EP2051027A2 - Heat pump assembly - Google Patents

Heat pump assembly Download PDF

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Publication number
EP2051027A2
EP2051027A2 EP08018307A EP08018307A EP2051027A2 EP 2051027 A2 EP2051027 A2 EP 2051027A2 EP 08018307 A EP08018307 A EP 08018307A EP 08018307 A EP08018307 A EP 08018307A EP 2051027 A2 EP2051027 A2 EP 2051027A2
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EP
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Prior art keywords
refrigerant
heat exchanger
compressor
heat pump
pump system
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Granted
Application number
EP08018307A
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German (de)
French (fr)
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EP2051027B1 (en
EP2051027A3 (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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Publication of EP2051027A3 publication Critical patent/EP2051027A3/en
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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
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/02741—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using one four-way valve
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/02742—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using two four-way valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/13—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
    • F25B40/00—Subcoolers, desuperheaters or superheaters

Definitions

  • the present invention relates to a heat pump system.
  • Heat pumps for heating heating water have been produced and marketed for years.
  • the provision of heating heat in heat pumps is done by the condensation of refrigerant under high pressure and thus at high temperature, while the heat to a heat transfer medium, such as heating water, will give.
  • the liquefied refrigerant is then in a throttle body, for example, an expansion valve, relaxed and then evaporates while absorbing ambient heat in the evaporator of the heat pump.
  • the refrigerant vapor is compressed by the compressor of the heat pump, so that it can then be liquefied again in the condenser of the heat pump.
  • the heat pump can be used for cooling the heat transfer medium such as the "heating water" become.
  • the "heating water” then flows through the space-heating surfaces, which are in cooling mode to space-cooling surfaces, heat from the room, which is then delivered to the working in the cooling operation as a condenser evaporator heat pump, so that the heating water is cooled.
  • a disadvantage of reversible heating heat pumps for heating and cooling is that the direction of flow of the heat exchangers on the refrigerant side changes when the refrigerant circuit is reversed.
  • the flow direction on the secondary side where either (heating) water or air flows, remains unchanged Reversing the refrigeration circuit from a countercurrent heat exchanger, a DC heat exchanger with reduced efficiency and increased mean temperature distance between the refrigerant and water or air. This reduces the coefficient of performance of the heat pump in one of the two operating modes.
  • Reversible heating heat pumps are therefore generally optimized for either heating or cooling operation and only achieve modest performance figures in the other operating mode.
  • DE 10 2005 061 480 B3 shows a heat pump system with a refrigerant circuit, a compressor, a first heat exchanger, a throttle body, a second heat exchanger and a 4-2-way valve unit for switching between a heating mode and a cooling mode.
  • the flow direction of the refrigerant located in the refrigerant circuit is switched such that the first heat exchanger in the heating mode for liquefying the refrigerant and in the cooling mode for vaporizing the refrigerant is used.
  • the second heat exchanger is used in the heating mode for evaporating the refrigerant and in the cooling mode for liquefying the refrigerant.
  • the first heat exchanger is connected in the refrigerant circuit such that it works in both modes as a countercurrent heat exchanger.
  • a heat exchanger which operates in the heating mode as an evaporator and operates in the cooling mode as a condenser, are flowed through in both modes of both refrigerant and, for example, heating water in the same direction, so that the heat exchanger in both modes as ( Cross) countercurrent heat exchanger can work, which causes an improvement in the effectiveness.
  • Fig. 1 shows a schematic representation of a heat pump system according to an embodiment of the invention.
  • the heat pump system has a compressor 1, a first heat exchanger (condenser) 2, a second heat exchanger (evaporator) 3, a 4-2-way valve 4, optionally a recuperator or an internal heat exchanger 5, optionally an economizer 6, optionally an interchange length 7 , two expansion valves 9, 19, a filter dryer 10, a collector 11, a sight glass 12, and valves 13-18, 20, and 21.
  • the valves 13-18, 20 and 21 may be designed as check valves, ie as a single-flow valve.
  • the output 1 a of the compressor 1 is coupled to a first port 4 a of the 4-way valve 4.
  • a second connection 4b of the 4-2-way valve 4 is coupled to a port of the recuperator 5.
  • a third port 4 c of the 4-way valve 4 is coupled to an input 1 b of the compressor 1.
  • a fourth port 4d of the 4-way valve 4 is coupled to a valve 13 and a valve 14.
  • the valve 14 is coupled to both the condenser 2 and the valve 16.
  • the valve 13 is coupled to both the condenser 2 and the valve 15.
  • a collector 11 and a filter drier 10 are arranged.
  • the filter drier 10 is coupled both to an electronic expansion valve 9 and to the recuperator 5.
  • a port 1 c of the compressor 1 is coupled to an economizer 6, which in turn is arranged in series with the electronic expansion valve 9.
  • the sighting glass 12 is in turn coupled to the economizer 6 and in series with a defrosting passage 7.
  • the defrosting passage 7 is in turn coupled to a port of the recuperator 5.
  • the electronic expansion valve 19 is coupled both to a valve 17 and to another sight glass 23.
  • injection capillaries 22 are provided, which are coupled to both the evaporator 3 and with a valve 20.
  • a valve 18 is arranged, which in turn is coupled to the evaporator and a valve 21.
  • the recuperator is coupled to both a valve 20 and a valve 21.
