EP3058289A1 - Machine frigorifique à absorption - Google Patents

Machine frigorifique à absorption

Info

Publication number
EP3058289A1
EP3058289A1 EP13785816.3A EP13785816A EP3058289A1 EP 3058289 A1 EP3058289 A1 EP 3058289A1 EP 13785816 A EP13785816 A EP 13785816A EP 3058289 A1 EP3058289 A1 EP 3058289A1
Authority
EP
European Patent Office
Prior art keywords
refrigerant
heat exchanger
solvent
component
absorber
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Withdrawn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
EP13785816.3A
Other languages
German (de)
English (en)
Inventor
Fabian Schmid
Thomas Brendel
Marius MÜLLER
René HAHN
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.)
Universitaet Stuttgart
Original Assignee
Universitaet Stuttgart
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 Universitaet Stuttgart filed Critical Universitaet Stuttgart
Publication of EP3058289A1 publication Critical patent/EP3058289A1/fr
Withdrawn legal-status Critical Current

Links

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
    • 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
    • F25B15/04—Sorption machines, plants or systems, operating continuously, e.g. absorption type without inert gas the refrigerant being ammonia evaporated from aqueous solution
    • 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
    • F25B33/00—Boilers; Analysers; Rectifiers
    • 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
    • F25B39/02—Evaporators
    • F25B39/026—Evaporators specially adapted for sorption type systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0031—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other
    • F28D9/0043—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another
    • F28D9/005—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another the plates having openings therein for both heat-exchange media
    • 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 refrigeration machine according to the preamble of claim 1.
  • Absorption refrigerators serve, for example, the cooling of rooms, where heat is used as drive energy.
  • a solvent consisting of a solvent and a refrigerant is subjected to a cyclic process in which the refrigerant is expelled from the solvent and re-absorbed by means of different components and heat supply or withdrawal.
  • Typical working substances may be ammonia / water mixtures in which ammonia is used as the refrigerant and water as the solvent, mixtures of lithium bromide and water in which water is used as the refrigerant, and the like.
  • the phase changes of the refrigerant and the mixing ratios of the working substance take place in appropriately designed, arranged in the cycle components.
  • a cyclic process includes at least one high-pressure operating section having a compressor driving the refrigerant with heat supply from the solvent as a first component and a second refrigerant expelled refrigerant condensing condenser, a low-pressure section having a third evaporator evaporating the refrigerant under heat removal, and an absorber for absorbing Refrigerant vapor in the solvent as the fourth component, a arranged between the high-pressure region and low-pressure refrigerant expansion valve, arranged between the high-pressure region and low pressure area solvent expansion valve and arranged between the absorber and expeller agent pump.
  • EP 2 584 287 A1 shows one possible form of absorption chiller. Due to the nature of the design of the components, for example using a heated container as an expeller, the efficiency of the absorption chiller, for example, their coefficient of performance in the form of the quotient of the heat extracted from the environment and the heat used for this purpose is not optimal. Furthermore, the individual components require a large amount of space.
  • plate heat exchangers for example from WO 201 1/003496 A2 are known for exchanging heat between two fluids, in which a plurality of juxtaposed plates form two flow channels with a large surface area for the two fluids in heat exchange. Operation under reduced pressure and for the separation of three-phase mixtures with such plate heat exchangers is not provided.
  • the object of the invention is the advantageous development of an absorption chiller.
  • the training should improve the coefficient of performance.
  • the training is intended to achieve a compact design.
  • a design should reduce the number of components.
  • the production is to be simplified and the cost of production to be reduced.
  • the proposed absorption chiller includes for performing a cyclic process such as thermodynamic cycle processes present in different mixing ratios of a solvent and a refrigerant agent, preferably an ammonia / water mixture with ammonia as a refrigerant, an aqueous lithium bromide solution with water as a refrigerant or the like.
  • the cyclic process is subdivided into one for ammonia / water mixtures below atmospheric pressure and for an aqueous lithium bromide solution above the
  • the refrigerant driven by heat from the solvent expeller driving, an expelled refrigerant condensing condenser and optionally arranged between expeller and condenser dephlegmator.
