EP0866291A1 - Compression heat pump or compression cooling machine and control method therefor - Google Patents

Compression heat pump or compression cooling machine and control method therefor Download PDF

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Publication number
EP0866291A1
EP0866291A1 EP98104767A EP98104767A EP0866291A1 EP 0866291 A1 EP0866291 A1 EP 0866291A1 EP 98104767 A EP98104767 A EP 98104767A EP 98104767 A EP98104767 A EP 98104767A EP 0866291 A1 EP0866291 A1 EP 0866291A1
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Prior art keywords
sensor
compression
temperature
heat pump
condenser
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EP98104767A
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German (de)
French (fr)
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EP0866291B1 (en
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Andreas Bangheri
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Krimbacher Peter
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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
    • F25B30/00—Heat pumps
    • F25B30/02—Heat pumps of the compression type
    • 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
    • F25B41/33—Expansion valves with the valve member being actuated by the fluid pressure, e.g. by the pressure of the refrigerant
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19—Pressures
    • F25B2700/195—Pressures of the condenser
    • 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
    • F25B2700/2116—Temperatures of a condenser
    • F25B2700/21161—Temperatures of a condenser of the fluid heated by the condenser
    • 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
    • F25B2700/21163—Temperatures of a condenser of the refrigerant at the outlet of the condenser

Definitions

  • the invention relates to a compression heat pump or compression refrigeration machine according to the preamble of claim 1.
  • the invention further relates to a Method for controlling such a compression heat pump or compression refrigeration machine.
  • Devices according to the preamble of claim 1 are from DE-OS 43 03 533 and WO 96/24016. With these, the regulation is primarily also based on the evaporator superheat temperature, as a secondary
  • the control parameter is also the hot gas temperature, i.e. the temperature of the Refrigerant measured in the area between the compressor and condenser, whereby at an inadmissibly high hot gas temperature, the expansion valve is opened further and the hot gas temperature is thereby lowered.
  • a disadvantage of the known control of the expansion valve based on the evaporator superheating temperature is that the temperature differences used for the control are only very small, so that the regulation is usually only very rough takes place because of a more precise regulation that the facility becomes too expensive would lead.
  • the object of the invention is a compression heat pump or compression refrigerator to provide the type mentioned at the outset, which without price increases allows the apparatus to control the expansion valve much more precisely. According to the invention, this is achieved by a compression heat pump or a compression refrigerator with the features of claim 1.
  • the device according to the invention is therefore to regulate the expansion valve arranged next to the first in the area between the compressor and the condenser Temperature sensor provided a second sensor that detects a value that is a direct one Represents a measure of the condensation temperature. Taking a direct measure for that Condensation temperature is understood to mean that for a given apperative Arrangement from the value recorded by the second sensor without using further measured variables reflecting the current state of the system at least approximately the condensation temperature can be determined.
  • the second sensor designed as a pressure sensor and in the high-pressure area of the refrigerant circuit thus arranged in the area between the compressor and expansion valve. From the dated The pressure recorded by the sensor will directly maintain the condensation temperature.
  • the second sensor as a temperature sensor and to be placed directly on the capacitor, in an area of the same, in which, as far as possible, approximately the condensation temperature under all operating conditions appropriate temperature is present.
  • the second sensor is one in the flow line of the heating circuit arranged temperature sensor.
  • the one recorded by this sensor Temperature deviates only a few degrees Kelvin from the condensation temperature and can use a correction factor in the condensation temperature can be converted.
  • the controlled variable varies significantly more than with a control
  • the expansion valve can be regulated based on the evaporator superheating temperature in the device according to the invention without large apparatus Additional effort can be carried out much more precisely.
  • Controlled variable the difference between the two determined by the two sensors Temperature values used.
  • the refrigerant circuit of the compression heat pump shown schematically in FIG. 1 comprises an evaporator 1, a compressor 2, a condenser 3 and an expansion valve 4.
  • the refrigerant is evaporated in the evaporator, one Amount of heat 5 is absorbed by the environment. That compressed by the compressor 2 Hot gas condenses in the condenser designed as a heat exchanger, wherein an amount of heat 6 is given to the heating circuit 7.
  • An optimal efficiency of the compression heat pump is achieved if that Refrigerant in the evaporator 1 is overheated as little as possible.
  • a small amount of non-evaporated refrigerant is irrelevant since the compressor is cooled by suction gas Compressor is formed, i.e. Engine heat is drawn to the intake gas emitted, remnants of coolant are evaporated.
  • the refrigerant however not heated enough when liquid refrigerant gets into the compressor oil and the oil in the compressor starts to foam. In this case, the supply of Refrigerant in the evaporator 1 is reduced by throttling the expansion valve 4 will.
  • a control device 8 is provided for exact control of the expansion valve 4, which is connected to a temperature sensor 9 and a second sensor 10.
  • the first sensor 9 is used to detect the hot gas temperature of the refrigerant in the area between compressor 2 and condenser 3.
  • the second sensor 10 is in the high pressure range, which extends from the compressor 2 to the expansion valve 4, arranged and is designed as a pressure sensor.
  • the value of the detected by the second sensor 10 Pressure corresponds to the condensation pressure of the refrigerant in the condenser 3 and can be converted directly into the condensation temperature in the condenser.
  • the actual value of the controlled variable is determined in the control device 8 from the difference between the temperatures determined by the two sensors.
  • This actual value lies, for example above a predetermined target value, the expansion valve 4 of the control device 8 opened further.
  • This causes more refrigerant to flow through the Evaporator, resulting in a lower vaporization temperature of the gaseous Refrigerant in the suction gas line 11 and thus also a lower hot gas temperature of the refrigerant in the area between compressor 2 and condenser 3
  • the change in vaporization superheat temperature is significant is less than the change in hot gas temperature.
  • the target value of the difference between the hot gas temperature determined by the first sensor 9 and the condensation temperature determined via the second sensor 10 becomes dependent on the condensation temperature determined via the second sensor 10 set, preferably proportional to this.
  • the reasons for introducing such a dependency are different Amounts of heat at different condensation temperatures in the condenser 3 must be dissipated and the resulting different requirements to the capacitor.
  • the hot gas is initially in one in the condenser in the first heating zone (e.g. from 70 to 50 ° C), then in a condensation zone condenses (e.g.
  • the second sensor 10 is designed as a temperature sensor and in the flow line 13 of the Heating circuit 7 is arranged in the region of the heat exchanger outlet.
  • the second Sensor 10 recorded temperature differs from the condensation temperature only by a few degrees Kelvin and can be entered into this by means of a constant Correction factor (which essentially depends on the refrigerant used and on the Dimensioning of the heat exchanger depends) can be converted.