  • the heat pump system according to the first embodiment can be operated in two modes, namely, a heating mode HB and a cooling mode KU.
  • the heating mode HB the heating heat is provided by a condensation of refrigerant under a high pressure and thus a high temperature, while the heat contained in the refrigerant is discharged to a heat transfer medium such as heating water.
  • a heat transfer medium such as heating water.
  • the liquefied refrigerant is decompressed by the valve 19 and evaporates while absorbing ambient heat in the evaporator 3.
  • the refrigerant vapor is compressed in the compressor 1 and then forwarded to the condenser.
  • the valve 19 serves as an expansion valve in the cooling and heating modes.
  • Fig. 2 shows a schematic representation of a heat pump system of Fig. 1 in a heating mode.
  • the flow direction of the refrigerant is indicated by arrows.
  • the compressor 1 the refrigerant flows to the left in the port 4a of the 4-2-way valve 4, where it emerges from the right port 4d and flows upward to the check valve 14.
  • the check valve 13 is closed.
  • the refrigerant flows through the first heat exchanger 2, which operates as a condenser in the heating operation HB.
  • the refrigerant flows to the check valve 15 and from there to the collector 11, via the filter drier 10 and on to a connection of the recuperator 5.
  • the refrigerant flows through the Ableylange 7, through the economizer. 6 and through the sight glass 12 and is relaxed by the electronic expansion valve 19. Thereafter, the refrigerant flows through the check valve 17 and the injection capillaries 22 through the second heat exchanger 3, which operates in the heating operation as an evaporator. Subsequently, the refrigerant flows through the check valve 21 and again through the recuperator 5 and into the left inlet 4b of the 4-2 valve 4 and from there again through the central outlet 4c and finally to the compressor 1.
  • Fig. 3 shows a schematic representation of the heat pump system of Fig. 1 in a cooling mode.
  • the flow direction of the coolant is again through Arrows displayed.
  • the coolant flows from the port 1a and turns to the left to enter the port 4a of the 4-2.Wegeventils 4, where it exits from the left outlet 4b again and through the recuperator 5 via the check valve 20th flows to the second heat exchanger 3, which serves as a condenser in the cooling operation.
  • the refrigerant flows via the check valve 18 and the sight glass 23 to the electronic expansion valve 19 to the valve 16.
  • the coolant flows to the first heat exchanger 2, which operates as an evaporator in the cooling mode.
  • the coolant can not turn to the right to the check valve 14 and flow through there, because the check valve 14 is locked for this flow direction.
  • the refrigerant flows through the first heat exchanger 2 and from there through the check valve 13 back to the right input 4d of the 4-2-way valve 4 to again through the central output 4c back to the input 1 b of the compressor 1 to flow.
  • a switching of the refrigerant circuit can be effected without causing a reversal of the refrigerant flow through the evaporator, so that the evaporator always works as a countercurrent evaporator.
  • a switching unit is arranged in front of the evaporator and a switching unit after the evaporator.
  • the switching unit before the evaporator can be composed of the two check valves 20, 21, while the second switching unit behind the evaporator can be composed of the check valves 17 and 18.
  • the two paths B. C are each arranged parallel to the evaporator.
  • Another mode namely the Kreisumlotabtauung can be activated in the same manner as the cooling operation during the heating operation, while the fan L1 of the second heat exchanger 3 is turned off.
  • the internal heat exchanger described during the heating operation namely the economizer 6, the recuperator 5 and the Ableylange are only optional.
  • the recuperator 5 serves to overheat the suction gas flowing to the compressor 1 during the heating operation.
  • the economizer 6 is used during the heating operation to evaporate a partial volume flow of the liquid refrigerant by absorbing energy from the main volume flow of the supercooled refrigerant before it is injected into the compressor 1.
  • the already compressed by a portion of the total pressure ratio pc / p0 main volume flow of the refrigerant can be intercooled. If the internal heat exchanger is not required, then a direct connection between the filter drier and the sight glass must be provided.
  • the two heat exchangers 2, 3 described above can each act as a plate heat exchanger, which is acted upon by water or a heat-antifreeze mixture on the secondary side, as a fin tube heat exchanger, which is acted upon by air on the secondary side, or as any air Be configured refrigerant heat exchanger.
  • the compressor 1 described above may be a scroll compressor or a scroll compressor designed for post-injection of vapor refrigerant.
  • the compressor may also be configured as a single-stage reciprocating compressor, a two-stage reciprocating compressor, a single-stage rotary piston compressor, or a two-stage rotary piston compactor.
  • the heat pump system described above may be configured as an air / water heat pump, an air / air heat pump, a brine / water heat pump, or a water / water heat pump.
  • the refrigerant used can be HFC refrigerants, hydrocarbons or CO 2 .
  • the described 4-2-way unit or 4-2-way valve unit 4 may also be formed by individual valves with appropriate diversion such as pipes and T-pieces.

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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)

Abstract

The system has valves (20, 21) provided in front of an evaporator (3), and valves (17, 18) provided behind the evaporator. Two paths (B, C) are provided parallel to the evaporator. The valves (17, 18, 20, 21) are designed such that a flow direction at the evaporator is unchanged independent of change of a flow direction of a refrigerant e.g. carbon hydride. The evaporator is used as a liquefier in an operation mode for liquefying the refrigerant and is used as a vaporizer in another operation mode for evaporating the refrigerant.

Description

Die vorliegende Erfindung betrifft eine Wärmepumpenanlage.The present invention relates to a heat pump system.

