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WO1994017341A1 - Machine frigorifique - Google Patents

Machine frigorifique Download PDF

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Publication number
WO1994017341A1
WO1994017341A1 PCT/EP1994/000087 EP9400087W WO9417341A1 WO 1994017341 A1 WO1994017341 A1 WO 1994017341A1 EP 9400087 W EP9400087 W EP 9400087W WO 9417341 A1 WO9417341 A1 WO 9417341A1
Authority
WO
WIPO (PCT)
Prior art keywords
propellant
inlet
water vapor
channel
condenser
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
WO1994017341A9 (fr
Inventor
Manfred Diehn
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.)
Dester Kalte-Anlagenbau GmbH
Original Assignee
Dester Kalte-Anlagenbau 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 Dester Kalte-Anlagenbau GmbH filed Critical Dester Kalte-Anlagenbau GmbH
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

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04F—PUMPING OF FLUID BY DIRECT CONTACT OF ANOTHER FLUID OR BY USING INERTIA OF FLUID TO BE PUMPED; SIPHONS
    • F04F5/00—Jet pumps, i.e. devices in which flow is induced by pressure drop caused by velocity of another fluid flow
    • F04F5/02—Jet pumps, i.e. devices in which flow is induced by pressure drop caused by velocity of another fluid flow the inducing fluid being liquid
    • F04F5/04—Jet pumps, i.e. devices in which flow is induced by pressure drop caused by velocity of another fluid flow the inducing fluid being liquid displacing elastic fluids
    • F04F5/06—Jet pumps, i.e. devices in which flow is induced by pressure drop caused by velocity of another fluid flow the inducing fluid being liquid displacing elastic fluids of rotary type
    • 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
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/06—Compression machines, plants or systems with non-reversible cycle with compressor of jet type, e.g. using liquid under pressure
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/07—Details of compressors or related parts
    • F25B2400/075—Details of compressors or related parts with parallel compressors

