EP1114285B1 - Installation frigorifique - Google Patents

Installation frigorifique Download PDF

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Publication number
EP1114285B1
EP1114285B1 EP99953709A EP99953709A EP1114285B1 EP 1114285 B1 EP1114285 B1 EP 1114285B1 EP 99953709 A EP99953709 A EP 99953709A EP 99953709 A EP99953709 A EP 99953709A EP 1114285 B1 EP1114285 B1 EP 1114285B1
Authority
EP
European Patent Office
Prior art keywords
water
condenser
energy
absorption
refrigeration
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
EP99953709A
Other languages
German (de)
English (en)
Other versions
EP1114285A1 (fr
Inventor
Joachim Paul
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.)
Integral Energietechnik GmbH
Original Assignee
Integral Energietechnik GmbH
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 Integral Energietechnik GmbH filed Critical Integral Energietechnik GmbH
Publication of EP1114285A1 publication Critical patent/EP1114285A1/fr
Application granted granted Critical
Publication of EP1114285B1 publication Critical patent/EP1114285B1/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
    • F25B39/00—Evaporators; Condensers
    • F25B39/04—Condensers
    • 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
    • F25B25/00—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00
    • F25B25/02—Compression-sorption 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
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/041—Details of condensers of evaporative condensers

Definitions

  • the invention relates to a refrigeration system.
  • thermal energy used in the form of hot water, hot water and steam.
  • This thermal energy can e.g. district heating be in the summer of thermal power stations (HKW) and Cogeneration plants (BKHW) partly offered in excess waste heat from industrial processes or solar or geothermal energy as drive energy come into question.
  • HKW thermal power stations
  • BKHW Cogeneration plants
  • District heating is a thermal energy, especially in summer and solar energy is particularly attractive for the operation of Refrigeration systems, because this energy is only generated when Cold e.g. is needed for summer air conditioning. But is also thermal for refrigeration systems operated all year round Energy an option.
  • the temperature level in a district heating network is in Winter typically 100-130 ° C, but in summer reduced to lower values by 90 ° C.
  • the usable Temperature level of waste heat from internal combustion engines A CHP is typically around due to its construction 90 ° C when talking about hot-cooled engines or the pure Except for exhaust gas use. These examples show that in numerous cases with temperatures around 90 ° C is what makes it difficult to use for refrigeration.
  • Blasting devices have a low efficiency a problem with hot water at such low temperatures which is not insoluble, but ecological and is difficult to economically represent.
  • Water / lithium bromide absorption chillers can with these low temperatures are still operated, however with poor efficiencies also difficult in the Location, cold water e.g. 6 ° C to provide.
  • Ammonia / water absorption refrigeration systems can reach temperatures reach below 6 ° C and even below 0 ° C, but the costs are very high and the efficiency is again bad.
  • the absorption systems mentioned which get along with low temperatures, however expensive to buy, very large and heavy as well are very energy intensive.
  • WO 83/00917 and US 4,438,633 are combined Compression / absorption chillers known, where the condenser of the compression part in the evaporator of the absorption part is arranged.
  • the invention has for its object a refrigeration system Specify the heat transfer at high outside temperatures is improved.
  • Refrigeration systems with electrical or mechanical drive are usually designed as compression refrigeration systems.
  • the energy required to drive the compressor is the evaporation and condensation temperature dependent. Since the evaporation temperature mostly through the Refrigeration application is determined in terms of the compressor's energy requirement only leaves room for maneuver the determination of the condensation temperature. This is supposed to be so be as deep as possible.
  • This is offered with increasing Condensation temperature e.g. operation with cooling water from a cooling tower, the condensation of the refrigerant in an evaporative cooler or the condensation with a air-cooled condenser.
  • the use of cooling towers and evaporative coolers is becoming increasingly difficult or even banned because the water requirement is significant. Air cooling is the more unfavorable because of the high temperature Solution, although no water is used.
  • Refrigeration systems with thermal drive are less Thermal drive energy temperature usually Absorption chillers. With the prevailing minor Temperatures it is difficult and / or energy intensive, to make usable usable temperatures available. At lower Thermal drive energy temperature is one high usable temperature, on the other hand, is becoming increasingly economical. Regarding the condensation of the refrigerant and the The removal of heat of absorption is otherwise the same Criteria as for the compression refrigeration system.
  • the compression refrigeration part with an air-cooled Condenser can be used in winter low outside temperature without cooling by the absorption refrigeration part the refrigerant with low energy consumption liquefy.
