EP1965154A2 - Heat pump device - Google Patents

Heat pump device Download PDF

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Publication number
EP1965154A2
EP1965154A2 EP08003313A EP08003313A EP1965154A2 EP 1965154 A2 EP1965154 A2 EP 1965154A2 EP 08003313 A EP08003313 A EP 08003313A EP 08003313 A EP08003313 A EP 08003313A EP 1965154 A2 EP1965154 A2 EP 1965154A2
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EP
European Patent Office
Prior art keywords
refrigerant
expansion valve
heat pump
pressure
injected
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Granted
Application number
EP08003313A
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German (de)
French (fr)
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EP1965154B1 (en
EP1965154A3 (en
Inventor
Steffen Smollich
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Stiebel Eltron GmbH and Co KG
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Stiebel Eltron GmbH and Co KG
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Application filed by Stiebel Eltron GmbH and Co KG filed Critical Stiebel Eltron GmbH and Co KG
Priority to EP10015257.8A priority Critical patent/EP2345858A3/en
Priority to PL08003313T priority patent/PL1965154T3/en
Publication of EP1965154A2 publication Critical patent/EP1965154A2/en
Publication of EP1965154A3 publication Critical patent/EP1965154A3/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • 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
    • F25B2400/13—Economisers
    • 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
    • F25B2600/21—Refrigerant outlet evaporator temperature
    • 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
    • F25B2600/2509—Economiser valves

Definitions

  • the present invention relates to a heat pump device.
  • Heat pumps are typically used to heat heating water or hot water.
  • the liquefied refrigerant is then expanded in a throttle body and evaporated while absorbing ambient heat in the evaporator.
  • the vaporized refrigerant is compressed by the compressor of the heat pump and liquefied in the condenser of the heat pump.
  • scroll compressors can be used with a steam injection in heat pumps.
  • the steam injection proves to be advantageous in that the heating power does not decrease as much as in a compressor without steam injection when the heat source temperature decreases.
  • Steam injection compressors are advantageous over liquid injection compressors because steam injection is more efficient than, for example, liquid injection.
  • the steam injection in a scroll compressor is performed such that the liquid refrigerant is throttled by an expansion valve and then evaporated in a heat exchanger or an economizer and overheated.
  • the superheated refrigerant is then injected into the compressor.
  • injection of slightly superheated refrigerant is more efficient than liquid refrigerant injection.
  • an additional solenoid valve must be placed in front of the expansion valve, which is closed at standstill to prevent liquid refrigerant from shifting in the compressors.
  • Fig. 2 shows a refrigerant circuit of a heat pump according to the prior art.
  • the refrigeration cycle includes a compressor 10, a condenser 20, an evaporator 30, a solenoid valve 40, a thermostatic expansion valve 50, an economizer 60 and an expansion valve 70.
  • the solenoid valve 40 is disposed in front of the expansion valve 50 and serves to prevent liquid refrigerant from entering the compressor 10 when the heat pump is at a standstill.
  • the thermostatic expansion valve 50, a solenoid valve 40 is connected upstream.
  • the solenoid valve 40 is closed at standstill to ensure that no liquid refrigerant enters the compressor during standstill.
  • refrigerant is evaporated in the evaporator 30; the vaporized refrigerant is compressed in the compressor 10 and thus heated.
  • the high-pressure refrigerant releases its heat in the condenser 20, for example, to heating water and condenses. Thereafter, the refrigerant is throttled into the expansion valve 50 and is then evaporated again in the evaporator 30.
  • the field of application of, for example, air / water heat pumps is limited, for example, by the hot gas temperature at low outside temperatures and high heating flow temperatures. If the hot gas temperature or the compression end temperature is too high (for example, greater than 120 ° C), thermal destruction of the oil in the compressor may occur, thereby reducing the lubrication of the compressor.
  • the invention relates to the idea of providing an electronic expansion valve for the steam injection in the refrigeration circuit instead of a thermostatic expansion valve.
  • the refrigerant flows to the condenser 20 and from the condenser to the economizer, which serves as a heat exchanger.
  • the economizer 60 By means of the economizer 60, a steam injection into the compressor 10 can be made possible.
  • vapor refrigerant is injected into the compressor, i. the refrigerant is slightly overheated.
  • the liquid refrigerant (which has been liquefied by the condenser 20) is supplied to the electronic expansion valve 80, then the thermal energy of the refrigerant is used by means in the economizer 60 to overheat the refrigerant to be injected.
  • Fig. 1 shows a refrigerant circuit of a heat pump device according to a first embodiment.
  • a compressor 10 In the refrigerant circuit is a compressor 10, a condenser 20, an economizer 60, an electronic expansion valve 80, a further expansion valve 70 and an evaporator 30 are provided.
  • the function of the compressor, the condenser, the economizer, the expansion valve 70 and the evaporator 30 corresponds to the arrangement and function of the compressor, condenser, economizer, expansion valve and evaporator according to Fig. 2 ,
  • the control required for the electronic expansion valve 80 may be based on measured values of an evaporator outlet pressure sensor and on measured values of a temperature sensor for detecting the suction gas temperature. With the help of the electronic expansion valve 80, the overheating of a refrigerant can thus be regulated accordingly. Since the steam injection takes place in an area with an average pressure, which is present between the high pressure and the low pressure, it can be assumed that the corresponding mean pressure should also be the same for the same high and low pressure and for the same overheating. Therefore, when the high and low pressures are measured by means of pressure sensors in the refrigerant circuit, the mean pressure of the steam injection for a defined superheat can also be calculated.
  • the overheating of the refrigerant can be detected by measuring the temperature of the injected refrigerant and the calculated mean pressure without another pressure sensor, especially if they are available for an electronic expansion valve 70.
  • the electronically controlled expansion valve 80 it is possible to regulate how much refrigerant flows through the economizer 60, for example, by opening the expansion valve beyond the calculated opening degree for a defined overheating, more refrigerant can flow through the economizer, so that the refrigerant is no longer sufficiently overheated and injected into the compressor 10 with portions of the liquid phase.
  • the hot gas temperature can be reduced.
  • the field of application of the heat pump can also be extended, especially at low evaporation and high condensation temperatures which typically exceeds the critical hot gas temperature. If the hot gas temperature is exceeded, the system switches over from an overheat control to a hot gas temperature control.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Heat-Pump Type And Storage Water Heaters (AREA)
  • Air Conditioning Control Device (AREA)
  • Central Heating Systems (AREA)
  • Sorption Type Refrigeration Machines (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

