EP2063201A2 - Procédé de fonctionnement d'un système frigorifique - Google Patents

Procédé de fonctionnement d'un système frigorifique Download PDF

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Publication number
EP2063201A2
EP2063201A2 EP09003503A EP09003503A EP2063201A2 EP 2063201 A2 EP2063201 A2 EP 2063201A2 EP 09003503 A EP09003503 A EP 09003503A EP 09003503 A EP09003503 A EP 09003503A EP 2063201 A2 EP2063201 A2 EP 2063201A2
Authority
EP
European Patent Office
Prior art keywords
measures
operating
refrigeration system
temperature
refrigerant
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
EP09003503A
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German (de)
English (en)
Other versions
EP2063201A3 (fr
EP2063201B1 (fr
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.)
Meister Remo
Original Assignee
BMS Energietechnik AG
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Filing date
Publication date
Application filed by BMS Energietechnik AG filed Critical BMS Energietechnik AG
Publication of EP2063201A2 publication Critical patent/EP2063201A2/fr
Publication of EP2063201A3 publication Critical patent/EP2063201A3/fr
Application granted granted Critical
Publication of EP2063201B1 publication Critical patent/EP2063201B1/fr
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.
  • this temperature difference can be smaller than when the refrigerant leaves the evaporator (1) "overheated" (P8 / T22) during dry expansion operation.
  • This constant can be achieved by various measures. For the sake of simplicity, we describe the constant maintenance by means of a heat exchanger (4) in the refrigerant liquid line in front of the injection valve, which keeps the outlet temperature of the liquid refrigerant constant by means of a second medium.
  • the medium used for keeping the refrigerant liquid temperature constant can be arbitrary in nature (gaseous, liquid, etc.).
  • One way of keeping constant the refrigerant liquid temperature before the injection valve (A) may be that the flow (D) of the medium to be cooled, for example water, brine, etc., is passed through a heat exchanger (4), in which on the second side the heat exchanger, the refrigerant is conducted either in cocurrent, cross or countercurrent, etc.
  • the refrigerant liquid temperature upstream of the injection valve (A) can also be regulated by the IWT (2) by means of mass flow control of the refrigerant liquid (9) by the IWT (2) (depending on the conditions, in some cases only partial mass flows flow through the IWT (2)).
  • New in the invention is that the refrigerant liquid temperature, especially in the two-stage evaporation process (1 + 2) in front of the injection valve (6) (A) at a very low value, near or on the left limit curve of the log (p), h diagram 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.
  • Measures may be appropriate, as in the constant maintenance of the refrigerant liquid before the injection valve (6) (A).
  • heat exchangers or storage or inertial masses are used for keeping the suction steam temperature constant.
  • Suction-plate temperature maintenance may also be performed by means such as external sub-coolers (3) which control the refrigerant liquid inlet temperature to the IWT (2) (8) and in this way control the suction vapor exit temperature from the IWT (2) (B).
  • the Saugdampftemperaturkonstantaria can also be regulated by means of mass flow control of the refrigerant liquid (9) by the IWT (2) or the suction steam (12) by the IWT (2).
  • Suction temperature maintenance can also be achieved by more or less "flooding" the IWT (2) (only in the two-stage evaporation process).
  • the "flooding" of the IWT (2) can by means of a temperature control of the suction steam at the inlet of the compressor (two-stage evaporator control) (T23), level control (7) directly through the evaporator (1), IWT (2) individually or together or a reference variable For example, the collector or other or a pressure difference control (7) directly via the evaporator (1), IWT (2) individually or together.
  • the invention is based on the fact that the refrigerant liquid temperature upstream of the injection valve (A) and the suction steam temperature upstream of the compressor (B) are at an arbitrary value by suitable measures (within the physically possible, however, as far as possible reaching the physical limits) is held.
  • 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 process of refrigeration 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 injector (A) and the suction steam in front of the compressor inlet (B) is controlled, controlled and 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.
  • the innovation is to control the two described refrigerant conditions (A + B), no matter which method this is used with, depending on the application, only one or the other measure (A or B or 7) must be taken. It is thus possible, only with the temperature control of the liquid refrigerant before the injection valve (A) or the temperature control of the suction steam before the compressor (B) or with the control of the liquid refrigerant before the injection valve and the temperature control of the suction steam (A + B) desired result to come.
  • the temperature in front of the injection valve is kept constant by means of suitable measures (as described above).
  • This temperature constant maintenance of the liquid refrigerant upstream of the injection valve can be done, for example, with a built-in between the liquid line and the medium flow heat exchanger (4).
  • the medium can be passed through the exchanger at a regulated or uncontrolled temperature.
  • the proportion of already evaporated refrigerant in the evaporator can be optimized and adjusted with a corresponding temperature of the liquid refrigerant upstream of the injection valve (A) to the Verdampferbauart (1) and thus the efficiency for starting the evaporation process.
  • the refrigerant liquid inlet temperature in the second evaporator stage (IWT) (2) (F), for example by means of an external Subcooler (3) are limited at high condensation temperatures.