Definitions

  • the invention relates to a refrigerator according to the preamble of claim 1.
  • a refrigerator is a device for generating low temperatures. It is designed to extract heat from a system whose temperature is below the ambient temperature in order to release it to the environment at a higher temperature.
  • the heat transport is carried out by a refrigerant as a heat carrier, which is usually carried out in a closed circuit.
  • Liquid refrigerants are used, which absorb large amounts of heat during evaporation and release again when condensed.
  • To take advantage of this Evaporative and condensation heat have refrigeration machines an evaporator which removes heat from the system to be cooled and a condenser for the coolant which emits heat to the environment.
  • the refrigerant vapor is drawn in by the evaporator with a mechanical compressor, compressed and conveyed into the condenser.
  • Halogenated hydrocarbons are mainly used. Fluorochlorine hydrocarbons are considered to be harmful to ozone, so that the use of such refrigeration machines is problematic.
  • the mechanical compressor In the absorption refrigeration system, the mechanical compressor is replaced by a thermal one. In the continuous In the absorption machine that works, the refrigerant vapor is compressed by being absorbed by the poor solution in the absorber at low pressure and being expelled from the rich solution in the expeller at high pressure.
  • the two best known material pairs for this process of refrigeration are ammonia / water and water / lithium bromide solution. Such systems are technically relatively complex.
  • the steam jet refrigeration machine is known in which a steam jet compressor is used to extract and compress the refrigerant vapors.
  • the motive steam passes through a motive nozzle into a chamber of the compressor, in which it expansively draws in and mixes refrigerant vapor at high speed.
  • the speed 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 refrigeration machine has the advantage that it works with water, ie a harmless refrigerant. If cooling to temperatures from -2 to +10 "C is to be carried out, the evaporator must be operated with relatively low pressures (the boiling points of water are, for example, at 760 Torr + 100 ° C and at 4.579 Torr 0 ° C). This refrigeration machine is therefore operated as a vacuum system. The large amounts of water vapor from the evaporator can also be processed in a vacuum by a steam jet compressor.
  • the steam jet refrigeration machine In addition to the low efficiency of the steam jet compressor, the steam jet refrigeration machine has the disadvantage that motive steam must be made available. As a rule, their use is therefore limited to cases in which process steam or steam can be used.
  • the object of the invention is to create a refrigeration machine which contains a harmless refrigerant, works with better efficiency and is not dependent on a propellant supplied from the outside.
  • the structure of a refrigerator according to the invention essentially corresponds to that of a known steam jet refrigerator.
  • a propellant compressor instead of a steam jet compressor a propellant compressor is provided, the centrifugal acceleration section of which has an increased suction power.
  • Liquid circulating water from the condenser is preferably used as the propellant, so that no external propellant supply is required.
  • the blowing agent compressor can simultaneously act as an injection condenser and take over at least part of the condensation power.
  • the propellant compressor works particularly effectively when propellant liquid particles are guided several times around the water vapor inlet in the ring channel delimiting the centrifugal acceleration path and repeatedly exert a suction effect on the latter.
  • the blowing agent inlet can be designed at the mouth of a blowing agent supply channel which is white in the circumferential direction of the ring channel.
  • the water vapor intake is favored if the water vapor inlet is formed at the mouth of a water vapor supply channel pointing in the same circumferential direction.
  • the water vapor feed channel can contain a plurality of guide plates arranged in a staggered manner in the circumferential direction, which can extend over a considerable part of the circumference of the ring channel.
  • the mixture outlet can be formed at the mouth of a mixture discharge channel pointing counter to this circumferential direction.
  • the blowing agent inlet for the liquid blowing agent preferably has a smaller cross section than the water vapor inlet, as a result of which high vapor throughputs are promoted.
  • the mixture outlet preferably has a larger cross section than the blowing agent inlet, so that the mixture is drawn off to a sufficient extent without problems.
  • the mixture outlet preferably has a smaller cross-section than the water vapor inlet, which favors the build-up of a negative pressure in the inlet region and multiple guiding of the propellant particles through the annular channel.
  • the propellant inlet, water vapor inlet and mixture outlet are preferably spaced apart from one another along the circumference of the annular channel. Since a maximum suction effect in the flow direction is to be expected in front of the propellant inlet, it will advantageously be arranged downstream of the water vapor inlet in a circumferential direction of the ring channel and upstream of the mixture outlet.
  • the water pump for the propellant delivery can be a conventional pump or a high-pressure pump.
  • the propellant compressor can be designed to save space and without rotating parts.
  • the propellant compressor has a pot-like housing, a disc inserted therein and a cover which is sealed on the disc and an edge of the housing. In a spacing area between the outer periphery of the disk and the inner periphery of the wall of the pot-like housing, the annular channel is formed, which is closed at the bottom by the housing base and at the top by the housing cover.
  • a blowing agent and a water vapor supply channel and a mixture removal channel are preferably formed in the disk. These each have an opening at one end on the outer circumference of the disk, which form the blowing agent inlet, water vapor inlet or mixture outlet. At the other end, they each communicate with a housing bore for propellant supply, water supply or mixture discharge. In this construction, propellant and water vapor pass through the housing bores and their supply channels as well as the inlets into the ring channel and are withdrawn from this through the outlet, mixture discharge channel and associated housing bore.
  • the water vapor supply channel and mixture discharge channel to the ring channel have a favorable influence on the flow conditions therein.
  • blowing agent supply channel, water vapor supply channel and mixture discharge channel can gradually widen towards their mouths on the outer circumference of the disk.
  • propellant supply channel, water vapor supply channel and mixture discharge channel can each end in a collecting space of the disk at the other end.
  • the collecting spaces can simply be designed as bores arranged perpendicular to the pane and are then closed by the housing cover and the housing base, which have the assigned housing bore.
  • the propellant supply duct, water vapor supply duct and mixture discharge duct are each aligned approximately tangentially to the associated collecting space. It is favorable for the fixed installation of supply and discharge lines if the housing bores for propellant, water vapor and mixture are each formed in the housing base.
  • Another propellant compressor has a tube which is closed to form a ring and delimits the ring channel (ring tube), the propellant inlet, water vapor inlet and mixture outlet being passed through the tube wall. Blowing agent inlet, steam inlet and mixture outlet are preferred. leave dip tubes guided through the tube walls at each of the mouths.
  • the ring channel preferably follows an arc.
  • the propellant compressor is designed as a pot with a disk, it preferably has a rectangular cross section.
  • the propellant compressor When designed as an annular tube, it preferably has a circular cross section.
  • the cross section can change in the circumferential direction, for example reduce in the inlet area and enlarge in the outlet area.
  • blowing agent compressors are very space-saving and easy to carry out and are therefore suitable for both commercial and private refrigeration systems.