An electronic expansion valve (80) is closed when a heating-pump device is inactive. It regulates overheating in an injected coolant when hot-gas temperatures are below a critical temperature. When hot-gas temperatures are in a range of a critical temperature, a partly liquid coolant is injected into a condenser (10) so that a defined maximum value is not reached in a hot-gas temperature. An independent claim is also included for a method for operating a heating-pump device.

Description

Die vorliegende Erfindung betrifft eine Wärmepumpenvorrichtung.The present invention relates to a heat pump device.

Wärmepumpen werden typischerweise zur Erwärmung von Heizungswasser oder Warmwasser verwendet. Hierbei erfolgt eine Kondensation des Kältemittels im Kältemittelkreis unter hohem Druck und bei einer hohen Temperatur, und die Wärme wird an ein Wärmeträgermedium wie beispielsweise Heizungswasser abgegeben. Das verflüssigte Kältemittel wird anschließend in einem Drosselorgan entspannt und verdampft unter Aufnahme von Umgebungswärme im Verdampfer. Das verdampfte Kältemittel wird von dem Verdichter der Wärmepumpe komprimiert und im Kondensator der Wärmepumpe verflüssigt.Heat pumps are typically used to heat heating water or hot water. Here, a condensation of the refrigerant in the refrigerant circuit under high pressure and at a high temperature, and the heat is delivered to a heat transfer medium such as heating water. The liquefied refrigerant is then expanded in a throttle body and evaporated while absorbing ambient heat in the evaporator. The vaporized refrigerant is compressed by the compressor of the heat pump and liquefied in the condenser of the heat pump.

