EP2176518A2 - Appareil de génération de puissance rotative, moteur et procédé de génération de puissance rotative - Google Patents

Appareil de génération de puissance rotative, moteur et procédé de génération de puissance rotative

Info

Publication number
EP2176518A2
EP2176518A2 EP08707957A EP08707957A EP2176518A2 EP 2176518 A2 EP2176518 A2 EP 2176518A2 EP 08707957 A EP08707957 A EP 08707957A EP 08707957 A EP08707957 A EP 08707957A EP 2176518 A2 EP2176518 A2 EP 2176518A2
Authority
EP
European Patent Office
Prior art keywords
working fluid
expander
heat
engine
heat exchanger
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.)
Granted
Application number
EP08707957A
Other languages
German (de)
English (en)
Other versions
EP2176518B1 (fr
Inventor
Anthony Osborne Dye
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.)
Epicam Ltd
Original Assignee
Epicam Ltd
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 Epicam Ltd filed Critical Epicam Ltd
Publication of EP2176518A2 publication Critical patent/EP2176518A2/fr
Application granted granted Critical
Publication of EP2176518B1 publication Critical patent/EP2176518B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G5/00—Profiting from waste heat of combustion engines, not otherwise provided for
    • F02G5/02—Profiting from waste heat of exhaust gases
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/08—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/08—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing
    • F01C1/12—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type
    • F01C1/14—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F01C1/16—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C11/00—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type
    • F01C11/006—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type of dissimilar working principle
    • F01C11/008—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type of dissimilar working principle and of complementary function, e.g. internal combustion engine with supercharger
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C2/00—Rotary-piston engines
    • F03C2/08—Rotary-piston engines of intermeshing-engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing

