WO2008046120A2 - Absorptionskältemaschine - Google Patents
Absorptionskältemaschine Download PDFInfo
- Publication number
- WO2008046120A2 WO2008046120A2 PCT/AT2007/000472 AT2007000472W WO2008046120A2 WO 2008046120 A2 WO2008046120 A2 WO 2008046120A2 AT 2007000472 W AT2007000472 W AT 2007000472W WO 2008046120 A2 WO2008046120 A2 WO 2008046120A2
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- pump
- absorber
- pressure
- solution
- generator
- Prior art date
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
- F25B15/025—Liquid transfer means
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B19/00—Machines or pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B1/00 - F04B17/00
- F04B19/20—Other positive-displacement pumps
- F04B19/24—Pumping by heat expansion of pumped fluid
-
- 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
- F04F1/00—Pumps using positively or negatively pressurised fluid medium acting directly on the liquid to be pumped
- F04F1/06—Pumps using positively or negatively pressurised fluid medium acting directly on the liquid to be pumped the fluid medium acting on the surface of the liquid to be pumped
-
- 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
-
- 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 chillers For solar chillers are adsorption and absorption chillers. At present, it is preferred to use the former, although absorption chillers, especially those operated with the refrigerant ammonia and the absorbent water, have significant advantages: much lower cooling temperatures can be achieved, and with a suitable design, the heat number could be much better than that of adsorption chillers. However, there are a number of obstacles in the current state of the art.
- the classic absorption chiller is based on the principle that a refrigerant in a liquid absorbent at low temperature and low pressure dissolves very well, which takes place in an absorber heat exchanger as an exothermic process, in contrast, in a so-called generator heat exchanger at high temperature even at much higher pressure in Vapor form, which is an endothermic process. If now this refrigerant vapor at high pressure in a condenser heat exchanger heat withdrawn at the so-called recooling temperature which is usually close to the ambient temperature, the refrigerant liquefies. If the pressure is then lowered, the refrigerant in the evaporator can evaporate again at a lower temperature. This endothermic process is the actual cooling process.
- the absorbent is also cooled to the recooling temperature. Subsequently, the gaseous refrigerant coming from the evaporator and the recooled absorbent are brought together again at low pressure in an absorber heat exchanger.
- High-refrigerant absorbents such as those derived from the absorber, are called strong solutions, low-refrigerant absorbents, as they come from the generator, are called weak solutions.
- the object of the invention is to propose an absorption chiller of the type mentioned, which has a long life and low wear. Further task It is to propose an absorption chiller of the type mentioned, which has no or only slight variations in the cooling temperature.
- the first object is achieved in an absorption refrigeration machine of the type mentioned by the features of claim 1.
- Pressure barrier of 5-15 bar can be dispensed with.
- Solution transport may be associated with thermal solar energy
- the concentration of the solution can be adapted to the respective heating temperature and thus an optimal operation can be achieved. Due to the features of claim 9 results in a very simple construction for a
- Chiller which differ essentially by the structure of the steam pump.
- the refrigerating machine comprises a steam pump 100, which has a pump inlet vessel 26, a pressure booster 27 arranged below its level, a pressure reducer 30 arranged below its level, and a pump outlet vessel 46 arranged below its level, it being provided according to the preferred embodiment Pumpenausgangsgefdata 46 with the pump inlet vessel 26 and the Druckabsenker 30, as well as with the generator 6 is in communication.
- This steam pump 100 is connected via a pump outlet pipe 1, in which a shut-off, in particular a check valve 12 is connected to a pressure stabilizer 3, which is surrounded by a heating jacket 101, and a shut-off device 4, preferably a check valve, and a flow resistance, such as a Throttle 5, connected to a generator 6 for driving the refrigerant out of the solution.
- the generator 6 is followed by a gas separator 7, the gas space is connected to a capacitor 8.
- the condenser is acted upon by a recooling medium, which enters at the inlet 42 and exits at the exit 43.
- the refrigerant condensate leaving the condenser is fed to a concentration regulator 9.