Abstract

A compression heat pump or compression cold energy machine has a coolant circuit which comprises an evaporator(1), a compressor (2), a condenser (3) and a controllable expansion valve (4). It is controlled by a control device (8) which is connected to a temperature sensor (9) located in the region between the compressor and the condenser and to a second sensor (10). The second sensor determines a value which represents a direct measurement for the condensation temperature in the condenser. The second sensor is a pressure sensor and is located in the high pressure region of the coolant circuit between the compressor and the expansion valve. The condenser of the compression heat pump is designed as a heat exchanger to transmit heat given up from the coolant to a heating medium of a heating circuit (7).

Description

Die Erfindung betrifft eine Kompressionswärmepumpe oder Kompressionskältemaschine nach dem Oberbegriff des Anspruchs 1. Weiters betrifft die Erfindung ein Verfahren zur Regelung einer solchen Kompressionswärmepumpe oder Kompressionskältemaschine.The invention relates to a compression heat pump or compression refrigeration machine according to the preamble of claim 1. The invention further relates to a Method for controlling such a compression heat pump or compression refrigeration machine.

Bei bekannten Kompressionswärmepumpen oder Kompressionskältemaschinen, welche ein regelbares Expansionsventil aufweisen, wird dieses in Abhängigkeit von der Verdampfungs-Überhitzungstemperatur geregelt, welche von einem Temperaturfühler im Bereich zwischen Verdampfer und Verdichter erfaßt wird.In known compression heat pumps or compression refrigeration machines, which have an adjustable expansion valve, this is dependent on the Evaporation superheat temperature controlled by a temperature sensor is detected in the area between the evaporator and the compressor.

