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WO2006018216A1 - Machine frigorifique a absorption - Google Patents

Machine frigorifique a absorption Download PDF

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Publication number
WO2006018216A1
WO2006018216A1 PCT/EP2005/008717 EP2005008717W WO2006018216A1 WO 2006018216 A1 WO2006018216 A1 WO 2006018216A1 EP 2005008717 W EP2005008717 W EP 2005008717W WO 2006018216 A1 WO2006018216 A1 WO 2006018216A1
Authority
WO
WIPO (PCT)
Prior art keywords
refrigerant
absorber
solvent
condenser
expeller
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.)
Ceased
Application number
PCT/EP2005/008717
Other languages
German (de)
English (en)
Inventor
Raoul Von Der Heydt
Andrea Costa
Paul Kohlenbach
Stefan Petersen
Christian Schweigler
Felix Ziegler
Franz Storkenmaier
Mario Harm
Christoph Kren
Martin Högenauer-Lego
Peter Lamp
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.)
Phonix Sonnenwarme AG
Original Assignee
Phonix Sonnenwarme 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 Phonix Sonnenwarme AG filed Critical Phonix Sonnenwarme AG
Publication of WO2006018216A1 publication Critical patent/WO2006018216A1/fr
Anticipated expiration legal-status Critical
Ceased 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
    • F25B27/00—Machines, plants or systems, using particular sources of energy
    • F25B27/002—Machines, plants or systems, using particular sources of energy using solar energy
    • F25B27/007—Machines, plants or systems, using particular sources of energy using solar energy in sorption type 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
    • F25B15/00—Sorption machines, plants or systems, operating continuously, e.g. absorption type
    • F25B15/02—Sorption machines, plants or systems, operating continuously, e.g. absorption type without inert gas
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02A—TECHNOLOGIES FOR ADAPTATION TO CLIMATE CHANGE
    • Y02A30/00—Adapting or protecting infrastructure or their operation
    • Y02A30/27—Relating to heating, ventilation or air conditioning [HVAC] technologies
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/62—Absorption based systems

Definitions

  • the invention relates to an absorption refrigerating machine containing
  • Refrigerant from the solvent and (F) a condenser for liquefying the refrigerant vapor at the higher pressure in the form of a flowing through coolant heat exchanger, which is arranged in the same housing as the expeller.
  • refrigeration is generally used to operate e.g.
  • Absorption refrigerators use heat at different temperature levels depending on the application, as drive energy for thermally compressing a refrigerant, e.g. Solar heat or waste heat. It is up to the small energy for pumping and control no electrical energy required. As a result, a high efficiency in the provision of cold can be achieved.
  • a refrigerant e.g. Solar heat or waste heat.
  • An absorption chiller essentially comprises four components: evaporator, absorber, expeller (also referred to as generator) and condenser.
  • the refrigerant eg water
  • the refrigerant extracts energy from an air conditioning circuit, ie the cooling capacity is provided. This is done, for example, in the form that water of a building-Klimakaltwasser cycle flows through the evaporator designed as a heat exchanger and is cooled there.
  • an absorber the refrigerant vapor is absorbed by an absorbent, for example, concentrated LiBr solution. As a result, the refrigerant is now present in the solution in liquid form.
  • the refrigerant dissolved in the Li-Br solution by the absorption process is pumped to a higher pressure level in an expeller.
  • the absorber comprises a heat exchanger, which is traversed by cooling liquid at a medium temperature level.
  • the generator comprises a heat exchanger through which hot water flows. The hot water is generated, for example, by solar energy.
  • the refrigerant is evaporated from the refrigerant-rich solution and thereby absorbs energy.
  • the low-refrigerant solution ie, for example, the concentrated LiBr solution is then available again for the absorption process.
  • the capacitor also includes a heat exchanger, which is traversed by cooling liquid at a medium temperature level, for example ambient temperature.
