EP0876576B1 - Installation frigorifique a compression - Google Patents

Installation frigorifique a compression Download PDF

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Publication number
EP0876576B1
EP0876576B1 EP96900877A EP96900877A EP0876576B1 EP 0876576 B1 EP0876576 B1 EP 0876576B1 EP 96900877 A EP96900877 A EP 96900877A EP 96900877 A EP96900877 A EP 96900877A EP 0876576 B1 EP0876576 B1 EP 0876576B1
Authority
EP
European Patent Office
Prior art keywords
refrigerant
filling
degree
heat exchanger
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.)
Expired - Lifetime
Application number
EP96900877A
Other languages
German (de)
English (en)
Other versions
EP0876576A1 (fr
Inventor
Jürgen Köhler
Michael Sonnekalb
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.)
Konvekta AG
Original Assignee
Konvekta AG
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 Konvekta AG filed Critical Konvekta AG
Publication of EP0876576A1 publication Critical patent/EP0876576A1/fr
Application granted granted Critical
Publication of EP0876576B1 publication Critical patent/EP0876576B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

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
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
    • 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
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
    • F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
    • 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
    • F25B2600/17—Control issues by controlling the pressure of the condenser

Definitions

  • the invention relates to a compression refrigeration system with a compressor, a gas cooler, an expansion device and an evaporator, which are connected to one another in a circuit in which a refrigerant is contained.
  • Such a compression refrigeration system is known for example from WO 90/07683.
  • This known system is designed as a transcritical system, i.e. it is transcritical.
  • Carbon dioxide is used as the refrigerant.
  • a compression refrigeration system of the type mentioned is also known from WO 94/14016. This well-known system also works transcritically with carbon dioxide as the refrigerant.
  • the refrigerant pressure on the high-pressure side is set precisely within relatively narrow limits.
  • This is according to the above mentioned WO 94/14016 achieved in that the degree of filling of the refrigerant, which is defined as the quotient of refrigerant charge to the total volume of the system, in the system to a value between 0.55 and 0.70 kg / ltr. preferably to 0.60 kg / ltr. is set.
  • the critical density of carbon dioxide as a refrigerant is 466 gr / liter, ie in this known system the degree of filling of the refrigerant is between 120 and 150%, preferably around 130%, of the critical density.
  • the known transcritical system according to WO 94/14016 results in a maximum of the cooling capacity.
  • the compression refrigeration system with an additional refrigerant store.
  • the store there also serves to absorb excess carbon dioxide when a certain resting pressure is exceeded on the low-pressure side of the system, for. B. at a standstill in a hot environment.
  • the invention has for its object to provide a compression refrigeration system of the type mentioned, which is comparatively simple and which can be used without problems in a relatively large outside temperature range, without thereby significantly impairing the refrigeration capacity of the system.
  • This object is achieved according to the invention in a compression refrigeration system of the type mentioned at the outset in that the degree of filling of the refrigerant is between 50 and 100% of the critical density of the refrigerant.
  • Carbon dioxide is preferably used as the refrigerant. Carbon dioxide is advantageously available as waste in industrial production and is therefore very inexpensive. As such, carbon dioxide has been known as a refrigerant since the turn of the 19th and 20th centuries.
  • the degree of filling of the carbon dioxide refrigerant is preferably between 0.25 and 0.45 kg of carbon dioxide / liter. Total volume of the cycle plant.
  • the degree of filling is actually constant in the system according to the invention.
  • the degree of filling can be adjustable depending on the average outside temperature of the climatic region in which the system according to the invention is used. This means that the degree of filling can be selected to be greater with increasing outside or ambient temperature.
  • the compression refrigeration system according to the invention is preferably designed to be transcritical.
  • the system according to the invention can also be operated subcritically.
  • FIG. 1 schematically shows in a circuit diagram representation an embodiment of the compression refrigeration system 10 with a compressor 12, a gas cooler 14 or condenser connected to the compressor 12, an expansion device 16 connected to the gas cooler 14 and an evaporator 18.
  • the compressor 12, the gas cooler 14, the expansion device 16 and the evaporator 18 are connected to one another in a circuit. Is in the cycle contain a refrigerant, which is preferably carbon dioxide.
  • FIG. 2 illustrates the functional relationship between the cooling coefficient E of the system 10 as a function of the high-pressure pressure p on the compressor 12 or on the inlet side of the gas cooler 14 assigned to the compressor 12. This is shown in FIG. 1 by the arrow 20 in combination with the symbol p for indicated the said pressure.
  • the coefficient of refrigeration ⁇ has a maximum ⁇ max at a certain pressure p o . This is achieved by a certain refrigerant filling level f, which - as has been explained above - according to WO 94/14016 between 0.55 and 0.70 kg / ltr., Preferably 0.60 kg / ltr. is.
  • FIG. 1 illustrates the functional relationship between the cooling coefficient E of the system 10 as a function of the high-pressure pressure p on the compressor 12 or on the inlet side of the gas cooler 14 assigned to the compressor 12.
  • p o the coefficient of refrigeration ⁇ has a maximum ⁇ max at a certain pressure p o .
  • f refriger
  • the degree of filling f is selected to be significantly smaller than that described last above. This is illustrated by Figure 3, in which f the filling level above the gas cooler Austrittstempertur t is from clarified.
  • the gas cooler exit temperature, the measurement point in Fig. 1 by the arrow 21 in connection with the label T is made clear, is usually on the order of 5 to 15 K above the ambient temperature etc. and is dependent on the compressor speed.
  • the degree of refrigerant filling f of the system 10 according to the invention see FIG.
  • FIG. 3 also illustrates the filling degree range according to the compression refrigeration system, as described in WO 94/14016 is disclosed. This last-mentioned degree of filling range is indicated as a cross-hatched area 24. It can be seen that the two filling degree ranges 22, 24 have no common ground.
  • FIG. 3 also illustrates in a line 26 the functional relationship f (t off ) of the optimal high pressure p converted into an optimal fill level f or a bandwidth for the fill level f. Line 26 shows that the course of line 26 becomes very flat above the critical temperature of 31 ° C.
  • FIG. 4 shows a schematic circuit diagram of a compression refrigeration system 10 with a compressor 12, a gas cooler 14 connected to the compressor, an intermediate heat exchanger 28, an expansion device 16 and an evaporator 18.
  • the intermediate heat exchanger 28 has a first heat exchanger branch 30 and a second heat exchanger branch 32 that are thermally coupled to each other.
  • the first heat exchanger strand 30 is connected between the gas cooler 14 and the expansion device 16.
  • the second heat exchanger strand 32 is connected between the evaporator 18 and the compressor 12.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Filling Or Discharging Of Gas Storage Vessels (AREA)
  • Air-Conditioning For Vehicles (AREA)
  • Separation By Low-Temperature Treatments (AREA)