  • the dephlegmator can also be provided as a rectifier for further purification of the refrigerant.
  • a refrigerant expansion valve for the controlled transport of the refrigerant from the high-pressure region into the low-pressure region rich.
  • a solvent expansion valve for the controlled transport of the solvent or a mixture of the working substance discharged from the refrigerant from the high-pressure region and in the low-pressure region.
  • the supply of the adjusted in the absorber to the substantially original mixing ratios of the working substance by means of a arranged between the absorber and expeller working fluid pump as circulating pump. Before the circulating pump, a collecting container may be provided for the working substance.
  • a plate heat exchanger is formed alone or in combination with at least one further component as a plate heat exchanger.
  • the expeller, the condenser, the evaporator and additionally provided components such as solvent heat exchangers, precoolers and the like can be designed as a plate heat exchanger and several of these components can be combined into a single component.
  • a plate heat exchanger in ammonia / water mixtures must be adapted to the specific requirements of the individual components, for example, be adapted to pressures below atmospheric pressure, the treatment of liquid and gaseous phase systems of the working material and the like.
  • a "rich solution” is to be understood as meaning a working substance in its original composition, for example ammonia-rich working substance having a concentration of, for example, 50% by weight of ammonia to understand.
  • Refrigerant vapor is the still more or less proportions of the solvent containing gaseous refrigerant.
  • Refrigerant means the condensed, liquid refrigerant.
  • a dephlegmator is provided between the absorber and the expeller with a supply container connected between the dephlegmator and the expeller
  • Dephlegmator cooled via a separator, solvent-contaminated, run between the expeller and condenser refrigerant vapor by means of a refrigerant-enriched, cooled by the supplied from the working fluid pump in the expeller agent.
  • the expeller is preferably formed as a plate heat exchanger, the master container and the separator are provided to secure its function in this environment.
  • the rich preheated in the dephlegmator Solution enters the reservoir and then flows through the plate heat exchanger.
  • the refrigerant is desorbed as ammonia.
  • the mode of operation takes place here without forced flow, so that even in the dephlegmator and in a solvent heat exchanger downstream of the solvent pump, expelled refrigerant vapor can be separated in the feed tank and can rise directly into the dephlegmator. This can lead to the refrigerant being saturated with refrigerant in the generator.
  • This constant mixing of the agent at the entrance to the expeller leads to a stable operation of the plate heat exchanger and thus to a stable operation of the entire absorption chiller.
  • fluctuations in the volume flow conveyed by the working fluid pump can be compensated by the reservoir.
  • the flow velocity of the refrigerant vapor is preferably, for example, by cross-sectional widening of the access, a baffle plate and / or reduced.
  • the separator may have surface-enlarging, solvent-promoting elements such as Raschig rings. Through an opening at the bottom of the separator, the poor solution is deposited.
  • the plate heat exchanger can be proposed in functional unit with the storage tank, which sets a constant level in the plate heat exchanger, and the separator discharging the poor solution as a three-component assembly corresponding to a container expander with reduced dimensions and improved separation properties.
  • Another advantage of this functional unit is its not forced flow operation. As a result, condensate rich in refrigerant in the dephlegmator can flow directly into the feed tank without being disadvantageously fed to the poor solution, as is the case, for example, in conventional expellers.
  • a solvent heat exchanger can be provided between the separator and the absorber.
  • the latter exchanges heat between the working fluid enriched with refrigerant, ie the rich solution and a refrigerant depleted in the refrigerant, from the separator via the solvent expansion valve to the absorber, ie the poor solution.
  • an absorber precooler can be arranged and thus preceded by the absorber which is operated with cooling medium, for example externally controlled by a 3-way valve supplied cooling water, an external recooling unit or the like and compared to the depleted refrigerant refrigerant further cooling causes.
  • This absorber precooler can be designed as a plate heat exchanger.
  • An absorption chiller designed as a plate heat exchanger as an absorber precooler can also be designed with a conventional expeller in an advantageous manner.
