WO2004072569A1 - Cooling system - Google Patents
Cooling system Download PDFInfo
- Publication number
- WO2004072569A1 WO2004072569A1 PCT/GB2004/000459 GB2004000459W WO2004072569A1 WO 2004072569 A1 WO2004072569 A1 WO 2004072569A1 GB 2004000459 W GB2004000459 W GB 2004000459W WO 2004072569 A1 WO2004072569 A1 WO 2004072569A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- water
- sump
- plenum
- heat exchanger
- collection surface
- Prior art date
Links
Classifications
-
- 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
- F28D5/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, using the cooling effect of natural or forced evaporation
- F28D5/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, using the cooling effect of natural or forced evaporation in which the evaporating medium flows in a continuous film or trickles freely over the conduits
-
- 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
- F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
-
- 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
- F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
-
- 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
- F28D5/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, using the cooling effect of natural or forced evaporation
-
- 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
- F25B2339/00—Details of evaporators; Details of condensers
- F25B2339/04—Details of condensers
- F25B2339/041—Details of condensers of evaporative condensers
-
- 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
- F25B2500/00—Problems to be solved
- F25B2500/06—Damage
Definitions
- This invention relates to cooling systems, more particularly to those including a closed circuit evaporative heat exchanger of the forced draught configuration.
- Closed circuit evaporative heat exchangers are used in a variety of industrial settings to provide cooling or condensing of refrigerants.
- cooling is provided by means of a cooling fluid which draws heat from the area to be cooled and transports it to a heat exchanger where the fluid is cooled again.
- refrigerant vapour enters the heat exchanger where it is condensed and leaves the heat exchanger as liquid.
- air is blown over the heat exchanger coils to remove heat from the liquid or vapour.
- the cooling process is enhanced by spraying water onto the coils so that a proportion of the water is evaporated by the air flow.
- dry operation requires the sump to be drained as the water therein would otherwise freeze and cause damage to the system as a result of the forced flow of cold air over it. This is problematic since the processes of draining and replenishing the sump are time consuming - typically taking several hours. Furthermore it is usually necessary to shut off the cooling system during at least some of the draining or replenishment period, in order to prepare the sump for dry or wet operation respectively by securing make-up valve floats, level controls etc. It is not therefore considered practically or economically feasible to drain and replenish the sump every day.
- a remote sump there are several disadvantages to a remote sump however. Firstly, additional space is required to accommodate it, which is generally expensive. Secondly, more powerful pumps are required to account for the additional static height through which the water must be pumped. Thirdly, the overall number of components required and the cost of installation is also increased. Together these factors can more than outweigh any cost saving in being able to operate the system more efficiently with respect to water consumption and spray pump energy. It may be however that a remote sump is necessary to allow dry operation and prevent over- cooling in some circumstances.
- the present invention provides a closed circuit evaporative heat exchanger comprising an air distribution plenum, means for spraying water into said plenum and a collection surface for collecting unevaporated water sprayed into said plenum, such that said water is arranged to drain into a sump within said plenum, substantially without remaining on the collection surface.
- a sump is still provided within the main air distribution plenum, but the sump is not used to collect the unevaporated water but instead a collection surface drains into the sump.
- the sump may be at least partially thermally isolated from the main part of the plenum. This makes it possible to prevent the water therein from freezing when ambient air temperatures are below freezing point, whereas this is not viable with the conventional sump arrangement which is exposed to the airflow in the plenum.
- Such arrangements have the advantage of substantial flexibility in that they are able to be swapped between wet and dry operation rapidly and as often as required, but without the disadvantages of providing a remotely located sump.
- the sump is arranged such that water therein is prevented from freezing during cold weather operation. This can be achieved by ensuring a sufficient degree of thermal isolation and providing heating means, preferably thermostatically controlled. This allows varying environmental temperatures to be accounted for as well.
- the collection surface could simply be arranged to drain into the sump below it - i.e. the arrangement could effectively be similar to a conventional one but with a lid or the like covering the sump and including a drain hole or holes. In this case the upper surface of the lid would form the collection surface.
- the drain interface between the collection surface and the sump is arranged to form a liquid lock between the two so that an uneven air pressure may be maintained between them.
- the benefit of this feature is that the sump may then be maintained at substantially atmospheric pressure, whilst the main part of the plenum is at an elevated pressure resulting from the forced airflow.
