EP2080960A2 - Appareil de production rapide de liquide chaud - Google Patents

Appareil de production rapide de liquide chaud Download PDF

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Publication number
EP2080960A2
EP2080960A2 EP09150883A EP09150883A EP2080960A2 EP 2080960 A2 EP2080960 A2 EP 2080960A2 EP 09150883 A EP09150883 A EP 09150883A EP 09150883 A EP09150883 A EP 09150883A EP 2080960 A2 EP2080960 A2 EP 2080960A2
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EP
European Patent Office
Prior art keywords
exchanger
combustion chamber
chamber
temperature exchanger
burner
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP09150883A
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German (de)
English (en)
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EP2080960A3 (fr
EP2080960A9 (fr
Inventor
Luciano Santi
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Individual
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Individual
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Filing date
Publication date
Application filed by Individual filed Critical Individual
Publication of EP2080960A2 publication Critical patent/EP2080960A2/fr
Publication of EP2080960A9 publication Critical patent/EP2080960A9/fr
Publication of EP2080960A3 publication Critical patent/EP2080960A3/fr
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H1/00—Water heaters, e.g. boilers, continuous-flow heaters or water-storage heaters
    • F24H1/10—Continuous-flow heaters, i.e. heaters in which heat is generated only while the water is flowing, e.g. with direct contact of the water with the heating medium
    • F24H1/12—Continuous-flow heaters, i.e. heaters in which heat is generated only while the water is flowing, e.g. with direct contact of the water with the heating medium in which the water is kept separate from the heating medium
    • F24H1/14—Continuous-flow heaters, i.e. heaters in which heat is generated only while the water is flowing, e.g. with direct contact of the water with the heating medium in which the water is kept separate from the heating medium by tubes, e.g. bent in serpentine form
    • F24H1/16—Continuous-flow heaters, i.e. heaters in which heat is generated only while the water is flowing, e.g. with direct contact of the water with the heating medium in which the water is kept separate from the heating medium by tubes, e.g. bent in serpentine form helically or spirally coiled
    • F24H1/165—Continuous-flow heaters, i.e. heaters in which heat is generated only while the water is flowing, e.g. with direct contact of the water with the heating medium in which the water is kept separate from the heating medium by tubes, e.g. bent in serpentine form helically or spirally coiled using fluid fuel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H1/00—Water heaters, e.g. boilers, continuous-flow heaters or water-storage heaters
    • F24H1/22—Water heaters other than continuous-flow or water-storage heaters, e.g. water heaters for central heating
    • F24H1/24—Water heaters other than continuous-flow or water-storage heaters, e.g. water heaters for central heating with water mantle surrounding the combustion chamber or chambers
    • F24H1/26—Water heaters other than continuous-flow or water-storage heaters, e.g. water heaters for central heating with water mantle surrounding the combustion chamber or chambers the water mantle forming an integral body
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H1/00—Water heaters, e.g. boilers, continuous-flow heaters or water-storage heaters
    • F24H1/22—Water heaters other than continuous-flow or water-storage heaters, e.g. water heaters for central heating
    • F24H1/40—Water heaters other than continuous-flow or water-storage heaters, e.g. water heaters for central heating with water tube or tubes
    • F24H1/43—Water heaters other than continuous-flow or water-storage heaters, e.g. water heaters for central heating with water tube or tubes helically or spirally coiled
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H1/00—Water heaters, e.g. boilers, continuous-flow heaters or water-storage heaters
    • F24H1/22—Water heaters other than continuous-flow or water-storage heaters, e.g. water heaters for central heating
    • F24H1/44—Water heaters other than continuous-flow or water-storage heaters, e.g. water heaters for central heating with combinations of two or more of the types covered by groups F24H1/24 - F24H1/40 , e.g. boilers having a combination of features covered by F24H1/24 - F24H1/40