Definitions

  • the present invention relates to an apparatus for generating rotary power, an engine and a method of generating rotary power.
  • US-A-7, 080, 512 discloses a heat regenerative engine in the form of a two-stroke piston engine into which super- critical water substance at 1200 0 F (649°C) and 3200 psi pressure (216 bar) is delivered.
  • the water substance is used as the working fluid from which output power is generated by the crankshaft of the engine.
  • the specific volume of the water substance is approximately 19.68, i.e. its volume is approximately twenty times that of liquid water at ambient temperature.
  • the thermal efficiency of the engine is - -
  • an apparatus for generating rotary power comprising a heat exchanger arranged to receive heat from a heat source to which, in use, the apparatus is connected and to transfer heat to a working fluid at high pressure; and, an expander comprising a low friction displacement device for receiving an amount of the heated high-pressure working fluid and for retrieving energy from the working fluid by being driven by the heated expanding working fluid.
  • a low friction displacement device enables low grade energy to be retrieved and used for generating rotary power.
  • the apparatus can be used for retrieving power from the exhaust that would otherwise go to waste.
  • This energy can be returned to the engine, e.g. in the form of a direct power supplement to the engine's output shaft or for driving a supercharger for providing forced aspiration to the engine.
  • the efficiency of the engine is improved since in the absence of the apparatus this energy would otherwise be wasted.
  • an engine comprising one or more combustion chambers; and, apparatus for retrieving power from exhaust heat from the engine, the apparatus comprising a first heat exchanger arranged to receive heated exhaust gas from the one or more combustion chambers and to transfer heat from the exhaust gas to a working fluid at high pressure; and, an expander comprising a low friction displacement device for receiving a metered amount of the heated high-pressure working fluid and for retrieving energy from the working fluid by being driven by the heated expanding working fluid.
  • apparatus for generating rotary power comprising a heat exchanger arranged to receive heat from a heat source to which, in use, the apparatus is connected and to transfer heat to a working fluid at high pressure; and, an expander comprising a displacement device for being driven by the expanding working fluid, wherein the expander has a transient chamber of variable volume operative, in use, to receive a metered amount of the heated high-pressure working fluid wherein the expansion ratio of the expander is greater than 50:1.
  • a method of generating rotary power from a heat source comprising providing a heat exchanger for transferring heat from the heat source to a working fluid at high pressure; providing the working fluid - -
  • an apparatus for retrieving power from exhaust heat from an engine comprising a heat exchanger arranged to receive heated exhaust gas from a said engine and to transfer heat from the exhaust gas to a working fluid at high pressure; and, an expander comprising a low friction displacement device for receiving a metered amount of the heated high-pressure working fluid and for retrieving energy from the working fluid by being driven by the heated expanding working fluid.
  • the engine could be any suitable type of engine. Examples include internal and external combustion engines.
  • the engine includes one or more combustion chambers and preferably the engine includes an exhaust manifold for coupling the exhaust gas away from the one or more combustion chambers.
  • the engine may be a solar engine in which the heat source for the working fluid is a solar concentrator.
  • the apparatus enables the conversion to shaft power of heat provided from a solar concentrator.
  • a lobe rotor and a recess rotor are used to define transient chambers of variable volume.
  • the expansion cycle of the device is completed in only 90° of rotation with respect to the lobe rotor. Therefore, leakage from the transient chamber can be minimised without the use of mechanical or physical seals.
  • This enables the device to operate with none of the friction normally associated with piston engines. Therefore, the efficiency of the device is significantly greater than that achievable by the engine described in US- A-7,080,512.
  • apparatus for retrieving power from exhaust heat from an engine comprising: a heat exchanger arranged to receive heated exhaust gas from a said engine and to transfer heat from the exhaust gas to a working fluid at high pressure; and, an expander comprising a displacement device for being driven by the expanding working fluid, wherein the expander has a transient chamber of variable volume operative, in use, to receive a metered amount of the heated high-pressure working fluid wherein the expansion ratio of the transient chamber of variable volume is greater than 50:1.
  • the expansion ratio is greater than or equal to 100:1. More preferably, the expansion ratio is greater than or equal to 200:1. In other examples, preferably the expansion ratio is greater than or equal to 500:1 or 1000:1.
  • a method of recovering power from the heat of exhaust gas from an engine comprising: providing a heat exchanger for transferring heat of the exhaust gas to a working fluid at high pressure; providing the working fluid at high pressure to an expander comprising a low friction displacement device; and deriving - -
  • Figures 1 to 6 show the end face of each of a recess rotor and a lobe rotor in various stages during an expansion cycle
  • Figure 7 shows a schematic representation of a shaped containment wall for use with the rotors of Figures 1 to 6;
  • Figure 8 shows an example of an end plate for use with the rotors of Figures 1 to 6;
  • Figure 9 shows a schematic representation of an engine
  • Figure 10 shows a schematic representation of an engine
  • Figure 11 shows a schematic representation of an engine . - -
  • Figure 1 is a schematic view of two rotors from an expander typically used in apparatus for generating rotary power from a heat source, e.g. apparatus for retrieving power from the heat of exhaust gas from an engine.
  • a heat source e.g. apparatus for retrieving power from the heat of exhaust gas from an engine.
