[go: up one dir, main page]

EP2711500B1 - Moteur à pistons axiaux - Google Patents

Moteur à pistons axiaux Download PDF

Info

Publication number
EP2711500B1
EP2711500B1 EP13004435.7A EP13004435A EP2711500B1 EP 2711500 B1 EP2711500 B1 EP 2711500B1 EP 13004435 A EP13004435 A EP 13004435A EP 2711500 B1 EP2711500 B1 EP 2711500B1
Authority
EP
European Patent Office
Prior art keywords
combustion chamber
axial piston
control piston
fuel
axial
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.)
Not-in-force
Application number
EP13004435.7A
Other languages
German (de)
English (en)
Other versions
EP2711500A3 (fr
EP2711500A2 (fr
Inventor
Ulrich Rohs
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.)
GETAS Gesellschaft fuer Themodynamische Antriebssysteme mbH
Original Assignee
GETAS Gesellschaft fuer Themodynamische Antriebssysteme mbH
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 GETAS Gesellschaft fuer Themodynamische Antriebssysteme mbH filed Critical GETAS Gesellschaft fuer Themodynamische Antriebssysteme mbH
Publication of EP2711500A2 publication Critical patent/EP2711500A2/fr
Publication of EP2711500A3 publication Critical patent/EP2711500A3/fr
Application granted granted Critical
Publication of EP2711500B1 publication Critical patent/EP2711500B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

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
    • F02G3/00—Combustion-product positive-displacement engine plants
    • F02G3/02—Combustion-product positive-displacement engine plants with reciprocating-piston engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F01B3/0002—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F01B3/0005—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders having two or more sets of cylinders or pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F01B3/04—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis the piston motion being transmitted by curved surfaces
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines
    • F02B75/26—Engines with cylinder axes coaxial with, or parallel or inclined to, main-shaft axis; Engines with cylinder axes arranged substantially tangentially to a circle centred on main-shaft axis
    • 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
    • F02G2254/00—Heat inputs
    • F02G2254/10—Heat inputs by burners