Wärmepumpen zur Erwärmung von Heizungswasser werden seit Jahren produziert und vermarktet. Die Bereitstellung der Heizwärme bei Wärmepumpen erfolgt durch die Kondensation von Kältemittel unter hohem Druck und damit bei hoher Temperatur, während die Wärme an ein Wärmeträgermedium, beispielsweise Heizungswasser, abgeben wird. Das verflüssigte Kältemittel wird anschließend in einem Drosselorgan, zum Beispiel einem Expansionsventil, entspannt und verdampft daraufhin unter Aufnahme von Umgebungswärme im Verdampfer der Wärmepumpe. Der Kältemitteldampf wird vom Verdichter der Wärmepumpe komprimiert, so dass er anschließend wieder im Kondensator der Wärmepumpe verflüssigt werden kann.Heat pumps for heating heating water have been produced and marketed for years. The provision of heating heat in heat pumps is done by the condensation of refrigerant under high pressure and thus at high temperature, while the heat to a heat transfer medium, such as heating water, will give. The liquefied refrigerant is then in a throttle body, for example, an expansion valve, relaxed and then evaporates while absorbing ambient heat in the evaporator of the heat pump. The refrigerant vapor is compressed by the compressor of the heat pump, so that it can then be liquefied again in the condenser of the heat pump.

Wird der Kreislauf des Kältemittels umgekehrt. d. h., wird das Kältemittel in dem Wärmeaustauscher, der im Heizbetrieb als Verdampfer dient, unter Wärmeabgabe verflüssigt und in dem Wärmeaustauscher, der im Heizbetrieb als Verflüssiger dient, unter Wärmeaufnahme verdampft, so kann die Wärmepumpe zum Kühlen des Wärmeträgermediums wie beispielsweise des "Heizungswassers" eingesetzt werden. Im Kühlbetrieb nimmt das "Heizungewasser" dann beim Durchströmen der Raum-Heizflächen, die im Kühlbetrieb zu Raum-Kühlflächen werden, Wärme aus dem Raum auf, die dann an den im Kühlbetrieb als Verflüssiger funktionierenden Verdampfer der Wärmepumpe abgegeben wird, so dass das Heizungswasser gekühlt wird.If the cycle of the refrigerant is reversed. ie, the refrigerant in the heat exchanger, which serves as an evaporator in the heating operation, liquefied under heat and in the heat exchanger, which serves as a condenser in the heating, evaporates under heat absorption, the heat pump can be used for cooling the heat transfer medium such as the "heating water" become. In cooling mode, the "heating water" then flows through the space-heating surfaces, which are in cooling mode to space-cooling surfaces, heat from the room, which is then delivered to the working in the cooling operation as a condenser evaporator heat pump, so that the heating water is cooled.

Ein Nachteil reversibler Heizungswärmepumpen zum Heizen und Kühlen besteht darin, dass sich beim Umkehren des Kältekreises die Durchströmungsrichtung der Wärmeaustauscher auf der Kältemittelseite ändert Da die Strömungsrichtung auf der Sekundärseite, auf der entweder (Heizungs)wasser oder Luft strömt, unverändert bleibt, wird dadurch mit der Umkehr des Kältekreises aus einem Gegenstrom-Wärmeaustauscher ein Gleichstromwärmeaustauscher mit verminderter Effizienz und vergrößertem mittleren Temperaturabstand zwischen Kältemittel und Wasser bzw. Luft. Dadurch sinkt die Leistungszahl der Wärmepumpe in einer der beiden Betriebsarten. Reversible Heizungswärmepumpen sind daher im Allgemeinen entweder für den Heiz- oder den Kühlbetrieb optimiert und erreichen in der jeweils anderen Betriebsart nur bescheidene Leistungszahlen.A disadvantage of reversible heating heat pumps for heating and cooling is that the direction of flow of the heat exchangers on the refrigerant side changes when the refrigerant circuit is reversed. The flow direction on the secondary side, where either (heating) water or air flows, remains unchanged Reversing the refrigeration circuit from a countercurrent heat exchanger, a DC heat exchanger with reduced efficiency and increased mean temperature distance between the refrigerant and water or air. This reduces the coefficient of performance of the heat pump in one of the two operating modes. Reversible heating heat pumps are therefore generally optimized for either heating or cooling operation and only achieve modest performance figures in the other operating mode.

DE 10 2005 061 480 B3 zeigt eine Wärmepumpenanlage mit einem Kältemittelkreislauf, einem Verdichter, einem ersten Wärmeüberträger einem Drosselorgan, einem zweiten Wärmeüberträger und einer 4-2-Wege-Ventileinheit zum Umschalten zwischen einer Heizbetriebsart und einer Kühlbetriebsart. Hierbei wird die Strömungsrichtung des in dem Kältemittelkreislaufs befindlichen Kältemittels derart umgeschaltet, dass der erste Wärmeüberträger in der Heizbetriebsart zum Verflüssigen des Kältemittels und in der Kühlbetriebsart zum Verdampfen des Kältemittels dient. Der zweite Wärmeüberträger dient in der Heizbetriebsart zum Verdampfen des Kältemittels und in der Kühlbetriebsart zum Verflüssigen des Kältemittels. Der erste Wärmeüberträger ist im Kältemittelkreislauf derart verschaltet, dass er in beiden Betriebsarten als Gegenstrom-Wärmeüberträger arbeitet. DE 10 2005 061 480 B3 shows a heat pump system with a refrigerant circuit, a compressor, a first heat exchanger, a throttle body, a second heat exchanger and a 4-2-way valve unit for switching between a heating mode and a cooling mode. Here, the flow direction of the refrigerant located in the refrigerant circuit is switched such that the first heat exchanger in the heating mode for liquefying the refrigerant and in the cooling mode for vaporizing the refrigerant is used. The second heat exchanger is used in the heating mode for evaporating the refrigerant and in the cooling mode for liquefying the refrigerant. The first heat exchanger is connected in the refrigerant circuit such that it works in both modes as a countercurrent heat exchanger.