  • the Absorbervorkühlers the poor solution can be cooled particularly effectively before entering the absorber, so that the absorption of gaseous refrigerant in the absorber improved and the thermally coupled at least via lines evaporator can be operated at lower temperatures or an increase in the refrigerant line and a improved coefficient of performance can be achieved.
  • the absorption process of the vaporous refrigerant in the poor solution is preferably divided into two areas.
  • the poor solution is injected into the absorber, as disclosed, for example, in WO 1998/012487 A1.
  • an absorption chiller In connection or independent of equipped with a trained as a plate heat exchanger expeller and / or Absorbervorkühler absorption chillers, an absorption chiller may be advantageous, the dephlegmator and condenser are designed as a common component as a unit in the form of a triple heat exchanger. By combining the dephlegmator and the capacitor, a single assembly is achieved that manages with less space and less manufacturing costs.
  • the individual plates can be arranged one behind the other, so that only two cover plates and six connections are required.
  • the triple heat exchanger advantageously has a refrigerant channel passing through the refrigerant vapor and two channels of the dephlegmator and the condenser arranged one behind the other along the refrigerant channel.
  • a refrigerant heat exchanger can be provided, which carries out a heat exchange between a guided between the condenser and evaporator refrigerant flow of condensed refrigerant and a guided between evaporator and absorber refrigerant vapor.
  • a refrigerant heat exchanger may be formed as a plate heat exchanger.
  • a refrigerant reservoir can be provided between the condenser and the refrigerant heat exchanger.
  • the capacitor may be formed of a plate heat exchanger.
  • Refrigerant heat exchanger and refrigerant reservoir form a common 3-way heat exchanger.
  • the triple heat exchanger may be formed as a unit from a single component such as plate heat exchanger, wherein the triple heat exchanger with a continuous flow for the refrigerant, separated from the refrigerant expansion valve in the high pressure region and the low pressure region refrigerant channel and two arranged along the refrigerant channel in a row Channels of the refrigerant heat exchanger and the evaporator forms.
  • the channel of the refrigerant heat exchanger can receive the refrigerant reservoir.
  • two heat exchangers and the refrigerant reservoir are housed in only one component by appropriate arrangement of the plates of a plate heat exchanger.
  • the integrated in this integrated refrigerant heat exchanger serves as a refrigerant reservoir.
  • the maximum heat transfer decreases due to a reduced transfer area.
  • the necessary transfer area is also lower due to a lower heat flux. It may be advantageous that the temperature of the
  • Refrigerant heat exchanger and the evaporator can be well below the ambient temperature and can be reduced by the lower total surface area of the combined component compared to separate components of the heat input into the absorption chiller. This leads to an increase in the number of these. Furthermore, the one-piece design of evaporator, refrigerant heat exchanger and refrigerant reservoir leads to material, weight and cost savings.
  • the use of a plate heat exchanger to expel refrigerant in the expeller leads to weight reduction and increased compactness of Absorptions Kol- temaschine.
  • the plate heat exchanger works in functional unit with a Reservoir and a separator.
  • the interconnection is a system that is not forced through.
  • the expulsion is stabilized by the open system consisting of expeller, storage tank and separator, since the coolant vapor expelled by the preheating is removed before the expeller, just like plate heat exchangers.
  • the use of the combination of a dephlegmator with a condenser increases the compactness of the absorption chiller and reduces necessary weld joints, weight, cost and pressure losses.
  • a heat exchanger for the combination of refrigerant reservoir, refrigerant heat exchanger and evaporator.
  • a heat input into the refrigerant heat exchanger and into the evaporator can be reduced.
  • the absorber pre-cooler ensures that at low evaporator temperatures and high absorber temperatures, the absorption can be carried out with a higher degree of efficiency and thus increases the coefficient of performance of the absorption chiller. Since the mass flow is only divided into two partial mass flows.
  • FIG. 1 shows a schematic diagram of an absorption refrigerating machine
  • FIG. 3 shows a refrigerant heat exchanger, cold-storage reservoir and evaporator-combining plate heat exchanger
  • Figure 4 shows the plate heat exchanger of Figure 3 in a schematic overview of functions
  • Figure 5 shows the expeller of the absorption chiller of Figure 1 in a schematic
  • the absorption chiller 1 shows the absorption chiller 1 in a schematic representation with the high-pressure region 2 and the low-pressure region 3 shown schematically.