Definitions

  • the invention relates to an axial piston motor with a combustion chamber.
  • the invention relates to an axial piston engine with continuous combustion, in which from a combustion chamber effluent working fluid via at least one firing channel successively at least two working cylinders is supplied.
  • Generic axial piston motors are for example in the EP 1 035 310 A2 disclosed and therefore already known from the prior art.
  • an axial piston motor may be provided with a main nozzle, a sub-nozzle and a combustion chamber, which operates with a two-stage combustion.
  • a combustion chamber is provided, which is constructed so that it can work with a two-stage combustion, existing in a fuel chemical energy can be used much more effectively on the axial piston motor according to the invention or converted into usable energy, whereby the efficiency of the axial piston motor improves is.
  • the combustion chamber has two areas, in which a fuel and / or air is injected.
  • the fuel and the air can be injected together or separately into the different areas of the combustion chamber.
  • a preferred embodiment provides that the combustion chamber has a first region in which a portion of the combustion air is introduced and in which a treatment nozzle injects a corresponding amount of fuel.
  • the treatment nozzle in which fuel is already mixed with a very small proportion of combustion air and thus processed for combustion, and the complementary supply of combustion air, the combustion process is particularly effectively initiated, whereby the combustion of the fuel can take place more effectively overall.
  • the combustion air fraction which is introduced as an additional proportion in the first region, less than 50% of the total combustion air, preferably less than 15%, in particular less than 10%, is. If the combustion air fraction is within such limits, this already makes it possible to improve the combustion of the fuel via the two-stage combustion.
  • a fuel can be injected into the combustion chamber of the axial piston motor particularly well if the axial piston engine has a main nozzle and a secondary nozzle.
  • the main nozzle therefore ensures that a substantial proportion of fuel in a certain preferred direction enters the combustion chamber of the axial piston engine, while by the auxiliary nozzle, which may be formed, for example, as a preparation nozzle, a certain amount of fuel or on a fuel-air mixture in enters the combustion chamber, which can be used for supporting purposes, such as an afterburner, a treatment or a temperature control.
  • an axial piston motor with a combustion chamber into which fuel can be injected via a main nozzle and fuel which is or is mixed with air via a treatment nozzle.
  • a virtually arbitrary fuel-air mixture can be injected into the combustion chamber, while ideally only fuel is injected by means of the main nozzle. Alone through this Allocation, the efficiency of an axial piston engine is already improved. If it is advantageous for an application, more than one treatment nozzle can be provided.
  • the aforesaid advantage also applies, in particular, independently of the use of a two-stage combustion or of a combustion chamber having two regions.
  • the fuel can be injected so particularly well into the combustion chamber that it can ignite and burn exceptionally effectively.
  • an ignited or combusted fuel-air mixture with higher kinetic energy can pass through the entire combustion chamber, further out through firing channels out of the combustion chamber and into working cylinder of the axial piston engine, especially if the fuel from the main nozzle out in the main combustion direction in the Combustion chamber is injected.
  • the fuel or the fuel-air mixture can be quickly fed to the areas of the axial piston motor, in which it should then do its job, such as the cylinders.
  • the main nozzle is aligned coaxially to an axis of symmetry of the combustion chamber, which is parallel to the main combustion direction in the combustion chamber. If the main nozzle is located centrally, ie centrally, on the axis of symmetry of the combustion chamber, a corresponding, essentially combustion takes place, so that the combustion gases can then also be taken out symmetrically from the combustion chamber for further use, even if further components are supplied by a secondary or conditioning nozzle but then they can not penetrate that much.
  • An advantageous embodiment provides that the treatment nozzle is aligned at an angle to the main nozzle. As a result, both the main nozzle and the treatment nozzle can be structurally placed and connected to the combustion chamber in a small space.
  • jet direction of the treatment nozzle intersects the jet direction of the main nozzle, whereby a fuel injected into the combustion chamber through the main nozzle and into the combustion chamber through the treatment nozzle Fuel-air mixture, for example, in the field of an antechamber of a processing chamber already swirled particularly well together and can be mixed.
  • the axial-piston engine has a treatment chamber into which both a main nozzle and a treatment nozzle are directed opens to the main combustion chamber. In this way, it is always ensured that the fuel from the main nozzle and the fuel-air mixture from the treatment nozzle can be thoroughly mixed thoroughly before they reach the second region of the combustion chamber, for example into a main combustion chamber of the combustion chamber.
  • the axial piston engine has a treatment chamber into which the exhaust gas or a fuel-air mixture is introduced from a treatment nozzle and into which fuel is injected from a main nozzle without air supply ,
  • an axial piston motor with a combustion chamber and a treatment chamber upstream of the combustion chamber can be provided, into which fuel is fed via a main nozzle, which is heated, preferably already thermally decomposed, in the processing chamber.
  • a main nozzle which is heated, preferably already thermally decomposed, in the processing chamber.
  • known axial piston motors can advantageously be developed further, since a fuel which could at least already be heated in the treatment chamber can be burned more effectively.
  • a sufficient and advantageous two-stage combustion can already be realized and permanently ensured on an axial piston engine.
  • a method for operating an axial-piston engine can accordingly be distinguished in that fuel is decomposed in a first step and then brought into contact with process air for combustion.