- a concentration regulator 9 This is essentially formed by a tube which is substantially horizontally aligned and pivotable about a horizontal axis 102. As a result, the tube can be pivoted about the horizontal by a predeterminable angle, whereby more or less refrigerant condensate can be held in the tube.
- the concentration regulator 9 is connected to a shut-off device, preferably a float valve 2, which in turn is connected to an evaporator 13, which is acted upon by a cooling medium, which enters via the input 44 and exits at the output 45 ,
- the evaporator 13 is connected via a line 15, in which a shut-off device, e.g. a check valve 14 is arranged, connected to a warm absorber 17, whose cooling circuit 105 is flowed through by the cooled heating medium, which exits at the output 41.
- a shut-off device e.g. a check valve 14
- a warm absorber 17 whose cooling circuit 105 is flowed through by the cooled heating medium, which exits at the output 41.
- the line 15 opens in front of the warm absorber 17, a line 16 which is connected to a connected to the liquid space of the gas separator 7 obturator, in particular a float valve 51, which only liquid, but not gas can pass.
- the warm absorber 17 is connected to a cold absorber 19 via a U-shaped tube 18, the legs of which drop off downwards.
- the cold absorber 19 is connected to a vacuum stabilizer 20, which, like the cold absorber 19, is acted upon by a recooling medium, which flows through a cooling circuit 104 in countercurrent.
- the vapor pump 100 stands - seen in the direction of the circulation of the refrigerant solution, for example a water-ammonia solution - between the absorber and the generator, the pump on the input side with the absorber 17, 19, in particular with the warm Absorber 17 and / or the cold absorber 19, and the output side with the generator 6 in
- the vacuum stabilizer 20 is connected to the steam pump 100 via a float valve 21 and a check valve 22.
- the booster 27 is acted upon according to the preferred embodiment of the heating medium, which enters at the entrance 40 and exits at the exit 41.
- the pressure reducer is acted upon according to the preferred embodiment of the heating medium, which enters at the entrance 40 and exits at the exit 41.
- the cooling circuit of the condenser 8 is flowed through by the recooling medium, which exits at 42 and 43.
- the cooling circuit of the evaporator 13 is traversed by the cooling medium and enters at 44 in this and leaves it at 45, wherein the heat exchanger of the evaporator, but preferably not necessarily, is operated in direct current, whereas the remaining
- Heat exchangers are operated in countercurrent.
- the cooling circuit of the vacuum stabilizer 20 and the cooling circuit of the cold absorber 19 are connected in series, wherein the recooling medium at the entrance 42 of the cooling jacket 103 of the
- Vacuum stabilizer 20 enters and at the exit 43 of the cooling circuit 104 of the cold
- a pump inlet line 23 connected to the non-return valve 22 opens from above into the pump inlet vessel 26, from which downwardly leads to an S-shaped lifting tube 24, to which a pressure increase
- Fluid lift tube 33 is connected, which in one with the liquid space of the
- the strong refrigerant solution is pressed by the vapor pump, or by the pump outlet vessel 46 via the blocking means 12 in the pressure stabilizer 3. This serves to convert the pump strokes of the solution flow into a uniformly flowing flow with an optimum pressure for the generator process.
- the pressure stabilizer 3 consists of a heated container of any shape, preferably a horizontal tube, which is surrounded by a flow-through by the heating medium jacket 101, wherein the tube is dimensioned so that always holds a gas bubble in its upper part. If cold solution is fed into the pressure stabilizer 3 by the pump 100, the pressure in the gas bubble of the pressure stabilizer 3 briefly drops, which allows unimpeded inflow of the solution.
- the gas pressure in the pressure stabilizer 3 rises again to just above the generator pressure, since the solution is warmed up to the evaporation temperature.
- the heating jacket 101 of the pressure stabilizer 3 is connected to the output of the generator heater 106.
- the flow resistance 5, preferably a throttle and by the blocking means 4, preferably a check valve it is ensured that in the generator 6, a uniform solution flow occurs.
- the solution flows in countercurrent to the heating medium flow input 40, heats up and forms gas bubbles.