  • the absorption chiller 1 is operated in a thermodynamic cycle, wherein the externally supplied energy essentially takes place via the heating circuit 4, which can be fed by waste heat from heat-generating technical processes and combustion plants such as natural gas firing, solar thermal energy and the like.
  • the thermodynamic cycle continues to output heat component amounts to the outside via the recooling circuits 5, 6.
  • the cooling capacity of the absorption chiller is provided via the refrigeration cycle 7, which is for example by means of a brine in connection with an external air conditioner or the like.
  • thermodynamic cycle is carried out by means of a working substance consisting of a mixture of a refrigerant and a substance absorbing this, which emit heat when mixed and absorb heat when they are separated.
  • the refrigerant is expelled through the various phases of the cycle from the absorbent in the gas phase, condensed in pure form and evaporated again and reunited with the absorbent.
  • evaporation takes place at low temperature with removal of heat at the heat exchanger of the refrigeration cycle 7.
  • Working substances are, for example, ammonia / water mixtures in which ammonia serves as a refrigerant and water as a solvent such as absorbent, aqueous lithium bromide solutions in which water as the refrigerant and lithium bromide serves as an absorbent, or the like.
  • ammonia serves as a refrigerant and water as a solvent
  • aqueous lithium bromide solutions in which water as the refrigerant and lithium bromide serves as an absorbent, or the like.
  • thermodynamic cycle is started at the transition of the ammonia-rich working substance from the low-pressure region 3 into the high-pressure region 2.
  • the ammonia-rich working substance is transferred via line 9 into the dephlegmator 10 by means of the preferably electrically operated working fluid pump 8.
  • the solvent heat exchanger 1 Between the working fluid pump 8 and the dephlegmator 10 takes place in the solvent heat exchanger 1 1, a heat exchange between the ammonia-rich working fluid of the line 9 and the recirculated in line 12 low-ammonia working fluid.
  • the ammonia-rich working substance is preheated by the guided in the line 13, expelled in the expeller 14 by supplying heat to the heating circuit 4 refrigerant vapor.
  • the feed tank 15 and the separator 16 are turned on.
  • the warmer refrigerant vapor enters this preheated in the expeller 14 a.
  • water entrained by the cooling of the refrigerant vapor in the dephlegmator 10 condenses with a high proportion of ammonia, which is supplied to the feed tank 15 by means of the line 64 and is thus utilized efficiently.
  • expeller 14 and separator 16 adjusts itself in the sense of communicating tubes in this one level of the liquid solution. When a predetermined level is exceeded low ammonia working fluid flows into the separator 16 and from there in line 12.
  • ammonia-rich working material from the master tank 15 is tracked in the expeller 14.
  • the expeller 14 is in this case preferably designed as a plate heat exchanger 17, which is partially filled with ammonia-rich working fluid. Due to the large heat exchange surface of the plate heat exchanger 17 and the forming phase transition gas / liquid without forced flow due to the open formation of expeller 14, feed tank 15 and separator 16 a particularly effective expulsion of the refrigerant vapor is achieved. Furthermore, just as much ammonia-rich working substance is supplied to the expeller 14, as is promoted by desorption and the associated reduction in the density in the separator 16. Furthermore, 15 pulsations and delivery fluctuations of the working fluid pump 8 are compensated in the storage tank.
  • the flow rate is reduced for example by cross-sectional widening of the conduit 18 and / or a baffle plate.
  • a surface enlargement in the separator 16 for example by Raschig rings and the like, a first deposition of entrained in the refrigerant vapor water.
  • the dephlegmator 10 and / or the condenser 20 may be formed as separate plate heat exchangers. In a particularly advantageous manner, the dephlegmator 10 and the condenser 20 are combined to form a unit forming plate heat exchanger 21.
  • the plate heat exchanger 21 forms a triple heat exchanger, in which the refrigerant vapor is passed continuously and the dephlegmator 10 a first, cooled by the guided in the line 9 ammonia-rich working fluid cooling stage and the condenser 20 a second, through the recooling circuit. 5 cooled cooling stage forms.
  • the structure of the absorption chiller 1 is simplified, since instead of a separate dephlegmator and a separate capacitor 20 only a single plate heat exchanger 21 with six connections and two end plates is necessary.
  • the condensed refrigerant is passed from the condenser 20 or from the plate heat exchanger 21 in the reservoir 22 and from there into the refrigerant Heat exchanger 23.
  • the refrigerant heat exchanger 23 a further cooling takes place by means of the now by the refrigerant expansion valve 24 in the
  • Low pressure range 3 transferred and behind the evaporator 25 in the conduit 26 through the refrigerant heat exchanger 23 guided gaseous refrigerant.