  • absorption chillers are operated in a power range above 200 kW. These systems are large, expensive for small applications and operate at relatively high drive temperatures. But there is also one. Need for small, cost-effective systems.
  • the object is achieved in that the expeller is designed such that refrigerant working fluid solution collects in a first region on the housing bottom and means for thermal insulation of this region of a region in which the refrigerant liquefied in the condenser collects.
  • the invention is based on the surprising finding that even in the area of very small cooling capacities, refrigeration systems with a very low temperature can reach a high heat ratio. This applies not only in full load operation, but especially in partial load operation.
  • the prevention of heat leakage from the generator to the condenser and / or from the absorber to the evaporator makes it possible to achieve low outputs.
  • the thermal insulation can be effected in that the lateral housing wall in the transition areas between the condenser and expeller has a reduced thermal conductivity, for example a reduced thickness.
  • the heat transfer between the areas also referred to as "swamps" on the housing bottom and the housing interior above these areas along the housing wall is substantially reduced.
  • thermally insulated partition wall can be effected by a thermally insulated partition wall.
  • This thermally insulated partition can double-walled with an intermediate, thermally insulating medium, in particular air or
  • Vacuum be trained. This further reduces the heat transfer between the swamps.
  • the partition may be welded to the housing bottom and the housing bottom along the wall with holes to further reduce the
  • the partition can be integrated by suitable shaping of the housing bottom in this.
  • the evaporator is also designed as a trickle-bed heat exchanger in which unevaporated refrigerant collects in a first region on the housing bottom and means for thermal insulation of this region from a region in which the solvent present in the absorber collects.
  • the thermal insulation can be done with the same measures as the thermal insulation of the sumps of expeller and condenser.
  • one or more of the trickle-bed heat exchangers comprise a bundle of raw materials, which is sprayed with liquid from a distributor trough via feed tubes, the feed troughs projecting downwardly from the underside of the distributor trough
  • the vacuum system is connected via suction lances in the absorber with the housing interior of the evaporator / absorber housing comprising a provided on the bottom with holes in the tube, which extends substantially horizontally.
  • the suction lances can additionally be provided with drop baffles, which deflect liquid flowing down the suction lances downwards away from the bores.
  • the drop deflectors may be formed by a cover extending substantially straight down from the top of the suction lance. The downwardly directed holes and the drop deflector prevents liquid from the
  • the crystallization in the solvent circuit must be avoided. In the case of the known large systems, this is initially cooled before the system is completely switched off. Initially, the hot water supply is switched off and continue to operate the cooling and the solvent pump for a certain time. This follow-up time is in the range of about half an hour and is fixed. At the same time, the solvent is diluted with liquid refrigerant from the evaporator.
  • means are provided for determining the concentration of the low-refrigerant solvent and means for determining the minimum required to avoid crystallization dilution of the working / refrigerant solution before switching off the
  • the means for determining the concentration of the low-refrigerant solvent may include:
  • (C) means for determining the temperature of the emerging from the condenser
  • Refrigerant condensate means for determining the temperatures of the cooling water entering and leaving the condenser
  • the regulation of the Abfahrroutine can be made particularly simple in this way.
  • other means are also suitable for determining the concentration.
  • For dilution of the solvent can be connected via a valve between a region in which in the. Evaporating refrigerant collects, and be produced to the absorber. Furthermore, means may be provided for cyclically opening the valve at a fixed clock interval, and means for calculating the minimum number of opening operations corresponding to the calculated minimum
  • the refrigerant is feedable only above a concentration of 55% of the solvent for dilution.
  • a particularly preferred value is 57%. Below this concentration dilution is no longer required. On the contrary. A higher dilution will increase the time required for the restart, because then it must be concentrated again with energy expenditure. Above this concentration, there is a risk of crystallization.
  • the dilution routine described ensures a dilution of the solution adapted to the last prevailing concentration, in order to set a specific state determined for the standstill of the system, regardless of the operating state before the shutdown of the system.
  • a further heat exchanger may be provided, in which heat from the through the absorber and / or condenser flowing coolant. the water of a swimming pool is released.