- the physical isolation of the interior of the sump from the interior of the main air distribution plenum also avoids contact with the water sprays .
- the amount of water used in the spray cycling system via the sump may, as in the prior art, be of a volume similar to that associated with a sump used in an open tower cooling system.
- the Applicants have appreciated that since, in accordance with invention, a new form of sump is contemplated, the minor benefit of commonality between sump modules is forfeited, but that this means that volume restriction imposed by using a common sump need no longer apply and that in fact additional benefit may be achieved by using less water.
- the evaporative water spray system is arranged to operate with just sufficient water for wet operation. In one exemplary embodiment the system operates with approximately 90 litres of water per square metre of coil area. This contrasts with a conventional system in which a volume of approximately 240 L/m 2 is used (which is consistent with use of a standard sized sump) .
- the preferred embodiment of the invention set out above is understood to involve using the minimum water volume needed for the evaporation process .
- this minimum quantity is dependent upon the capacity of the water distribution system including pipework, the proportion of the water which is falling through the air distribution plenum at any one time and the minimum quantity of water required by the pumping system to operate properly. This is to be contrasted with the prior art in which significantly larger volumes than the minimum for wet operation are used and indeed in which consideration has not previously been given to this minimum required quantity.
- Figure 1 is a cut-away view of a conventional closed circuit evaporative heat exchanger shown for the purposes of reference only;
- Figures 2a and 2b are cut-away side and end views respectively of a closed circuit evaporative heat exchanger in accordance with the invention.
- FIG. 1 a prior art closed circuit evaporative heat exchanger may be seen.
- a sealed heat exchanger coil A through which coolant liquid passes is provided in an air distribution plenum B.
- a fan system C driven by a motor D is provided at one end of the plenum B.
- At the top of plenum B is a series of nozzles E which are arranged to spray water over the heat exchanger coil A.
- a sump F is provided at the bottom of the plenum B with a capacity of 240 litres per square metre of coil area and a pump G is provided to pump water up from the sump F to the spray nozzles E.
- a water replenishment system H using a float valve ensures that a minimum quantity of water in the sump is maintained.
- coolant liquid or refrigerant vapour is fed to the heat exchanger coil A where heat is extracted from it to cool or condense it before it is returned, as is well known in the art.
- the fan C forces a rapid flow of air over the heat exchanger coil A in the air distribution plenum B to extracting heat from the coolant fluid or vapour.
- Evaporative cooling is provided by the water spray system which draws water from the sump F using the pump G. Some of the water sprayed from the nozzles E will evaporate. The remainder of the water is collected in the sump F from where it is recycled back up to the spray nozzles E. Water lost through evaporation is replaced by the water replenishment system H.
- the closed circuit evaporative heat exchanger comprises a heat exchanger coil 2 disposed in an air distribution plenum 4 and conveying a coolant fluid or refrigerant to and from an area to be cooled (not shown) via pipe couplings 6.
- a fan 8 driven by a motor 10 via a belt 12.
- the blades of the fan 8 are housed within a casing 14 and thus are not visible in Figure 2a.
- the sump 16 is defined in the lower part of one end of the air distribution plenum 4 by a sloping baffle wall 18.
- the sump has a capacity of ninety litres per square metre of coil area, but this is purely exemplary and this figure is - dependent e.g. upon the coil length.
- the baffle wall 18 depends downwardly from the rear end wall 20 of the plenum 4. It terminates so as to leave a gap between its end and the base of the sump 16.
- the baffle wall 18 extends between the two opposed side walls of the plenum 4 - in other words perpendicular to the plane of Fig. 2a or left to right in Fig. 2b.
- the area of the lower part of the air distribution plenum 4 not taken up by the sump 16 is formed as a sloping base 22.
- the base 22 slopes towards the baffle wall 18, but stops just short of its so as to leave a small gap 24 running from one side wall of the plenum 4 to the other.
- the base also extends between the two side walls so that the gap 24 runs along the width of the plenum 4.
- the baffle wall 18 and the base 22 each form collection surfaces onto which water falling from the heat exchanger coils 2 will land.
- a loat-operated valve 26 connected to an inlet spout 28 for maintaining a minimum level of water in the sump 16.
