EP1709372B1 - Hocheffiziente verdampfung bei kälteanlagen mit dem dazu nötigen verfahren zum erreichen stabilster verhältnisse bei kleinsten und/oder gewünschten temperaturdifferenzen der zu kühlenden medien zur verdampfungstemperatur - Google Patents

Hocheffiziente verdampfung bei kälteanlagen mit dem dazu nötigen verfahren zum erreichen stabilster verhältnisse bei kleinsten und/oder gewünschten temperaturdifferenzen der zu kühlenden medien zur verdampfungstemperatur Download PDF

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Publication number
EP1709372B1
EP1709372B1 EP04705750A EP04705750A EP1709372B1 EP 1709372 B1 EP1709372 B1 EP 1709372B1 EP 04705750 A EP04705750 A EP 04705750A EP 04705750 A EP04705750 A EP 04705750A EP 1709372 B1 EP1709372 B1 EP 1709372B1
Authority
EP
European Patent Office
Prior art keywords
refrigerant
temperature
injection valve
evaporation
evaporator
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
EP04705750A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP1709372A1 (de
Inventor
Remo Meister
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.)
BMS Energietechnik AG
Original Assignee
BMS Energietechnik 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 BMS Energietechnik AG filed Critical BMS Energietechnik AG
Priority to EP09003503A priority Critical patent/EP2063201B1/de
Publication of EP1709372A1 publication Critical patent/EP1709372A1/de
Application granted granted Critical
Publication of EP1709372B1 publication Critical patent/EP1709372B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
    • 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
    • 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
    • F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
    • F25B5/04—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in series
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2513—Expansion 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2103—Temperatures near a heat exchanger
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2115—Temperatures of a compressor or the drive means therefor
    • F25B2700/21151—Temperatures of a compressor or the drive means therefor at the suction side of the compressor

Definitions

  • the dry expansion operation in which the refrigerant undergoes a pressure reduction via an injection valve and the liquid state in a liquid / vapor mixture to completely evaporate in the evaporator, and then leave the evaporator with slightly superheated steam and so on Heat absorption a second medium cools down and secondly, the Thermosyphon ses in which the refrigerant is supplied via a balancing and separation vessel to the evaporator either by gravity or by means of a pump liquid and where at the evaporator outlet may still contain liquid fractions in the steam and so in the Usually there is no overheating of the refrigerant at the evaporator outlet.
  • Dry expansion systems have the advantage of simple design and small refrigerant contents.
  • the evaporator efficiency is essentially influenced by the smallest possible overheating of the evaporator.
  • Our innovation relates first to the dry expansion system (6) (1), to the dry expansion system (6) (1) with downstream IWT (2) (internal heat exchanger, ie with a heat exchange between the refrigerant liquid line before the expansion valve on the one hand and the suction steam after the evaporator on the other hand), to the two-stage evaporation system (6) (1 + 2) (a combination of dry expansion system and thermosyphon system, evaporator with IWT) and other refrigerators constructed on this basis.
  • IWT internal heat exchanger, ie with a heat exchange between the refrigerant liquid line before the expansion valve on the one hand and the suction steam after the evaporator on the other hand
  • x value is the value which indicates the proportion of the already vaporized refrigerant at the beginning of the evaporation process) of the refrigerant state in the injection valve (6 ) and in the evaporator start (1), which has an impact on the injection valve (6) and evaporator performance (1) and the control behavior of the injection valve (6) and its performance, respectively, the delivered refrigerant mass flow and on the other hand the suction steam at the inlet to the compressor (5 ), where the changed temperature (B), because of the specific temperature associated with the respective temperature (and pressure), has an influence on the delivery volume of the compressor (5), ie in turn on the delivered mass flow.
  • the aim of the invention is to achieve in cooling / Tiefkühlangel, chillers for cooling and heating operation, refrigeration systems, refrigeration sets, heat pumps and all systems with the use of refrigerants and Kälteträgem following:
  • the temperature of the refrigerant upstream of the injection valve (6) (A) is kept constant at a defined temperature value (A).
  • this temperature difference can be smaller than when the refrigerant leaves the evaporator (1) "overheated" (P8 / T22) during dry expansion operation.
  • the stabilization of the refrigerant liquid temperature upstream of the injection valve (A) takes place via storage, latent storage, inertial or storage masses (13).
  • New in the invention is that the refrigerant liquid temperature, especially in the two-stage evaporation process (1 + 2) before the injection valve (6) (A) at a very low value, near or on the left limit curve of the log (p), h Diagrarnms for refrigerant, (The refrigerant thus occurs liquid as in a thermosyphone system or with a minimum vapor content in the evaporator (1)) is kept constant.
  • the invention is based on the fact that the refrigerant liquid temperature upstream of the injection valve (A) is kept constant at an arbitrary value by appropriate measures (within the physically possible, however, as far as possible up to the physical limits).
  • valves, heat exchangers, etc. can be used individually or in any possible combination. Further representations will be omitted and refer to the text!
  • the invention is based on the fact that by means of suitable measures a stable operation of cooling systems is achieved with small temperature differences of the media to be cooled and thus higher efficiencies (and thereby highly efficient evaporation in refrigeration systems).
  • the method of cooling is supplemented or changed to the effect that in addition to the controlled suction and high pressures in refrigeration systems, the temperature of the liquid refrigerant before the injection valve (A) is kept constant.
  • Controlling the refrigerant temperature upstream of the injection valve (A) results in defined states in the refrigerant mixture (liquid / vapor). These defined conditions in the refrigerant lead to stable conditions in the refrigeration cycle.
  • This temperature (A) and the associated refrigerant conditions can be controlled and stabilized in many possible ways.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
  • Air Conditioning Control Device (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Greenhouses (AREA)
EP04705750A 2004-01-28 2004-01-28 Hocheffiziente verdampfung bei kälteanlagen mit dem dazu nötigen verfahren zum erreichen stabilster verhältnisse bei kleinsten und/oder gewünschten temperaturdifferenzen der zu kühlenden medien zur verdampfungstemperatur Expired - Lifetime EP1709372B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP09003503A EP2063201B1 (de) 2004-01-28 2004-01-28 Verfahren zum Betreiben einer Kälteanlage

