EP2812638B1 - Wärmepumpenvorrichtung - Google Patents

Wärmepumpenvorrichtung Download PDF

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Publication number
EP2812638B1
EP2812638B1 EP13707538.8A EP13707538A EP2812638B1 EP 2812638 B1 EP2812638 B1 EP 2812638B1 EP 13707538 A EP13707538 A EP 13707538A EP 2812638 B1 EP2812638 B1 EP 2812638B1
Authority
EP
European Patent Office
Prior art keywords
refrigerant
heat pump
pump device
collector
compressor
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.)
Active
Application number
EP13707538.8A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP2812638A2 (de
Inventor
Ulrich Hafner
Markus IMMEL
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Viessmann Generations Group GmbH and Co KG
Original Assignee
Viessmann Werke GmbH and Co KG
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Viessmann Werke GmbH and Co KG filed Critical Viessmann Werke GmbH and Co KG
Priority to PL13707538T priority Critical patent/PL2812638T3/pl
Publication of EP2812638A2 publication Critical patent/EP2812638A2/de
Application granted granted Critical
Publication of EP2812638B1 publication Critical patent/EP2812638B1/de
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
    • F25B43/006—Accumulators
    • 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
    • F25B41/39—Dispositions with two or more expansion means arranged in series, i.e. multi-stage expansion, on a refrigerant line leading to the same evaporator
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
    • 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
    • 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
    • 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
    • F25B2400/23—Separators