Es ist somit Aufgabe der Erfindung, eine Wärmepumpenanlage vorzusehen, die sowohl im Heiz- als auch im Kühlbetrieb effektiv arbeitet.It is therefore an object of the invention to provide a heat pump system that works effectively both in heating and cooling operation.

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

Durch eine geeignete Anordnung von Rückschlagventilen kann ein Wärmeüberträger, der im Heizbetrieb als Verdampfer arbeitet und im Kühlbetrieb als Verflüssiger arbeitet, in beiden Betriebsarten sowohl von Kältemittel als auch beispielsweise von Heizungswasser in der gleichen Richtung durchströmt werden, so dass der Wärmeüberträger in beiden Betriebsarten als (Kreuz)-Gegenstromwärmeüberträger arbeiten kann, was eine Verbesserung der Effektivität bewirkt.By a suitable arrangement of check valves, a heat exchanger, which operates in the heating mode as an evaporator and operates in the cooling mode as a condenser, are flowed through in both modes of both refrigerant and, for example, heating water in the same direction, so that the heat exchanger in both modes as ( Cross) countercurrent heat exchanger can work, which causes an improvement in the effectiveness.

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

Nachfolgend werden die Ausführungsbeispiele der vorliegenden Erfindung detailliert unter Bezugnahme auf die Zeichnung näher erläutert.

Fig. 1
zeigt eine schematische Darstellung einer Wärmepumpenanlage gemäß einem Ausführungsbeispiel der Erfindung,
Fig. 2
zeigt eine schematische Darstellung einer Wärmepumpenanlage von Fig. 1 in einem Heizbetrieb, und
Fig.3
zeigt eine schematische Darstellung einer Wärmepumpenanlage von Fig. 1 in einem Kühlbetrieb.
Hereinafter, the embodiments of the present invention will be explained in detail with reference to the drawings.
Fig. 1
shows a schematic representation of a heat pump system according to an embodiment of the invention,
Fig. 2
shows a schematic representation of a heat pump system of Fig. 1 in a heating mode, and
Figure 3
shows a schematic representation of a heat pump system of Fig. 1 in a cooling mode.

Fig. 1 zeigt eine schematische Darstellung einer Wärmepumpenanlage gemäß einem Ausführungsbeispiel der Erfindung. Die Wärmepumpenanlage weist einen Verdichter 1, einen ersten Wärmeüberträger (Verflüssiger) 2, einen zweiten Wärmeüberträger (Verdampfer) 3, ein 4-2-Wegeventil 4, optional einen Rekuperator bzw. einen inneren Wärmeüberträger 5, optional einen Economizer 6, optional eine Abtauschlange 7, zwei Expansionsventile 9,19, einen Filtertrockner 10. einen Sammler 11, ein Schauglas 12, und Ventile 13-18, 20 und 21 auf. Die Ventile 13-18, 20 und 21 können als Rückschlagventile, d. h. als einseitig durchströmbares Ventil ausgestaltet sein. Der Ausgang 1 a des Verdichters 1 ist mit einem ersten Anschluss 4a des 4-2-Wege-Ventils 4 gekoppelt. Ein zweiter Anschluss 4b des 4-2-Wege-Ventils 4 ist mit einem Anschluss des Rekuperators 5 gekoppelt. Ein dritter Anschluss 4c des 4-2-Wege-Ventils 4 ist mit einem Eingang 1 b des Verdichters 1 gekoppelt. Ein vierter Anschluss 4d des 4-2-Wege-Ventils 4 ist mit einem Ventil 13 und einem Ventil 14 gekoppelt. Das Ventil 14 ist sowohl mit dem Verflüssiger 2 als auch mit dem Ventil 16 gekoppelt. Das Ventil 13 ist sowohl mit dem Verflüssiger 2 als auch mit dem Ventil 15 gekoppelt. In Reihe zu dem Ventil 15 ist ein Sammler 11 und ein Filtertrockner 10 angeordnet. Der Filtertrockner 10 ist sowohl mit einem elektronischen Expansionsventil 9 als auch mit dem Rekuperator 5 gekoppelt. Ein Anschluss 1 c des Verdichters 1 ist mit einem Economizer 6 gekoppelt, welcher wiederum in Reihe mit dem elektronischen Expansionsventil 9 angeordnet ist. Fig. 1 shows a schematic representation of a heat pump system according to an embodiment of the invention. The heat pump system has a compressor 1, a first heat exchanger (condenser) 2, a second heat exchanger (evaporator) 3, a 4-2-way valve 4, optionally a recuperator or an internal heat exchanger 5, optionally an economizer 6, optionally an interchange length 7 , two expansion valves 9, 19, a filter dryer 10, a collector 11, a sight glass 12, and valves 13-18, 20, and 21. The valves 13-18, 20 and 21 may be designed as check valves, ie as a single-flow valve. The output 1 a of the compressor 1 is coupled to a first port 4 a of the 4-way valve 4. A second connection 4b of the 4-2-way valve 4 is coupled to a port of the recuperator 5. A third port 4 c of the 4-way valve 4 is coupled to an input 1 b of the compressor 1. A fourth port 4d of the 4-way valve 4 is coupled to a valve 13 and a valve 14. The valve 14 is coupled to both the condenser 2 and the valve 16. The valve 13 is coupled to both the condenser 2 and the valve 15. In series with the valve 15, a collector 11 and a filter drier 10 are arranged. The filter drier 10 is coupled both to an electronic expansion valve 9 and to the recuperator 5. A port 1 c of the compressor 1 is coupled to an economizer 6, which in turn is arranged in series with the electronic expansion valve 9.