Definitions

  • the present invention concerns apparatus for quick production of a hot liquid according to the preamble of the main claim.
  • the apparatus in question is intended to be advantageously used for the quick production of a hot liquid to be used for industrial applications or for sanitary and heating purposes both in residential and industrial environments.
  • the apparatus according to the invention is preferably intended to be used in cases where there can be various needs for instantaneous production of a hot liquid such as water, such as for example the need for heating water at a high pressure and high temperature for industrial applications or for needs regarding heating water at low pressure for sanitary and heating purposes.
  • a hot liquid such as water
  • the main industrial application of the apparatus according to the invention is related to instant production of a high pressure hot liquid for independent or single high-pressure water jet machines useable for washing in garages, slaughter houses etc
  • Patent EP 1398577 describes an apparatus for producing high pressure hot water for high-pressure water jet machines, which employs a boiler provided with a gas burner inserted into a combustion chamber, delimited at the upper part by a vat for preheating hot water subjected to atmospheric pressure. Derived from the abovementioned vat is a supply pipe which - by means of a pump - delivers water to a tubular exchanger which develops with a double winding in form of a cylinder, arranged inside the combustion chamber, and connected to the pipe jet to obtain a hot water jet.
  • the fumes exhaust port is arranged adjacent to the gas burner at the same side of the boiler.
  • the apparatus described in this patent is not particularly versatile in that it does not allow employing hot water produced for applications different from the high-pressure water jet machines for which it had been designed.
  • Patent WO 98/07530 describes an apparatus for producing high pressure hot water for high-pressure water jet machines similar to the one mentioned above and described in patent EP 1398577 , in which, in order to optimise heat transfer, the exchanger is obtained by means of a pipe which is wound in a helical manner forming a cylinder whose height is comprised between 3 and 7 times the internal diameter.
  • Patent DE 10041154 describes an apparatus for producing high pressure hot water for high-pressure water jet machines wherein the combustion chamber is partially surrounded by a jacket for preheating water which is then conveyed by means of a pump to the tubular exchanger.
  • patent DE 9310430 describes an analogous apparatus in which the external jacket of the combustion chamber is employed for preheating air.
  • Patent FR 2542854 regards an apparatus for producing high pressure hot water for industrial cleaning.
  • the exchanger is made up of a wound pipe 3 with two helixes, inserted in a combustion chamber having an external wall with a cavity defining a jacket for preheating water connected to a low-pressure recirculation system with an atmospheric pressure accumulation vat and to a high pressure circuit intercepted by a pump adapted to supply the tubular exchanger with high pressure preheated water.
  • the exchanger described in patent US 3,051,146 is provided with a tubular exchanger made up of three coaxial cylindrical tubular windings which defines a path for the fumes with exit of gases cooled by the specific part of the burner.
  • the essential object of the present finding is that of overcoming the drawbacks revealed by the solutions of the known type, by providing an apparatus for quick production of a hot liquid which allows meeting the various heating needs in an efficient and versatile manner.
  • Another object of the present finding is that of providing an apparatus for quick production of a hot liquid capable of exploiting the fumes pressure generated by a gas burner in the exchanger performance to the maximum.
  • Another object of the present finding is that of providing an apparatus for quick production of a hot liquid operatively entirely safe and operatively entirely reliable.
  • the apparatus 1 is adapted to be mainly used for instantaneous production of hot water or any other hot liquid, at high pressure in particular for the operation of high-pressure water jet machines in independent or centralised systems, both fixed and moveable, for example for cleaning garages, slaughter houses or more generally in the food industry, or anywhere a high pressure hot liquid is instantaneously required.
  • the apparatus 1 according to the present invention allows differentiating the operation selectively providing high and low pressure hot water for the specific required use.
  • the apparatus 1 is provided with a metal bearing structure 2, intended to be laid against the ground or bracketed and hanged on a wall, and comprising at least one front wall 3 bearing a burner 4 fixed and a bottom wall 5, removable, made on which is the fumes exhaust port 6.
  • the apparatus 1 comprises a substantially cylindrical combustion chamber 7 with a longitudinal development axis preferably horizontal, which is held by the bearing structure 2, and it is operatively connected to the gas burner 4 which is partially extended with a torch 4' thereof for a section into the combustion chamber 7 starting from the front wall 3.
  • the high temperature exchanger 9 is directly heated by means of radiation by the flame of the burner 4 while the low temperature exchanger 8 is touched by the fumes coming from the burner 4 and intended to be evacuated through the exhaust port 6.
  • the low temperature exchanger 8 is advantageously made up of several chambers arranged in series and in particular it comprises an annular cylindrical chamber 8', arranged outside the combustion chamber 7, and delimited by two coaxial cylindrical walls, one being internal 10 and the other external 11.
  • the low temperature exchanger 8 is used for preheating the required water flow.