Definitions

  • the invention relates to a heat pump device according to the preamble of patent claim 1.
  • a heat pump device of this kind is similar even after JP 2001 153482 A known.
  • This consists inter alia of a compressor (in particular screw compressor), which is followed by a condenser (also called a condenser), in turn, a refrigerant collector (also called refrigerant tank) is connected downstream.
  • the refrigerant collector is connected to the intermediate injection of refrigerant into the compressor with this via a refrigerant line.
  • the refrigerant collector is followed by a controllable expansion valve, which in turn is followed by an evaporator, which in turn is followed by the already mentioned compressor.
  • the refrigerant circuit of the JP 2001 153482 A So corresponds to a very classic refrigerant circuit, but added to the refrigerant collector for the intermediate injection of refrigerant in the compressor.
  • the invention has for its object to further improve a heat pump device of the type mentioned.
  • the limits of use or the efficiency of such a heat pump device should be even more expanded or enlarged.
  • the refrigerant line has a refrigerant inflow opening which selectively opens above and / or below the refrigerant level during operation of the heat pump device, a section of the refrigerant line being arranged in the refrigerant collector and the section having a vertical extension direction ,
  • the heat pump device is characterized in particular by the fact that via the expansion valve, the refrigerant level in the refrigerant receiver can be adjusted, wherein the refrigerant inflow opening is formed so that it is designed depending on the setting of the expansion valve either above and / or below the refrigerant level ausmündend.
  • the proviso "and / or” means that the refrigerant line is formed with its refrigerant inlet either so that the refrigerant inflow opens either above or below the refrigerant level, or that the refrigerant inflow opening is formed so that it opens both above and below the refrigerant level, which optionally by a correspondingly large Refrigerant inflow or even by a plurality of refrigerant inflow can be realized at the guided into the refrigerant collector refrigerant pipe.
  • the heat pump device In contrast to the heat pump device mentioned above, it is thus possible with the heat pump device according to the invention to supply optionally pure refrigerant vapor, liquid refrigerant or even refrigerant wet steam to the compressor.
  • the refrigerant In which aggregate state the refrigerant is injected into the compressor, can be determined via the controllable expansion valve and thus on the refrigerant level in the refrigerant collector.
  • liquid refrigerant offers the possibility of cooling the compressor, lowering the hot gas temperature and thus extending the operating limits.
  • FIGS. 1 . 3 . 4 and 6 illustrated heat pump devices consist in a known manner from a compressor 1, in particular a so-called screw or scroll compressor, which is followed by a condenser 2, which is particularly preferably designed as a plate capacitor.
  • This capacitor is a refrigerant collector 3 (also called high-pressure collector) downstream, which is connected to the intermediate injection of refrigerant in the compressor 1 with this via a refrigerant pipe 4.
  • This intermediate injection serves, as already explained, to increase the efficiency of the heat pump device or to expand the application limits of the heat pump device.
  • heat pump device for adjusting the refrigerant level in the refrigerant collector 3 between the condenser 2 and the refrigerant collector 3, an electronically controllable (and reversible working) expansion valve 5 is arranged and that the refrigerant pipe 4 depending on the setting of the expansion valve 5 during operation the heat pump device above and / or below the refrigerant level opening refrigerant inflow opening 6 has.
  • FIG. 2 the refrigerant collector 3 is shown enlarged for better understanding.
  • a section 7 of the refrigerant line 4 is arranged in the refrigerant collector 3.
  • the refrigerant inflow opening (s) 6 is (are) arranged on the section 7 of the refrigerant line 4.
  • the section 7 is tubular and in particular formed as a U-shaped piece of pipe.
  • the section 7 further has a vertical extension direction and an open end 8.
  • the open line end 8 forms at least one of the refrigerant inflow openings 6 and is preferably always arranged above the refrigerant level during operation of the heat pump device. How to continue FIG. 2 seen At section 7, a plurality of superposed refrigerant inflow openings 6 are provided.
  • the refrigerant collector 3 has a connected to the expansion valve 5, during operation of the heat pump device opening out below the refrigerant level refrigerant supply port 9. Furthermore, it is provided that the refrigerant collector 3 has a refrigerant discharge connection 11 connected to a second electronically controllable (and reversibly operating) expansion valve 10, opening out below the refrigerant level during operation of the heat pump device. Via this refrigerant discharge port 11, the refrigerant is discharged to the second expansion valve 10.
  • refrigerant enters the refrigerant receiver 3.
  • the electronically controllable expansion valves 5 and 10 which of course with a corresponding, not specifically shown heat pump control device (also called refrigeration circuit controller) is connected set the height of the refrigerant level.
  • the refrigerant level is increased, liquid refrigerant can also pass into the section 7 and thus to the compressor 1 via one or more refrigerant inflow openings 6.
  • This liquid refrigerant mixes with the rest of the rest Refrigerant inlet 6 inflowing refrigerant vapor to a refrigerant wet steam.
  • the refrigerant collector 3 is divided into a first and a second chamber 14, 15 by a separating element 13 or partition wall (preferably a perforated plate, metal mesh or the like) having at least one through-opening 12, in particular vertically oriented Chamber 14 of the refrigerant supply port 9 opens and leaving the first chamber 14 of the refrigerant discharge port 11.
  • a separating element 13 or partition wall preferably a perforated plate, metal mesh or the like
  • the flow in the first chamber 14 is highly turbulent.
  • the proviso of the separating element 13 leads to a calming of the refrigerant in the second chamber 15, in which the portion 7 of the refrigerant pipe 4 is arranged, which in turn is favorable for the desired precise adjustment of the ratio between liquid and vapor refrigerant.
  • the refrigerant collector 3 is followed by a second electronically controllable expansion valve 10, which in turn is followed by an evaporator 16 (in particular a lamella evaporator) connected to the compressor 1 is.
  • evaporator 16 in particular a lamella evaporator
  • FIG. 4 and 5 another feature of the inventive solution is that in the first chamber 14 of the refrigerant collector 3, a refrigerant-carrying and with the refrigerant in the refrigerant receiver 3 heat exchanging line 17 is arranged, which is connected on the one hand to the evaporator 16 and the other with the compressor 1.
  • This line 17 forms together with the refrigerant collector 3 a so-called Sauggastage (2004) for supercooling of the refrigerant, via the already mentioned, not shown heat pump control device and corresponding sensors for measuring Sauggasüberhitzung or subcooling influence on the expansion valves 5 and 10 and thus on the refrigerant level can be taken.
  • a (preferably bidirectionally operating) filter 18 also called filter dryer
  • a (preferably bidirectionally operating) filter 19 filter drier is also arranged between the second expansion valve 10 and the evaporator 16.
  • FIGS. 3 and 4 a downstream of the compressor 1 switching valve, in particular a 4/2-way switching valve 20 is provided:
  • the heating operation is shown, in which taken over the evaporator 16, for example geothermal and discharged through the condenser 2 to a room of a building to be heated.
  • the 4/2-way switching valve according to FIGS. 3 and 4 turn 90 ° (both clockwise and anticlockwise), due to the Symmetrical structure of the heat pump apparatus according to the invention is readily possible, the evaporator 16 would be the condenser and the condenser 2 to the evaporator. In this case, heat would be removed via the evaporator, for example, from a room of a building and discharged through the condenser, for example, to the environment of the building.
  • the solution according to FIG. 4 finally differs from the according to FIG. 3 in that there takes place via a pipe coil (line 17), a heat transfer from the warmer refrigerant in the refrigerant header 3 to the colder refrigerant in the coil (keyword: SauggasGermanhitzung).
  • line 17 runs from the evaporator 16 via the 4/2-way valve to the first chamber 14 and from there directly to the compressor. 1

