refrigerant is undercooled in a condenser (2, 25) and with which an internal heat exchanger (IWT (interner Wärmetauscher)) is used on the one hand between the evaporator (4) and a condenser (16), and on the other hand between a condenser (2, 25) and an injection valve (3), characterised in that the evaporation pressure (12) at the entry of the evaporator (4, 12) is used as a first controlled variable, and the refrigerant subcooling temperature (11) in front of the injection valve (3) is used as a second controlled variable, and the beginning of the evaporation (12) is fixed and regulated by way of this.
  2. A method according to claim 1, characterised in that as a further reading, the suction vapour temperature (13/14) at the entry into the condenser (1) optimises this regulation and ensures the protection of the condenser (1).
  3. A method according to claim 1 or 2, characterised in that further readings such as the hot gas temperature (15) at the exit of the condenser (1), the condenser oil temperature (16), the suction pressure at the condenser (23) and/or the high pressure (22) in front of the injection valve (3) or after the condenser (1), are used for optimising the regulation or for the protection of the condenser.
  4. A method according to one of the claims 1 to 3, characterised in that one regulates (12) near to the left limit curve of the lg(p, h) diagram for the refrigerant.
  5. A method according to one of the claims 1 to 4, characterised in that by way of this type of regulation, the evaporator (4) is flooded and the degree of flooding is determined and at the same time the refrigerant suction vapour temperature and refrigerant fluid temperature (13/11) are controlled and regulated.
  6. A method according to one of the claims 1 to 5, characterised in that the reading of the suction vapour temperature (13/14) in front of the condenser (1), or the hot gas temperature (15) at the exit of the condenser (1), or the condenser oil temperature (16) overcontrols the evaporation control (11, 12) and keeps the suction vapour temperature (14) constant to an optimal value and/or maximal value, in a manner which is dependent on the condenser.
  7. A method according to one of the claims 1 to 6, characterised in that the optimum of the process, by way of the maximal utilisation of the enthalpy in the evaporator (4) between the left and right limit curve of the lg(p, h) diagram for the refrigerant, and, depending on the temperature level of the IWTs (5, 21), with an overheating portion in the evaporator (4), always benefits the evaporator (4) and not the IWT (5).
  8. A method according to one of the claims 1 to 7, characterised in that an evaporator (4) is connected to an IWT (5), or several evaporators (4) are connected to an IWT (5), or several evaporators (4) are connected to several IWTs (5), into a refrigeration system.
  9. A method according to claim 8, characterised in that the injection valves (3) and the system are regulated with a reduced number of readings (9, 10, 11, 12, 13, 14, 15, 16, 22, 23) depending on the combination of evaporators (4), IWTs (5), injection valves (3) and condensers (1).
EP02782599A 2002-12-11 2002-12-11 Evaporation process control for use in refrigeration technology Expired - Lifetime EP1570215B1 (en)

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US20060242974A1 (en) 2006-11-02
AU2002347179A1 (en) 2004-06-30
EP1570215A1 (en) 2005-09-07
WO2004053406A1 (en) 2004-06-24
US7665321B2 (en) 2010-02-23
ATE380321T1 (en) 2007-12-15
DE50211329D1 (en) 2008-01-17
ES2298405T3 (en) 2008-05-16

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