  • Such flow generally supplies the exchanger 8 by means of a first inlet connection 12 coming from a water supply circuit (for example from the water pipeline) at a temperature generally comprised between 10 and 15°C and it exits from the exchanger through a first outlet connection 13 generally at a temperature comprised between 20 and 30°C.
  • the high temperature exchanger 9 indicated above is in turn obtained by means of a pipe which develops with a spiral winding coaxially inside the annular cylindrical chamber 8' of the first low temperature exchanger 8 and coaxially outside with respect to the torch 4' of the burner 4.
  • the tubular winding of the high temperature burner 9 laterally delimits the combustion chamber 7 given that the two ends 14, 15 are closed by other chambers of the low temperature exchanger 8 as explained in detail hereinafter.
  • the abovementioned high temperature exchanger 9 is supplied at the second connection 17 thereof with the preheated water coming from the low temperature exchanger 8 by means of at least one connection circuit 16, and in turn supplying by means of a second outlet connection 8 a system (or application) operating at high pressure 19 or low pressure 20, selected depending on the operative mode provided for according to the clarifications outlined hereinafter.
  • connection circuit 16 is provided with at least one first three-way valve 21 susceptible to communicate the first outlet connection 13 of the low temperature exchanger 8 with the second inlet connection 17 of the high temperature exchanger 9 selectively by means of a low pressure pump 22 or by means of a high pressure pump 23.
  • the second outlet connection 18 of the high temperature exchanger 9 is thus in turn connected by means of a second three-way valve 24 to a system or application operating at high pressure 19, such as for example a high-pressure water jet system, or at low pressure 20 for other usages of the hot fluid.
  • the two three-way valves 21 and 24, are controlled by a logic control unit, not illustrated in detail in the attached figures, in a constrained manner so that the low pressure pump 22 and the high pressure pump 23 convey low and high pressure hot water respectively only to the related systems 19 and 20 operating at low and high pressure.
  • three-way valves shall hereinafter include equivalent hydraulic solutions for selectively directing a flow towards various directions.
  • the previously mentioned gas burner 4 is of the modulating type with pre-mixture of air and methane gas, or lpg or biogas.
  • the burner 4 is provided with a pre-mixing chamber intended to generate a stoichiometric mixture of the fuel gas flow rate and of the oxidising air flow rate, and with a rotor intended to introduce - under pressure - the mixture thus obtained into the combustion chamber 7 so that the torch 4' triggers the combustion thereof generating a flow of hot fumes under pressure.
  • the pressure of the hot fumes must be sufficient to overcome the counterpressure in the combustion chamber 7 due to the particular configuration of the high temperature exchanger 9 which provides for the double inversion of the direction of the fumes to allow them to exit from the opposite part with respect to the burner 4 after having transferred their heating value to the two exchangers 8 and 9.
  • the exit of the fumes shall occur within the range of 60-80°C allowing condensation thereof to recover latent heat and optimise the efficiency.
  • the burner 4 has a maximum heat supply of 83 kW, at which it must overcome an internal counterpressure of the combustion circuit amounting to about 460 Pa to which further 40 Pa are to be added, for a total of 500 Pa, that the burner 4 must produce at that power to overcome the head loss of a fumes exhaust port 6 having a length of 10 m and a diameter of 100 mm.
  • the attached diagrams 1 and 2 indicate the characteristic curves of a preferred example of a rotor for the burner 4 of the apparatus 1 subject of the present invention.
  • the introduction pressure of the mixture shall be comprised between 400 and 600 Pa with a maximum thermal power comprised between 65 and 100 kW and preferably around 500 Pa with a maximum power of 83 kW.
  • the thermal power provided by the burner 4 is constantly modulable during the operation of the apparatus 1 to substantially maintain the temperature preset by the user constant. More clearly, the logic control unit of the apparatus selectively receives temperature signals from at least one first and at least one second temperature detection probe, one respectively associated to a system operating at high pressure and the other to a system operating at low pressure. The temperature signal detected by a probe on any of the two sides determines two different thermodynamic controls by the control unit of the burner 4. In any case, the burner is capable of accurately reproducing the thermal power required to meet the required temperature and water flow rate needs by modulating the introduced air-flow rate to which the corresponding amount of gas that is pre-mixed and introduced into the combustion chamber 7 is related in a suitably calibratable manner.
  • the apparatus 1 is dimensioned for the production of a hot water flow-rate (or of any other hot liquid) variable between 3 and 350 litres per minute at a pressure comprised between 1 and 200 bars. More in particular, in case the apparatus 1 is used for producing the hot fluid at low pressure, the production of hot fluid typically under pressure comprised in the range between 1-2.5 bars (for example for use in sanitary or heating systems) shall preferably be provided for.
  • the high temperature exchanger 9 is formed by two coaxial tubular windings, one being internal 9' and the other external 9", spaced from each other by a first cavity 25.
  • the two windings develop in a substantially longitudinal direction from the first end 14 of the combustion chamber 7 having the burner 4 associated mounted on the front wall 3, to the second end 15 of the combustion chamber 7 having the fumes evacuation port 6 associated.