  • the cooling liquid has a temperature in the middle range of about 30 °, and is generally above the temperatures, which has an unheated swimming pool.
  • the heat exchanger can use the heat from the cooling liquid and a cooling tower is superfluous.
  • the cooling liquid can also be cooled in other waters, such as lakes, rivers or the ocean.
  • Cooling arrangement for cooling ambient air and means for collecting condensed air humidity.
  • the cooling arrangement may be separated from a free-standing heat exchanger, e.g. a tube bundle or the like.
  • the temperature gradient condenses moisture in the air and is collected by means of a collecting means. In this way can be used in arid regions with
  • the absorption chiller can be operated with all common solvents and refrigerants, such as LiBr / water or water / NH 3 .
  • Fig.l shows a cross section through an absorption chiller
  • Fig. 2 is an external view of the absorption chiller of Fig. 1 with the water box open 3 is a schematic of the circuits required in the absorption refrigerating machine of FIG
  • a single-stage absorption chiller generally designated 10
  • the absorption chiller 10 comprises two housings 12 and 14.
  • the housing 12 is disposed above the housing 14.
  • a generally designated 16 expeller and next to a capacitor 18 is arranged.
  • an absorber 20 and an evaporator 22 is arranged in the housing 14.
  • the heat exchanger 24 comprises a bundle of Rob 100 of horizontally extending copper tubes 26. Copper tubes are inexpensive and have a high WameleitfäHgkeitskostoryen. They ensure good heat transfer.
  • the copper tubes 26 are arranged in 20 superimposed rows of five tubes side by side in a plane. The distances to each lying in the same plane adjacent pipe correspond to the distances of the rows. The pipe diameter is 12 mm.
  • the tubes are held in holes in two tube plates 28 (Fig.2).
  • the tube plates 28 are arranged parallel to the plane of representation in Fig.l. With them, the housing 12 is completed.
  • the tubes 26 protrude slightly beyond the tube plates 28 and open on the outside of the housing 12 on each side in a water tank 30 and 32.
  • the water tank 30 and 32 is via leads 34 and 36 ( Figure 2) with a solar thermal flat collector (not shown) connected.
  • a solar thermal flat collector instead of a solar thermal flat collector, another source of energy can be used.
  • the collector water is heated by solar heat to a weather and Unzeit ⁇ dependent temperature and pumped through a control system through the tubes 26 of Austreib er s 16
  • the capacitor 18 is further arranged.
  • the housing height of the housing 12 is reduced along the condenser 18 from the height along the expeller 16.
  • the heat exchanger 38 is similar to the heat exchanger 24 made of copper pipes.
  • the copper rotors are arranged in 10 rows of 5 horizontally extending tubes 40. However, the tubes are each offset from each other. Also, here open the tubes 40 behind the tube plate 28 in a water tank 42 with inlet 44 ( Figure 2).
  • Through the tubes 40 cooling water is passed. About the cooling water, the resulting heat in the condenser via a cooling tower or a heat exchanger (not shown) at a swimming pool, a lake, river or the like discharged into the environment.
  • the lower housing portions 46 and 48 of the housing 12 are through a partition
  • the partition wall 50 consists of one. the base plate 54 welded U-profile 56, with a cavity 58.
  • the U-profile 56 causes thermal isolation of the regions 46 and 48 from each other.
  • the base plate 54 is provided along the U-profile with holes. As a result, the heat transfer between the regions 46 and 48 is also reduced.
  • the tube plates 28 have in the transition region 60 between expeller 16 and capacitor 18 has a smaller thickness. The resulting edges are designated 62 and 64 in FIG. 1.
  • Both lower housing portions are provided with a strainer 66 in the form of a screen, which extends parallel to the base plate 54 and slightly above. About a U
  • Tube 68 and a shut-off valve 70 ( Figure 3), the condenser 18 is connected to the evaporator 22.
