[go: up one dir, main page]

WO1994017341A9 - Machine frigorifique - Google Patents

Machine frigorifique

Info

Publication number
WO1994017341A9
WO1994017341A9 PCT/EP1994/000087 EP9400087W WO9417341A9 WO 1994017341 A9 WO1994017341 A9 WO 1994017341A9 EP 9400087 W EP9400087 W EP 9400087W WO 9417341 A9 WO9417341 A9 WO 9417341A9
Authority
WO
WIPO (PCT)
Prior art keywords
propellant
inlet
refrigerating machine
machine according
compressor
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/EP1994/000087
Other languages
German (de)
English (en)
Other versions
WO1994017341A1 (fr
Filing date
Publication date
Priority claimed from DE19934301181 external-priority patent/DE4301181C2/de
Application filed filed Critical
Priority to AU58830/94A priority Critical patent/AU5883094A/en
Publication of WO1994017341A1 publication Critical patent/WO1994017341A1/fr
Publication of WO1994017341A9 publication Critical patent/WO1994017341A9/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Definitions

  • the invention relates to a refrigerator according to the preamble of claim 1.
  • a refrigerating machine is a device for generating low temperatures. It is intended to extract heat from a system whose temperature is below the ambient temperature in order to deliver it to the environment at a higher temperature. The heat transfer is taken over by a refrigerant as réelle ⁇ carrier, which is usually performed in a closed circuit. This liquid refrigerant can be used, which absorb large amounts of heat during evaporation and release it on condensation again. To use this Evaporation and condensation heat have chillers evaporating a heat to the system to be cooled and a condenser for the coolant which gives off heat to the environment.
  • the boiling point of the refrigerant increases with the pressure by the evaporation is carried out at relatively low pressure and un ⁇ ter ambient temperature and the condensation at higher pressure and above ambient temperature.
  • a compression of the refrigerant and between the condenser and the evaporator a relaxation of the refrigerant via a throttle body is required.
  • the individual types of refrigeration machines differ in principle only in the type of compression of the refrigerant.
  • the refrigerant vapor is sucked by a mechanical compressor from the evaporator, compressed and conveyed into the condenser.
  • Da ⁇ mainly halogenated hydrocarbons are used. Fluorine-chlorine hydrocarbons are considered harmful to ozone, so that the use of such refrigerating machines is problematic.
  • the mechanical compressor In the absorption refrigeration system, the mechanical compressor is replaced by a thermal one. In the continuous When the absorption machine is operating in the same way, the refrigerant vapor is compressed by absorbing it in the absorber at low pressure from the poor solution and expelling it from the rich solution in the expeller at high pressure.
  • the two best known pairs of materials for this process of refrigeration are ammonia / water and water / lithium bromide solution. Such systems are technically ver ⁇ relatively expensive.
  • the steam jet refrigerator is known in which a steam jet compressor is used for sucking and compressing the refrigerant vapors.
  • the motive steam passes through a motive nozzle into a chamber of the compressor in which it aspirates and mixes refrigerant vapor expanding at high speed.
  • the velocity energy is converted back into pressure energy, so that condensation pressure prevails at the diffuser outlet.
  • the processes are associated with considerable losses and the maximum efficiency is 22 to 26%.
  • the steam jet refrigerator has the advantage that it works with water, ie a harmless refrigerant works. If it is to be cooled to temperatures of -2 to + 10 ° C, however, it is necessary to work in the evaporator with relatively moderate pressures (the boiling points of water are for example at 760 Torr + 100 ° C and at 4.579 Torr 0 ° C). This refrigerating machine is thus operated as a vacuum system. The large amounts of water vapor from the evaporator can be processed by a steam jet compressor in a vacuum.
  • the steam jet refrigerating machine has the disadvantage that motive steam must be made available. In general, therefore, their application is limited to cases in which process or exhaust steam can be used.
  • the object of the invention is to create a refrigerating machine which contains a harmless refrigerant, works with better efficiency and is not dependent on an externally supplied propellant.
  • a refrigerating machine corresponds in its construction essentially to a known steam jet refrigerating machine.
  • a propellant compressor is provided whose centrifugal acceleration section has an increased suction power.