  • the path of the fumes produced by the burner 4 provides for that the fumes first touch the inner face of the internal winding 9' up to the second end 15 of the combustion chamber 7 at which they are conveyed by a closure plate 26 to perform a first inversion and return longitudinally into the abovementioned first cavity 25 touching the two windings 9' and 9".
  • the fumes pass through the widened turns of the pipe forming the internal winding 9' of the high temperature exchanger 9 and which is connected without interruption with the pipe forming the external winding 9".
  • the fumes are conveyed by a second closure plate 27 to perform a second inversion and to be inserted into a second cavity 28 which remains defined between the external face of the second winding 9" and the internal wall 10 of the annular chamber 8' of the low temperature exchanger 8.
  • a sealing bulkhead 50 adapted to prevent the fumes from passing directly into the second cavity 28 towards the exit.
  • the fumes are conveyed to exit from the fumes evacuation port 6 which is advantageously arranged in a coaxial and centred position with respect to the combustion chamber 7.
  • the low temperature exchanger 8 is made up of several chambers connected to each other forming a complete coating around the combustion chamber isolating it completely from the external environment and allowing a high heat recovery. Furthermore, the arrangement of such chambers, as explained hereinafter, serves to allow the extraction of the high temperature exchanger 9 to allow easy maintenance thereof.
  • the internal and external cylindrical walls 10, 11 of the annular cylindrical chamber 8' of the low temperature exchanger are connected to at least two septa 29 used for separating the annular chamber 8' in at least two sections connected to each other at the first end 14 of the combustion chamber 7 by means of a connection chamber 8" arranged close to the burner 4 and substantially delimited by the first closure plate 27 and by the front wall 3.
  • the low temperature exchanger 8 further comprises a bottom chamber 8"' fixed by welding at the head of the high temperature exchanger 9 at the second end 15 of the combustion chamber 7.
  • the abovementioned bottom chamber 8''' has a diametric overall dimension substantially equivalent to that of the second winding 9" of the high temperature exchanger 9, and it is defined between the first closure plate 26 and a further third closure plate 31 spaced from the first and made on which is the first outlet connection 13.
  • the low pressure pump 22 may be fixed on the third plate 31 (see figure 2 ) or advantageously to the support structure 2 adjacent to the annular chamber 8' (see figure 2' ).
  • the first three-way valve 21 communicates the first outlet connection 13 of the low temperature exchanger 8 to the high temperature exchanger 9 by means of the low pressure pump 22 or by means of the high pressure pump 23 arranged downstream of the valve 21.
  • the first three-way valve 21 is connected at the outlet with a branch, to the low pressure pump 22, and with the other branch to the high pressure pump 23 preferably arranged outside the apparatus and being part of a pumping group available separately.
  • such bottom chamber 8''' receives water through a suitable connection 30 from the annular chamber 8' and it sends it to said connection circuit 16 through the first outlet connection 13. Therefore, the water enters the first section of the annular chamber 8' of the first low temperature exchanger 8 and reaches the connection chamber 8" to invert its progress in the second section of the annular chamber 8'. At this point, through the connection 30, it passes into the bottom chamber 8'" integral with the high temperature exchanger 9, from which it exits definitely preheated through the connection 13 to be selectively directed through the first three-way valve 21 to the low pressure pump 22 or to the high pressure pump 23 and hence reach the two windings in series 9' and 9" of the high temperature exchanger 9.
  • the hot water is selectively conveyed through the second three-way valve 24 to a high 19 or low 20 pressure system for the desired applications, of the type already mentioned previously.
  • the hydraulic circuit of the low temperature exchanger 8 defined in the two sections of the annular chamber 8' is intercepted by an expansion vessel 40, while connected at the bottom chamber 8'" is a safety valve 41 provided in case of overpressures.
  • the internal winding 9' of the high temperature exchanger 9 has at least one end portion 60 (see figure 3' ) at the second end 15 of the combustion chamber 7, which is narrowed in particular with a conical shape to convey the hot fumes which progress longitudinally in the combustion chamber 7 towards the bottom chamber 8'" facilitating the inversion towards la the connection chamber 8".
  • the high pressure exchanger 9 is slidingly extractable from the second end 15 of the combustion chamber 7 upon removal of the preset removable fixing means 31, the bottom wall 5 and the connection between 30 the bottom chamber 8'" and the annular chamber 8'.
  • the abovementioned removable fixing means 31 are advantageously of the screw/female-screw type and they provide for that the ends of the inlet and outlet connections 17 and 18 of the pipe forming the windings 9', 9" of the high pressure exchanger 9 be threaded and projecting from through holes obtained in the front wall 3 to be engaged by counter-threaded bolts thus positioned in such manner to block the high pressure exchanger 9 inside the combustion chamber 7.
  • bottom wall 5 may be easily removed by unscrewing stop screws 32 which engage it in a removable manner against the support structure 2.
  • the finding thus conceived attains the preset objects.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Feeding And Controlling Fuel (AREA)
EP09150883A 2008-01-18 2009-01-19 Appareil de production rapide de liquide chaud Withdrawn EP2080960A3 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
ITPD20080017 ITPD20080017A1 (it) 2008-01-18 2008-01-18 Apparecchiatura per la rapida produzione di un liquido caldo