  • the apparatus will be described primarily with reference to the retrieval of power from the exhaust heat from an engine such as an internal combustion engine. It will be appreciated that in fact any form of heat source cold be used and the apparatus is suitable in a general sense for generating rotary power using heat from the heat source.
  • the expander of Figure 1 would typically be arranged within an expander housing which is not shown for the purposes of explanation of the operation of the expander.
  • the housing includes side walls and end walls.
  • One of the end walls includes an injector for injecting a working fluid into the expander as it operates. This wall may be referred to as the injector end wall.
  • the rotors are shown with the injector end wall removed, the rotors being shown in a position early on in an expansion cycle, i.e. 1° (with reference to the lobe rotor) after the start position.
  • a moveable containment wall may also be included.
  • the expansion cycle begins with the rotors already in a position where the volume of the transient chamber is limited to the clearance volume only, i.e. it is effectively zero. Therefore, whatever the volume reached - -
  • the expansion ratio is very large indeed.
  • it is at least 50:1 and more preferably greater than this, e.g. 100:1 or 200:1 etc.
  • the expander device has two expansion rotors 1 and 2.
  • the first rotor 2 has six equiangularly spaced recesses and is therefore referred to herein as a recess rotor.
  • the second rotor 1 has four equiangularly spaced lobes and is referred to herein as a lobe rotor.
  • the rotors 1, 2 are mounted on respective shafts 6 and 7 which are supported in bearings fitted into the end walls (not shown) of the housing.
  • the bearings are geared having a 3:2 speed ratio.
  • the required speed ratio depends on the ratio of the number of recesses in the recess rotor to the number of lobes on the lobe rotor.
  • the ends of the rotors are precisely located so as to form a close fit with the inner surfaces of the end walls of the housing, but without physical contact, i.e. there is only a clearance volume between the mating surfaces.
  • the expander is substantially frictionless .
  • the cycle of expansion lasts for 90° of rotation of the lobe rotor 1 and 60° of rotation of the recess rotor 2.
  • the interaction between a recess and respective lobe forms a sliding near contact which leaves only clearance volume - -
  • a new transient chamber of variable volume 3 is beginning to emerge between the lobe and the recess.
  • the position of the injector tip 4 is shown at a location in the end wall immediately opposite the emerging transient chamber 3 towards the tip of the lobe.
  • the injection of a working fluid such as super-critical water substance takes place directly into the transient chamber 3. Any suitable working fluid could be used.
  • the super-critical water expands and forces the transient chamber 3 to increase in volume, thereby doing work on the rotors .
  • the work or power can be retrieved from the expander by use of an output shaft connected to the shaft of rotation of, say, the lobe rotor.
  • the transient chamber 3 enlarges progressively.
  • the increase in volume of the transient chamber is shown in stages at 3° after the start of the cycle ( Figure 2) and 10° after the start of the cycle ( Figure 3) . - -
  • the transient chamber 3 enlarges to extend within the containment wall 5 although the lobe and pocket have ceased to interact.
  • the transient chamber 3 is shown nearing its maximum volume, 85° after the start of the cycle.
  • Figure 6 shows the end point of the expansion cycle, 90° after the start, at which the transient chamber reaches its maximum possible volume .
  • the rotors function as an expander comprising a low friction displacement device.
  • the low friction displacement device is arranged to receive a metered amount of a heated high-pressure working fluid and is suitable for retrieving energy from the working fluid by being driven by the heated expanding working fluid. It is most preferred that the working fluid is super-critical water and as will be explained below, the energy for heating the water to this condition may be easily retrieved from the hot exhaust gas of a conventional engine, such as an internal combustion engine.
  • the expander being a low friction displacement device
  • the apparatus including it is a suitable and convenient apparatus for retrieving the low-grade heat from the exhaust heat produced by an internal combustion engine.
  • the apparatus can be arranged to return power to the engine directly or indirectly in the form of rotary power, e.g. via an output shaft connected to a main crank shaft of an engine to which the apparatus will be connected in use.
  • the expansion ratio is at least 50:1 which is significantly more than is obtainable using a conventional expander e.g such as that shown in US-A- 7,080,512.
  • the expansion ratio is greater than or equal to 100:1 or 200:1. More preferably an even larger expansion ratio is utilised such as greater than or equal to 500:1 or 1000:1.
  • the mass of the charge of working fluid delivered to the transient chamber at the start of the expansion cycle can be optimised for the current operating condition. This is preferably done in such a way that when the maximum volume of the transient chamber is reached at the end of the cycle, then the pressure of the working fluid is close to that of the local ambient pressure. Thus, as the expansion of the working fluid is fully resisted by the cooperating rotors, all of the pressure energy available is converted into shaft power.
  • Figure 7 shows a perspective view of a sliding containment wall 5, in which an arcuate recess 6 is shaped to communicate with the lobe rotor 1 and an arcuate recess - -
  • Axial in this sense refers to movement substantially parallel to the axes of rotation of the lobe and recess rotors.
  • the containment wall 5 may be moved in an axial direction such as to vary the maximum possible volume of the transient chamber of variable volume.
  • the expansion ratio can be controlled or the maximum possible volume of the transient chamber of variable volume can be varied to take into account a varying mass of charge. If the mass of the charge is varied or variable then by having the ability to vary the maximum possible volume of the transient chamber of variable volume it is possible to vary the expansion ratio and thereby keep it within desired limits .
  • Figure 8 is an external view of the apparatus viewed from the end wall in which the working fluid injector 4 is located between the shaft 9 of the pocket rotor and the shaft 8 of the lobe rotor.
