EP1808655A2 - Installation de refroidissement - Google Patents

Installation de refroidissement Download PDF

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Publication number
EP1808655A2
EP1808655A2 EP07000185A EP07000185A EP1808655A2 EP 1808655 A2 EP1808655 A2 EP 1808655A2 EP 07000185 A EP07000185 A EP 07000185A EP 07000185 A EP07000185 A EP 07000185A EP 1808655 A2 EP1808655 A2 EP 1808655A2
Authority
EP
European Patent Office
Prior art keywords
expansion valve
refrigeration system
evaporator
overheating
heat exchanger
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.)
Withdrawn
Application number
EP07000185A
Other languages
German (de)
English (en)
Other versions
EP1808655A3 (fr
Inventor
Uwe Dipl.-Ing. Regin
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.)
Guentner GmbH and Co KG
Original Assignee
Guentner 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 Guentner GmbH and Co KG filed Critical Guentner GmbH and Co KG
Publication of EP1808655A2 publication Critical patent/EP1808655A2/fr
Publication of EP1808655A3 publication Critical patent/EP1808655A3/fr
Withdrawn legal-status Critical Current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
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/31—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
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • 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
    • F25B2600/21—Refrigerant outlet evaporator temperature
    • 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
    • F25B2700/2117—Temperatures of an evaporator
    • F25B2700/21175—Temperatures of an evaporator of the refrigerant at the outlet of the evaporator