Publications (3)

Publication Number Publication Date
EP2080960A2 true EP2080960A2 (fr) 2009-07-22
EP2080960A9 EP2080960A9 (fr) 2009-10-14
EP2080960A3 EP2080960A3 (fr) 2012-01-11

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Family Applications (1)

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EP09150883A Withdrawn EP2080960A3 (fr) 2008-01-18 2009-01-19 Appareil de production rapide de liquide chaud

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EP (1) EP2080960A3 (fr)
IT (1) ITPD20080017A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2016160711A1 (fr) * 2015-03-27 2016-10-06 Gas Technology Institute Chauffe-eau à la demande à haute pression et à haute température

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3051146A (en) 1955-02-18 1962-08-28 Vapor Heating Corp Water tube boiler or steam generator
US3785363A (en) 1972-04-07 1974-01-15 J Machado Cleaning apparatus for automobiles with indirect heat exchange for heating the cleaning fluid
EP0027055A1 (fr) 1979-10-09 1981-04-15 Stelrad Group Limited Chauffe-eau
FR2542854A1 (fr) 1983-03-18 1984-09-21 Dieppedalle Francois Appareil de production instantanee d'eau chaude a haute pression
DE9310430U1 (de) 1993-07-13 1993-09-09 Alfred Kärcher GmbH & Co., 71364 Winnenden Brenner für einen Durchlauferhitzer insbesondere für Hochdruckreinigungsgeräte
WO1998007530A1 (fr) 1996-08-22 1998-02-26 Alfred Kärcher GmbH & Co. Appareil de nettoyage haute pression
DE10041154A1 (de) 2000-08-21 2002-03-14 Kups Umwelttechnik Gmbh & Co K Hochdruckreinigungsgerät
EP1398577A1 (fr) 2002-09-10 2004-03-17 Alfred Kärcher GmbH & Co. KG Nettoyeur à haute pression

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH84212A (de) * 1919-06-18 1920-02-16 Josef Mueller Flüssigkeitserhitzer
US1773806A (en) * 1929-05-15 1930-08-26 Ernest A Conaway Heater
FR1461061A (fr) * 1965-02-05 1966-12-10 Electricite Et Electromecaniqu Chaudière de chauffage d'un liquide, en particulier d'une huile, destiné au transport de chaleur
IE802479L (en) * 1980-11-28 1982-05-28 Helot And Co Ltd Water heating apparatus suitable for use as domestic central¹heating boiler

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3051146A (en) 1955-02-18 1962-08-28 Vapor Heating Corp Water tube boiler or steam generator
US3785363A (en) 1972-04-07 1974-01-15 J Machado Cleaning apparatus for automobiles with indirect heat exchange for heating the cleaning fluid
EP0027055A1 (fr) 1979-10-09 1981-04-15 Stelrad Group Limited Chauffe-eau
FR2542854A1 (fr) 1983-03-18 1984-09-21 Dieppedalle Francois Appareil de production instantanee d'eau chaude a haute pression
DE9310430U1 (de) 1993-07-13 1993-09-09 Alfred Kärcher GmbH & Co., 71364 Winnenden Brenner für einen Durchlauferhitzer insbesondere für Hochdruckreinigungsgeräte
WO1998007530A1 (fr) 1996-08-22 1998-02-26 Alfred Kärcher GmbH & Co. Appareil de nettoyage haute pression
DE10041154A1 (de) 2000-08-21 2002-03-14 Kups Umwelttechnik Gmbh & Co K Hochdruckreinigungsgerät
EP1398577A1 (fr) 2002-09-10 2004-03-17 Alfred Kärcher GmbH & Co. KG Nettoyeur à haute pression

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2016160711A1 (fr) * 2015-03-27 2016-10-06 Gas Technology Institute Chauffe-eau à la demande à haute pression et à haute température
US10151508B2 (en) 2015-03-27 2018-12-11 Gas Technology Institute High pressure, high temperature, on demand water heater

Also Published As

Publication number Publication date
ITPD20080017A1 (it) 2009-07-19
EP2080960A3 (fr) 2012-01-11
EP2080960A9 (fr) 2009-10-14

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