  • a propellant liquid Kreis ⁇ is preferably used running water from the condenser, so that no ex ⁇ ternal propellant supply is required.
  • the propellant compressor can simultaneously act as an injection condenser and take over at least one part of the condensation power.
  • the propellant compressor works particularly effectively when propellant liquid particles are conducted several times around the water vapor inlet in the annular channel delimiting the centrifuge acceleration section, and repeatedly exert a suction effect on them.
  • the propellant inlet may be formed at the mouth of a propellant feed channel communicating in the circumferential direction of the annular channel.
  • the steam suction is favored when the water vapor inlet is formed at the mouth of a water vapor feed channel pointing in the same circumferential direction.
  • the water vapor supply channel may comprise a plurality of guide plates which are arranged graduated in the circumferential direction and which can extend over a considerable part of the annular channel circumference.
  • sufficiently large intake cross sections for the large steam intake volumes can be used. be made available, which may correspond approximately to those of the steam An ⁇ suction.
  • the mixture outlet may be formed on the mouth of a mixing outlet channel pointing counter to this circumferential direction.
  • the propellant inlet for the liquid propellant preferably has a smaller cross-section than the water vapor inlet, whereby high vapor throughputs are promoted.
  • the mixture outlet has a larger cross section than the propellant inlet, so that the mixture is sufficiently removed trouble-free.
  • the mixture outlet has a smaller cross-section than the water vapor inlet, which promotes the build-up of a negative pressure in the inlet region and multiple guidance of the blowing agent particles through the annular channel.
  • the propellant inlet, steam inlet and mixture outlet along the U beginning of the annular channel are each beab ⁇ tandet each other. Since a maximum suction effect is to be expected in the flow direction before the propellant inlet, it will be advantageous to rearrange this in a circumferential direction of the annular channel the water vapor inlet and arrange the mixture outlet.
  • the water pump for the propellant delivery may be a pump of conventional type or a high pressure pump.
  • the propellant compressor can be designed to save space and without rotating parts.
  • thekulturmit ⁇ telverêtr has a pot-like housing, a disc inserted therein and a sealingly fixed on the disc and an edge of the housing lid. In a Ab ⁇ range between the outer periphery of the disc and the inner circumference of the wall of the pot-like housing of the annular channel is formed, which is closed at the bottom of the housing bottom and top of the housing cover.
  • a propellant and a steam supply channel and a Gemischab fertilkanal are ⁇ forms in the disc. These have at one end on the outer circumference of the disc an orifice, which form the propellant inlet, Was ⁇ serdampfeinlella or Gemischauslenfin. At the other end, they each communicate with a housing bore for the supply of fuel, the supply of water or the discharge of the mixture.
  • propellant and water vapor pass through the housing bores and their feed channels as well as the inlet into the annular channel and are withdrawn therefrom through the outlet, the mixing discharge channel and the associated housing bore.
  • the flow conditions are favorably influenced therein.
  • Treibschzu 1500 ⁇ channel, steam supply and Gemischab2020kanal can gradually expand to their mouths on the outer circumference of the disc.
  • the propellant feed channel, the steam feed channel and the mixture discharge channel can each lead into a collecting space of the disc.
  • the collecting chambers can simply be constructed as bores arranged perpendicular to the disc and are then closed by the housing cover and the housing bore, which have the associated housing bore.
  • the propellant feed channel, the water vapor feed channel and the mixture discharge channel are each oriented approximately tangentially to the associated plenum. Convenient for the fixed installation of supply and discharge lines is when the housing bores for blowing agent, water vapor and mixture are each formed in the housing bottom.
  • Another propellant compressor has a closed to a ring and the annular channel limiting tube (Ring ⁇ tube), wherein the propellant inlet, steam inlet and Gemischauslador are passed through the pipe wall.
  • Preferred are blowing agent inlet, water vapor inlet and mixture outlet. let each formed at the mouths through the tube walls ge-guided immersion tubes.