Das Ventil 16 ist sowohl mit einem Schauglas 12 als auch mit einem elektronischen Expansionsventil 19 gekoppelt, Das Schauglas 12 ist wiederum mit dem Economizer 6 und in Reihe dazu mit einer Abtauschlange 7 gekoppelt, Die Abtauschlange 7 ist wiederum mit einem Anschluss des Rekuperators 5 gekoppelt. Das elektronische Expansionsventil 19 ist sowohl mit einem Ventil 17 als auch mit einem weiteren Schauglas 23 gekoppelt. In Reihe zu dem Expansionsventil 17 sind Einspritzkapillaren 22 vorgesehen, welche sowohl mit dem Verdampfer 3 als auch mit einem Ventil 20 gekoppelt sind. In Reihe zu dem Schauglas 23 ist ein Ventil 18 angeordnet, welches wiederum mit dem Verdampfer und einem Ventil 21 gekoppelt ist. Der Rekuperator ist sowohl mit einem Ventil 20 als auch mit einem Ventil 21 gekoppelt.The sighting glass 12 is in turn coupled to the economizer 6 and in series with a defrosting passage 7. The defrosting passage 7 is in turn coupled to a port of the recuperator 5. The electronic expansion valve 19 is coupled both to a valve 17 and to another sight glass 23. In line with the expansion valve 17 injection capillaries 22 are provided, which are coupled to both the evaporator 3 and with a valve 20. In series with the sight glass 23, a valve 18 is arranged, which in turn is coupled to the evaporator and a valve 21. The recuperator is coupled to both a valve 20 and a valve 21.

Die Wärmepumpenanlage gemäß dem ersten Ausführungsbeispiel kann in zwei Betriebsarten, nämlich einer Heizbetriebsart HB und einer Kühlbetriebsart KU betrieben werden. Bei der Heizbetriebsart HB erfolgt eine Bereitstellung der Heizwärme durch eine Kondensation von Kältemittel unter einem hohen Druck und somit einer hohen Temperatur, während die sich in dem Kältemittel befindliche Wärme an ein Wärmeträgermedium wie beispielsweise Heizungswasser abgegeben wird. Dies erfolgt in dem Verflüssiger 2, wobei das Wärmeträgermedium durch den Eingang E eintritt und den Ausgang A austritt, und das austretende Wärmeträgermedium die Wärme von dem Kältemittel zumindest teilweise aufgenommen hat. Das verflüssigte Kältemittel wird durch das Ventil 19 entspannt und verdampft unter Aufnahme von Umgebungswärme im Verdampfer 3. Der Kältemitteldampf wird in dem Verdichter 1 komprimiert und anschließend an den Verflüssiger weitergeleitet.The heat pump system according to the first embodiment can be operated in two modes, namely, a heating mode HB and a cooling mode KU. In the heating mode HB, the heating heat is provided by a condensation of refrigerant under a high pressure and thus a high temperature, while the heat contained in the refrigerant is discharged to a heat transfer medium such as heating water. This takes place in the condenser 2, wherein the heat transfer medium enters through the inlet E and the outlet A exits, and the exiting heat transfer medium, the heat from the refrigerant at least partially has recorded. The liquefied refrigerant is decompressed by the valve 19 and evaporates while absorbing ambient heat in the evaporator 3. The refrigerant vapor is compressed in the compressor 1 and then forwarded to the condenser.

Das Ventil 19 dient als Expansionsventil in der Kühl- und der Heizbetriebsart.The valve 19 serves as an expansion valve in the cooling and heating modes.

Fig. 2 zeigt eine schematische Darstellung einer Wärmepumpenanlage von Fig. 1 in einem Heizbetrieb. Die Strömungsrichtung des Kältemittels ist durch Pfeile angezeigt. Von dem Verdichter 1 aus fließt das Kältemittel nach links in den Anschluss 4a des 4-2-Wegeventils 4, wo es aus dem rechten Ausgang 4d heraustritt und nach oben zu dem Rückschlagventil 14 fließt. Hierbei ist das Rückschlagventil 13 geschlossen. Von dem Rückschlagventil 14 aus fließt das Kältemittel durch den ersten Wärmeüberträger 2, weicher in dem Heizbetrieb HB als ein Verflüssiger arbeitet. Von dem ersten Wärmeüberträger 2 fließt das Kältemittel zu dem Rückschlagventil 15 und von dort aus weiter zu dem Sammler 11, über den Filtertrockner 10 und weiter zu einem Anschluss des Rekuperators 5. Von dort aus fließt das Kältemittel durch die Abtauschlange 7, durch den Economizer 6 und durch das Schauglas 12 und wird durch das elektronische Expansionsventil 19 entspannt. Danach fließt das Kältemittel über das Rückschlagventil 17 und die Einspritzkapillaren 22 durch den zweiten Wärmeüberträger 3, der in dem Heizbetrieb als Verdampfer arbeitet. Anschließend fließt das Kältemittel durch das Rückschlagventil 21 und wiederum durch den Rekuperator 5 und in den linken Eingang 4b des 4-2-Ventils 4 und von dort wiederum durch den mittleren Ausgang 4c hinaus und schließlich zu dem Verdichter 1. Fig. 2 shows a schematic representation of a heat pump system of Fig. 1 in a heating mode. The flow direction of the refrigerant is indicated by arrows. From the compressor 1, the refrigerant flows to the left in the port 4a of the 4-2-way valve 4, where it emerges from the right port 4d and flows upward to the check valve 14. Here, the check valve 13 is closed. From the check valve 14, the refrigerant flows through the first heat exchanger 2, which operates as a condenser in the heating operation HB. From the first heat exchanger 2, the refrigerant flows to the check valve 15 and from there to the collector 11, via the filter drier 10 and on to a connection of the recuperator 5. From there, the refrigerant flows through the Abtauschlange 7, through the economizer. 6 and through the sight glass 12 and is relaxed by the electronic expansion valve 19. Thereafter, the refrigerant flows through the check valve 17 and the injection capillaries 22 through the second heat exchanger 3, which operates in the heating operation as an evaporator. Subsequently, the refrigerant flows through the check valve 21 and again through the recuperator 5 and into the left inlet 4b of the 4-2 valve 4 and from there again through the central outlet 4c and finally to the compressor 1.