Definitions

  • the invention relates to a refrigeration system according to the preamble of claim 1.
  • Such a refrigeration system operates on the principle that a gaseous refrigerant is liquefied, wherein the heat occurring is derived, for example by air or water cooling.
  • a gaseous refrigerant When relaxing the refrigerant vaporizes and thereby removes the necessary heat, for example, a refrigerator, in which food is stored.
  • Such refrigeration is therefore based on a cycle with the refrigerant.
  • the refrigerant in such a refrigeration system is capable of absorbing heat by evaporation at low temperature and low pressure, for example, warm air from a space to be cooled, and to give off heat by liquefying at higher temperature and higher pressure.
  • a refrigerant is so to speak, the working fluid in a refrigeration system, also called chiller.
  • a refrigeration system according to the preamble of claim 1 is for example from the DE 203 13 777.9 U1 known.
  • the thermostatic expansion valve described here is a so-called standard expansion valve, which opens only at a static overheating from about 5 K. In this respect, the actual goal of keeping the driving temperature difference as low as possible and of saving energy can hardly be achieved with this refrigeration system.
  • the invention has for its object to provide a refrigeration system of the type mentioned, which is more economical operable.
  • the expansion valve is one with a static superheat ⁇ 2 K and the overheat sensor is arranged in the flow direction of the refrigerant behind the evaporator and in front of the inner heat exchanger, overheating of the refrigerant in the evaporator is largely excluded.
  • the driving temperature difference between the air inlet temperature and the evaporation temperature before the evaporator can thus extremely low, ie be set to about 3 to 4 K. This can be saved directly on the compressor energy, because the efficiency of the refrigeration system is increased, on the other hand, defrost energy can be saved because, for example, less dehumidification and thus less icing of the slats takes place in a refrigerator.
  • this evaporator is particularly suitable for fruit and vegetable cooling, ie for the cooling of fresh food.
  • the overheating of the gaseous refrigerant, also called suction gas thus no longer takes place exclusively in the evaporator but rather in the inner heat exchanger.
  • the evaporator can be dimensioned small, which can be achieved in addition to the energy advantages even lower production costs.
  • the superheating of the gaseous refrigerant ultimately caused by the internal heat exchanger is ensured in such a way that liquid blows in the compressor due to liquid drops still present in the suction gas are excluded.
  • the overheating zone in the evaporator can be kept as small as possible with the refrigeration system according to the invention by the low static overheating on the expansion valve.
  • the expansion valve is designed so that it opens already from a static overheating of 0 or 1 K and at a total or work overheating of about 4 K has a valve performance of 100%. It follows that the valve according to the invention is already fully open at a total or work overheating of about 4 K, whereas a conventional expansion valve starts at a static overheating of about 5 K in the first to open. It also follows that the expansion valve according to the invention has a relatively steep characteristic, thus even at extremely low superheat or already from an overheating of 1 K. It also follows that the valve performance is available quickly even at low driving temperature difference.
  • the expansion valve is a thermostatic or an electronic expansion valve.
  • a thermostatic expansion valve is characterized by a favorable price / performance ratio compared to an electronic expansion valve.
  • a refrigeration system 1 is shown schematically, in which a not-shown refrigerant in a cyclic process, ie in the circuit, is performed.
  • the refrigeration system 1, also called chiller, has an evaporator 2, an evaporator in the flow direction of the gaseous refrigerant (see arrow A) downstream inner heat exchanger 3, a downstream of the inner heat exchanger 3 compressor 4, a compressor downstream condenser 5, in which the gaseous refrigerant is condensed, wherein the condenser 5 in the flow direction of the now liquid refrigerant (see arrow B) turn the inner heat exchanger 3 is followed, and a the inner heat exchanger 3 in the flow direction of the liquid refrigerant (see arrow B) downstream and upstream of the evaporator 2 Expansion valve 6.
  • the aforementioned components are, as previously mentioned, connected to a cyclic process.
  • the expansion valve 6 has an overheating sensor 11.
  • the expansion valve 6 is one with a static superheat ⁇ 2 K and is the superheat sensor 11 in the flow direction of the refrigerant, in this case the gaseous refrigerant (see arrow A), behind the evaporator 2 and in front of the inner heat exchanger 3, thus in the suction gas line 7 between the evaporator 2 and the inner heat exchanger 3 is arranged.
  • the expansion valve 6 is designed according to a particularly preferred embodiment of the invention such that it opens already from a static overheating of 0 or 1 K and causes a valve performance of 100% at a static overheating of about 4 K.
  • the expansion valve 6 is a thermostatic or an electronic expansion valve.
  • valve characteristics of thermostatic expansion valves are schematically shown in a diagram. On the ordinate is plotted the valve performance in%, on the abscissa the superheating in Kelvin is plotted.
  • the inventive expansion valve 6 with a static superheat ⁇ 2 K has, for example, a valve characteristic 12, which is shown in a solid line, or a valve characteristic 13, which is shown in phantom.
  • a conventional thermostatic expansion valve according to the prior art has a valve characteristic 14, which is shown in dashed lines.
  • Fig. 2 illustrates a static overheating 15 with respect to the dashed line valve characteristic 14 of a conventional expansion valve of about 5 K.
  • Fig. 2 for the inventive expansion valve according to the valve characteristic 12 a static overheating of 0 K and the other valve characteristic 13 of a inventive expansion valve, which is shown in phantom in Fig. 2, a static overheating of 1 K.
  • Fig. 2 is shown in each case also the opening superheating 16, which in the case of the valve characteristic 14 about 14 K minus 5 K, ie about 9 K and in the case of the valve characteristic 12 4 K minus 0 K, ie 4 K, and in the case of Valve characteristic 13 4 K minus 1 K, ie 3 K, is.
  • the sum of respective static overheating 15 and opening superheating 16 is then the so-called total or working superheating 17.
  • This is in the case of a conventional expansion valve with the valve characteristic 14 14 K, in the case of an expansion valve according to the invention with the valve characteristic 12 about 5 K and im Case of an expansion valve according to the invention with the valve characteristic curve 13 also about 5 K.
  • the static overheating is reduced from about 5 to 1 or 0 K and the opening superheat 16 at 100% valve power from 7 K (12 K minus 5 K) to 3 K (4 K minus 1 K) in the case of Valve characteristic 13 or 4 K (4 K minus 0 K) in the case of the valve characteristic 12 is reduced.
  • Table 1 for a case A with a constant evaporation temperature t0, individual temperatures are given for a conventional refrigeration system according to the prior art and for a refrigeration system according to the invention.
  • Table 2 also shows, for a case B with a constant air inlet temperature tLe, the resulting temperatures for a prior art refrigeration system and one according to the invention.
  • the subcooling temperature tu1 is that of the liquid refrigerant in the flow direction (see arrow B in FIG. 1) before the inner heat exchanger 3, the subcooling temperature tu2 that of the liquid refrigerant after the inner heat exchanger 3.
  • the evaporation temperature t0 is tapped after the evaporator 2.
  • the inlet temperature of the air into the evaporator 2, denoted tLe, is usually the air to be cooled by the refrigeration system, for example, of a cooling space.
  • the cooled air enters at the temperature tLa, i. with an air outlet temperature, which is lower than the air inlet temperature, from the evaporator 2.
  • the temperature difference ⁇ t1 denotes the difference between the aforementioned temperatures tLe and t0.
  • the amount of heat 20 required by the evaporation of the refrigerant in the evaporator 2 can, for example, be withdrawn from the air of a cooling space. Conversely, the amount of heat 21 is released during the liquefaction of the refrigerant. This is indicated in Fig. 2 by the arrows 20 and 21, respectively.
  • the evaporation temperature t0 in the case of the refrigeration system according to the invention can be selected to be significantly higher than would be possible in a refrigeration system according to the prior art.
  • a higher overall efficiency (COP - called "coefficient of performance”) ultimately allows a more economical operation of the refrigeration system.
  • the dehumidification for example a cooling space is reduced, so that the goods contained therein is not withdrawn as much liquid as in the case of a conventional refrigeration system.
  • Another advantage of the refrigeration system according to the invention is that at an increased compared to the prior art evaporation temperature (according to Table 2 0 ° C in the case of the invention and - 8 ° C in the case of the prior art), the ice build-up and the condensate on reduces the cooling fins of the evaporator.
  • a less strongly iced evaporator has a better heat transfer than a strongly iced evaporator.
  • the defrost energy can also be reduced as a result.