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)
EP09003503A 2004-01-28 2004-01-28 Procédé de fonctionnement d'un système frigorifique Expired - Lifetime EP2063201B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP04705750A EP1709372B1 (fr) 2004-01-28 2004-01-28 Evaporation a haut rendement dans des dispositifs frigorifiques et procede correspondant d'obtention de conditions stables avec des differences de temperature minimales et/ou requises des produits a refroidir par rapport a la temperature d'evaporation
PCT/CH2004/000046 WO2005073645A1 (fr) 2004-01-28 2004-01-28 Evaporation a haut rendement dans des dispositifs frigorifiques et procede correspondant d'obtention de conditions stables avec des differences de temperature minimales et/ou requises des produits a refroidir par rapport a la temperature d'evaporation

Related Parent Applications (2)

Application Number Title Priority Date Filing Date
EP04705750.0 Division 2004-01-28
EP04705750A Division EP1709372B1 (fr) 2004-01-28 2004-01-28 Evaporation a haut rendement dans des dispositifs frigorifiques et procede correspondant d'obtention de conditions stables avec des differences de temperature minimales et/ou requises des produits a refroidir par rapport a la temperature d'evaporation

Publications (3)

Publication Number Publication Date
EP2063201A2 true EP2063201A2 (fr) 2009-05-27
EP2063201A3 EP2063201A3 (fr) 2009-10-14
EP2063201B1 EP2063201B1 (fr) 2013-02-27

Family

ID=34812843

Family Applications (2)

Application Number Title Priority Date Filing Date
EP09003503A Expired - Lifetime EP2063201B1 (fr) 2004-01-28 2004-01-28 Procédé de fonctionnement d'un système frigorifique
EP04705750A Expired - Lifetime EP1709372B1 (fr) 2004-01-28 2004-01-28 Evaporation a haut rendement dans des dispositifs frigorifiques et procede correspondant d'obtention de conditions stables avec des differences de temperature minimales et/ou requises des produits a refroidir par rapport a la temperature d'evaporation

Family Applications After (1)

Application Number Title Priority Date Filing Date
EP04705750A Expired - Lifetime EP1709372B1 (fr) 2004-01-28 2004-01-28 Evaporation a haut rendement dans des dispositifs frigorifiques et procede correspondant d'obtention de conditions stables avec des differences de temperature minimales et/ou requises des produits a refroidir par rapport a la temperature d'evaporation

Country Status (6)

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

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9010136B2 (en) 2004-01-28 2015-04-21 Bms-Energietechnik Ag Method of obtaining stable conditions for the evaporation temperature of a media to be cooled through evaporation in a refrigerating installation
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

Citations (15)