- This level of water is set to be the minimum amount required for wet operation of the heat exchanger (taking into account the capacity of the pipes etc. in the rest of the system) .
- a strainer 30 through which water from the sump may be drawn by a pump 32 and pumped up a vertical pipe 34 on the outside of the rear end 20 of the plenum, where it re-enters the plenum 4 to feed a water distribution pipe 36.
- a series of nozzles 38 is spaced along the water distribution pipe 36 so that water is forced out in a conical spray over the heat exchanger coils 2 under the pressure imparted by the pump 32.
- One such nozzle 38 may be seen more clearly in the scrap detail view above it.
- Above the water distribution pipe 36 is a series of drift eliminators 40, one of which is also shown more clearly in a scrap detail view.
- a pair of access doors 42 are provided in the lower part of the end wall 20 of the plenum to allow external access to the interior of the sump 16. Operation of the apparatus will now be described. As in the prior art system the fan 8 forces air to flow over the heat exchanger coils 2 to extract heat from the coolant fluid therein. When additional cooling is required the pump 32 is operated to draw water from the sump 16 through the strainer 30 and force it through the nozzles 38 so as to form a fine spray over the heat exchanger coils. A significant cooling effect is achieved by evaporation of some of the water. The unevaporated water falls down towards the bottom of the air distribution plenum 4 and onto the collection surfaces formed by either the baffle wall 18 or the sloping base 22.
- the pump 32 is shut off and the remaining water drains through the gap 24 into the sump 16.
- the water is no longer in direct contact with the air stream generated by the fan 12. It will be appreciated therefore that since no water remains in the main part of the air distribution plenum 4, i.e. in contact with the cold air flow, the likelihood of it being frozen is significantly reduced.
- thermostatically controlled heaters are provided to maintain the temperature of the water in the sump 16 above freezing. However, since the sump 16 is relatively small compared to the distribution plenum 4, and is separated from the cold air stream by the baffle wall 18, the power required for such heaters is relatively low.
- the quantity of water in the sump 16 is significantly less than in the sump F in Figure 1. Not only does this give savings on the amount of water required to fill the equipment, but also the cost of chemical treatment needed and the amount of heat required to prevent it from freezing.
- the embodiment described above gives the overall advantage that it is fully flexible in that it can be operated in either wet or dry mode as required and moreover can be switched very quickly between these modes .
- a prototype apparatus similar to that described above with reference to Figs. 2a and 2b was constructed and tested.
- the sump water volume of the test apparatus was 860 litres and the fan gave an airflow of 27 cubic metres per second over the heat exchanger coils. However, a normal atmospheric pressure was maintained in the sump interior by virtue of the water lock.
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
- Devices For Blowing Cold Air, Devices For Blowing Warm Air, And Means For Preventing Water Condensation In Air Conditioning Units (AREA)
Abstract
Description
Claims
Priority Applications (8)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE602004006719T DE602004006719T2 (en) | 2003-02-12 | 2004-02-06 | COOLING SYSTEM |
BR0407423-8A BRPI0407423A (en) | 2003-02-12 | 2004-02-06 | Closed Circuit Evaporative Heat Exchanger |
MXPA05008542A MXPA05008542A (en) | 2003-02-12 | 2004-02-06 | Cooling system. |
JP2006502245A JP4238263B2 (en) | 2003-02-12 | 2004-02-06 | Cooling system |