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)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Air-Conditioning For Vehicles (AREA)
EP07000185A 2006-01-11 2007-01-05 Installation de refroidissement Withdrawn EP1808655A3 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE202006000385U DE202006000385U1 (de) 2006-01-11 2006-01-11 Kälteanlage

Publications (2)

Publication Number Publication Date
EP1808655A2 true EP1808655A2 (fr) 2007-07-18
EP1808655A3 EP1808655A3 (fr) 2008-04-02

Family

ID=36062845

Family Applications (1)

Application Number Title Priority Date Filing Date
EP07000185A Withdrawn EP1808655A3 (fr) 2006-01-11 2007-01-05 Installation de refroidissement

Country Status (2)

Country Link
EP (1) EP1808655A3 (fr)
DE (1) DE202006000385U1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP4170270A1 (fr) 2021-10-22 2023-04-26 Cabero Beteiligungs-GmbH Système de refroidissement

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102019001638A1 (de) * 2019-03-08 2020-09-10 Stiebel Eltron Gmbh & Co. Kg Verfahren zum Betreiben einer Wärmepumpe mit einem Dampfkompressionssystem

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4475686A (en) * 1977-11-03 1984-10-09 Danfoss A/S Valve for liquid injection into a refrigerant evaporator
US5005370A (en) * 1988-12-19 1991-04-09 Fuji Koki Mfg. Co. Ltd. Thermal expansion valve
EP1026459A1 (fr) * 1999-01-11 2000-08-09 Sanden Corporation Système frigorifique à compression de vapeur
JP2001108314A (ja) * 1999-10-05 2001-04-20 Zexel Valeo Climate Control Corp 冷凍サイクル制御装置
US6427454B1 (en) * 2000-02-05 2002-08-06 Michael K. West Air conditioner and controller for active dehumidification while using ambient air to prevent overcooling
EP1369648A2 (fr) * 2002-06-04 2003-12-10 Sanyo Electric Co., Ltd. Système de cycle à frigorigène supercritique
WO2004053406A1 (fr) * 2002-12-11 2004-06-24 Bms-Energietechnik Ag Systeme de commande de processus d'evaporation utilise dans la technique frigorifique
WO2004055454A1 (fr) * 2002-12-14 2004-07-01 Volkswagen Aktiengesellschaft Circuit de refrigerant pour une installation de climatisation de vehicule automobile
DE102004005802A1 (de) * 2004-02-06 2005-08-25 Lauda Dr. R. Wobser Gmbh & Co. Kg. Verfahren zur Regelung einer Kältemaschine nach dem Verdampferprinzip sowie Anordnung zur Ausübung des Verfahrens
US20070074538A1 (en) * 2005-09-07 2007-04-05 Denso Corporation Refrigeration cycle device

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4475686A (en) * 1977-11-03 1984-10-09 Danfoss A/S Valve for liquid injection into a refrigerant evaporator
US5005370A (en) * 1988-12-19 1991-04-09 Fuji Koki Mfg. Co. Ltd. Thermal expansion valve
EP1026459A1 (fr) * 1999-01-11 2000-08-09 Sanden Corporation Système frigorifique à compression de vapeur
JP2001108314A (ja) * 1999-10-05 2001-04-20 Zexel Valeo Climate Control Corp 冷凍サイクル制御装置
US6427454B1 (en) * 2000-02-05 2002-08-06 Michael K. West Air conditioner and controller for active dehumidification while using ambient air to prevent overcooling
EP1369648A2 (fr) * 2002-06-04 2003-12-10 Sanyo Electric Co., Ltd. Système de cycle à frigorigène supercritique
WO2004053406A1 (fr) * 2002-12-11 2004-06-24 Bms-Energietechnik Ag Systeme de commande de processus d'evaporation utilise dans la technique frigorifique
WO2004055454A1 (fr) * 2002-12-14 2004-07-01 Volkswagen Aktiengesellschaft Circuit de refrigerant pour une installation de climatisation de vehicule automobile
DE102004005802A1 (de) * 2004-02-06 2005-08-25 Lauda Dr. R. Wobser Gmbh & Co. Kg. Verfahren zur Regelung einer Kältemaschine nach dem Verdampferprinzip sowie Anordnung zur Ausübung des Verfahrens
US20070074538A1 (en) * 2005-09-07 2007-04-05 Denso Corporation Refrigeration cycle device

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
CHEN W ET AL: "Experimental investigation of a minimum stable superheat control system of an evaporator" INTERNATIONAL JOURNAL OF REFRIGERATION, OXFORD, GB, Bd. 25, Nr. 8, Dezember 2002 (2002-12), Seiten 1137-1142, XP004388595 ISSN: 0140-7007 *

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP4170270A1 (fr) 2021-10-22 2023-04-26 Cabero Beteiligungs-GmbH Système de refroidissement
DE102021127498A1 (de) 2021-10-22 2023-04-27 Cabero Beteiligungs-Gmbh Kühlsystem

Also Published As

Publication number Publication date
DE202006000385U1 (de) 2006-03-02
EP1808655A3 (fr) 2008-04-02

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