  • the mixture outlet of the propellant compressor can be connected to the condenser via a diffuser.
  • the diffuser is a channel section gradually widened in the direction of flow, in which the flow rate of the mixture is converted into pressure. This ensures that the condensation pressure is reached.
  • a further embodiment provides at least one further propellant compressor, the propellant inlet of which is connected to the condenser via a water pump, the water vapor inlet of which is connected to a water vapor space of the condenser and the mixture outlet of which is connected to the condenser.
  • This propellant compressor condenses water vapor located in the water vapor space of the condenser and improves the overall efficiency of the refrigeration system.
  • the mixture outlet of the further propellant compressor is preferably connected to the condenser via a further condenser.
  • 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 increase in flow velocity is at least due to the addition of further blowing agent in the subsequent compressor stage.
  • the respective flow cross section of the ring channel can be reduced.
  • the refrigeration machine according to the invention is not limited to the use of water as a refrigerant. Rather, water vapor or steam from another conventional refrigerant can be used as a blowing agent, the refrigerant vapor being able to be generated by a steam generator which is connected downstream of the pump device at the outlet of the condenser and upstream of the blowing agent inlet.
  • FIG. 1 shows a flow diagram of a refrigerator with two propellant compressors and two condensers
  • Fig. 2 propellant compressor of the same refrigerator in a highly schematic, enlarged section
  • Fig. 4 further blowing agent compressor for the same refrigeration 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 to a propellant compressor 4 via a suction line 3.
  • the blowing agent compressor 4 is in turn connected to a condenser 6 via a pressure line 5.
  • the condenser 6 is connected to a pump 8 via a bottom-side suction line 7 and a bottom-side suction line 7 'leads from the condenser 6' to the condenser 6.
  • the water pump 8 feeds water 2 in the bottom area of the.
  • the pressure line 9 is connected in parallel to the two propellant compressors 4, 4 '.
  • the system is evacuated by means of a vacuum pump (not shown), so that a pressure of approximately 4.5 to 5 Torr prevails in particular in the evaporator 1.
  • the vacuum pump maintains this pressure in the evaporator 1 by intermittent work.
  • the water in the evaporator 1 evaporates at a temperature of slightly more than 0 ° C. This is the cooling temperature to which the evaporator can cool an assigned system.
  • the water pump 8 operates, supplying the propellant compressor 4 with a continuous flow of water.
  • This water acts in the propellant compressor 4 as a blowing agent that creates a suction effect in a centrifugal acceleration section.
  • the suction acts in the suction line 3, through which water vapor is drawn off from the evaporator 1.
  • the liquid is mixed with the vaporous water, it being possible to pass through an annular channel several times. Details of the propellant compressor 4 will be discussed below.
  • the mixture leaves the propellant compressor 4 at high speed and arrives via a venturi nozzle (not shown) via the pressure line 5 into the condenser 6. There is condensation pressure so that water 2 is obtained in liquid form and via the suction line 7 withdrawn into the pump 8 and can be conveyed in a circle.
  • the pump 8 not only provides water for operating the blowing agent compressors 4, 4 ', but also water as a refrigerant for the evaporator 1. For this purpose, it feeds via the pressure line 9 and a throttle element 10 into the bottom region 1 of the evaporator 1, the throttle element allowing the pressure to be reduced to the evaporation pressure.
  • the propellant compressor 4 ' which is fed in parallel by the pump 8, sucks water vapor out of the Steam chamber of the condenser 6.
  • the operation of the propellant compressor 4 ' is the same as that of the compressor 4.
  • a mixture of water and water vapor at condensation pressure thus passes through the pressure line 5 'into the condenser 6' via a Venturi nozzle, which is also not shown.
  • the majority of the water vapor precipitates there as condensate 2 and is drawn off via a suction line 7 ′ into the condenser 6 and from there with the pump 8.
  • the propellant compressor 4 can have a pot-like housing 11 with a disk 12 inserted therein. Between the wall 13 of the housing 11 and the outer circumference 14 of the disk 12, the annular channel 15 is formed, which is closed at the bottom by a housing base 16. At the top, the ring channel 15 is closed by a housing cover (not shown), which lies sealingly on the upper side of the disk 12 and on the housing jacket 11 and is fastened to the latter.
  • the disk 12 has a propellant feed channel 17, a water vapor feed channel 18 and a mixture discharge channel 19. These channels widen towards their respective openings on the outer periphery of the disk 12, which form the propellant inlet 20, water vapor inlet 21 and mixture outlet 22. the.
  • the channels 17, 18, 19 each have a collecting space 23, 24, 25, which are designed as a bore perpendicular to the disk 12.
  • the channels 17, 18, 19 open tangentially into the collecting spaces 23, 24, 25.
  • housing bores (not shown) which communicate with the collecting spaces 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 ring channel 15 and flows through it due to the orientation of the feed channel in the direction of the circumferential arrow u.
  • a negative pressure is created which causes water vapor to be sucked in through the water vapor feed channel 18. Since the centrifugal force presses the water against the outer wall 13 of the channel 16, the pressure on the outer circumference of the disk and thus on the mouth 21 of the water vapor supply is particularly low and the suction effect is particularly great.
  • the water particles can flow through the ring channel 15 several times in the direction of circulation U, so that their kinetic energy is used to a particular extent for the suction of water vapor.
  • a mixture of water and water vapor constantly emerges from the mixture outlet 22 in order to taper the flow cross sections to be brought to condensation pressure.
  • the water vapor can at least partially already be condensed in the annular channel 15 by injection condensation.
  • the width of the mouth 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 ring channel is typically 2 mm wide, the average flow velocities in the ring channel being 400 m / s. To avoid corrosion and deposits, the system is operated with distilled water.
  • the speed in the ring channel 15 is primarily determined by the pressure of the propellant at the mouth 20. High peripheral speeds in the direction of the arrow U increase the suction power. At the same time, a compression of approximately 1: 3 is possible with this arrangement.
  • the disk 12 ' has a propellant feed channel 17', a water vapor feed channel 18 'and a mixture removal guide channel 19 '. These channels widen towards their respective mouths on the outer periphery of the disk 12 ', which form the blowing agent inlet 20', water vapor inlet 21 'and mixture outlet 22'.
  • the blowing agent inlet 20 ' has a much smaller cross section than the water vapor inlet 21'.
  • the cross section of the mixture outlet 22 ' is much smaller than that of the water vapor inlet 21', but larger than that of the blowing agent inlet 20 '.
  • the disk 12 ' like the disk 12, is inserted into a pot-like propellant compressor with a lid and held immovably therein. The cross-section and size relationships explained above 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.
  • Immersion tubes 28, 29, 30 are sealingly guided into the tube ring, the inner openings 31, 32, 33 form the blowing agent inlet, the water vapor inlet and the mixture outlet.
  • propellant and water vapor are injected by the alignment of the assigned dip tubes 28, 29 in the direction of the arrow U, and favors the alignment of the dip tube 30 with its outlet opening 32 against the direction of rotation U to allow the mixture to be drawn off.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid Mechanics (AREA)
  • Thermal Sciences (AREA)
  • Jet Pumps And Other Pumps (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