Einrichtungen gemäß dem Oberbegriff des Anspruchs 1 sind aus der DE-OS 43 03 533 und der WO 96/24016 bekannt. Bei diesen wird zwar die Regelung primär ebenfalls anhand der Verdampfer-Überhitzungstemperatur durchgeführt, als sekundärer Regelparameter wird aber zusätzlich die Heißgastemperatur, d.h. die Temperatur des Kältemittels im Bereich zwischen Verdichter und Kondensator gemessen, wobei bei einer unzulässig hohen Heißgastemperatur das Expansionsventil weiter geöffnet wird und die Heißgastemperatur dadurch abgesenkt wird.Devices according to the preamble of claim 1 are from DE-OS 43 03 533 and WO 96/24016. With these, the regulation is primarily also based on the evaporator superheat temperature, as a secondary The control parameter is also the hot gas temperature, i.e. the temperature of the Refrigerant measured in the area between the compressor and condenser, whereby at an inadmissibly high hot gas temperature, the expansion valve is opened further and the hot gas temperature is thereby lowered.

Nachteilig an der bekannten Regelung des Expansionsventils anhand der Verdampfer-Überhitzungstemperatur ist es, daß die für die Regelung herangezogenen Temperaturunterschiede nur sehr gering sind, sodaß die Regelung normalerweise nur sehr grob erfolgt, da eine genauere Regelung zu einer zu starken Verteuerung der Einrichtung führen würde.A disadvantage of the known control of the expansion valve based on the evaporator superheating temperature is that the temperature differences used for the control are only very small, so that the regulation is usually only very rough takes place because of a more precise regulation that the facility becomes too expensive would lead.

Aufgabe der Erfindung ist es, eine Kompressionswärmepumpe oder Kompressionskältemaschine der eingangs genannten Art bereitzustellen, welche ohne Verteuerung der Apparatur eine wesentlich genauere Regelung des Expansionsventils ermöglicht. Erfindungsgemäß gelingt dies durch eine Kompressionswärmepumpe oder Kompressionskältemaschine mit den Merkmalen des Anspruchs 1.The object of the invention is a compression heat pump or compression refrigerator to provide the type mentioned at the outset, which without price increases allows the apparatus to control the expansion valve much more precisely. According to the invention, this is achieved by a compression heat pump or a compression refrigerator with the features of claim 1.

Bei der erfindungsgemäßen Einrichtung ist also zur Regelung des Expansionsventils neben dem ersten im Bereich zwischen Verdichter und Kondensator angeordneten Temperaturfühler ein zweiter Fühler vorgesehen, der einen Wert erfaßt, der ein direktes Maß für die Kondensationstemperatur darstellt. Unter einem direkten Maß für die Kondensationstemperatur wird dabei verstanden, daß bei gegebener apperativer Anordnung aus dem vom zweiten Fühler erfaßten Wert ohne Hinzuziehung von weiteren den momentanen Zustand des Systems wiedergebenden Meßgrößen zumindest annähernd die Kondensationstemperatur ermittelbar ist.In the device according to the invention is therefore to regulate the expansion valve arranged next to the first in the area between the compressor and the condenser Temperature sensor provided a second sensor that detects a value that is a direct one Represents a measure of the condensation temperature. Taking a direct measure for that Condensation temperature is understood to mean that for a given apperative Arrangement from the value recorded by the second sensor without using further measured variables reflecting the current state of the system at least approximately the condensation temperature can be determined.

In einem ersten bevorzugten Ausführungsbeispiel der Erfindung ist der zweite Fühler als Druckaufnehmer ausgebildet und im Hochdruckbereich des Kältemittelkreislaufs also im Bereich zwischen Verdichter und Expansionsventil angeordnet. Aus dem vom Fühler aufgenommenen Druck wird direkt die Kondensationstemperatur erhalten.In a first preferred embodiment of the invention, the second sensor designed as a pressure sensor and in the high-pressure area of the refrigerant circuit thus arranged in the area between the compressor and expansion valve. From the dated The pressure recorded by the sensor will directly maintain the condensation temperature.

Denkbar und möglich wäre es auch, den zweiten Fühler als Temperaturfühler auszubilden und direkt am Kondensator anzuordnen, und zwar in einem Bereich desselben, in dem möglichst unter allen Betriebsbedingungen eine etwa der Kondensationstemperatur entsprechende Temperatur vorliegt.It would also be conceivable and possible to design the second sensor as a temperature sensor and to be placed directly on the capacitor, in an area of the same, in which, as far as possible, approximately the condensation temperature under all operating conditions appropriate temperature is present.