- the use of the pressure stabilizer 3 allows the use of a heat exchanger for the generator 6 with a narrow cross-section, but with a very large hydraulic length, ie a heat exchanger with high flow resistance, preferably a spiral heat exchanger, and because of the large flow rate is an extremely high heat transfer per unit area reached. This results in a particularly large temperature range of the heating medium on the way from the heating medium flow input 40 to the output of the generator 6. Since the heating medium during the passage through the heating jacket of the pressure stabilizer 3 further cools, its temperature is suitable to the warmer part of the absorption process cool.
- the heating medium from the pressure stabilizer 3 is passed to the heat exchanger of the warm absorber 17, where it is reheated by the absorption process and finally out at 41 Bankmediumshne output back to the heater, not shown.
- the hot weak solution passes together with the gas bubbles formed in the gas separator 7.
- the blocking means 51 preferably a float valve
- the hot solution then passes to the warm absorber 17th
- Gas separator 7 passes the gas into the heat exchanger of the condenser 6, where heat is withdrawn by the recooling medium flowing in at 42 and 43, resulting in the condensation of the refrigerant. This now runs through the flexible inflow pipe 10 to the concentration regulator 9.
- the concentration regulator 9 is rotatable about a rotatable suspension in the form of a horizontal axis 102 upwards or downwards and can be fixed in this position. Depending on the angle of inclination of the concentration regulator 9, a different amount of refrigerant then accumulates in the container 9 before it can continue to flow via the second flexible discharge pipe 11 via the float valve 2 to the evaporator 13. The amount of refrigerant accumulated in the concentration regulator 9 is withdrawn from the refrigeration cycle, so that the average concentration of the refrigerant solution in the entire machine is reduced. This adjustment is advantageous for solar cooling, since the optimum solution temperature is dependent on heating temperature, recooling temperature and desired cooling temperature, these three temperatures are climate-dependent.
- the evaporation process of the refrigerant cools the cooling medium flow through 44 and 45.
- the resulting refrigerant vapor passes through the supply line 15 to the warm absorber 17.
- the supply line 15 unites with the supply line 16, which the Generator 6 incoming weak solution to the warm absorber 17 feeds.
- the warm absorber 17 is cooled in countercurrent to the solution by the coming from the pressure stabilizer 3 cooled heating medium. The temperature of the heating medium rises, so that its temperature at the outlet of the warm absorber 17 reflects the amount of energy recovered from the absorption process.
- the absorption process in the warm absorber 17 can not be completed, since in this a lower pressure than in the generator 6 prevails, thus the temperature for a complete absorption also must be lower than in the pressure stabilizer 3.
- the mixture of solution and residual refrigerant vapor is therefore conducted via the connecting line 18 into the cold absorber 19.
- the absorption process is completed and the resulting strong refrigerant solution is fed into the vacuum stabilizer 20.
- This is similar in construction to the pressure stabilizer 3, but its outer jacket is cooled, so that in the inner tube Stored solution is always almost at the recooling temperature.
- the vacuum stabilizer 20 It is also important with the vacuum stabilizer 20 that it is dimensioned such that a gas bubble can always be obtained in its upper part.
- the pressure in the vacuum stabilizer 20 is then always lower than the vapor pressure of the coming of the generator 6 through the supply line 16 hot solution or coming from the evaporator 13 through the supply line 15 refrigerant vapor. Therefore, the negative pressure stabilizer 20 sucks the mixture of refrigerant vapor and weak refrigerant solution through the two absorbers 17 and 19, even if they are formed as a high-performance heat exchanger with a narrow cross-section and large hydraulic length, which also have a relatively large flow resistance.
- the recooling medium should first flow through the vacuum stabilizer 20 and then only the cold absorber 19, the latter in countercurrent to the mixture of solution and refrigerant vapor.
- the vacuum stabilizer 20 also serves as a refrigerant solution reserve for the pump 100 so that it can work uniformly.
- the strong solution enters the vapor pump, but only during the periods when the pressure in the vapor pump is low enough. If this is the case, then the main part of the solution flows through the first pump inlet pipe 38 and the controllable flow resistance 39 into the pump outlet vessel 46 and fills it. At the same time, however, also a smaller part of the solution flows through the second pump inlet pipe 23 into the pump inlet vessel 26.