  • the end wall has an opening suitably shaped for receiving the movable containment wall 5 and for enabling axial movement of the wall 5 so that the maximum possible volume of the transient chamber can be varied as required.
  • the expander described herein is capable of delivering power over a wide range of speeds and loads.
  • the efficiency of the engine and expander can be optimised by matching the mass of working fluid delivered into the transient chamber of the expander to the maximum possible volume that the transient chamber can have.
  • FIG 9 is a schematic representation of an internal combustion engine including an expander as described above with reference to Figures 1 to 6.
  • the apparatus may be used to recover reject heat present in the exhaust gas of the engine.
  • the engine includes a heat exchanger 13 which is used to heat water substance prior to injection into the expander.
  • a high pressure pump 14 is provided for pumping water through the heat exchanger 13 and onwards into the expander 16.
  • a second heat exchanger 17 is also provided which serves to preheat water before it is provided to the first heat exchanger 13.
  • a condenser 18 is provided for condensing steam that is exhausted from the expander 16.
  • the engine comprises a number of combustion chambers 29 from which hot exhaust gases are passed via the exhaust manifold 12 of the engine into the heat exchanger 13.
  • Water is delivered into the cool end of the heat exchanger 13 at high pressure, e.g. at at least 200 bar.
  • the water or other working fluid is provided at a pressure of at least 300 bar, or at least 400 bar or at least 500 bar.
  • the water is provided at 1000 bar pressure.
  • the water is provided via high pressure piping of small bore, by means of a high pressure pump 14. - -
  • a signal from a shaft encoder (not shown) which is preferably provided to monitor the angular position of the lobe rotor shaft 8, triggers injection of super-critical water substance directly into the very small volume of the emerging transient chamber 3.
  • the super-critical water immediately expands to the maximum extent possible within the limited volume of the transient chamber. This expansion is fully resisted by the cooperating recess and lobe rotors 2 and 1, which thereby convert the pressure exerted by the expanding super-critical water into shaft power, delivered by the output shaft extension of the lobe rotor 21.
  • the expander 16 is coupled, in this example, by direct drive on a common shaft 21 with the lobe rotor shaft of a supercharging compressor 27.
  • the supercharging compressor is preferably of a low-friction or frictionless displacement type device much like the expander described above except operating to compress a working fluid (air) instead of operating to be worked upon by an expanding hot substance.
  • This common shaft is preferably coupled to the engine crankshaft via a geared pulley drive 23 or any other suitable connection.
  • the water vapour released at ambient pressure from the transient chamber at the end of each expansion cycle is still very hot. Typically, it might be at approximately 375°C and thus it still carries a significant amount of heat. In this example, recovery of much of this heat then takes place as the water vapour in the form of dry steam passes from the expander 16 into a water/steam heat exchanger 17.
  • the heat exchanger 17 may be supplied with water, in this example, from a reservoir 20, which enters the heat exchanger at its cool end. Having gained heat from the steam, it leaves at the warm end of the heat exchanger 17, drawn by the intake end of the high pressure pump 14. Thus, the heat recovered from the steam emerging from the expander is re-cycled through the high pressure section of the exhaust heat recovery heat exchanger 13.
  • Cooling for the condenser can be obtained via a cool water supply using the cooling radiator 24 of the - -
  • cooling radiator can be provided and used if required or desired.
  • the apparatus comprising in combination the heat exchanger 13 and the expander 16 serves to provide means by which the heat of exhaust gas produced by the combustion chambers 29 of the engine may be retrieved and converted to shaft power to improve the efficiency of the engine.
  • a low-friction or frictionless expander such as that shown in and described above with reference to Figures 1 to 6, enables the low- grade heat to be recovered. In the absence of such a heat exchanger and expander, the energy of this heat and power derivable from it would merely be wasted.
  • apparatus is also provided for the recovery and recirculation via the heat exchanger 13 of heat from the cooling jacket (not shown) around the cylinders and cylinder head of the engine.
  • this heat may be delivered to a point in the heat exchanger 13 at which the temperature has already reached the working temperature of the coolant, i.e. usually about 90 0 C.
  • the proportion of the fuel energy used by a normal IC engine and which is rejected to atmosphere through the cooling radiator is typically about 8% to 10%. This compares with 30% to 40% in the case of heat rejected via the exhaust.
  • FIG 10 shows a schematic layout for an external combustion engine also utilising an expander and a heat exchanger as shown in and described above with reference to Figure 9.
  • the heat source is a fuel burner (not shown) located in the high pressure heat exchanger 13.
  • the high pressure injection, expansion, steam heat recovery and condensing processes are as indicated above with respect to the internal combustion engine. Heat may also be recovered from the condenser cooling radiator 24 and returned in the air entering the fuel burner. Similarly, further heat recovery can be made from the products of combustion exiting from the burner/high pressure heat exchanger 13 at the outlet 26.
  • FIG 11 shows a schematic layout for enabling the conversion of heat provided by a solar concentrator to shaft power.
  • Heat is delivered directed from the solar concentrator (not shown) into the body of the high pressure heat exchanger 13.
  • the heat exchanger may be of solid construction made from good conducting metal or contained liquid. Heat radiated onto the surface of the heat exchanger 13 is thus conducted directly to the water for subsequent injection into the expander 16, as before.
  • any suitable means may be utilised for providing heat to the heat exchanger 13 to enable the heat to be converted into shaft power.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)