Als Verdichter können beispielsweise Scroll-Verdichter mit einer Dampfeinspritzung in Wärmepumpen verwendet werden. Die Dampfeinspritzung erweist sich dahingehend als vorteilhaft, dass die Heizleistung nicht so stark wie bei einem Verdichter ohne Dampfeinspritzung abnimmt, wenn die Wärmequellentemperatur sinkt. Verdichter mit Dampfeinspritzung sind vorteilhaft im Vergleich zu Verdichtern mit Flüssigkeitseinspritzung, weil die Dampfeinspritzung effizienter ist als z.B eine Flüssigkeitseinspritzung.As a compressor, for example, scroll compressors can be used with a steam injection in heat pumps. The steam injection proves to be advantageous in that the heating power does not decrease as much as in a compressor without steam injection when the heat source temperature decreases. Steam injection compressors are advantageous over liquid injection compressors because steam injection is more efficient than, for example, liquid injection.

Die Dampfeinspritzung bei einem Scroll-Verdichter erfolgt derart, dass das flüssige Kältemittel durch ein Expansionsventil gedrosselt und anschließend in einem Wärmeübertrager bzw. einem Economiser verdampft und überhitzt wird. Das überhitzte Kältemittel wird anschließend in den Verdichter eingespritzt. Wie bereits vorstehend angeführt, ist eine Einspritzung von leicht überhitztem Kältemittel effizienter als eine Einspritzung von flüssigem Kältemittel. Wenn sich die Wärmepumpe im Stillstand befindet, muss vor dem Expansionsventil ein zusätzliches Magnetventil platziert werden, welches im Stillstand geschlossen ist, um zu verhindern, dass flüssiges Kältemittel sich in den Verdichtern verlagert.The steam injection in a scroll compressor is performed such that the liquid refrigerant is throttled by an expansion valve and then evaporated in a heat exchanger or an economizer and overheated. The superheated refrigerant is then injected into the compressor. As already As noted above, injection of slightly superheated refrigerant is more efficient than liquid refrigerant injection. When the heat pump is at a standstill, an additional solenoid valve must be placed in front of the expansion valve, which is closed at standstill to prevent liquid refrigerant from shifting in the compressors.

Fig. 2 zeigt einen Kältekreis einer Wärmepumpe gemäß dem Stand der Technik. Der Kältekreis weist einen Verdichter 10, einen Verflüssiger 20, einen Verdampfer 30, ein Magnetventil 40, ein thermostatisches Expansionsventil 50, einen Economiser 60 und ein Expansionsventil 70 auf. Das Magnetventil 40 ist vor dem Expansionsventil 50 angeordnet und dient dazu, zu verhindern, dass flüssiges Kältemittel in den Verdichter 10 eintreten kann, wenn die Wärmepumpe sich im Stillstand befindet. Somit wird dem thermostatischen Expansionsventil 50 ein Magnetventil 40 vorgeschaltet. Das Magnetventil 40 wird im Stillstand geschlossen, um sicherzustellen, dass während des Stillstandes kein flüssiges Kältemittel in den Verdichter kommt. Durch die Wärmezufuhr auf einem niedrigen Temperaturniveau wird Kältemittel in dem Verdampfer 30 verdampft; das verdampfte Kältemittel wird in dem Verdichter 10 verdichtet und somit erhitzt. Das unter hohem Druck stehende Kältemittel gibt seine Wärme in dem Verflüssiger 20 beispielsweise an Heizungswasser ab und kondensiert dabei. Danach wird das Kältemittel in den Expansionsventil 50 gedrosselt und wird anschliessend in dem Verdampfer 30 wieder verdampft. Fig. 2 shows a refrigerant circuit of a heat pump according to the prior art. The refrigeration cycle includes a compressor 10, a condenser 20, an evaporator 30, a solenoid valve 40, a thermostatic expansion valve 50, an economizer 60 and an expansion valve 70. The solenoid valve 40 is disposed in front of the expansion valve 50 and serves to prevent liquid refrigerant from entering the compressor 10 when the heat pump is at a standstill. Thus, the thermostatic expansion valve 50, a solenoid valve 40 is connected upstream. The solenoid valve 40 is closed at standstill to ensure that no liquid refrigerant enters the compressor during standstill. By the heat supply at a low temperature level, refrigerant is evaporated in the evaporator 30; the vaporized refrigerant is compressed in the compressor 10 and thus heated. The high-pressure refrigerant releases its heat in the condenser 20, for example, to heating water and condenses. Thereafter, the refrigerant is throttled into the expansion valve 50 and is then evaporated again in the evaporator 30.

