EP2051027A2 - Installation de pompe de chaleur - Google Patents

Installation de pompe de chaleur 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
Authority
EP
European Patent Office
Prior art keywords
refrigerant
heat exchanger
compressor
heat pump
pump system
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.)
Granted
Application number
EP08018307A
Other languages
German (de)
English (en)
Other versions
EP2051027B1 (fr
EP2051027A3 (fr
Inventor
Steffen Smollich
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.)
Stiebel Eltron GmbH and Co KG
Original Assignee
Stiebel Eltron 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 Stiebel Eltron GmbH and Co KG filed Critical Stiebel Eltron GmbH and Co KG
Publication of EP2051027A2 publication Critical patent/EP2051027A2/fr
Publication of EP2051027A3 publication Critical patent/EP2051027A3/fr
Application granted granted Critical
Publication of EP2051027B1 publication Critical patent/EP2051027B1/fr
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
    • 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.

Landscapes

  • 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)
EP08018307.2A 2007-10-19 2008-10-20 Installation de pompe à chaleur Active EP2051027B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102007050469A DE102007050469A1 (de) 2007-10-19 2007-10-19 Wärmepumpenanlage

Publications (3)

Publication Number Publication Date
EP2051027A2 true EP2051027A2 (fr) 2009-04-22
EP2051027A3 EP2051027A3 (fr) 2014-11-19
EP2051027B1 EP2051027B1 (fr) 2018-05-16

Family

ID=40239791

Family Applications (1)

Application Number Title Priority Date Filing Date
EP08018307.2A Active EP2051027B1 (fr) 2007-10-19 2008-10-20 Installation de pompe à chaleur

Country Status (2)

Country Link
EP (1) EP2051027B1 (fr)
DE (1) DE102007050469A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102494439A (zh) * 2011-12-07 2012-06-13 南京大学 一种光伏光热蓄能热泵系统
CN110645736A (zh) * 2019-06-28 2020-01-03 江苏雪龙新能源科技有限公司 直流变频二氧化碳热泵冷热机组

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102022211369A1 (de) * 2022-10-26 2024-05-02 Robert Bosch Gesellschaft mit beschränkter Haftung Vorrichtung zur Klimatisierung eines Gebäudes

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102005061480B3 (de) 2005-12-22 2007-04-05 Stiebel Eltron Gmbh & Co. Kg Wärmepumpenanlage

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH07324844A (ja) * 1994-05-31 1995-12-12 Sanyo Electric Co Ltd ６方向切替弁及びそれを用いた冷凍装置
JPH1073334A (ja) * 1996-08-28 1998-03-17 Sanyo Electric Co Ltd 冷凍装置
JP4273588B2 (ja) * 1999-08-30 2009-06-03 ダイキン工業株式会社 空気調和装置の冷媒回路
JP2003042583A (ja) * 2001-07-27 2003-02-13 Saginomiya Seisakusho Inc 空気調和機の制御装置及び空気調和機
US7257955B2 (en) * 2004-09-08 2007-08-21 Carrier Corporation Discharge valve to increase heating capacity of heat pumps
JP5309424B2 (ja) * 2006-03-27 2013-10-09 ダイキン工業株式会社 冷凍装置

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102005061480B3 (de) 2005-12-22 2007-04-05 Stiebel Eltron Gmbh & Co. Kg Wärmepumpenanlage

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102494439A (zh) * 2011-12-07 2012-06-13 南京大学 一种光伏光热蓄能热泵系统
CN102494439B (zh) * 2011-12-07 2013-07-24 南京大学 一种光伏光热蓄能热泵系统
CN110645736A (zh) * 2019-06-28 2020-01-03 江苏雪龙新能源科技有限公司 直流变频二氧化碳热泵冷热机组

Also Published As

Publication number Publication date
EP2051027B1 (fr) 2018-05-16
DE102007050469A1 (de) 2009-04-23
EP2051027A3 (fr) 2014-11-19

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