Claims (5)

  1. Installation de réfrigération par compression, du type comprenant un compresseur (12), un réfrigérateur de gaz (14), un dispositif d'expansion (15) et un évaporateur (18) qui vont réunir les uns avec les autres suivant un circuit fermé, dans lequel est contenu un agent de réfrigération,
       caractérisée en ce que le degré de remplissage (f) de l'agent de réfrigération représente entre 50% et 100% de la masse spécifique critique de l'agent de réfrigération.
  2. Installation selon la revendication 1, caractérisée en ce que l'agent de réfrigération consiste en anhydride carbonique.
  3. Installation selon les revendications 1 et 2, caractérisée en ce que le degré de remplissage (11) de l'anhydride carbonique-agent de réfrigération est compris entre 0,25 et 0,45 kg/l.
  4. Installation selon l'une des revendications précédentes, caractérisée en ce que l'installation fonctionne en mode transcritique.
  5. Installation selon l'une des revendications précédentes, caractérisée en ce qu'il est prévu un échangeur de chaleur intermédiaire (28) se composant d'un premier faisceau d'échange de chaleur et d'un second faisceau d'échange de chaleur associés thermiquement l'un à l'autre (30, 32), le premier faisceau d'échange de chaleur (30) étant relié au réfrigérateur de gaz (14) et au dispositif d'expansion (16), et le second faisceau d'échange de chaleur (32) étant relié à l'évaporateur (18) et au compresseur (12).
EP96900877A 1996-01-26 1996-01-26 Installation frigorifique a compression Expired - Lifetime EP0876576B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
PCT/DE1996/000140 WO1997027437A1 (fr) 1996-01-26 1996-01-26 Installation frigorifique a compression
CN96199783.4A CN1113205C (zh) 1996-01-26 1996-01-26 压缩制冷装置
US09/119,484 US6085544A (en) 1996-01-26 1998-07-20 Compression refrigeration unit

Publications (2)

Publication Number Publication Date
EP0876576A1 EP0876576A1 (fr) 1998-11-11
EP0876576B1 true EP0876576B1 (fr) 2000-04-05

Family

ID=27179115

Family Applications (1)

Application Number Title Priority Date Filing Date
EP96900877A Expired - Lifetime EP0876576B1 (fr) 1996-01-26 1996-01-26 Installation frigorifique a compression

Country Status (9)