In einem weiteren bevorzugten Ausführungsbeispiel der Erfindung, wenn es sich bei der erfindungsgemäßen Einrichtung um eine Wärmepumpe handelt, bei der der Kondensator als Wärmetauscher ausgebildet ist, ist der zweite Fühler ein in der Verlaufleitung des Heizkreises angeordneter Temperaturfühler. Die von diesem Fühler aufgenommene Temperatur weicht nur um wenige Grad Kelvin von der Kondensationstemperatur ab und kann über einen Korrekturfaktor in die Kondensationstemperatur umgerechnet werden.In a further preferred embodiment of the invention, if it is the device according to the invention is a heat pump in which the condenser is designed as a heat exchanger, the second sensor is one in the flow line of the heating circuit arranged temperature sensor. The one recorded by this sensor Temperature deviates only a few degrees Kelvin from the condensation temperature and can use a correction factor in the condensation temperature can be converted.

Da bei einer Regelung des Expansionsventils anhand der Heißgastemperatur und der Kondensationstemperatur die Regelgröße wesentlich stärker variiert als bei einer Regelung anhand der Verdampfer-Überhitzungstemperatur kann die Regelung des Expansionsventils bei der erfindungsgemäßen Einrichtung ohne großen apparativen Mehraufwand wesentlich genauer durchgeführt werden. Vorteilhafterweise wird als Regelgröße die Differenz zwischen den beiden über die beiden Fühler ermittelten Temperaturwerten verwendet. Since in a control of the expansion valve based on the hot gas temperature and Condensation temperature, the controlled variable varies significantly more than with a control The expansion valve can be regulated based on the evaporator superheating temperature in the device according to the invention without large apparatus Additional effort can be carried out much more precisely. Advantageously, as Controlled variable the difference between the two determined by the two sensors Temperature values used.

Weitere Vorteile und Einzelheiten der Erfindung werden im folgenden anhand der beiliegenden Zeichnung erläutert.Further advantages and details of the invention are described below with reference to the accompanying Drawing explained.

In dieser zeigt

die Fig. 1
eine schematische Darstellung eines ersten Ausführungsbeispieles einer erfindungsgemäßen Kompressionswärmepumpe und
die Fig. 2
eine schematische Darstellung eines zweiten Ausführungsbeispieles einer erfindungsgemäßen Kompressionswärmepumpe.
In this shows
1
a schematic representation of a first embodiment of a compression heat pump according to the invention and
2
is a schematic representation of a second embodiment of a compression heat pump according to the invention.

Der Kältemittelkreislauf der in der Fig. 1 schematisch dargestellten Kompressionswärmepumpe umfaßt einen Verdampfer 1, einen Verdichter 2, einen Kondensator 3 und ein Expansionsventil 4. Im Verdampfer wird das Kältemittel verdampft, wobei eine Wärmemenge 5 von der Umgebung aufgenommen wird. Das vom Verdichter 2 komprimierte Heißgas kondensiert in dem als Wärmetauscher ausgebildeten Kondensator, wobei eine Wärmemenge 6 an den Heizkreislauf 7 abgegeben wird.The refrigerant circuit of the compression heat pump shown schematically in FIG. 1 comprises an evaporator 1, a compressor 2, a condenser 3 and an expansion valve 4. The refrigerant is evaporated in the evaporator, one Amount of heat 5 is absorbed by the environment. That compressed by the compressor 2 Hot gas condenses in the condenser designed as a heat exchanger, wherein an amount of heat 6 is given to the heating circuit 7.

Ein optimaler Wirkungsgrad der Kompressionswärmepumpe wird erreicht, wenn das Kältemittel im Verdampfer 1 möglichst wenig überhitzt wird. Eine geringe Menge von nichtverdampftem Kältemittel ist dabei unerheblich, da der Verdichter als sauggasgekühlter Kompressor ausgebildet ist, d.h. Motorwärme wird an das angesaugte Gas abgegeben, wobei Reste von Kühlmittel verdampft werden. Das Kältemittel wird aber zuwenig erwärmt, wenn flüssiges Kältemittel in das Öl des Kompressors gelangt und das Öl im Kompressor aufzuschäumen beginnt. In diesem Fall muß die Zufuhr von Kältemittel in den Verdampfer 1 durch Drosselung des Expansionsventils 4 verringert werden.An optimal efficiency of the compression heat pump is achieved if that Refrigerant in the evaporator 1 is overheated as little as possible. A small amount of non-evaporated refrigerant is irrelevant since the compressor is cooled by suction gas Compressor is formed, i.e. Engine heat is drawn to the intake gas emitted, remnants of coolant are evaporated. The refrigerant, however not heated enough when liquid refrigerant gets into the compressor oil and the oil in the compressor starts to foam. In this case, the supply of Refrigerant in the evaporator 1 is reduced by throttling the expansion valve 4 will.