  • the annular channel follows a circular arc.
  • the propellant compressor is designed as a pot with disc, it preferably has a rectangular cross-section.
  • the propellant compressor When trained as a ring tube, it preferably has a circular cross-section.
  • the cross section may change in the circumferential direction, for example in the inlet region, and increase in the outlet region.
  • the aforementioned propellant compressors are very platzspa ⁇ rend and easy to carry out and are therefore suitable for both commercial, as well as privately used refrigeration systems.
  • the mixture outlet of the propellant compressor can be connected to the condenser via a diffuser.
  • the diffuser is a channel piece which is gradually widened in the flow direction and in which the flow velocity of the mixture is converted into pressure. In this way, the achievement of the condensation pressure is ensured.
  • a further embodiment provides at least one further propellant compressor whose propellant inlet is connected via a water pump to the condenser whose steam inlet is connected to a steam trap of the condenser and whose mixture outlet is connected to the condenser. This propellant compressor acts to condense water vapor, which is located in the water vapor space of the condenser, and improves the overall efficiency of the refrigeration system.
  • the Ge mixed outlet of the further propellant compressor is connected via a further capacitor to the capacitor.
  • the water vapor space of the further condenser can in turn be connected to a next propellant compressor. All propellant compressors can be fed by the same water pump.
  • the refrigerating machine according to the invention is not limited to the use of water as a refrigerant. Rather, steam or steam of another conventional refrigerant can also be used as blowing agent, wherein the refrigerant vapor can be generated by a steam generator, which downstream of the pumping device at the outlet of the Kondensa ⁇ and the blowing agent inlet is connected upstream.
  • FIG. 1 shows a flow diagram of a refrigerating machine with twomaschine ⁇ medium compressors and two capacitors.
  • Fig. 2 propellant compressor of the same refrigerator in a highly schematic, enlarged section
  • Fig. 4 further blowing agent compressor for the same Kälte ⁇ machine in a highly schematic, enlarged section.
  • evaporator 1 has an evaporator 1, which is partially filled with water 2 as a refrigerant.
  • the vapor space of the evaporator 1 is connected via a suction line 3 with a propellant compressor 4.
  • the distru ⁇ telverêtr 4 is in turn connected via a pressure line 5 to a capacitor 6.
  • om steam space of the condenser 6 is another Suction line 3 'to another propellant compressor 4'. From this, a further pressure line 5 'leads to a further capacitor 6'.
  • the condenser 6 is connected to a pump 8 via a bottom-side suction line 7 and from the condenser 6 'a bottom-side suction line 7' leads to the condenser 6.
  • the water pump 8 feeds water 2 in the bottom area of the water via a pressure line 9 and a throttle element 10 located there Evaporator 1 on.
  • the pressure line 9 pa ⁇ rallel with the two propellant compressors 4, 4 'verbun ⁇ the.
  • the plant is evacuated by means of a vacuum pump, not shown, so that in particular in the evaporator 1 a pressure of approximately 4.5 to 5 Torr prevails.
  • the vacuum pump maintains this pressure in the evaporator 1 by intermittent working. At this pressure, the water contained in the evaporator 1 evaporates at a temperature of more than 0 ° C. This is the cooling temperature to which the evaporator is able to cool an associated system.
  • the water pump 8 operates, wherein it leads themaschine ⁇ medium compressor 4 a continuous flow of water zu ⁇ .
  • This water acts in the propellant compressor 4 as blowing agent, which generates a suction effect in a centrifugal acceleration section.
  • the suction acts in the suction line 3, is pulled by the water vapor from the evaporator 1 ab ⁇ .
  • the propellant compressor 4 the liquid is mixed with the vaporous water, wherein an annular channel can be repeated several times. Details of the propellant compressor 4 will be discussed below.
  • the mixture leaves themaschine ⁇ medium compressor 4 and passes through a - not ge Service ⁇ te - Venturi nozzle via the pressure line 5 in the condenser tor 6 where condensation pressure prevails, so that water 2 is obtained in liquid form and the suction line. 7 can be withdrawn into the pump 8 and conveyed in a circle.
  • the pump 8 not only provides water for the operation of the medium compressors 4, 4 ', but also water as refrigerant for the evaporator 1. For this purpose, it feeds via the pressure line 9 and a throttle element 10 into the bottom area 1 of the evaporator 1, wherein the throttle element makes it possible to lower the pressure to the evaporation pressure.