US10/545,240 US20060168981A1 (en) | 2003-02-12 | 2004-02-06 | Cooling system |
CA2515736A CA2515736C (en) | 2003-02-12 | 2004-02-06 | Cooling system |
AU2004211510A AU2004211510B2 (en) | 2003-02-12 | 2004-02-06 | Cooling system |
EP04708825A EP1592936B1 (en) | 2003-02-12 | 2004-02-06 | Cooling system |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
GB0303195.2 | 2003-02-12 | ||
GBGB0303195.2A GB0303195D0 (en) | 2003-02-12 | 2003-02-12 | Cooling system |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2004072569A1 true WO2004072569A1 (en) | 2004-08-26 |
Family
ID=9952888
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/GB2004/000459 WO2004072569A1 (en) | 2003-02-12 | 2004-02-06 | Cooling system |
Country Status (14)
Country | Link |
---|---|
US (1) | US20060168981A1 (en) |
EP (1) | EP1592936B1 (en) |
JP (1) | JP4238263B2 (en) |
KR (1) | KR100731834B1 (en) |
CN (1) | CN100398972C (en) |
AU (1) | AU2004211510B2 (en) |
BR (1) | BRPI0407423A (en) |
CA (1) | CA2515736C (en) |
DE (1) | DE602004006719T2 (en) |
ES (1) | ES2285424T3 (en) |
GB (1) | GB0303195D0 (en) |
MX (1) | MXPA05008542A (en) |
MY (1) | MY137660A (en) |
WO (1) | WO2004072569A1 (en) |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US9033318B2 (en) | 2009-03-03 | 2015-05-19 | Munters Corporation | Direct forced draft fluid cooler/cooling tower and liquid collector therefor |
EP3306246A1 (en) * | 2016-10-06 | 2018-04-11 | Jaeggi HybridTechnologie AG | Heat exchange device, cover and rail |
US10107001B2 (en) | 2014-03-28 | 2018-10-23 | Syntech Towers, L.L.C. | CMU cooling tower and method of construction |
US10852079B2 (en) | 2017-07-24 | 2020-12-01 | Harold D. Curtis | Apparatus for cooling liquid and collection assembly therefor |
US11609051B2 (en) | 2020-04-13 | 2023-03-21 | Harold D. Revocable Trust | Apparatus for cooling liquid and collection assembly therefor |
Families Citing this family (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US7698906B2 (en) * | 2005-12-30 | 2010-04-20 | Nexajoule, Inc. | Sub-wet bulb evaporative chiller with pre-cooling of incoming air flow |
US20080041087A1 (en) * | 2006-08-18 | 2008-02-21 | Jaeggi/Guntner (Schweiz) Ltd. | Hybrid dry cooler heat exchange with water-droplet slit and water-droplet splitting louver for heat exchangers with primarily latent heat transfer |
EP2482008B1 (en) * | 2008-01-11 | 2014-10-08 | Johnson Controls Technology Company | Evaporator |
US20110048051A1 (en) * | 2009-08-27 | 2011-03-03 | Duffy Robert D | Heating Ventilation Air Conditioner (HVAC) Compressor Efficiency Enhancement Apparatus |
US9546804B2 (en) * | 2009-12-16 | 2017-01-17 | Heatcraft Refrigeration Products Llc | Microchannel coil spray system |
KR102043173B1 (en) | 2011-09-30 | 2019-11-12 | 웅진코웨이 주식회사 | Ice-storage tank and water cooler having the same |
CN103134343B (en) * | 2011-11-25 | 2015-02-25 | 北京紫荆信达节能科技有限公司 | Heat source tower with solution capable of regeneration function |
US9207018B2 (en) | 2012-06-15 | 2015-12-08 | Nexajoule, Inc. | Sub-wet bulb evaporative chiller system with multiple integrated subunits or chillers |
CN103353243A (en) * | 2013-07-03 | 2013-10-16 | 无锡宇吉科技有限公司 | Spraying-type heat exchanger |
CN105466246B (en) * | 2015-12-31 | 2018-02-16 | 广州爱高空调设备有限公司 | Falling film type evaporation cooling coil, the method and falling-film heat exchanger for manufacturing the coil pipe |
US11761707B2 (en) * | 2020-12-23 | 2023-09-19 | Alfa Laval Corporate Ab | Evaporative wet surface air cooler |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2890864A (en) * | 1956-04-18 | 1959-06-16 | Niagara Blower Co | Heat exchanger |
US3677029A (en) * | 1970-12-03 | 1972-07-18 | Frick Co | Evaporative condenser |
US3784171A (en) * | 1968-02-16 | 1974-01-08 | Baltimore Aircoil Co Inc | Evaporative heat exchange apparatus |