- the pump inlet vessel 26 must be at the highest point of the vapor pump - the entire system between the shut-off means 22 and 12 - the pressure booster 27 must be below it, the pressure reducer 30 must be below the pressure booster 27 and again below it must be the pump outlet vessel 46.
- the lowest level of the vapor pump forms the horizontal branch of the first pump inflow pipe 38 and the pump output pipe 1 is intended to branch off from the vertical leg of the first pump inflow pipe 38 below the pump output vessel 46. This height positioning is necessary because the solution in the vapor pump is moved by gravity alone.
- the phases of the pumping cycle are as follows:
- 1st phase The pump inlet vessel 26 and the pump outlet vessel 46 fill.
- 2nd phase As soon as the pump inlet vessel 26 has filled, the siphon tube 24 is filled up to its upper vertex. As solution flows over this apex, the siphon tube 24 draws solution from the pump inlet vessel 26 and allows it to flow into the lower portion of the pump, namely, the depressurizer 30 and the pressure riser 27. However, the solution can not flow immediately to the lowermost part of the pump via the fluid lift tube 33, which connects the suction tube 32 to the pump outlet vessel 46, since the static hydraulic pressure of the solution filled pump outlet vessel 46 prevents this.
- the amount of solution per pump stroke must be dimensioned so that the pressure booster 27, preferably a horizontal tube, surrounded by a heating jacket, partially filled.
- the pressure booster 27 preferably a horizontal tube, surrounded by a heating jacket, partially filled.
- Druckabsenker 30, which is preferably formed by a horizontal tube, surrounded by a cooling jacket, while a gas bubble remains, due to the suction pipe 32, which opens from above into the pressure dropper 30.
- FIG. 2 shows a refrigerating machine according to the invention with another vapor pump.
- the filling of the pump takes place only via the pump inlet pipe 23 into the pump inlet vessel 26. Once the latter has been filled with solution, this flows through the siphon tube 24 to the pressure booster 27. Exactly on the level, however, where in the booster 27, the solution surface is located in the siphon tube 24 a branch to the overflow 107 out, which directs the excess solution through the pump inlet pipe 38 to the pump outlet vessel 46.
- a vent 108 of the overflow 107 in order to prevent this cross-connection between the siphon tube 24 and the pump inlet tube 38 itself acts as a liquid lift.
- the purpose of the overflow 107 is to convey a majority of the solution directly to the pump outlet vessel 46, which thus does not participate in the heating and cooling in the pressure booster 27 and the pressure drop 30, thereby saving energy.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Sorption Type Refrigeration Machines (AREA)
Abstract
Description
Claims
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CA002666172A CA2666172A1 (en) | 2006-10-19 | 2007-10-04 | Absorption refrigerator |
EP07815139A EP2082175A2 (de) | 2006-10-19 | 2007-10-04 | Absorptionskältemaschine |
AU2007312922A AU2007312922A1 (en) | 2006-10-19 | 2007-10-04 | Absorption refrigerator |
NO20091911A NO20091911L (no) | 2006-10-19 | 2009-05-15 | Absorbsjonskulde maskin |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
AT0174406A AT504399B1 (de) | 2006-10-19 | 2006-10-19 | Absorptionskältemaschine |
ATA1744/2006 | 2006-10-19 |
Publications (2)
Publication Number | Publication Date |
---|---|
WO2008046120A2 true WO2008046120A2 (de) | 2008-04-24 |
WO2008046120A3 WO2008046120A3 (de) | 2008-11-13 |
Family
ID=39314378