  • the propellant compressor 4 'supplied in parallel by the pump 8 draws water vapor from it via the suction line 3' Wasserdampf syndromem the capacitor 6 from.
  • a Venturi nozzle also not shown
  • a mixture of water and water vapor passes through the pressure line 5 'into the condenser 6 at the condensation pressure.
  • the propellant compressor 4 can have a pot-shaped housing 11 with a disk 12 inserted therein. Between wall 13 of the housing 11 and the outer circumference 14 of the disc 12, the annular channel 15 is formed, which is closed at the bottom of a housing bottom 16. At the top, the annular channel 15 is closed by a housing cover (not shown), which bears sealingly against the upper side of the disc 12 and on the housing jacket 11 and is fastened to the latter.
  • the disc 12 has amaschinendzu Switzerlandkanal 17, a Wasserdampfzu Switzerlandkanal 18 and a Gemischab technicallykanal 19. These channels extend to their respective mouths on the outer periphery of the disc 12, which themaschineffen ⁇ inlet 20, steam inlet 21 and mixture outlet 22 bil- the. At the other end, the channels 17, 18, 19 each have a collecting space 23, 24, 25, which are formed as a bore perpendicular to the disk 12. The channels 17, 18, 19 open tangentially into the collecting chambers 23, 24, 25 a. Housing baffles 16 are located in the housing base 16 and communicate with the collecting chambers 23, 24, 25 and are connected to the pressure line 9, the suction line 3 and the pressure line 5.
  • liquid water passes through the propellant feed channel 17 into the annular channel 15 and flows through it in the direction of the circumferential arrow U. Due to the orientation of the feed channel in circumferential direction U.
  • the water particles can flow through the annular channel 15 several times in the direction of circulation U, so that their kinetic energy is used to a great extent for the absorption of water vapor.
  • a mixture of water and water vapor emerges from the mixture outlet 22 in order to be rejuvenated.
  • the flow cross sections are brought to condensation pressure.
  • the water vapor can be condensed at least partially be ⁇ already in the annular channel 15 by injection condensation.
  • the width of the opening 20 for the propellant is typically 0.5 mm, the mouth 21 for the water vapor 3.5 mm and the mouth 22 for the mixture 6 mm.
  • the annular channel is typically 2 mm wide, wherein the average flow velocities in the annular channel can be 400 m / s. To avoid corrosion and deposits, the system is operated with de ⁇ tillatorm water.
  • the speed in the annular channel 15 is determined mainly by the pressure of the propellant at the mouth 20. Ho ⁇ he peripheral speeds in the direction of arrow U increase the suction power. At the same time, a seal of about 1: 3 is possible with this arrangement.
  • the disc 12 ' has amaschineschzu Switzerland 17', a steam supply channel 18 'and a Gemischab- leading channel 19 '. These channels expand toward their respective mouths on the outer circumference of the disc 12, which form the propellant inlet 20 , 'water vapor inlet 21' and mixed outlet 22 'Ge.
  • the blowing agent inlet 20 ' has a much smaller cross section than the Wasserdampf ⁇ inlet 21'.
  • the cross-section of the mixture outlet 22 ' is much smaller than that of the steam inlet 21', but larger than that of the blowing agent inlet 20 '.
  • the channels 17 ', 18', 19 'have in the disc 12' each have a collecting space 23 ', 24', 25 ', which are formed as a bore perpendicular to the disc plane.
  • the channels 17 ', 18', 19 ' open tangentially into the collecting spaces 23', 24 ', 25'.
  • the size ratios of the collecting spaces 23 ', 24', 25 ' correspond to the size ratios of the respective outlets 17', 21 'and inlets 19' connected to them.
  • the disk 12 ' like the disk 12, is inserted into a pot-type blowing medium compressor with cover and held immovably therein. The above-described cross-sectional and size ratios favor the efficiency of the propellant compressor.
  • the propellant compressor 4 can also be formed by a closed pipe bend 26, which delimits the annular channel 27.
  • the tube ring In the tube ring are sealingly guided dip tubes 28, 29, 30, the inner mouths 31, 32, 33 form the propellant inlet, the steam inlet and the Gemischauslcorro.
  • propellant and water vapor are injected by the orientation of the adjoining dip tubes 28, 29 in the direction of the circular arrow U and favors the alignment of the dip tube 30 with its outlet opening 32 against the circulation direction U.