  • the refrigerant vaporizes in the evaporator 25 and thus removes heat from the working substance in the refrigeration cycle 7, for example a cooling brine, so that the actual cooling process such as room air conditioning, room cooling, cooling system and the like is initiated outside the absorption refrigeration machine 1.
  • the refrigerant expansion valve 24 to form a structural unit in the form of the plate heat exchanger 27.
  • the volume of the plate heat exchanger 27 in the region of the refrigerant heat exchanger 23 is preferably expanded so that the reservoir 22 can be accommodated therein.
  • the refrigerant is completely evaporated and transported via the line 26 into the absorber 28.
  • the refrigerant is completely evaporated and transported via the line 26 into the absorber 28.
  • Solvent heat exchanger 1 1 the absorber precooler 29 and the solvent expansion valve 30 transported in the absorber 28 and the ammonia-poor working fluid and the refrigerant vapor combined to the ammonia-rich working fluid which is supplied via the line 32 and the reservoir 33 of the working fluid pump 8, whereby the cycle process running is held.
  • the 25 29 are each separately cooled by means of the 3-way valve 34 from the recooling circuit 6, for example, cooling water and the like.
  • the absorber precooler 29 can be cooled by a separate recooling plant.
  • the controlled pre-cooling of the ammonia-lean working substance, the absorption can be controlled in an improved manner.
  • the absorber precooler 29 is preferably in the form of plate heat
  • FIG. 2 shows the plate heat exchanger 21 of Figure 1 in a schematic exploded view with the two end plates 36, 37 and arranged therebetween 35 separating plates 38, 39, 40, 41, 42.
  • the separation is achieved in the dephlegmator 10 and in the condenser 20 of Figure 1 in terms of a triple heat exchanger.
  • the refrigerant vapor in the line 19 of Figure 1 along all the separator plates 38, 39, 40, 41, 42 from the port 43 to the port 44 is performed.
  • the ammonia-rich agent for dephlegmation of the refrigerant vapor 5 is passed between the ports 45, 46 via the partition plates 41, 42.
  • the recooling circuit 5 for condensing the refrigerant vapor to form the condenser 20 is guided between the connections 47, 48 via the separating plates 38, 39.
  • FIG. 3 shows a schematic exploded view and with reference to FIG. 1
  • the plate heat exchanger 27 which combines the function of the refrigerant heat exchanger 23 and the evaporator 25 in itself in the form of a 3-fold Wärnmeübertragers.
  • the two end plates 49, 50 between them include the partition plates 51, 52, 53, 54, 55 a.
  • the refrigerant flows along the refrigerant channel 65 over the entire plate heat exchanger 27.
  • the refrigerant heat exchanger 23 is characterized by the between
  • Evaporator represented by the refrigerant channel 67 formed by the partition plates 54, 55 and the end plate 50.
  • the liquid refrigerant from the condenser 20 enters the plate heat exchanger 27 and exits again at the connection 57 in order to be discharged from the high-pressure region 2 into the low-pressure region via the refrigerant expansion valve 24.
  • the condensed refrigerant enters the plate heat exchanger 27 again at the connection 58 and is evaporated there and cools the condensed refrigerant at the separating plates 51, 52. Subsequently, the refrigerant vapor exits again at the port 59 and is then transferred to the absorber. Between the terminals 60, 61 and the partition plates 54, 55 circulates the
  • the refrigerant reservoir 66 is still the reservoir 22 accommodated for the refrigerant.
  • FIG. 4 shows a schematic representation of a detail of the absorption chiller 1 of FIG. 1 with expeller 14, designed as a plate heat exchanger, the receiver tank 15, the separator 16 and the dephlegmator 10.
  • expeller 14 designed as a plate heat exchanger
  • ammonia-rich working fluid flows through the line 9 ammonia-rich working fluid, which is preheated by the guided in the conduit 13 refrigerant vapor.
  • ammonia-rich working substance is condensed out.
  • water contaminants of the refrigerant vapor are conducted into the feed tank 15.
  • the heated generator 14 drives from the ammonia-rich working water hydrous ammonia, ie refrigerant vapor from the
  • FIG. 5 shows a schematic representation of the plate heat exchanger 27 of Figures 1 and 3.
  • refrigerant heat exchanger 23 and evaporator 25 are combined.
  • the reservoir 22 is housed for the condensed refrigerant.
  • the level of the condensed refrigerant behaves proportional to the heat flow to be transferred in the refrigerant heat exchanger 23. In a large heat flow to be transmitted, due to a large temperature difference between gaseous refrigerant and condensed refrigerant, the level is high and thus the heat exchange surface is large, so that this heat flow can also be transmitted.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Power Engineering (AREA)
  • Sorption Type Refrigeration Machines (AREA)