  • the U-tube 68 acts as a throttle due to the pressure difference. This will be a. Pressure difference between the condenser 18 and the evaporator 22 realized.
  • the droplet traps 72 consist of horizontally extending, flat sheets, which are inclined in the direction of Austreib ers down.
  • the expeller 16 is provided with a feed trough 74.
  • the tundish 74 is located just above the tubes 26.
  • the tundish 74 has tundish 76.
  • the dispensing tubes 76 extend on the underside of the Feed tray 74 down. They are located exactly above the center of the tube of the respective underlying tube. Refrigerant-rich LiBr solution, which is located in the hopper, then drips through the feed tube 76 very evenly on the tubes 26. The good distribution, a particularly good heat transfer between the hot water flowed through pipes 26 and the solution is achieved.
  • the poor, i. concentrated LiBr solution arriving at the lower end of the expeller 18 is first passed to a solution heat exchanger 77.
  • the solvent heat exchanger 77 is of the warmer, low-refrigerant solvent on the one hand and the countercurrent of the slightly colder,
  • refrigerant-rich solvents flow through. This is illustrated by arrows 79 corresponding to the poor solvent and 81 corresponding to the rich solvent.
  • the refrigerant-rich solvent is preheated and requires less energy in the expeller.
  • the low-refrigerant solvent coming from the expeller into the absorber has already cooled down a bit.
  • the low-refrigerant solvent is passed into the feed trough 82 of the absorber 20.
  • the U-tube 78 and the shut-off valve 80 allow for the PaIl occurring in the solution heat exchanger 77 crystallization of the solution an overflow of the solution directly from the expeller in the absorber. Crystallization blocks the flow of solution in path 79.
  • the solvent heat exchanger 77 throttles the pressure at the absorption level.
  • the absorber 20 is constructed substantially identical, as the expeller 16.
  • the poor solution trickles through a heat exchanger 84 and is thereby cooled by the cooling water to dissipate the heat of absorption. It absorbs the refrigerant vapor generated in the evaporator.
  • the rich solution is pumped by means of a solvent pump 86 ( Figure 3) back into the feed trough 74 of the expeller 16.
  • the absorber 20 and the evaporator 22 are operated at about 10 mbar internal operating pressure, which is determined by the vapor pressure of the refrigerant.
  • two "suction lances" 88 and 90 to which a vacuum system is connected, are provided.
  • the suction lances 88 and 90 consist of a tube with holes on the bottom 92.
  • Above the tube is a drop deflector in the form of a sheet, which extends from the top of the tube from straight down, down. As a result, no coming from above drops in the Rohröffhungen.
  • Such an arrangement 89 in the condenser 18 - also in conjunction with a vacuum system - is used to remove residual gases from the
  • Capacitor 18 and evaporator 22 are used.
  • the absorber 20 and the vaporized * 22 are equipped in the lower part with a strainer 94 and a thermally insulating partition 96 with partition plate 98. Also liier is the tube plates are tapered in the transition region between absorber and evaporator.
  • the tubes of the heat exchangers 102 and 104 in the absorber and evaporator open, as in the expeller 16 in water tanks and therefore need not be further described here.
  • the heat exchanger 102 of the absorber has 18 rows of five tubes each.
  • the heat exchanger 104 of the evaporator has 16 rows of four tubes each. He is one with the climate cycle, for example
  • the water passing into the evaporator via pipe 68 refrigerant is pumped by the pump 112 in the task tray 106 and flows through the heat exchanger 104. In this case, it evaporates due to external Wännemfuhi * from the Nutzkarlteniklauf at a low pressure level.
  • the refrigerant vapor is absorbed in the absorber by a concentrated, low-refrigerant LiBr solution.
  • LiBr solution In the transition region between the evaporator and the absorber four lamellar droplet traps 110 are provided. This have a roof shape. The droplets flow back into their area of origin.
  • the liquid, non-evaporated refrigerant is pumped by means of a pump 112 from below the heat exchanger 104 back into the task ewanne 106.