Der Einsatzbereich von beispielsweise Luft-/Wasserwärmepumpen wird bei tiefen Außentemperaturen und hohen Heizungsvorlauftemperaturen beispielsweise von der Heißgastemperatur begrenzt. Wenn die Heißgastemperatur bzw. die Verdichtungsendtemperatur zu hoch ist (beispielsweise größer 120°C), kann eine thermische Zerstörung des Öls in dem Verdichter stattfinden, wodurch die Schmierung des Verdichters reduziert wird.The field of application of, for example, air / water heat pumps is limited, for example, by the hot gas temperature at low outside temperatures and high heating flow temperatures. If the hot gas temperature or the compression end temperature is too high (for example, greater than 120 ° C), thermal destruction of the oil in the compressor may occur, thereby reducing the lubrication of the compressor.

Es ist Aufgabe der vorliegenden Erfindung, eine Wärmepumpenvorrichtung vorzusehen, welche kostengünstiger herzustellen ist.It is an object of the present invention to provide a heat pump device which is less expensive to produce.

Diese Aufgabe wird durch eine Wärmepumpenvorrichtung gemäß Anspruch 1 gelöst.This object is achieved by a heat pump device according to claim 1.

Die Erfindung betrifft den Gedanken, ein elektronisches Expansionsventil für die Dampfeinspritzung in dem Kältekreis anstatt eines thermostatischen Expansionsventils vorzusehen.The invention relates to the idea of providing an electronic expansion valve for the steam injection in the refrigeration circuit instead of a thermostatic expansion valve.

Von dem Verdichter fließt das Kältemittel zu dem Verflüssiger 20 und von dem Verflüssiger zu dem Economiser, welcher als Wärmeüberträger dient. Mittels des Economisers 60 kann eine Dampfeinspritzung in den Verdichter 10 ermöglicht werden. Hierbei wird dampfförmiges Kältemittel in den Verdichter eingespritzt, d.h. das Kältemittel ist leicht überhitzt. Das flüssige Kältemittel (welches durch den Verflüssiger 20 verflüssigt worden ist) wird dem elektronischen Expansionsventil 80 zugeführt, anschließend wird die thermische Energie des Kältemittels mittels im Economisers 60 zur Überhitzung des einzuspritzenden Kältemittels verwendet.From the compressor, the refrigerant flows to the condenser 20 and from the condenser to the economizer, which serves as a heat exchanger. By means of the economizer 60, a steam injection into the compressor 10 can be made possible. Here, vapor refrigerant is injected into the compressor, i. the refrigerant is slightly overheated. The liquid refrigerant (which has been liquefied by the condenser 20) is supplied to the electronic expansion valve 80, then the thermal energy of the refrigerant is used by means in the economizer 60 to overheat the refrigerant to be injected.

Durch die Verwendung eines elektronischen Expansionsventils anstatt eines thermostatischen Expansionsventils kann das zusätzliche Magnetventil entfallen.By using an electronic expansion valve instead of a thermostatic expansion valve, the additional solenoid valve can be eliminated.

Weitere Ausgestaltungen der Erfindung sind Gegenstand der Unteransprüche.Further embodiments of the invention are the subject of the dependent claims.

Vorteile und Ausführungsbeispiele der Erfindung werden nachstehend auf Bezugnahme auf die Zeichnungen näher erläutert.

Fig. 1
zeigt einen Kältekreis einer Wärmepumpenvorrichtung gemäß einem ersten Ausführungsbeispiel, und
Fig. 2
zeigt einen Kältekreis einer Wärmepumpenvorrichtung gemäß dem Stand der Technik.
Advantages and embodiments of the invention are explained below with reference to the drawings.
Fig. 1
shows a refrigerant circuit of a heat pump device according to a first embodiment, and
Fig. 2
shows a refrigerant circuit of a heat pump device according to the prior art.