Zur exakten Regelung des Expansionsventils 4 ist eine Regeleinrichtung 8 vorgesehen, die mit einem Temperaturfühler 9 und einem zweiten Fühler 10 verbunden ist. Der erste Fühler 9 dient zur Erfassung der Heißgastemperatur des Kältemittels im Bereich zwischen Verdichter 2 und Kondensator 3. Der zweite Fühler 10 ist im Hochdruckbereich, der vom Verdichter 2 bis zum Expansionsventil 4 reicht, angeordnet und ist als Druckaufnehmer ausgebildet. Der vom zweiten Fühler 10 erfaßte Wert des Druckes entspricht dem Kondensationsdruck des Kältemittels im Kondensator 3 und kann direkt in die Kondensationstemperatur im Kondensator umgewandelt werden. Der Istwert der Regelgröße wird in der Regeleinrichtung 8 aus der Differenz zwischen den von den beiden Fühlern ermittelten Temperaturen bestimmt. Liegt dieser Istwert beispielsweise über einem vorgegebenen Sollwert, so wird das Expansionsventil 4 von der Regeleinrichtung 8 weiter geöffnet. Dadurch strömt mehr Kältemittel durch den Verdampfer, was eine geringere Verdampfungs-Überhitzungstemperatur des gasförmigen Kältemittels in der Sauggasleitung 11 und damit auch eine geringere Heißgastemperatur des Kältemittels im Bereich zwischen Verdichter 2 und Kondensator 3 zur Folge hat, wobei die Änderung der Verdampfungs-Überhitzungstemperatur wesentlich geringer ist als die Änderung der Heißgastemperatur.A control device 8 is provided for exact control of the expansion valve 4, which is connected to a temperature sensor 9 and a second sensor 10. The first sensor 9 is used to detect the hot gas temperature of the refrigerant in the area between compressor 2 and condenser 3. The second sensor 10 is in the high pressure range, which extends from the compressor 2 to the expansion valve 4, arranged and is designed as a pressure sensor. The value of the detected by the second sensor 10 Pressure corresponds to the condensation pressure of the refrigerant in the condenser 3 and can be converted directly into the condensation temperature in the condenser. Of the The actual value of the controlled variable is determined in the control device 8 from the difference between the temperatures determined by the two sensors. This actual value lies, for example above a predetermined target value, the expansion valve 4 of the control device 8 opened further. This causes more refrigerant to flow through the Evaporator, resulting in a lower vaporization temperature of the gaseous Refrigerant in the suction gas line 11 and thus also a lower hot gas temperature of the refrigerant in the area between compressor 2 and condenser 3 As a result, the change in vaporization superheat temperature is significant is less than the change in hot gas temperature.

Der Sollwert der Differenz zwischen der vom ersten Fühler 9 ermittelten Heißgastemperatur und der über den zweiten Fühler 10 ermittelten Kondensationstemperatur wird dabei in Abhängigkeit von der über den zweiten Fühler 10 ermittelten Kondensationstemperatur eingestellt, vorzugsweise proportional zu dieser. Beispielsweise beträgt der Sollwert der Temperaturdifferenz bei einer Kondensationstemperatur von 25°C 17 K, während er bei einer Kondensationstemperatur von 50°C 25 K beträgt. Der Grund für die Einführung einer solchen Abhängigkeit sind die unterschiedlichen Wärmemengen, die bei unterschiedlichen Kondensationstemperaturen im Kondensator 3 abgeführt werden müssen und die daraus folgenden unterschiedlichen Anforderungen an den Kondensator. Im Kondensator wird ja das Heißgas zunächst in einer ersten Enthitzungszone enthitzt (z.B. von 70 auf 50°C), anschließend in einer Kondensationszone kondensiert (z.B. bei 50°C) und schließlich in einer Unterkühlungszone unterkühlt (z.B. von 50 auf 46°C). Bei niedrigen Temperaturen liegt eine hohe Leistung am Kondensator 3 an und durch einen geringeren Sollwert der Temperaturdifferenz wird die Kondensationszone vergrößert (auf Kosten der Enthitzungszone), während sie bei höheren Temperaturen, bei denen eine niedrigere Leistung anliegt, mittels eines größeren Sollwertes der Temperaturdifferenz verkleinert wird (und die Enthitzungszone vergrößert).The target value of the difference between the hot gas temperature determined by the first sensor 9 and the condensation temperature determined via the second sensor 10 becomes dependent on the condensation temperature determined via the second sensor 10 set, preferably proportional to this. For example the setpoint of the temperature difference at a condensation temperature of 25 ° C 17 K, while it is 25 K at a condensation temperature of 50 ° C. Of the The reasons for introducing such a dependency are different Amounts of heat at different condensation temperatures in the condenser 3 must be dissipated and the resulting different requirements to the capacitor. The hot gas is initially in one in the condenser in the first heating zone (e.g. from 70 to 50 ° C), then in a condensation zone condenses (e.g. at 50 ° C) and finally in a sub-cooling zone supercooled (e.g. from 50 to 46 ° C). There is high performance at low temperatures at the capacitor 3 and by a lower setpoint of the temperature difference the condensation zone is enlarged (at the expense of the desuperheating zone) while it at higher temperatures, at which a lower power is applied, by means of a larger setpoint of the temperature difference is reduced (and the desuperheating zone enlarged).