Da der Sekundärkreislauf in dem ersten Wärmeüberträger 2 (Wasser) die entgegengesetzte Strömungsrichtung aufweist wie das Kältemittel, wird ein Gegenstrom-Wärmeüberträger realisiert, welcher eine verbesserte Effizienz im Vergleich zu einem Gleichstrorn-Wärmeüberträger aufweist.Since the secondary circuit in the first heat exchanger 2 (water) has the opposite flow direction as the refrigerant, a countercurrent heat exchanger is realized, which has an improved efficiency compared to a direct-current heat exchanger.

Fig. 3 zeigt eine schematische Darstellung der Wärmepumpenanlage von Fig. 1 in einem Kühlbetrieb. Die Strömungsrichtung des Kühlmittels ist wiederum durch Pfeile angezeigt. Von dem Verdichter 1 fließt das Kühlmittel aus dem Anschluss 1a und biegt nach links ab, um in den Anschluss 4a des 4-2.Wegeventils 4 zu gelangen, wo es aus dem linken Ausgang 4b wieder austritt und durch den Rekuperator 5 über das Rückschlagventil 20 zu dem zweiten Wärmeüberträger 3 fließt, welcher in dem Kühlbetrieb als Verflüssiger dient. Anschließend fließt das Kältemittel über das Rückschlagventil 18 und das Schauglas 23 zu dem elektronischen Expansionsventil 19 zu dem Ventil 16. Von dem Ventil 16 fließt das Kühlmittel zu dem ersten Wärmeüberträger 2, welcher im Kühlbetrieb als Verdampfer arbeitet. Das Kühlmittel kann nicht nach rechts zu dem Rückschlagventil 14 abbiegen und dort durchfließen, weil das Rückschlagventil 14 für diese Strömungsrichtung gesperrt ist. Somit fließt das Kältemittel durch den ersten Wärmeüberträger 2 und von dort durch das Rückschlagventil 13 zurück zu dem rechten Eingang 4d des 4-2-Wegeventils 4, um wiederum durch den mittleren Ausgang 4c zurück zu dem Eingang 1 b des Verdichters 1 zu fließen. Fig. 3 shows a schematic representation of the heat pump system of Fig. 1 in a cooling mode. The flow direction of the coolant is again through Arrows displayed. From the compressor 1, the coolant flows from the port 1a and turns to the left to enter the port 4a of the 4-2.Wegeventils 4, where it exits from the left outlet 4b again and through the recuperator 5 via the check valve 20th flows to the second heat exchanger 3, which serves as a condenser in the cooling operation. Subsequently, the refrigerant flows via the check valve 18 and the sight glass 23 to the electronic expansion valve 19 to the valve 16. From the valve 16, the coolant flows to the first heat exchanger 2, which operates as an evaporator in the cooling mode. The coolant can not turn to the right to the check valve 14 and flow through there, because the check valve 14 is locked for this flow direction. Thus, the refrigerant flows through the first heat exchanger 2 and from there through the check valve 13 back to the right input 4d of the 4-2-way valve 4 to again through the central output 4c back to the input 1 b of the compressor 1 to flow.

Durch die Verschaltung des Verdampfers 3 mit den beiden Pfaden B, C kann ein Umschalten des Kältemittelkreislaufes bewirkt werden, ohne dass es zu einer Umkehrung des Kältemittelflusses durch den Verdampfer kommt, so dass der Verdampfer immer als ein Gegenstrom-Verdampfer arbeitet. Erfindungsgemäß wird eine Umschalteineinheit vor dem Verdampfer und eine Umschalteinheit nach dem Verdampfer angeordnet. Die Umschalteinheit vor dem Verdampfer kann sich aus den beiden Rückschlagventilen 20, 21 zusammensetzen, während die zweite Umschalteinheit hinter dem Verdampfer sich aus den Rückschlagventilen 17 und 18 zusammensetzen kann. Die beiden Pfade B. C sind jeweils parallel zu dem Verdampfer angeordnet. Durch die erste und zweite Umschalteinheit kann sichergestellt werden, dass das Kältemittel durch den Verdampfer immer nur in eine Richtung fließt.By the connection of the evaporator 3 with the two paths B, C, a switching of the refrigerant circuit can be effected without causing a reversal of the refrigerant flow through the evaporator, so that the evaporator always works as a countercurrent evaporator. According to the invention, a switching unit is arranged in front of the evaporator and a switching unit after the evaporator. The switching unit before the evaporator can be composed of the two check valves 20, 21, while the second switching unit behind the evaporator can be composed of the check valves 17 and 18. The two paths B. C are each arranged parallel to the evaporator. By the first and second switching unit can be ensured that the refrigerant flows through the evaporator always in one direction.