Fig. 1 zeigt einen Kältekreis einer Wärmepumpenvorrichtung gemäß einem ersten Ausführungsbeispiel. In dem Kältekreis ist ein Verdichter 10, ein Verflüssiger 20, ein Economiser 60, ein elektronisches Expansionsventil 80, ein weiteres Expansionsventil 70 und ein Verdampfer 30 vorgesehen. Die Funktion des Verdichters, des Verflüssigers, des Economisers, des Expansionsventils 70 und des Verdampfers 30 entspricht dabei der Anordnung und Funktion des Verdichters, Verflüssigers, Economisers, Expansionsventil und Verdampfers gemäß Fig. 2. Fig. 1 shows a refrigerant circuit of a heat pump device according to a first embodiment. In the refrigerant circuit is a compressor 10, a condenser 20, an economizer 60, an electronic expansion valve 80, a further expansion valve 70 and an evaporator 30 are provided. The function of the compressor, the condenser, the economizer, the expansion valve 70 and the evaporator 30 corresponds to the arrangement and function of the compressor, condenser, economizer, expansion valve and evaporator according to Fig. 2 ,

Die für das elektronische Expansionsventil 80 benötigte Regelung kann auf Messwerte eines Verdampferausgangsdrucksensors und auf Messwerte eines Temperatursensors zur Erfassung der Sauggastemperatur basieren. Mit Hilfe des elektronischen Expansionsventils 80 kann die Überhitzung eines Kältemittels somit entsprechend geregelt werden. Da die Dampfeinspritzung in einem Bereich mit einem mittleren Druck erfolgt, welcher zwischen dem Hochdruck und dem Niederdruck vorhanden ist, kann davon ausgegangen werden, dass der entsprechende Mitteldruck bei gleichem Hoch- und Niederdruck sowie bei gleicher Überhitzung ebenfalls gleich sein sollte. Wenn der Hoch- und der Niederdruck mittels Drucksensoren in dem Kältemittelkreis gemessen wird, kann daher der Mitteldruck der Dampfeinspritzung für eine definierte Überhitzung ebenfalls berechnet werden.The control required for the electronic expansion valve 80 may be based on measured values of an evaporator outlet pressure sensor and on measured values of a temperature sensor for detecting the suction gas temperature. With the help of the electronic expansion valve 80, the overheating of a refrigerant can thus be regulated accordingly. Since the steam injection takes place in an area with an average pressure, which is present between the high pressure and the low pressure, it can be assumed that the corresponding mean pressure should also be the same for the same high and low pressure and for the same overheating. Therefore, when the high and low pressures are measured by means of pressure sensors in the refrigerant circuit, the mean pressure of the steam injection for a defined superheat can also be calculated.

Somit kann die Überhitzung des Kältemittels durch Messung der Temperatur des eingespritzten Kältemittels und des berechneten Mitteldrucks ohne einen weiteren Drucksensor ermittelt werden, insbesondere wenn diese für ein elektronisches Expansionsventil 70 vorhanden sind.Thus, the overheating of the refrigerant can be detected by measuring the temperature of the injected refrigerant and the calculated mean pressure without another pressure sensor, especially if they are available for an electronic expansion valve 70.

Mittels des elektronisch geregelten Expansionsventils 80 kann geregelt werden, wie viel Kältemittel durch den Economiser 60 fließt, beispielsweise kann durch Öffnen des Expansionsventils über den berechneten Öffnungsgrad für eine definierte Überhitzung hinaus mehr Kältemittel durch den Economiser fließen, so dass das Kältemittel nicht mehr ausreichend überhitzt wird und mit Anteilen der flüssigen Phase in den Verdichter 10 eingespritzt wird. Durch das Einspritzen von zumindest teilweise flüssigem Kältemittel kann die Heißgastemperatur reduziert werden. Somit kann ebenfalls der Einsatzbereich der Wärmepumpe insbesondere bei tiefen Verdampfungs- und hohen Kondensationstemperaturen erweitert werden, bei denen typischerweise die kritische Heißgastemperatur überschritten wird. Bei einer Überschreitung der Heissgastemperatur wird von einer Überhitzungsregelung auf eine Heißgastemperaturregelung umgeschaltet.By means of the electronically controlled expansion valve 80, it is possible to regulate how much refrigerant flows through the economizer 60, for example, by opening the expansion valve beyond the calculated opening degree for a defined overheating, more refrigerant can flow through the economizer, so that the refrigerant is no longer sufficiently overheated and injected into the compressor 10 with portions of the liquid phase. By injecting at least partially liquid refrigerant, the hot gas temperature can be reduced. Thus, the field of application of the heat pump can also be extended, especially at low evaporation and high condensation temperatures which typically exceeds the critical hot gas temperature. If the hot gas temperature is exceeded, the system switches over from an overheat control to a hot gas temperature control.