Der einzige Unterschied des Ausführungsbeispieles nach Fig. 2 besteht darin, daß der zweite Fühler 10 als Temperaturfühler ausgebildet ist und in der Vorlaufleitung 13 des Heizkreises 7 im Bereich des Wärmetauscherausgangs angeordnet ist. Die vom zweiten Fühler 10 aufgenommene Temperatur unterscheidet sich von der Kondensationstemperatur nur um wenige Grad Kelvin und kann in diese mittels eines konstanten Korrekturfaktors (der im wesentlichen vom verwendeten Kältemittel und von der Dimensionierung des Wärmetauschers abhängt) umgerechnet werden.The only difference of the embodiment of FIG. 2 is that the second sensor 10 is designed as a temperature sensor and in the flow line 13 of the Heating circuit 7 is arranged in the region of the heat exchanger outlet. The second Sensor 10 recorded temperature differs from the condensation temperature only by a few degrees Kelvin and can be entered into this by means of a constant Correction factor (which essentially depends on the refrigerant used and on the Dimensioning of the heat exchanger depends) can be converted.

Claims (7)

Kompressionswärmepumpe oder Kompressionskältemaschine mit einem Kältemittelkreislauf, der einen Verdampfer (1), einen Verdichter (2), einen Kondensator (3) und ein regelbares Expansionsventil (4) umfaßt, welches von einer Regeleinrichtung (8) angesteuert wird, die mit einem im Bereich (12) zwischen Verdichter (2) und Kondensator (3) angeordneten Temperaturfühler (9) und einem zweiten Fühler (10) verbunden ist, dadurch gekennzeichnet, daß der zweite Fühler (10) einen Wert erfaßt, der ein direktes Maß für die Kondensationstemperatur im Kondensator (3) darstellt.Compression heat pump or compression chiller with a refrigerant circuit, an evaporator (1), a compressor (2), a condenser (3) and a controllable expansion valve (4), which by a control device (8) is controlled with one in the area (12) between the compressor (2) and capacitor (3) arranged temperature sensor (9) and a second Sensor (10) is connected, characterized in that the second sensor (10) detects a value that is a direct measure of the condensation temperature in the condenser (3). Kompressionswärmepumpe oder Kompressionskältemaschine nach Anspruch 1, dadurch gekennzeichnet, daß der zweite Fühler (10) ein Druckaufnehmer ist und im Hochdruckbereich des Kältemittelkreislaufes zwischen Verdichter (2) und Expansionsventil (4) angeordnet ist.Compression heat pump or compression refrigerator according to claim 1, characterized in that the second sensor (10) is a pressure sensor and in the high pressure area of the refrigerant circuit between the compressor (2) and Expansion valve (4) is arranged. Kompressionswärmepumpe oder Kompressionskältemaschine nach Anspruch 1, dadurch gekennzeichnet, daß der Kondensator (3) der Kompressionswärmepumpe als Wärmetauscher zur Übertragung der vom Kältemittel abgegebenen Wärme (6) auf ein Heizmittel eines Heizkreises (7) ausgebildet ist und der zweite Fühler (10) als Temperaturfühler ausgebildet ist, der in der Vorlaufleitung (13) des Heizkörpers, vorzugsweise im Bereich des Wärmetauscherausganges angeordnet ist.Compression heat pump or compression refrigerator according to claim 1, characterized in that the condenser (3) of the compression heat pump as a heat exchanger for the transfer of the refrigerant Heat (6) is formed on a heating medium of a heating circuit (7) and the second Sensor (10) is designed as a temperature sensor in the flow line (13) of the Radiator, preferably arranged in the area of the heat exchanger outlet is. Kompressionswärmepumpe oder Kompressionskältemaschine nach Anspruch 1, dadurch gekennzeichnet, daß der zweite Fühler (10) ein Temperaturfühler ist und am Kondensator (3) angeordnet ist.Compression heat pump or compression refrigerator according