* 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
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
EP0325163A1 (fr) * 1988-01-21 1989-07-26 Linde Aktiengesellschaft Procédé de fonctionnement d'une installation frigorifique et installation frigorifique pour la mise en oeuvre du procédé
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
DE29800048U1 (de) * 1998-01-03 1998-04-23 Koenig Harald Wärmepumpe mit Anordnung eines Wärmetauschers zur Leistungszahlverbesserung
EP1043550A1 (fr) * 1997-12-26 2000-10-11 Zexel Corporation Cycle de refrigeration
US6164086A (en) * 1996-08-14 2000-12-26 Daikin Industries, Ltd. Air conditioner
US6293123B1 (en) * 1999-07-30 2001-09-25 Denso Corporation Refrigeration cycle device
US6330802B1 (en) * 2000-02-22 2001-12-18 Behr Climate Systems, Inc. Refrigerant loss detection
US6438978B1 (en) * 1998-01-07 2002-08-27 General Electric Company Refrigeration system
US6446450B1 (en) * 1999-10-01 2002-09-10 Firstenergy Facilities Services, Group, Llc Refrigeration system with liquid temperature control
WO2003051657A1 (fr) * 2001-12-19 2003-06-26 Sinvent As Systeme de compression de la vapeur destine au chauffage et au refroidissement des vehicules
WO2004053406A1 (fr) * 2002-12-11 2004-06-24 Bms-Energietechnik Ag Systeme de commande de processus d'evaporation utilise dans la technique frigorifique

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3952533A (en) * 1974-09-03 1976-04-27 Kysor Industrial Corporation Multiple valve refrigeration system
JP3598604B2 (ja) * 1995-09-08 2004-12-08 ダイキン工業株式会社 熱搬送装置
US5970732A (en) * 1997-04-23 1999-10-26 Menin; Boris Beverage cooling 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
US6216481B1 (en) * 1999-09-15 2001-04-17 Jordan Kantchev Refrigeration system with heat reclaim and with floating condensing pressure
NO318864B1 (no) * 2002-12-23 2005-05-18 Sinvent As Forbedret varmepumpesystem
US9010136B2 (en) 2004-01-28 2015-04-21 Bms-Energietechnik Ag Method of obtaining stable conditions for the evaporation temperature of a media to be cooled through evaporation in a refrigerating installation

Patent Citations (15)

* 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
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
EP0325163A1 (fr) * 1988-01-21 1989-07-26 Linde Aktiengesellschaft Procédé de fonctionnement d'une installation frigorifique et installation frigorifique pour la mise en oeuvre du procédé
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
US6164086A (en) * 1996-08-14 2000-12-26 Daikin Industries, Ltd. Air conditioner
EP1043550A1 (fr) * 1997-12-26 2000-10-11 Zexel Corporation Cycle de refrigeration
DE29800048U1 (de) * 1998-01-03 1998-04-23 Koenig Harald Wärmepumpe mit Anordnung eines Wärmetauschers zur Leistungszahlverbesserung
US6438978B1 (en) * 1998-01-07 2002-08-27 General Electric Company Refrigeration system
US6293123B1 (en) * 1999-07-30 2001-09-25 Denso Corporation Refrigeration cycle device
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
WO2003051657A1 (fr) * 2001-12-19 2003-06-26 Sinvent As Systeme de compression de la vapeur destine au chauffage et au refroidissement des vehicules
WO2004053406A1 (fr) * 2002-12-11 2004-06-24 Bms-Energietechnik Ag Systeme de commande de processus d'evaporation utilise dans la technique frigorifique

Also Published As

Publication number Publication date
WO2005073645A1 (fr) 2005-08-11
EP1709372A1 (fr) 2006-10-11
US20070137229A1 (en) 2007-06-21
ATE426785T1 (de) 2009-04-15
DE502004009247D1 (de) 2009-05-07
US9010136B2 (en) 2015-04-21
ES2401946T3 (es) 2013-04-25
ES2322152T3 (es) 2009-06-17
EP1709372B1 (fr) 2009-03-25
EP2063201A3 (fr) 2009-10-14
EP2063201B1 (fr) 2013-02-27

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