  • the described arrangement uses gravity to transfer refrigerant from the condenser 18 into the evaporator 22, as well as from the expeller 16 to the absorber 20. It therefore only requires two circulation pumps 86 and 112 and is particularly compact.
  • the throttling of the pressure from condenser to evaporator level takes place via a U-Rolir 68 and the height difference of the water columns, the throttling of the pressure of Austrreiber- on absorber level via the solution heat exchanger 77 in conjunction with a U-tube 180.
  • a separate Abfahrroutine can be used.
  • the internal operating temperatures at the condenser and expeller outlet are determined. From the measurements, prior to initiating the shutdown routine, the concentration of the working / refrigerant solution, i. the current
  • Cooling water when passing through the condenser occupied The detection of these temperatures by means of TemperaturFillers 116 and 120 is also part of the Abfahrroutine.
  • the concentration of the refrigerant-inert solvent will also be determined differently.
  • the temperature of the solvent emerging from the expeller is determined by means of temperature sensor 174.
  • the pressure in the expeller 22 and condenser 18 is determined by means of a pressure gauge 176.
  • the temperature of the refrigerant condensate leaving the condenser is determined by means of temperature sensor 172. From these
  • the temperature values vary due to e.g. Changing solar radiation with the time of day and season At low hot water temperatures, the system therefore operates at a different operating point than at high temperatures. Accordingly, there is a lower risk of crystallization.
  • the temperature difference between the cooling water inlet and outlet at the condenser is determined by temperature sensors 116 and 120. If this difference falls below one given, small value, for example, 0.4K, it is assumed that no more heating power is provided. For this case, the maximum solvent concentration of about 62% for the low-refrigerant solution is assumed. In this case, a solenoid valve 122 opens, via which a connection between the refrigerant circuit 124 and the solvent circuit 126 is established. Refrigerant is then to
  • the solenoid valve 122 opens clocked at a constant clock interval.
  • the degree of dilution and the duration of dilution depend on the number of
  • Opening operations can thus significantly reduce the dilution time of the plant.
  • a generally designated 130 vacuum system is used (Figure 3).
  • the extraction takes place via the suction lances 88, 89 and 90 and supply lines 134, 136 and 138 to the respective components.
  • Ball valves 140 and 142 are provided in the supply lines. In this way, both housings 12 and 14 are connected to the vacuum pump 144.
  • the vacuum pump 144 is formed by a jet pump. In front of the jet pump 144 is designated 132
  • the rich solvent pumped by the pump 86 is diverted as a drive jet from the solvent circuit 146 toward the pump 144. This is called 148.
  • the jet pump 144 generates at the terminal 150 the desired one. Vacuum.
  • the supply lines 134 and 138 are connected via the common supply line 136 to the terminal 150, in a separator 152 in the form of a bubble separator, the solvent / gas mixture coming from the pump is separated.
  • the solvent flows back into the circuit 146 via a line 154.
  • the gas is collected in a tank 156.
  • the tank 156 is arranged spatially higher than the absorber 20 and connected to it via a tube.
  • the separator 152 is located at the lowest point of this tube.
  • the gases from the separator 152 rise in the riser to the tank and displace thereby standing in the riser liquid. According to the height difference between separator 152 and minimum liquid level in the absorber 20, a relative overpressure in the tank
  • the tank 156 above the absorber 20 is freed from the gas at regular intervals of about a few weeks by flooding.
  • the liquid level in the tank is measured with liquid sensor 168.
  • the already existing solvent pump 86 is used.
  • a pressure above the ambient pressure in the tank is established by the solution pump 86.
  • the line between the solution pump and the L ⁇ sungskorleyer is closed by means of the valve 160, as are the valves 140 and 142 in the suction lines 138 and 134.
  • the line between separator 152 and absorber 20 is closed by means of valve 162.
  • the pump then promotes solution in the residual gas tank.
  • Residual gas tank is opened and the residual gases are expressed against the environment.