  • the absorption refrigeration unit can then be switched off or used for other purposes.
  • This circuit achieves the following: In winter reduces the low air temperature for condenser cooling of the compression refrigeration part the electrical or mechanical energy requirement of the system.
  • the absorption refrigeration part can remain switched off when thermal Drive energy is scarce or expensive. Likewise can the absorption refrigeration unit also for other cooling tasks be used when there is a need.
  • the Absorption refrigeration part serves to liquefy the Compression refrigeration system to cool, making the electrical or mechanical energy requirement of the compression refrigeration unit is low.
  • the useful temperature of the absorption refrigeration part high, e.g. with an air-cooled Condenser the refrigerant without water consumption to liquefy. Condenser water cooling of course also possible.
  • the absorption refrigeration part is designed as a water cooler (For frost protection or corrosion protection reasons, too another liquid, e.g. a brine can be used; summarized below under "water”).
  • the Compression refrigeration unit is a smooth or finned tube condenser, the refrigerant to be liquefied by the pipes, the cooling air flows around the pipes. fans provide for air flow, which is usually are arranged sucking.
  • a compression refrigeration unit consisting of an evaporator 1, a compressor 2, a condenser 3 and one Throttle body 4, with a substantially from one Evaporator 5, a condenser 6 and an absorber / desorber part 7 absorption refrigeration part coupled.
  • the compression refrigeration part becomes electrical or mechanical driven while the absorber with thermal Energy is supplied. This ensures that the low usable temperature thanks to an electrical / mechanical driven compression refrigeration part is shown at the same time, the condensation temperature of the compression refrigeration unit by cooling with the absorption refrigeration system kept low.
  • the absorption refrigeration part can therefore with low temperature thermal Energy the energy requirement of the compression refrigeration unit keep far less than this without the absorption refrigeration part it is possible.
  • the absorption refrigeration part needs do not provide cold at low temperature and can therefore be economical at high condensation temperature operate.
  • Fig. 2 shows an example of such a system.
  • the air-cooled heat exchanger 8 is located in a housing 9, on the top of which sucking fans 10 are attached. The air flow thus takes place from the bottom up. Above the heat exchanger 8 and Below the fans 10 is a water sprinkler 11 arranged. Depending on the geometry, air speed and sensitivity of fans 10 are drop cutters 12 above the water sprinkler 11 and arranged below 10.
  • the Housing 9 is with the elements 8, 10, 11, 12 as well as necessary Accessories e.g. Electrical wiring, control cabinet, Regulation, drive motors, etc. arranged in a tub 13, that the tub 13 e.g. by a valve operated Drain device 14 can be emptied.
  • a pump 15 delivers water from a template 16 in tub 13.
  • a opens Three-way valve 17 in such a way that the pumped water flows into the tub 13.
  • the water level in the tub 13 is regulated so that the heat exchanger 8 completely is immersed.
  • the fans 10 remain off.
  • the absorption refrigeration system 18 cools it Water in tub 13 or 16: by cooling through the The absorption refrigeration part becomes the condensing temperature of the compression refrigeration section is low and thus the energy requirement of the compression refrigeration part kept low.
  • Water droplets and aerosols can pass through the droplet separator 12 before impermissible entry into fans 10 are held.
  • the tub 13 can have an overflow or a suitable control device be to avoid overfilling the tub 13.
  • the absorption refrigeration system can be used instead of water cooling in the tub 13 also in the template 16 cool or pre-cool. It is also possible to use the water run continuously through the drain device 14 and to run on the pump 15.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Sorption Type Refrigeration Machines (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
  • Surgical Instruments (AREA)
  • Greenhouses (AREA)
  • Details Of Measuring And Other Instruments (AREA)

Claims (3)

  1. Installation frigorifique comprenant une section de compression et une section d'absorption, dans laquelle le condenseur de la section de compression est relié à l'évaporateur de la section d'absorption, caractérisé en ce que l'échangeur de chaleur (8) du liquéfacteur (3) de la section de compression est agencé dans une cuve (13) prévue pour recevoir l'eau, grâce à quoi la section d'absorption refroidit l'eau.
  2. Installation selon la revendicatron 1, caractérisée par un collecteur (16) alimentant la cuve (13).
  3. Installation selon l'une des revendications précédentes, caractérisée par un moyen de pulvérisation (11) dirigé vers l'échangeur de chaleur (8).
EP99953709A 1998-09-11 1999-08-31 Installation frigorifique Expired - Lifetime EP1114285B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19841548A DE19841548C2 (de) 1998-09-11 1998-09-11 Kälteanlage
DE19841548 1998-09-11
PCT/DE1999/002796 WO2000016024A1 (fr) 1998-09-11 1999-08-31 Procede pour faire fonctionner une installation frigorifique