to claim 1, characterized in that the second sensor (10) is a temperature sensor and is arranged on the capacitor (3). Verfahren zur Regelung einer Kompressionswärmepumpe oder Kompressionskältemaschine nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, daß die Regelgroße aus der Differenz zwischen der vom ersten Fühler (9) erfaßten Temperatur und einer Temperatur, die dem vom zweiten Fühler erfaßten Wert entspricht und ein direktes Maß für die Kondensationstemperatur im Kondensator darstellt, gebildet wird. Method of controlling a compression heat pump or a compression refrigerator according to one of claims 1 to 4, characterized in that the controlled variable from the difference between that detected by the first sensor (9) Temperature and a temperature equal to the value detected by the second sensor corresponds and a direct measure of the condensation temperature in the condenser represents is formed. Verfahren nach Anspruch 5, dadurch gekennzeichnet, daß der Sollwert der Regelgröße von dem vom zweiten Fühler (10) erfaßten Wert abhängig ist, vorzugsweise mit steigendem vom zweiten Fühler erfaßten Wert zunimmt.A method according to claim 5, characterized in that the setpoint of the controlled variable is dependent on the value detected by the second sensor (10), preferably increases with the value detected by the second sensor. Verfahren nach Anspruch 6, dadurch gekennzeichnet, daß der Sollwert der Regelgröße etwa proportional zu dem vom zweiten Fühler (10) ermittelten Wert ist.Method according to claim 6, characterized in that the setpoint of the controlled variable is approximately proportional to the value determined by the second sensor (10).
EP98104767A 1997-03-18 1998-03-17 Compression heat pump or compression cooling machine and control method therefor Expired - Lifetime EP0866291B1 (en)

Applications Claiming Priority (3)

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AT46797 1997-03-18
AT467/97 1997-03-18
AT46797 1997-03-18

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EP1134518A2 (en) * 2000-03-15 2001-09-19 Carrier Corporation Method for controlling an electronic expansion valve based on cooler pinch and discharge superheat
EP1148307A2 (en) * 2000-04-19 2001-10-24 Denso Corporation Heat-pump water heater
WO2004097308A1 (en) * 2003-04-30 2004-11-11 Lg Electronics, Inc. Apparatus for controlling operation of outdoor unit and its method
CN1329695C (en) * 2003-05-15 2007-08-01 乐金电子(天津)电器有限公司 Apparatus and method for safety operation of outdoor unit

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DE102013004786A1 (en) 2013-03-20 2014-09-25 SKA GmbH Gesellschaft für Kältetechnik Compression heat pump or compression refrigeration machine and method for Regelug the same
DE102020122713A1 (en) 2020-08-31 2022-03-03 Andreas Bangheri Heat pump and method for operating a heat pump

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Publication number Priority date Publication date Assignee Title
EP1134518A2 (en) * 2000-03-15 2001-09-19 Carrier Corporation Method for controlling an electronic expansion valve based on cooler pinch and discharge superheat
EP1134518A3 (en) * 2000-03-15 2002-01-16 Carrier Corporation Method for controlling an electronic expansion valve based on cooler pinch and discharge superheat
EP1148307A2 (en) * 2000-04-19 2001-10-24 Denso Corporation Heat-pump water heater
EP1148307A3 (en) * 2000-04-19 2002-01-16 Denso Corporation Heat-pump water heater
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CN1311205C (en) * 2003-04-30 2007-04-18 Lg电子株式会社 Apparatus and method for controlling operation of outdoor unit
CN1329695C (en) * 2003-05-15 2007-08-01 乐金电子(天津)电器有限公司 Apparatus and method for safety operation of outdoor unit

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