  • the decomposed fuel can react more effectively with the process air, so that the combustion process is correspondingly more effective.
  • the decomposition of the fuel takes place thermally.
  • a heat or heat required for this purpose can be easily generated and provided directly on the axial piston motor.
  • other decomposition process such as elktrolytician or kathalytician processes cumulatively or alternatively can be used in a corresponding processing chamber.
  • the thermal energy for the decomposition can be generated in different ways. If the thermal energy for the decomposition is provided by a treatment flame, the fuel can be thermally decomposed on the axial piston motor in a particularly simple manner and, in particular, by utilizing the technology already used anyway for the combustion of the fuel.
  • the conditioning flame is generated by means of a fuel-air mixture, then the conditioning flame can be constructively produced and provided in accordance with the design of the axial piston engine.
  • the axial-piston engine can be operated in a particularly fuel-efficient manner, since in this way Only a minimum of fuel is used for the preparation of the combustion, namely the preparatory decomposition, while the remainder of the fuel is available for the performance of the desired work. It should also be taken into account in particular that the fuel used for the treatment is ultimately just as energetically available to the process and used accordingly for the process.
  • the two-step approach ensures that the decomposition of the fuel used for work has already taken place or is well advanced until it ignites, which increases the effectiveness of the overall process.
  • a treatment nozzle opens into the processing chamber, via which the fuel can be heated in the processing chamber.
  • combustion air or a combustion air-fuel mixture is introduced into the processing chamber by means of the treatment nozzle, the can via a Main nozzle also charged in the processing chamber fuel design particularly simple in the treatment chamber heated, preferably even thermally decomposed, and the main combustion chamber are fed.
  • combustion air / fuel mixture or other gas mixture or gas passed from the treatment nozzle into the processing chamber can be metered in such a way that sufficient temperatures prevail in the processing chamber to ensure that the remaining fuel, for example a thermal decomposition, is processed ,
  • the processing chamber is aligned parallel to a main combustion direction in the combustion chamber. This leads in particular to the fact that the flow of combustion gases is uniform and can be distributed uniformly according to different cylinders.
  • the flow of combustion gases can be made uniform according to.
  • the air-fuel mixture from the Aufbreitungshunt can be particularly advantageously mixed with combustion air in the main combustion chamber when the treatment chamber has a smaller diameter than the combustion chamber.
  • the main combustion chamber should be in volume only as much larger as the treatment chamber, that an undisturbed stream from the processing chamber can be formed with complementary supply of combustion air through the main combustion chamber in the cylinder to prevent unnecessary expansion in the main combustion chamber, which in itself would lead to losses, since the work should actually be done in de cylinder.
  • the treatment chamber comprises a pre-chamber and a main chamber.
  • the main nozzle and / or the treatment nozzle can open into the prechamber of the treatment chamber, an ignition and / or pre-combustion may take place in the main chamber of the treatment chamber.
  • the mixtures introduced into the processing chamber can already be in an extraordinarily well-prepared state in the main chamber of the processing chamber.
  • Both the main nozzle and the treatment nozzle can advantageously lead to a small space in the processing chamber or in the antechamber of the processing chamber when the antechamber of the Aufbreitungshunt is conical and widens towards the main chamber.
  • the fact is taken into account that the amount of gas increases by the addition of the volume flows from the main nozzle and the treatment nozzle.
  • an advantageous further embodiment accordingly provides that the pre-chamber widens towards the main chamber.
  • the jet direction of the preparation nozzle and the jet direction of the main nozzle intersect in the prechamber. In this way, a particularly good and intimate mixing of the given by the main nozzle on the one hand and the conditioning nozzle on the other hand blended mixtures can be achieved.
  • a preferred embodiment provides that a quantity of air corresponding to the quantity of fuel introduced into the main combustion chamber through a main nozzle is introduced into the main combustion chamber behind a treatment chamber. In this way, it is ensured that a treatment process of the fuel in the processing chamber can be performed reliably without already combustion of the abandoned by the main nozzle of the main combustion chamber air.
  • the axial piston motor has a separate air supply to the combustion chamber.
  • the separate air supply can be provided in a structurally particularly simple manner if a perforated ring for an air supply has a nozzle, preferably a conditioning nozzle.
  • the air supply can however also be realized by separate channels, which open into corresponding openings or separate nozzles in a combustion chamber.
  • an axial piston motor may be provided with a combustion chamber insulated by a ceramic assembly, the ceramic assembly being air cooled. If the ceramic assembly is air-cooled, the thermal budget of the combustion chamber of the axial piston motor can be controlled much better. In this respect, thereby the life of the axial piston motor can be improved.
  • the air heated in this way can be used for combustion, whereby the efficiency, in deviation from corresponding water-cooled combustion chambers, can be further increased. It is also easier to control air cooling in the region of the combustion chamber, in particular a ceramic combustion chamber.
  • an axial piston motor with a combustion chamber can be further provided for optimized efficiency, which is isolated by a ceramic assembly, the ceramic assembly is tubular and surrounded by a tube with a profiling, preferably with a thread.
  • a profiling can achieve an increase in surface area, as a result of which cooling of the ceramic assembly can be substantially improved.
  • this can also increase the service life of the axial piston motor, since in this case the thermal budget of the axial piston motor can be improved.