Publications (2)

Publication Number Publication Date
EP1114285A1 EP1114285A1 (fr) 2001-07-11
EP1114285B1 true EP1114285B1 (fr) 2002-11-06

Family

ID=7880588

Family Applications (1)

Application Number Title Priority Date Filing Date
EP99953709A Expired - Lifetime EP1114285B1 (fr) 1998-09-11 1999-08-31 Installation frigorifique

Country Status (8)

Country Link
US (1) US6484527B1 (fr)
EP (1) EP1114285B1 (fr)
JP (1) JP2002525546A (fr)
AT (1) ATE227412T1 (fr)
AU (1) AU1030900A (fr)
DE (2) DE19841548C2 (fr)
DK (1) DK1114285T3 (fr)
WO (1) WO2000016024A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20090090131A1 (en) * 2007-10-09 2009-04-09 Chevron U.S.A. Inc. Process and system for removing total heat from base load liquefied natural gas facility
US8613839B2 (en) * 2009-10-13 2013-12-24 Idalex Technologies Water distillation method and apparatus
US9546804B2 (en) * 2009-12-16 2017-01-17 Heatcraft Refrigeration Products Llc Microchannel coil spray system
DE102018109577B3 (de) 2018-04-20 2019-05-09 Karlsruher Institut für Technologie Hybrid-Wärmepumpe mit Kompressions- und Adsorptionskreislauf, sowie Verfahren zumBetrieb und Verwendung

Family Cites Families (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1975945A (en) * 1932-08-22 1934-10-09 James P Curry Cooling unit for refrigerating systems
US1933703A (en) * 1933-01-20 1933-11-07 Emile P Brus Device for cooling condenser water
US2353233A (en) * 1941-06-04 1944-07-11 Curtis Mfg Co Heat exchanger
US2672024A (en) * 1951-01-12 1954-03-16 Carrier Corp Air conditioning system employing a hygroscopic medium
DE1215181B (de) * 1962-01-31 1966-04-28 Carl Schmid Inh C Kombinierte Kompressions-Absorptions-Kaeltemaschine
DE2340645A1 (de) * 1973-08-10 1975-02-20 Carl Aake Sandmark Kaeltemaschine
US3824804A (en) * 1973-08-22 1974-07-23 C Sandmark Refrigerating machines
DE2931147A1 (de) * 1979-08-01 1981-02-19 Rolf Dr Ing Schroedter Waermepumpe mit zwei kompressoren
WO1983000917A1 (fr) * 1981-08-28 1983-03-17 Chinnappa, James, Chandrasekaran, Virasinghe Installation de refroidissement
US4438633A (en) * 1982-11-12 1984-03-27 Hiser Leland L Method and apparatus for using low grade thermal energy to improve efficiency of air conditioning and refrigeration systems
EP0149413A3 (fr) * 1984-01-12 1986-02-19 Dori Hershgal Procédé et dispositif de réfrigération
US4626387A (en) * 1985-05-29 1986-12-02 Leonard Oboler Evaporative condenser with helical coils and method
US4869069A (en) * 1987-04-09 1989-09-26 Frank J. Scherer Integrated cascade refrigeration system
US4918943A (en) * 1989-01-26 1990-04-24 Faust Paul A Condenser
US5687579A (en) * 1994-09-12 1997-11-18 Vaynberg; Mikhail M. Double circuited refrigeration system with chiller

Also Published As

Publication number Publication date
DE19841548A1 (de) 2000-03-23
WO2000016024A1 (fr) 2000-03-23
DK1114285T3 (da) 2003-03-03
EP1114285A1 (fr) 2001-07-11
JP2002525546A (ja) 2002-08-13
US6484527B1 (en) 2002-11-26
ATE227412T1 (de) 2002-11-15
DE19841548C2 (de) 2002-03-28
AU1030900A (en) 2000-04-03
DE59903345D1 (de) 2002-12-12

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