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Power Engineering (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
EP13707538.8A 2012-02-09 2013-01-30 Wärmepumpenvorrichtung Active EP2812638B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PL13707538T PL2812638T3 (pl) 2012-02-09 2013-01-30 Urządzenie pompy ciepła

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102012101041A DE102012101041A1 (de) 2012-02-09 2012-02-09 Wärmepumpenvorrichtung
PCT/DE2013/100033 WO2013117187A2 (de) 2012-02-09 2013-01-30 Wärmepumpenvorrichtung

Publications (2)

Publication Number Publication Date
EP2812638A2 EP2812638A2 (de) 2014-12-17
EP2812638B1 true EP2812638B1 (de) 2018-04-11

Family

ID=47826781

Family Applications (1)

Application Number Title Priority Date Filing Date
EP13707538.8A Active EP2812638B1 (de) 2012-02-09 2013-01-30 Wärmepumpenvorrichtung

Country Status (6)

Country Link
EP (1) EP2812638B1 (pl)
DE (1) DE102012101041A1 (pl)
DK (1) DK2812638T3 (pl)
ES (1) ES2669223T3 (pl)
PL (1) PL2812638T3 (pl)
WO (1) WO2013117187A2 (pl)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102017107051A1 (de) 2017-04-01 2018-10-04 Viessmann Werke Gmbh & Co Kg Wärmepumpe
CN112146314B (zh) * 2020-09-22 2022-03-11 华商国际工程有限公司 氨泵供液制冷系统及其控制方法

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2010039682A2 (en) * 2008-10-01 2010-04-08 Carrier Corporation Liquid vapor separation in transcritical refrigerant cycle

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3329661A1 (de) 1982-12-14 1984-06-14 VEB Kombinat Luft- und Kältetechnik, DDR 8080 Dresden Regelung von temperaturen, temperaturdifferenzen bzw. fuellstaenden in kaeltemittelkreislaeufen
JPH04371759A (ja) * 1991-06-21 1992-12-24 Hitachi Ltd 二段圧縮二段膨張式の冷凍サイクル
JP2001056157A (ja) * 1999-08-16 2001-02-27 Daikin Ind Ltd 冷凍装置
JP2001153482A (ja) 1999-11-26 2001-06-08 Mitsubishi Electric Corp スクリュー冷凍装置
JP2007303709A (ja) * 2006-05-10 2007-11-22 Sanden Corp 冷凍サイクル
DE202007019159U1 (de) 2007-03-02 2010-10-28 Stiebel Eltron Gmbh & Co. Kg Wärmepumpenvorrichtung
DE102010024986A1 (de) * 2010-06-24 2011-12-29 Stiebel Eltron Gmbh & Co. Kg Verfahren zum Steuern einer Wärmepumpeneinheit und Wärmepumpeneinheit

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2010039682A2 (en) * 2008-10-01 2010-04-08 Carrier Corporation Liquid vapor separation in transcritical refrigerant cycle

Also Published As

Publication number Publication date
EP2812638A2 (de) 2014-12-17
DE102012101041A1 (de) 2013-08-14
WO2013117187A3 (de) 2013-11-21
PL2812638T3 (pl) 2018-09-28
WO2013117187A2 (de) 2013-08-15
ES2669223T3 (es) 2018-05-24
DK2812638T3 (en) 2018-06-25

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