EP0866291B1 - 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 PDFInfo
- Publication number
- EP0866291B1 EP0866291B1 EP98104767A EP98104767A EP0866291B1 EP 0866291 B1 EP0866291 B1 EP 0866291B1 EP 98104767 A EP98104767 A EP 98104767A EP 98104767 A EP98104767 A EP 98104767A EP 0866291 B1 EP0866291 B1 EP 0866291B1
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- EP
- European Patent Office
- Prior art keywords
- sensor
- compression
- temperature
- heat pump
- condenser
- 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
Links
- 230000006835 compression Effects 0.000 title claims abstract description 30
- 238000007906 compression Methods 0.000 title claims abstract description 30
- 238000000034 method Methods 0.000 title claims description 5
- 238000001816 cooling Methods 0.000 title description 2
- 238000009833 condensation Methods 0.000 claims abstract description 21
- 230000005494 condensation Effects 0.000 claims abstract description 21
- 238000010438 heat treatment Methods 0.000 claims abstract description 9
- 239000002826 coolant Substances 0.000 claims abstract description 7
- 239000003990 capacitor Substances 0.000 claims description 4
- 230000001419 dependent effect Effects 0.000 claims description 3
- 230000001105 regulatory effect Effects 0.000 claims description 2
- 230000001960 triggered effect Effects 0.000 claims 1
- 238000005259 measurement Methods 0.000 abstract 1
- 239000003507 refrigerant Substances 0.000 description 15
- 238000005057 refrigeration Methods 0.000 description 3
- 238000009834 vaporization Methods 0.000 description 2
- 230000008016 vaporization Effects 0.000 description 2
- 239000010725 compressor oil Substances 0.000 description 1
- 230000001276 controlling effect Effects 0.000 description 1
- 238000001704 evaporation Methods 0.000 description 1
- 230000008020 evaporation Effects 0.000 description 1
- 239000006260 foam Substances 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 239000003921 oil Substances 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- 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 apparatus 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 become.
- a control device 8 is provided, which is connected to a temperature sensor 9 and a second sensor 10.
- the first sensor 9 is used to record the hot gas temperature of the refrigerant in the area between the compressor 2 and the condenser 3.
- the second sensor 10 is arranged in the high pressure area, which extends from the compressor 2 to the expansion valve 4, and is designed as a pressure sensor.
- the value of the pressure detected by the second sensor 10 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.
- the expansion valve 4 is opened further by the control device 8.
- the control device 8 As a result, more refrigerant flows through the evaporator, which results in a lower vaporization superheating 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 the compressor 2 and the condenser 3, the change in the vaporization superheating temperature being substantially less is 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 condensed (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.
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Fluid Mechanics (AREA)
- Heat-Pump Type And Storage Water Heaters (AREA)
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
- Air Conditioning Control Device (AREA)
Abstract
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 apparativer 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 apparatus 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.
- 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 become.
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.For exact control of the expansion valve 4, a control device 8 is provided, which is connected to a temperature sensor 9 and a
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
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
Claims (7)
- Compression heat pump or compression refrigerating machine having a coolant cycle comprising an evaporator (1), a compressor (2), a condenser (3) and an adjustable expansion valve (4), which is triggered by a control device (8), which is connected to a temperature sensor (9) disposed between the compressor (2) and condenser (3) and to second sensor (10), characterised in that the second sensor (10) detects a value which is a direct measure of the condensation temperature in the capacitor (3).
- Compression heat pump or compression refrigerating machine according to claim 1, characterised in that the second sensor (10) is a pressure sensor and is disposed in the high-pressure region of the coolant cycle between the compressor (2) and the expansion valve (4).
- Compression heat pump or compression refrigerating machine according to claim 1, characterised in that the condenser (3) of the compression heat pump is formed as a heat exchanger for transferring the heat (6) discharged from the coolant to a heating means of a heating circuit (7), and the second sensor (10) is in the form of a temperature sensor, which is disposed in the advance line (13) of the heating element, preferably in the region of the heat exchanger output.
- Compression heat pump or compression refrigerating machine according to claim 1, characterised in that the second sensor (10) is a temperature sensor and is disposed at the condenser (3).
- Method of regulating a compression heat pump or compression refrigerating machine according to one of claims 1 to 4, characterised in that the control variable is formed from the differential between the temperature detected by the first sensor (9) and a temperature corresponding to the value detected by the second sensor (10) and representing a direct measure of the condensation temperature in the condenser.
- Method according to claim 5, characterised in that the setpoint value of the control variable is dependent on the value detected by the second sensor (10), and preferably increases as the value detected by the second sensor rises.
- Method according to claim 6, characterised In that the setpoint value of the control variable is roughly proportional to the value determined by the second sensor (10).
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
AT46797 | 1997-03-18 | ||
AT46797 | 1997-03-18 | ||
AT467/97 | 1997-03-18 |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0866291A1 EP0866291A1 (en) | 1998-09-23 |
EP0866291B1 true EP0866291B1 (en) | 2002-08-14 |
Family
ID=3491393
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP98104767A Expired - Lifetime EP0866291B1 (en) | 1997-03-18 | 1998-03-17 | Compression heat pump or compression cooling machine and control method therefor |
Country Status (3)
Country | Link |
---|---|
EP (1) | EP0866291B1 (en) |
AT (1) | ATE222344T1 (en) |
DE (1) | DE59805146D1 (en) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
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 |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US6318101B1 (en) * | 2000-03-15 | 2001-11-20 | Carrier Corporation | Method for controlling an electronic expansion valve based on cooler pinch and discharge superheat |
EP1148307B1 (en) * | 2000-04-19 | 2004-03-17 | Denso Corporation | Heat-pump water heater |
US6948326B2 (en) | 2003-04-30 | 2005-09-27 | Lg Electronics Inc. | Apparatus for controlling operation of outdoor unit and its method |
KR100827876B1 (en) * | 2003-05-15 | 2008-05-07 | 엘지전자 주식회사 | Safety operation apparatus and its method for outdoor's unit |
Family Cites Families (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3801711A1 (en) * | 1988-01-21 | 1989-07-27 | Linde Ag | METHOD FOR OPERATING A REFRIGERATION SYSTEM AND REFRIGERATION SYSTEM FOR IMPLEMENTING THE PROCESS |
JPH05106922A (en) * | 1991-10-18 | 1993-04-27 | Hitachi Ltd | Control system for refrigerating equipment |
DE4303533A1 (en) | 1993-02-06 | 1994-08-11 | Stiebel Eltron Gmbh & Co Kg | Method for limiting the hot-gas temperature in a refrigerant circuit and expansion valve |
US5551248A (en) | 1995-02-03 | 1996-09-03 | Heatcraft Inc. | Control apparatus for space cooling system |
EP0762064A1 (en) * | 1995-09-08 | 1997-03-12 | Fritz Ing. Weider | Refrigerant flow control for a heat pump and method |
-
1998
- 1998-03-17 EP EP98104767A patent/EP0866291B1/en not_active Expired - Lifetime
- 1998-03-17 AT AT98104767T patent/ATE222344T1/en active
- 1998-03-17 DE DE59805146T patent/DE59805146D1/en not_active Expired - Lifetime
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
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 |
Also Published As
Publication number | Publication date |
---|---|
ATE222344T1 (en) | 2002-08-15 |
DE59805146D1 (en) | 2002-09-19 |
EP0866291A1 (en) | 1998-09-23 |
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