  • An embodiment improved in this respect provides that the profiled tube is profiled on both sides, for simplicity on both sides is provided with a thread. This allows the profiled tube with a larger contact surface with the ceramic Combustion chamber of the axial piston motor are in contact or and possibly even screwed.
  • a thread also has the advantage that it can ensure a uniform air flow in a structurally simple manner.
  • an axial piston motor in which compressed process air for cooling, in particular for cooling a combustion chamber, is used.
  • this compressed process air can flow around the profiled tube described above and additionally cool it.
  • such a compressed process air at the axial piston motor to a sufficient extent already exist, so that it can be readily used advantageously for cooling the axial piston motor.
  • a cooling effect can be further improved if the process air is given up water. If suitable means for supplying water into a process air of the axial piston motor are provided on the axial piston motor, water can also be added to the process air in an easily metered manner.
  • the process air can be used excellently for cooling.
  • the water can cumulatively or alternatively be given up before or during the compression of the process air or of a fuel-air mixture. There then remains enough time to heat the process air enriched with water in order to maximize the efficiency of the axial piston, for which purpose in particular waste heat from the combustion process, for example from cooling processes, can be used accordingly.
  • the residual heat of the exhaust gas can be used accordingly.
  • the water is injected into a compression cylinder, whereby a uniform distribution of the water can be ensured.
  • the water can also be used advantageously in the combustion process.
  • an injection of an excessively high amount of water can be avoided, so that the risk can be reduced that the axial piston motor at a lower workload too is strongly cooled.
  • the water can also be used in the combustion process as a reagent and / or catalyst to ensure, for example, a chemical reaction of undesirable exhaust gas constituents. The amount of water required thereby corresponds advantageously to the amount of fuel converted in each case.
  • the water can also be split up thermally before it reaches the main combustion chamber. This can for example also be done in the processing chamber. On the other hand, the splitting can also take place chemically or catalytically and / or elsewhere, for example in feed channels or in the immediate vicinity of inlet openings into the combustion chamber.
  • an axial piston motor is proposed with a continuous combustion in which from a combustion chamber effluent working fluid is fed through at least one firing channel successively at least two working cylinders, wherein each working cylinder a firing channel is provided, via a Control piston can be closed and opened.
  • the control piston By means of the control piston, the shot channels between a combustion chamber and working cylinders on the one hand particularly tightly closed and on the other hand very quickly reopened, which is not possible, for example, by rotary valves or rotating shot channels, which are already known from the prior art. In this respect, this alone the efficiency of an axial piston motor can be improved.
  • Such control piston can also structurally very simple and robust seal a shot channel and release again, whereby the life of the axial piston motor can be further increased.
  • control piston can execute a substantially radially directed lifting movement in order to be able to release a firing channel again.
  • the control piston carry out a substantially radially directed lifting movement, so that axial space can be saved.
  • a control piston alternatively carries out a substantially axially directed lifting movement, that is to say a substantially axially directed lifting movement, cooling of the control piston can be realized more simply.
  • with a between axial and radial stroke, ie at an angle are selected which, however, usually leads to more complex and costlier results.
  • control piston is water-cooled, whereby overheating can be avoided particularly effectively, since the control pistons in the firing channel are exposed to particularly high temperatures.
  • control pistons can be driven hydraulically or pneumatically, so that very fast shutter speeds or sequences of movements of the pistons can be realized.
  • control piston is desmodromisch driven. In the case of a desmodromic drive, the control piston can always close a firing channel even at high speeds reliably and exceptionally tight.
  • control piston If the control piston is driven via a curved path, it can be accelerated and decelerated particularly quickly.
  • a desmodromic drive can be implemented particularly well in practice.
  • a piston cover of the control piston has a larger diameter than the closing channel, the heat load of the control piston can be reduced much more advantageously.
  • a particularly simple attachment and guidance of the control piston can be realized in particular by sliding blocks or plain bearings, whereby the control piston can be secured against rotation in a preferred embodiment at the same time.
  • An exceptionally good seal with respect to the control piston can be achieved if the control piston carries a control piston ring. If the control piston ring has a slot, the sealing function of the control piston ring can be further improved since the control piston ring can better adapt to the structural conditions, in particular to a control piston cylinder, in particular when it is pressurized.
  • control piston ring is secured against rotation, as this can be improved by the sealing function on the control piston again.
  • the Indian FIG. 1 illustrated axial piston engine 1 has a combustion chamber 2, in which a fuel-air mixture can be ignited and burned.
  • the axial piston engine 1 operates in this case with a two-stage combustion.
  • the combustion chamber 2 has a first region 3 and a second region 4, into which fuel and / or air can be injected.
  • a portion of a combustion air of the axial-piston engine 1 can be introduced, wherein in this embodiment the proportion of the combustion air can be set smaller than 15% of the total combustion air.
  • the combustion chamber 2 of the axial piston motor 1 can be divided into a treatment chamber 5 and a main combustion chamber 6.
  • the treatment chamber 5 has a smaller diameter than the main combustion chamber 6, wherein the treatment chamber 5 is additionally divided into an antechamber 7 and into a main chamber 8.