Eine weitere Betriebsart, nämlich die Kreisumkehrabtauung, kann auf die gleiche Art und Weise wie der Kühlbetrieb während des Heizbetriebs aktiviert werden, wobei dabei der Lüfter L1 des zweiten Wärmeüberträgers 3 ausgeschaltet wird.Another mode, namely the Kreisumkehrabtauung can be activated in the same manner as the cooling operation during the heating operation, while the fan L1 of the second heat exchanger 3 is turned off.

Der während des Heizbetriebs beschriebene innere Wärmetauscher, nämlich der Economizer 6, der Rekuperator 5 und die Abtauschlange sind lediglich optional. Der Rekuperator 5 dient dabei dazu, das zum Verdichter 1 strömende Sauggas während des Heizbetriebs weiter zu überhitzen. Der Economizer 6 dient während des Heizbetriebs dazu, einen Teilvolumenstrom des flüssigen Kältemittels unter Aufnahme von Energie aus dem Hauptvolumenstrom des unterkühlten Kältemittels zu verdampfen, bevor es in den Verdichter 1 eingespritzt wird. Somit kann der bereits um einen Teil des gesamten Druckverhältnisses pc/p0 komprimierte Hauptvolumenstrom des Kältemittels zwischengekühlt werden. Falls der innere Wärmetauscher nicht benötigt wird, dann muss eine direkte Verbindung zwischen dem Filtertrockner und dem Schauglas vorgesehen werden.The internal heat exchanger described during the heating operation, namely the economizer 6, the recuperator 5 and the Abtauschlange are only optional. The recuperator 5 serves to overheat the suction gas flowing to the compressor 1 during the heating operation. The economizer 6 is used during the heating operation to evaporate a partial volume flow of the liquid refrigerant by absorbing energy from the main volume flow of the supercooled refrigerant before it is injected into the compressor 1. Thus, the already compressed by a portion of the total pressure ratio pc / p0 main volume flow of the refrigerant can be intercooled. If the internal heat exchanger is not required, then a direct connection between the filter drier and the sight glass must be provided.

Die beiden oben beschriebenen Wärmeüberträger 2, 3 können jeweils als Platten-Wärmeüberträger, welcher auf der Sekundärseite von Wasser oder einem Wärme-Frostschutzgemisch beaufschlagt wird, als ein Lamellenrohr-Wärmeüberträger, welcher auf der Sekundärseite von Luft beaufschlagte wird, oder als ein beliebiger Luft-Kältemittel-Wärmeüberträger ausgestaltet sein.The two heat exchangers 2, 3 described above can each act as a plate heat exchanger, which is acted upon by water or a heat-antifreeze mixture on the secondary side, as a fin tube heat exchanger, which is acted upon by air on the secondary side, or as any air Be configured refrigerant heat exchanger.

Der oben beschriebene Verdichter 1 kann einen Scroll-Verdichter darstellen oder einen Scroll-Verdichter, der für die Nacheinspritzung von dampfförmigem Kältemittel ausgestaltet ist. Der Verdichter kann ferner als ein einstufiger Hubkolben-Verdichter, als ein zweistufiger Hubkolben-Verdichter, als ein einstufiger Rollkolben-Verdichter oder als ein zweistufiger Rollkolben-Verdichtsr ausgestaltet sein.The compressor 1 described above may be a scroll compressor or a scroll compressor designed for post-injection of vapor refrigerant. The compressor may also be configured as a single-stage reciprocating compressor, a two-stage reciprocating compressor, a single-stage rotary piston compressor, or a two-stage rotary piston compactor.

Die oben beschriebene Wärmepumpenanlage kann als eine Luft/Wasserwärmepumpe, als eine Luft/Luftwärmepumpe, als eine Sole/Wassörwärmepumpe oder als eine Wasser/Wasserwärmepumpe ausgestaltet sein.The heat pump system described above may be configured as an air / water heat pump, an air / air heat pump, a brine / water heat pump, or a water / water heat pump.

Als Kältemittel kann H-FKW-Kältemittel, Kohlenwasserstoffe oder CO2 verwendet werden.The refrigerant used can be HFC refrigerants, hydrocarbons or CO 2 .

Die beschriebene 4-2-Wegeeinheit bzw. 4-2-Wegeventileinheit 4 kann auch durch einzelne Ventile mit entsprechender Umleitung wie beispielsweise Rohrleitungen und T-Stücken ausgebildet sein.The described 4-2-way unit or 4-2-way valve unit 4 may also be formed by individual valves with appropriate diversion such as pipes and T-pieces.

Claims (9)