Abstract

L'invention concerne une machine frigorifique qui comprend un évaporateur (1), un compresseur pour l'agent réfrigérant (4), relié à l'évaporateur (1) pour aspirer la vapeur d'eau qui sort de l'évaporateur et comprimer la vapeur d'eau aspirée à une pression de condensation, un condenseur (6) relié au compresseur (4) pour condenser la vapeur d'eau comprimée et un organe d'étranglement (10) reliant le condenseur (6) à l'évaporateur (1), pour détendre l'eau afin qu'elle passe de la pression de condensation à la pression d'évaporation. Le compresseur de l'agent réfrigérant (1) comporte une section d'accélération à force centrifuge pour l'agent réfrigérant, munie d'un canal annulaire (15) qui la délimite à l'extérieur. Ce canal annulaire (15) comporte un orifice d'admission (20, 30) alimenté en agent réfrigérant, un orifice d'admission de la vapeur d'eau (21, 31) situé radialement à l'intérieur et relié à l'évaporateur, un orifice de sortie combiné (22, 32) relié au condenseur (6) et situé à distance de l'orifice d'admission de l'agent réfrigérant (20, 30) et un orifice d'admission de la vapeur d'eau (21, 31). L'orifice d'admission de la vapeur d'eau (20, 30) est relié au condenseur (6) par l'intermédiaire d'une pompe à eau (8).
PCT/EP1994/000087 1993-01-19 1994-01-12 Machine frigorifique Ceased WO1994017341A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AU58830/94A AU5883094A (en) 1993-01-19 1994-01-12 Refrigerating machine

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19934301181 DE4301181C2 (de) 1993-01-19 1993-01-19 Kältemaschine
DEP4301181.0 1993-01-19

Publications (2)

Publication Number Publication Date
WO1994017341A1 WO1994017341A1 (fr) 1994-08-04
WO1994017341A9 true WO1994017341A9 (fr) 1994-09-15

Family

ID=6478415

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP1994/000087 Ceased WO1994017341A1 (fr) 1993-01-19 1994-01-12 Machine frigorifique

Country Status (3)

Country Link
AU (1) AU5883094A (fr)
DE (2) DE4301181C2 (fr)
WO (1) WO1994017341A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4301181C2 (de) * 1993-01-19 1996-06-27 Dester Kaelte Anlagenbau Gmbh Kältemaschine
DE4446036C2 (de) * 1994-12-23 1999-06-02 Ruesch Willy Ag Platzhalter zum Anordnen in einer Körperröhre
DE19508805C2 (de) * 1995-03-06 2000-03-30 Lutz Freitag Stent zum Anordnen in einer Körperröhre mit einem flexiblen Stützgerüst aus mindestens zwei Drähten mit unterschiedlicher Formgedächtnisfunktion