  • the antechamber 7 is conical in this case and expands towards the main chamber 8.
  • a main nozzle 9 and on the other hand a treatment nozzle 10 is connected.
  • a fuel can be introduced into the combustion chamber 2, wherein the fuel which is injected by means of the treatment nozzle 10 is already mixed with air or is.
  • the main nozzle 9 is aligned parallel to a main combustion direction 11 in the combustion chamber 2 on the axial piston motor 1.
  • the main nozzle 9 is coaxial with an axis of symmetry 12 of the combustion chamber 2, which is parallel to the main combustion direction 11 in the combustion chamber 2, aligned.
  • the treatment nozzle 10 is aligned with respect to the main nozzle 9 at an angle 13. In this respect, a jet direction 14 of the treatment nozzle 10 intersects with a jet direction 15 of the main nozzle 9 at an intersection point 16.
  • fuel from the main nozzle 9 is injected without further air supply. This is already preheated in the treatment chamber 5, ideally thermally decomposed.
  • the quantity of air corresponding to the quantity of fuel flowing through the main nozzle 9 is introduced into the main combustion chamber 6 behind a deposition chamber 5, for which purpose a separate air supply 17 is provided, which opens substantially into the main combustion chamber 6.
  • the separate air supply 17 is for this purpose connected to a process air supply 18, wherein from the first another air supply 19 can be supplied with air, which in this case supplies a hole ring 20 with air.
  • the hole ring 20 is in this case associated with the treatment nozzle 10, so that the fuel injected with the treatment nozzle 10 can additionally be injected with process air into the prechamber 7 of the treatment chamber 5.
  • the combustion chamber 2 in particular the main combustion chamber 6 of the combustion chamber 2, has a ceramic assembly 21, which is air-cooled.
  • the ceramic assembly 21 in this case has a ceramic combustion chamber wall 22, which of a profiled tube 23 is surrounded.
  • a cooling air chamber 24 which is operatively connected via a cooling air chamber supply 25 with the process air supply 18.
  • the axial piston motor 1 has known working cylinders 30 (see in particular FIG. 2 ), in which working piston 31 can be moved back and forth.
  • compressor pistons 32 of the axial-piston engine 1 are driven, which can be moved correspondingly in suitable compressor cylinders 33 of the axial-piston engine 1.
  • the working piston 31 are in each case by means of a connecting rod 34 with the compressor piston 32 in connection, between the piston 31 and the connecting rod 34 and between the compressor piston 32 and the connecting rod 34 each have a Pleuellaufrad 35 is arranged.
  • a drive cam track 36 In each case enclosed between two connecting-rod wheels 35 is a drive cam track 36, which is guided on a drive cam track carrier 37.
  • the axial piston engine 1 has a drive shaft 38, by means of which the power generated by the axial piston motor 1 can be delivered.
  • Each of the working cylinder 30 is connected via a firing channel 39 with the combustion chamber 2 of the axial piston motor 1, so that the fuel-air mixture from the combustion chamber 2 via the firing channel 39 into the working cylinder 30 and there can drive the working piston 31.
  • the effluent from the combustion chamber 2 working medium via at least one firing channel 39 successively at least two working cylinders 30 are supplied, each working cylinder 30, a firing channel 39 is provided which via a control piston 40th closed and can be opened.
  • the number of control pistons 40 of the axial piston motor 1 is predetermined by the number of working cylinders 30.
  • a closing of the firing channel 39 takes place here essentially via the control piston 40 with its piston cover 41.
  • the control piston 40 is driven by means of a control piston cam track 42, wherein a spacer 43 is provided for the control piston cam track 42 to the drive shaft 38, in particular also a thermal decoupling serves.
  • the control piston 40 can perform a substantially axially directed stroke 44.
  • Each control piston 40 is for this purpose by means not unnatural sliding blocks, which are mounted in the control piston cam track 42, guided, wherein the sliding blocks each have a safety cam which runs in an unnumbered guide groove back and forth and prevents rotation of the control piston 40.
  • control piston 40 comes into contact with the hot working medium from the combustion chamber 2 in the region of the firing channel 39, it is advantageous if the control piston 40 is water-cooled.
  • the axial piston motor 1, in particular in the region of the control piston 40, a water cooling 45, the water cooling 45 inner cooling channels 46, middle cooling channels 47 and outer cooling channels 48 includes. Cooled so well, the control piston 40 can be reliably moved in a corresponding control piston cylinder 49.
  • the shot channels 39 and the control piston 40 can be provided on the axial piston motor 1 structurally particularly simple if the axial piston motor 1 has a firing channel ring 50, as in particular in the FIG. 3 is illustrated.
  • the firing channel ring 50 in this case has a central axis 51 around which concentric around the particular parts of the working cylinder 30 and the control piston cylinder 49 of the axial piston motor 1 are arranged. Between each working cylinder 30 and control piston cylinder 49, a firing channel 39 is provided, each firing channel 39 spatially with a recess 52 (see FIG. 3 ) of a combustion chamber bottom 53 (see FIG. 1 ) of the combustion chamber 2 of the axial piston motor 1 is connected.
  • the in the FIGS. 4 and 5 exemplified alternative control piston 60 has an impeller 61 for the control piston cam 37 of the axial piston motor 1.
  • the impeller 61 is provided as well as a ball 62 formed as a rotation lock 63 on a piston cap 41 facing away from the end 64 of the control piston 60.
  • the ball 62 may advantageously serve in the present case as a longitudinal guide of the control piston 60.
  • the control piston 60 comprises a piston ring 65, which sits directly below the piston cover 41.
  • the piston ring 65 is secured to the control piston 60 by means of a piston ring lock 66. Between the piston ring 65 and the ball 62, a pressure equalization 67 is still provided for the control piston 60.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Combustion Methods Of Internal-Combustion Engines (AREA)
  • Pistons, Piston Rings, And Cylinders (AREA)
  • Hydraulic Motors (AREA)