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 true WO1994017341A1 (fr) 1994-08-04
WO1994017341A9 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

Citations (12)

* 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
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
GB1125103A (en) * 1965-05-24 1968-08-28 Babcock & Wilcox Ltd Improvements in and relating to the compression of vapour
DE1426974A1 (de) * 1963-09-13 1969-04-24 Joseph Kaye & Company Inc Mehrphasenejektor-Kuehlsystem
DE1906650A1 (de) * 1968-02-14 1969-09-18 Gas Council Injektorpumpe
DE1501079A1 (de) * 1965-09-22 1969-10-30 Joseph Kaye & Company Inc Kuehlverfahren und Einrichtung zu dessen Durchfuehrung
WO1992000494A1 (fr) * 1990-06-26 1992-01-09 Natural Energy Systems, Inc. Systeme de refrigeration a un seul ou plusieurs etages et procede utilisant des hydrocarbures
DE9301266U1 (de) * 1993-01-19 1993-04-01 M. Diehn GmbH, 2000 Hamburg Kältemaschine

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2088609A (en) * 1936-07-28 1937-08-03 Randel Bo Folke Method of and apparatus for refrigerating
DE2948559A1 (de) * 1979-12-03 1981-06-04 Wolfgang Dipl.-Kfm. Dr. 4300 Essen Ramms Mehrzweck-foerderduese
DE4301181C2 (de) * 1993-01-19 1996-06-27 Dester Kaelte Anlagenbau Gmbh Kältemaschine

Patent Citations (12)

* 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
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
DE1426974A1 (de) * 1963-09-13 1969-04-24 Joseph Kaye & Company Inc Mehrphasenejektor-Kuehlsystem
GB1125103A (en) * 1965-05-24 1968-08-28 Babcock & Wilcox Ltd Improvements in and relating to the compression of vapour
DE1501079A1 (de) * 1965-09-22 1969-10-30 Joseph Kaye & Company Inc Kuehlverfahren und Einrichtung zu dessen Durchfuehrung
DE1906650A1 (de) * 1968-02-14 1969-09-18 Gas Council Injektorpumpe
WO1992000494A1 (fr) * 1990-06-26 1992-01-09 Natural Energy Systems, Inc. Systeme de refrigeration a un seul ou plusieurs etages et procede utilisant des hydrocarbures
DE9301266U1 (de) * 1993-01-19 1993-04-01 M. Diehn GmbH, 2000 Hamburg Kältemaschine

Also Published As

Publication number Publication date
DE4417911B4 (de) 2004-12-09
DE4301181A1 (de) 1994-07-21
DE4301181C2 (de) 1996-06-27
DE4417911A1 (de) 1995-11-23
AU5883094A (en) 1994-08-15

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