Claims (5)

Wärmepumpenvorrichtung, mit einem Verdichter (10), einem Verflüssiger (20), einem Economiser (60), einem Verdampfer (30) und einem elektronischen Expansionsventil (80), wobei das elektronische Expansionsventil im Stillstand der Wärmepumpenvorrichtung geschlossen ist.A heat pump apparatus comprising a compressor (10), a condenser (20), an economizer (60), an evaporator (30) and an electronic expansion valve (80), the electronic expansion valve being closed when the heat pump device is at a standstill. Wärmepumpenvorrichtung nach Anspruch 1, wobei das elektronische Expansionsventil (80) bei Heißgastemperaturen unterhalb einer kritsichen Temperatur die Überhitzung des eingespritzten Kältemittels regelt.The heat pump apparatus according to claim 1, wherein the electronic expansion valve (80) controls superheat of the injected refrigerant at hot gas temperatures below a critical temperature. Wärmepumpenvorrichtung nach Anspruch 1 oder 2, wobei das elektronische Expansionsventil (80) derart betrieben wird, dass bei Heißgastemperaturen im Bereich einer kritischen Temperatur zumindest teilweise flüssiges Kältemittel in den Verdampfer (10) eingespritzt wird, so dass eine definierter Maximalwert der Heißgastemperatur nicht erreicht wird.Heat pump device according to claim 1 or 2, wherein the electronic expansion valve (80) is operated such that at hot gas temperatures in the range of a critical temperature at least partially liquid refrigerant is injected into the evaporator (10), so that a defined maximum value of the hot gas temperature is not reached. Verfahren zum Betrieb einer Wärmepumpenvorrichtung, mit den Verfahrensschritten, dass die Dampfeinspritzung in einem Bereich mit einem mittleren Druck erfolgt, welcher zwischen dem Hochdruck und dem Niederdruck liegt, so dass der entsprechende Mitteldruck bei gleichem Hoch- und Niederdruck sowie bei gleicher Überhitzung des einzuspritzenden Kältemittels gleich ist, wobei der Hoch- und der Niederdruck mittels Drucksensoren in dem Kältemittelkreis gemessen wird und damit der Mitteldruck der Dampfeinspritzung zur Berechnung der Überhitzung berechnet wird.Method for operating a heat pump device, with the method steps that the steam injection takes place in a region with an average pressure, which is between the high pressure and the low pressure, so that the corresponding mean pressure at the same high and low pressure and the same overheating of the injected refrigerant equal is, wherein the high and the low pressure is measured by means of pressure sensors in the refrigerant circuit and thus the mean pressure of the steam injection is calculated to calculate the superheat. Verfahren zum Betrieb einer Wärmepumpenvorrichtung nach Anspruch 4, mit den Verfahrensschritten, dass mittels des elektronisch geregelten Expansionsventils 80 geregelt wird, wie viel Kältemittel durch den Economiser 60 fließt, wobei insbesondere durch weiteres Öffnen des Expansionsventils über den berechneten Öffnungsgrad hinaus mehr Kältemittel durch den Economiser fließt, so dass das Kältemittel nicht mehr ausreichend überhitzt wird und mit Anteilen der flüssigen Phase in den Verdichter 10 eingespritzt wird und durch das Einspritzen von zumindest teilweise flüssigem Kältemittel die Heißgastemperatur reduziert bzw. im Bereich einer kritischen Temperatur gehalten wird.A method of operating a heat pump apparatus according to claim 4, comprising the steps of controlling how much refrigerant flows through the economizer 60 by means of the electronically controlled expansion valve 80, and in particular by further opening the expansion valve beyond the calculated opening degree, more refrigerant flows through the economizer so that the refrigerant is no longer sufficiently overheated and injected with portions of the liquid phase in the compressor 10 and by the injection of at least partially liquid refrigerant, the hot gas temperature is reduced or maintained in the range of a critical temperature.
EP08003313A 2007-03-02 2008-02-23 Heat pump device Active EP1965154B1 (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP10015257.8A EP2345858A3 (en) 2007-03-02 2008-02-23 Heat pump device
PL08003313T PL1965154T3 (en) 2007-03-02 2008-02-23 Heat pump device

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DE102007010646.9A DE102007010646B4 (en) 2007-03-02 2007-03-02 Heat pump device

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EP10015257.8 Division-Into 2010-12-03