Abstract

L'invention concerne un appareil et un procédé de génération d'énergie rotative, l'appareil comprenant un échangeur de chaleur conçu pour recevoir la chaleur d'une source de chaleur à laquelle, lors de l'utilisation, l'appareil est relié et pour transférer la chaleur à un fluide de travail à haute pression; et, un dispositif de dilatation comprenant un dispositif de déplacement à faible frottement destiné à recevoir une quantité mesurée du fluide de travail à haute pression chauffé et à récupérer l'énergie du fluide de travail entraîné par le fluide de travail dilaté, chauffé.
EP08707957.0A 2007-02-08 2008-01-17 Appareil de génération de puissance rotative, moteur et procédé de génération de puissance rotative Active EP2176518B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GB0702466A GB2446457A (en) 2007-02-08 2007-02-08 Rotary power generation
PCT/EP2008/050510 WO2008095756A2 (fr) 2007-02-08 2008-01-17 Appareil de génération de puissance rotative, moteur et procédé de génération de puissance rotative

Publications (2)

Publication Number Publication Date
EP2176518A2 true EP2176518A2 (fr) 2010-04-21
EP2176518B1 EP2176518B1 (fr) 2020-06-24

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP08707957.0A Active EP2176518B1 (fr) 2007-02-08 2008-01-17 Appareil de génération de puissance rotative, moteur et procédé de génération de puissance rotative

Country Status (3)

Country Link
EP (1) EP2176518B1 (fr)
GB (1) GB2446457A (fr)
WO (1) WO2008095756A2 (fr)

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Publication number Priority date Publication date Assignee Title
US7942000B2 (en) * 2007-09-25 2011-05-17 Engine-Uity Limited Rotary vane engine system
DE102010001118B4 (de) * 2010-01-22 2021-05-12 Robert Bosch Gmbh Verfahren zum Betreiben einer Brennkraftmaschine mit einer Dampfkraftanlage
US9004156B2 (en) 2011-03-22 2015-04-14 Schlumberger Technology Corporation Flow activated sensor assembly
CN106593797A (zh) * 2016-10-20 2017-04-26 兰州理工大学 车用余热回收的热力循环系统

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JPS6176710A (ja) * 1984-09-25 1986-04-19 Hisaka Works Ltd 排熱回収装置
US5195881A (en) * 1991-04-09 1993-03-23 George Jr Leslie C Screw-type compressor/expander with valves at each axial end of rotors
GB2309748B (en) * 1996-01-31 1999-08-04 Univ City Deriving mechanical power by expanding a liquid to its vapour
BR0009245A (pt) * 1999-03-05 2001-11-20 Honda Motor Co Ltd Máquina de fluido do tipo rotativo, máquina defluido do tipo palheta e dispositivo derecuperação de calor residual para motor decombustão interna
US20040020206A1 (en) * 2001-05-07 2004-02-05 Sullivan Timothy J. Heat energy utilization system
JP2003097205A (ja) * 2001-09-21 2003-04-03 Honda Motor Co Ltd 回転流体機械
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GB0511864D0 (en) * 2005-06-10 2005-07-20 Univ City Expander lubrication in vapour power systems
CA2610762C (fr) * 2005-06-10 2015-02-10 City University Lubrifiant d'expansion dans de systemes a vapeur
JP4779513B2 (ja) * 2005-08-31 2011-09-28 いすゞ自動車株式会社 回転式容積型蒸気エンジン

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Also Published As

Publication number Publication date
WO2008095756A2 (fr) 2008-08-14
WO2008095756A3 (fr) 2009-04-09
GB2446457A (en) 2008-08-13
GB0702466D0 (en) 2007-03-21
EP2176518B1 (fr) 2020-06-24

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