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/AT2007/000472 WO2008046120A2 (de) | 2006-10-19 | 2007-10-04 | Absorptionskältemaschine |
Country Status (6)
Country | Link |
---|---|
EP (1) | EP2082175A2 (de) |
AT (1) | AT504399B1 (de) |
AU (1) | AU2007312922A1 (de) |
CA (1) | CA2666172A1 (de) |
NO (1) | NO20091911L (de) |
WO (1) | WO2008046120A2 (de) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2011032978A1 (en) | 2009-09-15 | 2011-03-24 | Aquasolair As | Water extraction unit |
WO2012126023A3 (de) * | 2011-03-23 | 2013-05-10 | Solar Frost Labs Pty Ltd | Solarkühlung mit einer ammoniak-wasser-absorptionskältemaschine |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
AT514997B1 (de) * | 2013-10-21 | 2015-11-15 | Gerhard Dr Kunze | Modulare Absorptionskältemaschine in Plattenbauweise |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2688923A (en) * | 1951-11-05 | 1954-09-14 | Filiberto A Bonaventura | Solar energy pump |
US3053198A (en) * | 1958-02-21 | 1962-09-11 | Midland Ross Corp | Thermopump system |
GB2044907A (en) * | 1979-03-15 | 1980-10-22 | Vaillant J Gmbh & Co | Heat pump, particularly vapour- compressing jet type heat pump |
DE3417880A1 (de) * | 1983-07-11 | 1985-01-24 | VEB Wärmeanlagenbau "DSF" im VE Kombinat Verbundnetze Energie, DDR 1020 Berlin | Absorptionswaermepumpe |
Family Cites Families (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB382654A (en) * | 1930-08-13 | 1932-10-31 | Electrolux Ltd | Improvements in or relating to absorption refrigerating apparatus |
GB434978A (en) * | 1933-07-17 | 1935-09-12 | Hoover Ltd | Improvements in or relating to continuous absorption refrigerating apparatus |
US2454344A (en) * | 1944-08-21 | 1948-11-23 | Montcalm Inc | Absorption refrigeration system |
US5157942A (en) * | 1991-06-14 | 1992-10-27 | Kim Dao | Regenerative absorption cycles with multiple stage absorber |
DE10240659B4 (de) * | 2001-11-30 | 2011-07-07 | Fraunhofer-Gesellschaft zur Förderung der angewandten Forschung e.V., 80686 | Verfahren und Vorrichtung zur solarthermischen Kälteerzeugung |
-
2006
- 2006-10-19 AT AT0174406A patent/AT504399B1/de not_active IP Right Cessation
-
2007
- 2007-10-04 AU AU2007312922A patent/AU2007312922A1/en not_active Abandoned
- 2007-10-04 EP EP07815139A patent/EP2082175A2/de not_active Withdrawn
- 2007-10-04 CA CA002666172A patent/CA2666172A1/en not_active Abandoned
- 2007-10-04 WO PCT/AT2007/000472 patent/WO2008046120A2/de active Application Filing
-
2009
- 2009-05-15 NO NO20091911A patent/NO20091911L/no not_active Application Discontinuation
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2688923A (en) * | 1951-11-05 | 1954-09-14 | Filiberto A Bonaventura | Solar energy pump |
US3053198A (en) * | 1958-02-21 | 1962-09-11 | Midland Ross Corp | Thermopump system |
GB2044907A (en) * | 1979-03-15 | 1980-10-22 | Vaillant J Gmbh & Co | Heat pump, particularly vapour- compressing jet type heat pump |
DE3417880A1 (de) * | 1983-07-11 | 1985-01-24 | VEB Wärmeanlagenbau "DSF" im VE Kombinat Verbundnetze Energie, DDR 1020 Berlin | Absorptionswaermepumpe |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2011032978A1 (en) | 2009-09-15 | 2011-03-24 | Aquasolair As | Water extraction unit |
WO2012126023A3 (de) * | 2011-03-23 | 2013-05-10 | Solar Frost Labs Pty Ltd | Solarkühlung mit einer ammoniak-wasser-absorptionskältemaschine |
Also Published As
Publication number | Publication date |
---|---|
CA2666172A1 (en) | 2008-04-24 |
AU2007312922A1 (en) | 2008-04-24 |
AT504399B1 (de) | 2008-12-15 |
WO2008046120A3 (de) | 2008-11-13 |
EP2082175A2 (de) | 2009-07-29 |
AT504399A1 (de) | 2008-05-15 |
NO20091911L (no) | 2009-05-15 |
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