Country Link
US (1) US6085544A (fr)
EP (1) EP0876576B1 (fr)
JP (1) JP3665346B2 (fr)
CN (1) CN1113205C (fr)
AU (1) AU4482496A (fr)
BR (1) BR9612461A (fr)
DE (2) DE19681212D2 (fr)
ES (1) ES2144722T3 (fr)
WO (1) WO1997027437A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010001929A1 (de) 2010-02-15 2011-08-18 Konvekta AG, 34613 Kälteanlage zur Kühlung eines umschlossenen Raumes

Families Citing this family (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3262110B2 (ja) 1999-10-26 2002-03-04 松下電器産業株式会社 コンプレッサおよびそれを用いた冷媒システム装置
US6871511B2 (en) 2001-02-21 2005-03-29 Matsushita Electric Industrial Co., Ltd. Refrigeration-cycle equipment
CN1228594C (zh) * 2001-07-02 2005-11-23 三洋电机株式会社 热泵装置
NO20014258D0 (no) 2001-09-03 2001-09-03 Sinvent As System for kjöle- og oppvarmingsformål
DE10161254A1 (de) 2001-12-13 2003-07-03 Konvekta Ag Klimatisierungseinrichtung für ein Fahrzeug
US6631617B1 (en) 2002-06-27 2003-10-14 Tecumseh Products Company Two stage hermetic carbon dioxide compressor
US6923011B2 (en) * 2003-09-02 2005-08-02 Tecumseh Products Company Multi-stage vapor compression system with intermediate pressure vessel
US6959557B2 (en) * 2003-09-02 2005-11-01 Tecumseh Products Company Apparatus for the storage and controlled delivery of fluids
US7024883B2 (en) * 2003-12-19 2006-04-11 Carrier Corporation Vapor compression systems using an accumulator to prevent over-pressurization
US7096679B2 (en) * 2003-12-23 2006-08-29 Tecumseh Products Company Transcritical vapor compression system and method of operating including refrigerant storage tank and non-variable expansion device
NL1026728C2 (nl) 2004-07-26 2006-01-31 Antonie Bonte Verbetering van koelsystemen.
WO2006097229A1 (fr) * 2005-03-15 2006-09-21 Behr Gmbh & Co. Kg Circuit frigorifique
US20060260657A1 (en) * 2005-05-18 2006-11-23 Jibb Richard J System and apparatus for supplying carbon dioxide to a semiconductor application
WO2007012225A1 (fr) * 2005-07-28 2007-02-01 Tianjin University Appareil réfrigérant
EP2150755A4 (fr) * 2007-04-23 2011-08-24 Carrier Corp Système de réfrigérant à co<sb>2</sb>avec circuit intensificateur
NO327832B1 (no) 2007-06-29 2009-10-05 Sinvent As Dampkompresjons-kjolesystem med lukket krets samt fremgangsmate for drift av systemet.
US9989280B2 (en) * 2008-05-02 2018-06-05 Heatcraft Refrigeration Products Llc Cascade cooling system with intercycle cooling or additional vapor condensation cycle
JP2011521195A (ja) * 2008-05-14 2011-07-21 キャリア コーポレイション 輸送冷凍システムおよび運転方法
DE102014214656A1 (de) * 2014-07-25 2016-01-28 Konvekta Ag Kompressionskälteanlage und Verfahren zum Betrieb einer Kompressionskälteanlage

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US63413A (en) * 1867-04-02 Improved mode of manufacturing ioe
NO890076D0 (no) * 1989-01-09 1989-01-09 Sinvent As Luftkondisjonering.
NO175830C (no) * 1992-12-11 1994-12-14 Sinvent As Kompresjonskjölesystem

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010001929A1 (de) 2010-02-15 2011-08-18 Konvekta AG, 34613 Kälteanlage zur Kühlung eines umschlossenen Raumes
DE102010001929B4 (de) * 2010-02-15 2014-06-18 Konvekta Ag Kälteanlage zur Kühlung eines umschlossenen Raumes

Also Published As

Publication number Publication date
JP2000515958A (ja) 2000-11-28
JP3665346B2 (ja) 2005-06-29
CN1207803A (zh) 1999-02-10
EP0876576A1 (fr) 1998-11-11
AU4482496A (en) 1997-08-20
WO1997027437A1 (fr) 1997-07-31
CN1113205C (zh) 2003-07-02
DE19681212D2 (de) 1999-03-11
DE59604923D1 (de) 2000-05-11
US6085544A (en) 2000-07-11
ES2144722T3 (es) 2000-06-16
BR9612461A (pt) 1999-07-13

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