Wärmepumpenanlage, mit
einem Verdichter (1), einem ersten Wärmeüberträger (2), einem zweiten Wärmeüberträger, (3) und einer 4-2-Wegeeinheit (4) zum Umschalten zwischen einer ersten und einer zweiten Betriebsart, wobei die Strömungsrichtung des sich in dem Kältemittelkreislauf befindlichen Kältemittels derart umgeschaltet werden kann, dass der erste Wärmeüberträger (2) in der ersten Betriebsart zum Verflüssigen des Kältemittels, und in der zweiten Betriebsart zum Verdampfen des Kältemittels dient, und der zweite Wärmeüberträger (3) in der ersten Betriebsart zum Verdampfen des Kältemittels, und in der zweiten Betriebsart zum Verflüssigen des Kältemittels dient,
gekennzeichnet durch eine erste Umschalteinheit (20, 21) vor, und einer zweiten Umschalteinheit (18, 17) hinter dem zweiten Wärmeüberträger (3), und einem ersten und zweiten Pfad (A, B) parallel zu dem zweiten Wärmeüberträger,
wobei die erste und zweite Umschalteinheit (20,21,17,18) derart ausgestaltet sind, dass die Strömungsrichtung am zweiten Wärmeüberträger (3) unabhängig von einer Umschaltung der Strömungsrichtung des Kältemittels im Wärmeüberträger 3 unverändert bleibt.Heat pump system, with
a compressor (1), a first heat exchanger (2), a second heat exchanger, (3) and a 4-2-way unit (4) for switching between a first and a second mode, wherein the flow direction of the refrigerant located in the refrigerant circuit can be switched such that the first heat exchanger (2) in the first mode for liquefying the refrigerant, and in the second mode for vaporizing the refrigerant, and the second heat exchanger (3) in the first mode for evaporating the refrigerant, and in the second mode is used to liquefy the refrigerant,
characterized by a first switching unit (20, 21) in front, and a second switching unit (18, 17) behind the second heat exchanger (3), and a first and second path (A, B) parallel to the second heat exchanger,
wherein the first and second switching unit (20,21,17,18) are designed such that the flow direction at the second heat exchanger (3) remains unchanged regardless of a switching of the flow direction of the refrigerant in the heat exchanger 3. Wärmepumpenanlage nach Anspruch 1, wobei die erste Umschalteinheit ein erstes Ventil (20) in dem ersten Pfad (A) und ein zweites Ventil (21) aufweist,
wobei das erste und zweite Ventil (20, 21) aufeinander abgestimmt sind.Heat pump system according to claim 1, wherein the first switching unit has a first valve (20) in the first path (A) and a second valve (21),
wherein the first and second valves (20, 21) are matched. Wärmepumpenanlage nach einem der vorherigen Ansprüche, wobei die zweite Umschalteinheit ein drittes Ventil (17) und ein viertes Ventil (18) in dem zweiten Pfad (B) aufweist, wobei das dritte und vierte Ventil (17, 18) aufeinander abgestimmt sind.Heat pump system according to one of the preceding claims, wherein the second switching unit comprises a third valve (17) and a fourth valve (18) in the second path (B), wherein the third and fourth valve (17, 18) are coordinated. Wärmepumpenanlage nach einem der Ansprüche 1-3. wobei der erste oder der zweite Wärmeüberträger (2, 3) einen Platten-Wärmeüberträger, der auf der Sekundärseite von Wasser oder einem Wasser-Frostschutz-Gemisch beaufschlagt wird, einen Lamellenrohr-Wärmeüberträger, der auf der Sekundärseite von Luft beaufschlagt wird oder einen beliebigen Luft-Kältemittel-Wärmeüberträger darstellt.Heat pump system according to one of claims 1-3. wherein the first or the second heat exchanger (2, 3) a plate heat exchanger, which is acted upon on the secondary side of water or a water-antifreeze mixture, a fin heat exchanger, which on the secondary side is acted upon by air or represents any air-refrigerant heat exchanger. Wärmepumpenanlage nach einem der vorherigen Ansprüche, mit einem Rekuperator (5) zum Überhitzen des zum Verdichter (1) strömenden Sauggases während der ersten und/oder zweiten Betriebsart.Heat pump system according to one of the preceding claims, comprising a recuperator (5) for overheating the suction gas flowing to the compressor (1) during the first and / or second operating mode. Wärmepumpenanlage nach einem der vorherigen Ansprüche, mit einem Economizer (6) zum Verdampfen eines Teilvolumenstromes des flüssigen Kältemittels in der ersten oder zweiten Betriebsart zur Aufnahme von Energie aus dem Hauptvolumenstrom des unterkühlten Kältemittels, bevor es in den Verdichter (1) eingespritzt wird.Heat pump system according to one of the preceding claims, comprising an economizer (6) for vaporizing a partial volume flow of the liquid refrigerant in the first or second mode for receiving energy from the main volume flow of the supercooled refrigerant before it is injected into the compressor (1). Wärmepumpenanlage nach einem der vorherigen Ansprüche, wobei der Verdichter als ein Scroll-Verdichter ausgestaltet ist oder als ein Scroll-Verdichter, der für die Nacheinspritzung von dampfförmigem Kältemittel ausgestaltet ist.Heat pump system according to one of the preceding claims, wherein the compressor is designed as a scroll compressor or as a scroll compressor, which is designed for the post-injection of vapor refrigerant. Wärmepumpenanlage nach einem der Ansprüche 1 bis 7, wobei der Verdichter (1) als ein einstufiger oder zweistufiger Hubkolben-Verdichter, als ein zweistufiger Hubkolben-Verdichter, oder als ein einstufiger oder zweistufiger Rollkolben-Verdichter ausgestaltet ist.Heat pump system according to one of claims 1 to 7, wherein the compressor (1) as a single-stage or two-stage reciprocating compressor, as a two-stage reciprocating compressor, or as a single-stage or two-stage rotary piston compressor is configured. Wärmepumpenanlage nach einem der vorherigen Ansprüche, wobei das Kältemittel ein H-FKW-Kältemittel, ein Kohlenwasserstoff oder CO2 darstellt.Heat pump system according to one of the preceding claims, wherein the refrigerant is a HFC refrigerant, a hydrocarbon or CO 2 .
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EP2051027B1 (en) 2018-05-16
EP2051027A3 (en) 2014-11-19

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