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/CH2004/000046 WO2005073645A1 (de) 2004-01-28 2004-01-28 Hocheffiziente verdampfung bei kälteanlagen mit dem dazu nötigen verfahren zum erreichen stabilster verhältnisse bei kleinsten und/oder gewünschten temperaturdifferenzen der zu kühlenden medien zur verdampfungstemperatur

Related Child Applications (1)

Application Number Title Priority Date Filing Date
EP09003503A Division EP2063201B1 (de) 2004-01-28 2004-01-28 Verfahren zum Betreiben einer Kälteanlage

Publications (2)

Publication Number Publication Date
EP1709372A1 EP1709372A1 (de) 2006-10-11
EP1709372B1 true EP1709372B1 (de) 2009-03-25

Family

ID=34812843

Family Applications (2)

Application Number Title Priority Date Filing Date
EP09003503A Expired - Lifetime EP2063201B1 (de) 2004-01-28 2004-01-28 Verfahren zum Betreiben einer Kälteanlage
EP04705750A Expired - Lifetime EP1709372B1 (de) 2004-01-28 2004-01-28 Hocheffiziente verdampfung bei kälteanlagen mit dem dazu nötigen verfahren zum erreichen stabilster verhältnisse bei kleinsten und/oder gewünschten temperaturdifferenzen der zu kühlenden medien zur verdampfungstemperatur

Family Applications Before (1)

Application Number Title Priority Date Filing Date
EP09003503A Expired - Lifetime EP2063201B1 (de) 2004-01-28 2004-01-28 Verfahren zum Betreiben einer Kälteanlage

Country Status (6)

Country Link
US (1) US9010136B2 (es)
EP (2) EP2063201B1 (es)
AT (1) ATE426785T1 (es)
DE (1) DE502004009247D1 (es)
ES (2) ES2401946T3 (es)
WO (1) WO2005073645A1 (es)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2063201B1 (de) 2004-01-28 2013-02-27 Remo Meister Verfahren zum Betreiben einer Kälteanlage
DE202007017723U1 (de) * 2007-11-21 2008-03-20 Meister, Remo Anlage für die Kälte-, Heiz- oder Klimatechnik, insbesondere Kälteanlage
DE102008043823B4 (de) * 2008-11-18 2011-05-12 WESKA Kälteanlagen GmbH Wärmepumpenanlage
DE102012002593A1 (de) * 2012-02-13 2013-08-14 Eppendorf Ag Zentrifuge mit Kompressorkühleinrichtung und Verfahren zur Steuerung einer Kompressorkühleinrichtung einer Zentrifuge
CA3137384C (en) * 2019-08-23 2024-04-16 Guangdong Meizhi Compressor Co., Ltd. Rotary compressor and refrigeration cycle device