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EP1965154A2 true EP1965154A2 (en) 2008-09-03
EP1965154A3 EP1965154A3 (en) 2009-07-08
EP1965154B1 EP1965154B1 (en) 2011-10-26

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EP08003313A Active EP1965154B1 (en) 2007-03-02 2008-02-23 Heat pump device
EP10015257.8A Withdrawn EP2345858A3 (en) 2007-03-02 2008-02-23 Heat pump device

Family Applications After (1)

Application Number Title Priority Date Filing Date
EP10015257.8A Withdrawn EP2345858A3 (en) 2007-03-02 2008-02-23 Heat pump device

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EP (2) EP1965154B1 (en)
AT (1) ATE530864T1 (en)
DE (2) DE202007019159U1 (en)
ES (1) ES2374091T3 (en)
PL (1) PL1965154T3 (en)

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Publication number Priority date Publication date Assignee Title
EP2479517A1 (en) * 2011-01-21 2012-07-25 LG Electronics, Inc. Air conditioner
CN113188269A (en) * 2020-01-13 2021-07-30 上海海立电器有限公司 Shutdown control method and device of enthalpy-increasing heat pump system

Families Citing this family (3)

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Publication number Priority date Publication date Assignee Title
DE102011086476A1 (en) 2011-09-30 2013-04-04 Siemens Aktiengesellschaft High temperature heat pump and method of using a working medium in a high temperature heat pump
DE102012101041A1 (en) 2012-02-09 2013-08-14 Viessmann Werke Gmbh & Co Kg heat pump device
DE102018105609A1 (en) 2018-03-12 2019-09-12 Ipetronik Gmbh & Co. Kg Method for cooling in a vehicle

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JPH0237259A (en) * 1988-07-26 1990-02-07 Toshiba Corp Two-stage compression refrigerating cycle
JPH1089779A (en) * 1996-09-11 1998-04-10 Daikin Ind Ltd Air conditioner
JPH10148404A (en) * 1996-11-20 1998-06-02 Matsushita Electric Ind Co Ltd Controller for refrigerating device
EP1139039A1 (en) * 2000-03-27 2001-10-04 Carrier Corporation Economizer circuit enhancement
US20060277931A1 (en) * 2005-06-10 2006-12-14 Satoshi Nakamura Scroll compressor and refrigerating apparatus

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US5095712A (en) * 1991-05-03 1992-03-17 Carrier Corporation Economizer control with variable capacity
US6474087B1 (en) * 2001-10-03 2002-11-05 Carrier Corporation Method and apparatus for the control of economizer circuit flow for optimum performance
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Publication number Priority date Publication date Assignee Title
JPH0237259A (en) * 1988-07-26 1990-02-07 Toshiba Corp Two-stage compression refrigerating cycle
JPH1089779A (en) * 1996-09-11 1998-04-10 Daikin Ind Ltd Air conditioner
JPH10148404A (en) * 1996-11-20 1998-06-02 Matsushita Electric Ind Co Ltd Controller for refrigerating device
EP1139039A1 (en) * 2000-03-27 2001-10-04 Carrier Corporation Economizer circuit enhancement
US20060277931A1 (en) * 2005-06-10 2006-12-14 Satoshi Nakamura Scroll compressor and refrigerating apparatus

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2479517A1 (en) * 2011-01-21 2012-07-25 LG Electronics, Inc. Air conditioner
US9091464B2 (en) 2011-01-21 2015-07-28 Lg Electronics Inc. Air conditioner
CN113188269A (en) * 2020-01-13 2021-07-30 上海海立电器有限公司 Shutdown control method and device of enthalpy-increasing heat pump system
CN113188269B (en) * 2020-01-13 2022-08-09 上海海立电器有限公司 Shutdown control method and device of enthalpy-increasing heat pump system

Also Published As

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DE102007010646B4 (en) 2022-01-05
ATE530864T1 (en) 2011-11-15
EP2345858A2 (en) 2011-07-20
EP1965154B1 (en) 2011-10-26
PL1965154T3 (en) 2012-03-30
DE202007019159U1 (en) 2010-10-28
EP1965154A3 (en) 2009-07-08
ES2374091T3 (en) 2012-02-13
EP2345858A3 (en) 2013-05-15
DE102007010646A1 (en) 2008-09-04

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