Abstract

L'invention concerne une machine frigorifique à absorption (1) comprenant : un fluide de travail acheminé dans un processus cyclique dans des rapports de mélange d'un solvant et d'un frigorigène différents en fonction du processus cyclique ; une zone haute pression (2) comprenant en tant que premier élément un bouilleur (14) qui libère le frigorigène du solvant sous l'effet d'un apport de chaleur et, en tant que deuxième élément, un condenseur (20) qui condense le frigorigène dégagé ; une zone basse pression (3) comprenant en tant que troisième élément un évaporateur (25) qui évapore le frigorigène sous l'effet du prélèvement de la chaleur et, en tant que quatrième composant, un absorbeur (28) qui absorbe la vapeur du frigorigène dans le solvant ; une soupape d'expansion (24) du frigorigène agencée entre la zone haute pression et la zone basse pression ; une soupape d'expansion (30) du solvant agencée entre la zone haute pression et la zone basse pression ; et une pompe (8) de fluide de travail agencée entre l'absorbeur et le bouilleur, ainsi qu'éventuellement un déflegmateur (10), disposé entre le bouilleur et le condenseur, en tant que cinquième élément ; et éventuellement un échangeur de chaleur (23) du solvant en tant que sixième élément. L'invention vise à réduire le coût et à augmenter l'efficacité d'une machine frigorifique à absorption. A cet effet, au moins un des éléments, à lui seul ou combiné à au moins un autre élément, est réalisé sous la forme d'un échangeur de chaleur à plaques.
EP13785816.3A 2013-10-18 2013-10-18 Machine frigorifique à absorption Withdrawn EP3058289A1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/DE2013/100356 WO2015055159A1 (fr) 2013-10-18 2013-10-18 Machine frigorifique à absorption

Publications (1)

Publication Number Publication Date
EP3058289A1 true EP3058289A1 (fr) 2016-08-24

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Application Number Title Priority Date Filing Date
EP13785816.3A Withdrawn EP3058289A1 (fr) 2013-10-18 2013-10-18 Machine frigorifique à absorption

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EP (1) EP3058289A1 (fr)
WO (1) WO2015055159A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102016010741A1 (de) * 2016-09-03 2018-03-08 Eco ice Kälte GmbH Ammoniak/Wasser- Absorptionskältemaschine
DE102018002201B4 (de) 2018-03-19 2021-03-18 EAW Energieanlagenbau GmbH Westenfeld Wasser-Lithiumbromid-Absorptionskälteanlage
DE102018205810A1 (de) 2018-04-17 2019-10-17 Robert Bosch Gmbh Desorbervorrichtung für eine Wärmepumpe

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19637821A1 (de) 1996-09-17 1998-03-19 Deutsche Forsch Luft Raumfahrt Wärmetauschverfahren und Wärmetauscher
CN1766462B (zh) * 2005-10-31 2010-05-05 庞启东 一种利用尾气余热的氨水吸收式制冷装置
DE202009009007U1 (de) 2009-07-03 2009-09-03 Beumer Gmbh & Co. Kg Sortierförderer mit Doppeltragschale
EP2584287B1 (fr) 2011-10-21 2016-01-27 AGO AG Energie + Anlagen Cycle destiné au fonctionnement d'une machine de refroidissement par absorption et machine de refroidissement par absorption

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