Claims (15)

  1. Moteur à pistons axiaux (1) avec combustion continue, pour lequel un milieu opérationnel s'échappant d'une chambre de combustion (2) est acheminé successivement par au moins un canal d'admission (39) au moins à deux cylindres de travail (30), caractérisé en ce qu'un canal d'admission (39) est prévu pour chaque cylindre de travail (30) qui peut être fermé et ouvert par un piston de commande (40 ; 60).
  2. Moteur à pistons axiaux (1) selon la revendication 1, caractérisé en ce que le piston de commande (40 ; 60) effectue une course d'élévation pour l'essentiel orientée dans le sens radial.
  3. Moteur à pistons axiaux (1) selon la revendication 1, caractérisé en ce que le piston de commande (40 ; 60) effectue une course d'élévation (44) pour l'essentiel orientée dans le sens axial.
  4. Moteur à pistons axiaux (1) selon l'une quelconque des revendications 1 à 3, caractérisé en ce que le piston de commande (40 ; 60) est refroidi à l'eau.
  5. Moteur à pistons axiaux (1) selon l'une quelconque des revendications 1 à 4, caractérisé en ce que le piston de commande (40 ; 60) est entraîné de manière desmodromique.
  6. Moteur à pistons axiaux (1) selon l'une quelconque des revendications 1 à 5, caractérisé en ce que le piston de commande (40 ; 60) est entraîné sur une trajectoire courbe.
  7. Moteur à pistons axiaux (1) selon l'une quelconque des revendications 1 à 6, caractérisé en ce qu'un couvercle de piston (41) du piston de commande (40 ; 60) comporte un diamètre plus grand que le canal d'admission (39).
  8. Moteur à pistons axiaux (1) selon l'une quelconque des revendications 1 à 7, caractérisé en ce que le piston de commande (40 ; 60) est fixe en rotation.
  9. Moteur à pistons axiaux (1) selon l'une quelconque des revendications 1 à 8, caractérisé en ce que le piston de commande (40 ; 60) porte un segment de piston de commande (65).
  10. Moteur à pistons axiaux (1) selon la revendication 9, caractérisé en ce que le segment de piston de commande (65) comporte une fente.
  11. Moteur à pistons axiaux (1) selon la revendication 9 ou 10 caractérisé en ce que le segment de piston de commande (65) est fixe en rotation.
  12. Moteur à pistons axiaux (1) selon l'une quelconque des revendications précédentes, caractérisé en ce que la chambre de combustion (2) fonctionne avec une combustion à deux phases.
  13. Moteur à pistons axiaux (1) selon l'une quelconque des revendications précédentes, caractérisé en ce que du carburant peut être injecté dans la chambre de combustion (2) par un gicleur principal (9) et par un gicleur de préparation de mélange (10) qui sera ou est mélangé à l'air, pour lequel une quantité d'air correspondant de préférence à une quantité de carburant introduite par le gicleur principal (9) dans la chambre de combustion principale (6) est introduite dans la chambre de combustion principale (6) derrière une chambre de préparation de mélange (7).
  14. Moteur à pistons axiaux (1) selon l'une quelconque des revendications précédentes, caractérisé en ce que la chambre de combustion (2) est isolée au moyen d'un ensemble céramique (21) qui est constitué refroidi à l'air et/ou de manière tubulaire et est entouré d'un tuyau (23) avec profilage.
  15. Moteur à pistons axiaux (1) selon l'une quelconque des revendications précédentes, caractérisé en ce que l'air de cycle comprimé est utilisé pour le refroidissement, en particulier pour le refroidissement de la chambre de combustion (2) et/ou de l'eau est ajoutée à l'air de cycle.
EP13004435.7A 2007-11-12 2008-11-10 Moteur à pistons axiaux Not-in-force EP2711500B1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE102007054204 2007-11-12
DE102007055337 2007-11-19
DE102007056814 2007-11-23
EP08849887.8A EP2220341B1 (fr) 2007-11-12 2008-11-10 Moteur à pistons axiaux et procédé pour faire fonctionner un moteur à pistons axiaux