  • Liquid sensor 166 indicates when the tank is filled with solution and the squeezing procedure is completed. In this vacuum system, no separate motor is required, but the power of the pump 86 is shared via the jet pump. Alternatively, an external vacuum pump can be connected.
  • the driving jet can be cooled during operation of the plant.
  • a double-walled tube is used, in the inner region of the propulsion jet and in its outer region cooling water is passed from a pitch circle 170 of the cooling water circuit parallel to the absorber. - The Solution is subcooled in this way below the level in the absorber 20 and the vapor pressure is reduced.
  • Solvent in the absorber strongly undercooled and the vapor pressure decreases compared to the operating condition. Since there is usually still refrigerant in the evaporator sump, which has a much higher vapor pressure than the solvent, an equilibrium pressure builds up. There is a Dampfbewegtmg from the evaporator sump to the absorber sump. Now, if the solvent is passed through the jet pump 144, as the maximum negative pressure of the vapor pressure of the solvent to reach. This results in a continuous Voluinenstrom through the suction lances 88, 89 and 90. The residual gases are entrained.
  • an auxiliary absorber or a spray absorber may be used instead of the jet pump.
  • the poor solution is continuously withdrawn from the circuit 146 as in the use of the jet pump.
  • this solution is passed through cooling coils, in which cooling water flows before / or parallel to the actual main cooling water flow.
  • the solution is undercooled more than in the absorber 20.
  • Via a pipe the vapor space of the absorber 20 is connected to the vapor space of the auxiliary absorber.
  • the strong subcooling in the auxiliary absorber leads to a continuous steam mass flow through this line. This also non-condensable gases are taken.
  • the water vapor is absorbed in the auxiliary absorber.
  • the solvent is supplied to the separator. Over a slight Krürnniung at the inlet to this downpipe uncondensable gases are entrained.
  • a spray absorber instead of the auxiliary absorber we used in a third exemplary embodiment, a spray absorber. At standstill of the system is as described above with reference to the first embodiment to generate a relative negative pressure. By means of a spray nozzle, a solution mist is generated. The fog is at plant stop strongly undercooled and therefore acts hygroscopic. It generates a vapor stream from the absorber 20 and condenser 18 through the suction lances 88, 89 and 90 to the spray absorber. Again, the solvent is passed to the separator as in the auxiliary absorber through a curved in the inlet fair pipe.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Sustainable Energy (AREA)
  • Sorption Type Refrigeration Machines (AREA)

Abstract

L'invention concerne une machine frigorifique à absorption (10) contenant un évaporateur (2) sous forme d'échangeur de chaleur (104) relié à un circuit d'eau froide de climatisation, pour évaporer un agent réfrigérant, à basse pression, un absorbeur (20) pour absorber la vapeur d'agent réfrigérant produite dans l'évaporateur (22), par un solvant à teneur réduite en agent réfrigérant, à basse pression, qui se trouve dans le même boîtier (14) que l'évaporateur (22), une pompe à solvant (86) pour refouler le solvant à teneur élevée en agent réfrigérant, à une pression plus élevée, des moyens pour acheminer de l'eau chaude provenant d'une source d'eau chaude, un générateur (16) parcouru par l'eau chaude, pour évaporer l'agent réfrigérant hors du solvant et un condenseur (18) pour liquéfier la vapeur d'agent réfrigérant, à pression plus élevée, sous forme d'échangeur de chaleur (38) parcouru par le liquide de refroidissement, qui se trouve dans le même boîtier (12) que le générateur (16). Ladite machine frigorifique à absorption se caractérise en ce que le générateur (16) se présente de manière que le solvant de traitement de l'agent réfrigérant s'accumule dans une première zone (46) sur le fond du boîtier, ainsi que des milieux (50; 60) servant à l'isolation thermique de cette zone par rapport à une zone (48) dans laquelle l'agent réfrigérant liquéfié s'accumule dans le condenseur (18).