US4519450A (en) * | 1983-05-04 | 1985-05-28 | Niagara Blower Company | Vacuum producing condenser |
Family Cites Families (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN2144287Y (en) * | 1992-11-24 | 1993-10-20 | 山东建筑工程学院 | Closed cooling tower |
CN2304095Y (en) * | 1997-01-15 | 1999-01-13 | 李永光 | Tightly-closed cooling tower |
US6213200B1 (en) * | 1999-03-08 | 2001-04-10 | Baltimore Aircoil Company, Inc. | Low profile heat exchange system and method with reduced water consumption |
-
2003
- 2003-02-12 GB GBGB0303195.2A patent/GB0303195D0/en not_active Ceased
-
2004
- 2004-01-29 MY MYPI20040255A patent/MY137660A/en unknown
- 2004-02-06 DE DE602004006719T patent/DE602004006719T2/en not_active Expired - Lifetime
- 2004-02-06 WO PCT/GB2004/000459 patent/WO2004072569A1/en active IP Right Grant
- 2004-02-06 KR KR1020057014990A patent/KR100731834B1/en active IP Right Grant
- 2004-02-06 JP JP2006502245A patent/JP4238263B2/en not_active Expired - Fee Related
- 2004-02-06 US US10/545,240 patent/US20060168981A1/en not_active Abandoned
- 2004-02-06 EP EP04708825A patent/EP1592936B1/en not_active Expired - Lifetime
- 2004-02-06 CA CA2515736A patent/CA2515736C/en not_active Expired - Lifetime
- 2004-02-06 ES ES04708825T patent/ES2285424T3/en not_active Expired - Lifetime
- 2004-02-06 AU AU2004211510A patent/AU2004211510B2/en not_active Ceased
- 2004-02-06 BR BR0407423-8A patent/BRPI0407423A/en not_active IP Right Cessation
- 2004-02-06 CN CNB2004800068066A patent/CN100398972C/en not_active Expired - Lifetime
- 2004-02-06 MX MXPA05008542A patent/MXPA05008542A/en active IP Right Grant
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2890864A (en) * | 1956-04-18 | 1959-06-16 | Niagara Blower Co | Heat exchanger |
US3784171A (en) * | 1968-02-16 | 1974-01-08 | Baltimore Aircoil Co Inc | Evaporative heat exchange apparatus |
US3677029A (en) * | 1970-12-03 | 1972-07-18 | Frick Co | Evaporative condenser |
US4519450A (en) * | 1983-05-04 | 1985-05-28 | Niagara Blower Company | Vacuum producing condenser |
Cited By (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US9033318B2 (en) | 2009-03-03 | 2015-05-19 | Munters Corporation | Direct forced draft fluid cooler/cooling tower and liquid collector therefor |
US9562729B2 (en) | 2009-03-03 | 2017-02-07 | Munters Corporation | Direct forced draft fluid cooler/cooling tower and liquid collector therefor |
US9644904B2 (en) | 2009-03-03 | 2017-05-09 | Syntech Towers, LLC | Direct forced draft fluid cooler/cooling tower and liquid collector therefor |
US10107001B2 (en) | 2014-03-28 | 2018-10-23 | Syntech Towers, L.L.C. | CMU cooling tower and method of construction |
EP3306246A1 (en) * | 2016-10-06 | 2018-04-11 | Jaeggi HybridTechnologie AG | Heat exchange device, cover and rail |
US10852079B2 (en) | 2017-07-24 | 2020-12-01 | Harold D. Curtis | Apparatus for cooling liquid and collection assembly therefor |
US11609051B2 (en) | 2020-04-13 | 2023-03-21 | Harold D. Revocable Trust | Apparatus for cooling liquid and collection assembly therefor |
Also Published As
Publication number | Publication date |
---|---|
EP1592936A1 (en) | 2005-11-09 |
EP1592936B1 (en) | 2007-05-30 |
KR100731834B1 (en) | 2007-06-25 |
MY137660A (en) | 2009-02-27 |
CA2515736A1 (en) | 2004-08-26 |
CN1759290A (en) | 2006-04-12 |
JP4238263B2 (en) | 2009-03-18 |
KR20050100399A (en) | 2005-10-18 |
AU2004211510B2 (en) | 2008-01-17 |
JP2006517647A (en) | 2006-07-27 |
GB0303195D0 (en) | 2003-03-19 |
DE602004006719T2 (en) | 2008-01-31 |
AU2004211510A1 (en) | 2004-08-26 |
BRPI0407423A (en) | 2006-01-24 |
US20060168981A1 (en) | 2006-08-03 |
CN100398972C (en) | 2008-07-02 |
CA2515736C (en) | 2010-07-13 |
MXPA05008542A (en) | 2005-10-20 |
DE602004006719D1 (en) | 2007-07-12 |
ES2285424T3 (en) | 2007-11-16 |
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