Family Cites Families (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE188333C (fr) *
GB170841A (en) * 1920-10-29 1922-07-06 Vickers Electrical Co Ltd Improvements in fluid pressure operated ejectors
GB269214A (en) * 1926-04-12 1928-01-05 Henri Victor Riehl A device for the suction and delivery of gaseous or liquid fluids
US2088609A (en) * 1936-07-28 1937-08-03 Randel Bo Folke Method of and apparatus for refrigerating
FR948969A (fr) * 1946-05-31 1949-08-17 Procédés de transformation de la chaleur
US3022743A (en) * 1959-06-19 1962-02-27 Erie Mfg Co Injector pump
US3215088A (en) * 1962-11-01 1965-11-02 Ralph C Schlichtig Ejectors
BE652968A (fr) * 1963-09-13 1964-12-31
GB1125103A (en) * 1965-05-24 1968-08-28 Babcock & Wilcox Ltd Improvements in and relating to the compression of vapour
GB1132477A (en) * 1965-09-22 1968-11-06 Joseph Kaye & Company Inc Multiple-phase ejector refrigeration system
GB1193913A (en) * 1968-02-14 1970-06-03 Gas Council London Improvements in or relating to Injector Pumps
DE2948559A1 (de) * 1979-12-03 1981-06-04 Wolfgang Dipl.-Kfm. Dr. 4300 Essen Ramms Mehrzweck-foerderduese
US5056323A (en) * 1990-06-26 1991-10-15 Natural Energy Systems Hydrocarbon refrigeration system and method
DE4301181C2 (de) * 1993-01-19 1996-06-27 Dester Kaelte Anlagenbau Gmbh Kältemaschine
DE9301266U1 (de) * 1993-01-19 1993-04-01 M. Diehn GmbH, 2000 Hamburg Kältemaschine

Similar Documents

Publication Publication Date Title
US5097677A (en) Method and apparatus for vapor compression refrigeration and air conditioning using liquid recycle
EP2341300B1 (fr) Pompe à chaleur
DE112008000519B4 (de) Einheit für Ejektorkältekreislauf und Kältekreislaufvorrichtung unter Verwendung desselben
DE102005038858A1 (de) Dampfkompressionskreis mit Ejektorpumpe
DE102008016664A1 (de) Vertikal angeordnete Wärmepumpe und Verfahren zum Herstellen der vertikal angeordneten Wärmepumpe
EP3423765B1 (fr) Pompe à chaleur pourvue d'une chambre de collecte de gaz étranger, procédé pour faire fonctionner une pompe à chaleur et procédé de fabrication d'une pompe à chaleur
EP0927327B1 (fr) Procede et installation pour produire du froid et/ou du chaud
DE60101057T2 (de) Anordnung einer mehrstufigen wärmepumpenanlage
DE609405C (de) Luftkaeltemaschine
WO1994017341A9 (fr) Machine frigorifique
EP0354263B1 (fr) Compresseur alimentant un réfrigérateur cryogénique en hélium
DE4301181C2 (de) Kältemaschine
DE9301266U1 (de) Kältemaschine
EP3423766B1 (fr) Pompe à chaleur dotée d'un piège à gaz, procédé de fonctionnement d'une pompe à chaleur dotée d'un piège à gaz et procédé de fabrication d'une pompe à chaleur dotée d'un piège à gaz
EP4602307A1 (fr) Dispositif de pompe à chaleur pour la génération économe en énergie d'une chaleur de traitement, dispositif de séchage permettant de sécher un matériau devant être séché, et procédé de fonctionnement d'un dispositif de pompe à chaleur
EP0523035B1 (fr) Processus de fonctionnement d'une thermopompe a compression et thermopompe a compression
DE19711117C1 (de) Anlage zum Verdichten eines gasförmigen Mediums oder zur Erzeugung eines Vakuum
DE2405300A1 (de) Dampfverdichtungs- und kuehlverfahren sowie kuehlanlage zur durchfuehrung des verfahrens
DE3622743A1 (de) Waermepumpe
DE1035669B (de) Verfahren zum Betrieb einer Kompressor-Kuehlanlage mit mindestens zweistufiger Kompression eines in der Anlage umlaufenden Kaeltemittels sowie Kompressor-Kuehlanlage zur Durchfuehrung des Verfahrens
DE2200553A1 (de) Entspannungs- und Verdampfungsvorrichtung fuer Kuehlmaschinen
DE2839415B1 (de) Kondensator-Verdampfer
DE102020213554B4 (de) Gaskältemaschine, Verfahren zum Betreiben einer Gaskältemaschine und Verfahren zum Herstellen einer Gaskältemaschine mit einer gekühlten Elektronik
US1922712A (en) Refrigerating method and apparatus
WO2019043009A1 (fr) Pompe à chaleur comprenant un système de refroidissement intermédiaire fermé et procédé servant à pomper de la chaleur ou procédé servant à fabriquer la pompe à chaleur