PCT/EP2005/008717 2004-08-12 2005-08-11 Machine frigorifique a absorption Ceased WO2006018216A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102004039327A DE102004039327A1 (de) 2004-08-12 2004-08-12 Absorptionskältemaschine
DE102004039327.3 2004-08-12

Publications (1)

Publication Number Publication Date
WO2006018216A1 true WO2006018216A1 (fr) 2006-02-23

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WO (1) WO2006018216A1 (fr)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102007030911A1 (de) 2007-07-03 2009-01-08 Sk Sonnenklima Gmbh Absorptionskältemaschine
DE102009001998A1 (de) 2009-02-14 2010-08-19 MIWE-ÖKOKÄLTE GmbH Absorptionskältemaschine mit Konzentrationsmessvorrichtung
DE102009001997A1 (de) 2009-02-14 2010-08-19 MIWE-ÖKOKÄLTE GmbH Absorptionskältemaschine mit wässrigem Kältemittel
CN109931786A (zh) * 2017-12-18 2019-06-25 沈阳天洁环保新能源有限公司 自蒸发式蒸汽冷凝器
DE102018002201A1 (de) 2018-03-19 2019-09-19 EAW Energieanlagenbau GmbH Westenfeld Wasser-Lithiumbromid-Absorptionskälteanlage
FR3107340A1 (fr) 2020-02-18 2021-08-20 Solar Energy Future Equipement de climatisation à panneaux solaires comprenant une machine à absorption
US20240027106A1 (en) * 2022-07-19 2024-01-25 King Fahd University Of Petroleum And Minerals Absorption chiller refrigerator system

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT504548B1 (de) * 2006-11-30 2010-01-15 Oesterreichisches Forschungs U Modul für eine absorptionskältemaschine

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DE102007030911A1 (de) 2007-07-03 2009-01-08 Sk Sonnenklima Gmbh Absorptionskältemaschine
DE102009001998A1 (de) 2009-02-14 2010-08-19 MIWE-ÖKOKÄLTE GmbH Absorptionskältemaschine mit Konzentrationsmessvorrichtung
DE102009001997A1 (de) 2009-02-14 2010-08-19 MIWE-ÖKOKÄLTE GmbH Absorptionskältemaschine mit wässrigem Kältemittel
CN109931786A (zh) * 2017-12-18 2019-06-25 沈阳天洁环保新能源有限公司 自蒸发式蒸汽冷凝器
DE102018002201A1 (de) 2018-03-19 2019-09-19 EAW Energieanlagenbau GmbH Westenfeld Wasser-Lithiumbromid-Absorptionskälteanlage
EP3543626A1 (fr) 2018-03-19 2019-09-25 EAW Energieanlagenbau GmbH Installation frigorifique à absorption eau-lithium
DE102018002201B4 (de) * 2018-03-19 2021-03-18 EAW Energieanlagenbau GmbH Westenfeld Wasser-Lithiumbromid-Absorptionskälteanlage
FR3107340A1 (fr) 2020-02-18 2021-08-20 Solar Energy Future Equipement de climatisation à panneaux solaires comprenant une machine à absorption
WO2021165597A1 (fr) 2020-02-18 2021-08-26 Solar Energy Future Équipement de climatisation à panneaux solaires comprenant une machine à absorption
US20240027106A1 (en) * 2022-07-19 2024-01-25 King Fahd University Of Petroleum And Minerals Absorption chiller refrigerator system
US12092376B2 (en) * 2022-07-19 2024-09-17 King Fahd University Of Petroleum And Minerals Absorption chiller refrigerator system
US12146689B1 (en) 2022-07-19 2024-11-19 King Fahd University Of Petroleum And Minerals Evaporator-absorber chiller system
US12152811B1 (en) 2022-07-19 2024-11-26 King Fahd University Of Petroleum And Minerals Liquid chiller and absorption refrigerator system
US12152812B1 (en) 2022-07-19 2024-11-26 King Fahd University Of Petroleum And Minerals Perforated plate adsorption chiller system

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