Family Cites Families (24)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3640086A (en) * 1970-02-27 1972-02-08 American Standard Inc Refrigerant flow control employing plural valves
US3952533A (en) * 1974-09-03 1976-04-27 Kysor Industrial Corporation Multiple valve refrigeration system
DE2451361A1 (de) * 1974-10-29 1976-05-06 Jakob Verfahren zum regeln einer kompressorkuehlanlage
US4493193A (en) 1982-03-05 1985-01-15 Rutherford C. Lake, Jr. Reversible cycle heating and cooling system
DE3801711A1 (de) * 1988-01-21 1989-07-27 Linde Ag Verfahren zum betreiben einer kaelteanlage und kaelteanlage zur durchfuehrung des verfahrens
US5150584A (en) 1991-09-26 1992-09-29 General Motors Corporation Method and apparatus for detecting low refrigerant charge
US5533352A (en) * 1994-06-14 1996-07-09 Copeland Corporation Forced air heat exchanging system with variable fan speed control
JP3598604B2 (ja) * 1995-09-08 2004-12-08 ダイキン工業株式会社 熱搬送装置
JPH1054616A (ja) * 1996-08-14 1998-02-24 Daikin Ind Ltd 空気調和機
US5970732A (en) * 1997-04-23 1999-10-26 Menin; Boris Beverage cooling system
JPH11193967A (ja) * 1997-12-26 1999-07-21 Zexel:Kk 冷凍サイクル
DE29800048U1 (de) * 1998-01-03 1998-04-23 König, Harald, 04934 Hohenleipisch Wärmepumpe mit Anordnung eines Wärmetauschers zur Leistungszahlverbesserung
US6438978B1 (en) * 1998-01-07 2002-08-27 General Electric Company Refrigeration system
US5921092A (en) * 1998-03-16 1999-07-13 Hussmann Corporation Fluid defrost system and method for secondary refrigeration systems
FR2779994B1 (fr) * 1998-06-23 2000-08-11 Valeo Climatisation Circuit de climatisation de vehicule muni d'un dispositif de predetente
US6170270B1 (en) * 1999-01-29 2001-01-09 Delaware Capital Formation, Inc. Refrigeration system using liquid-to-liquid heat transfer for warm liquid defrost
JP3985394B2 (ja) * 1999-07-30 2007-10-03 株式会社デンソー 冷凍サイクル装置
US6216481B1 (en) * 1999-09-15 2001-04-17 Jordan Kantchev Refrigeration system with heat reclaim and with floating condensing pressure
US6446450B1 (en) * 1999-10-01 2002-09-10 Firstenergy Facilities Services, Group, Llc Refrigeration system with liquid temperature control
US6330802B1 (en) 2000-02-22 2001-12-18 Behr Climate Systems, Inc. Refrigerant loss detection
NO320664B1 (no) * 2001-12-19 2006-01-16 Sinvent As System for oppvarming og kjoling av kjoretoy
ATE380321T1 (de) * 2002-12-11 2007-12-15 Bms Energietechnik Ag Verdampfungsprozesssteuerung in der kältetechnik
NO318864B1 (no) * 2002-12-23 2005-05-18 Sinvent As Forbedret varmepumpesystem
EP2063201B1 (de) 2004-01-28 2013-02-27 Remo Meister Verfahren zum Betreiben einer Kälteanlage

Also Published As

Publication number Publication date
WO2005073645A1 (de) 2005-08-11
ES2322152T3 (es) 2009-06-17
ATE426785T1 (de) 2009-04-15
US20070137229A1 (en) 2007-06-21
EP2063201B1 (de) 2013-02-27
EP2063201A3 (de) 2009-10-14
DE502004009247D1 (de) 2009-05-07
ES2401946T3 (es) 2013-04-25
EP1709372A1 (de) 2006-10-11
EP2063201A2 (de) 2009-05-27
US9010136B2 (en) 2015-04-21

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