Related Parent Applications (2)

Application Number Title Priority Date Filing Date
EP08849887.8A Division EP2220341B1 (fr) 2007-11-12 2008-11-10 Moteur à pistons axiaux et procédé pour faire fonctionner un moteur à pistons axiaux
EP08849887.8A Division-Into EP2220341B1 (fr) 2007-11-12 2008-11-10 Moteur à pistons axiaux et procédé pour faire fonctionner un moteur à pistons axiaux

Publications (3)

Publication Number Publication Date
EP2711500A2 EP2711500A2 (fr) 2014-03-26
EP2711500A3 EP2711500A3 (fr) 2015-01-21
EP2711500B1 true EP2711500B1 (fr) 2016-02-10

Family

ID=40636953

Family Applications (3)

Application Number Title Priority Date Filing Date
EP13004435.7A Not-in-force EP2711500B1 (fr) 2007-11-12 2008-11-10 Moteur à pistons axiaux
EP20130004434 Withdrawn EP2711499A3 (fr) 2007-11-12 2008-11-10 Moteur à pistons axiaux
EP08849887.8A Not-in-force EP2220341B1 (fr) 2007-11-12 2008-11-10 Moteur à pistons axiaux et procédé pour faire fonctionner un moteur à pistons axiaux

Family Applications After (2)

Application Number Title Priority Date Filing Date
EP20130004434 Withdrawn EP2711499A3 (fr) 2007-11-12 2008-11-10 Moteur à pistons axiaux
EP08849887.8A Not-in-force EP2220341B1 (fr) 2007-11-12 2008-11-10 Moteur à pistons axiaux et procédé pour faire fonctionner un moteur à pistons axiaux

Country Status (10)

Country Link
US (2) US9879635B2 (fr)
EP (3) EP2711500B1 (fr)
JP (1) JP5598763B2 (fr)
KR (1) KR101514859B1 (fr)
CN (2) CN101932792B (fr)
BR (1) BRPI0817366A2 (fr)
DE (1) DE112008003003A5 (fr)
ES (1) ES2711318T3 (fr)
RU (1) RU2490488C2 (fr)
WO (1) WO2009062473A2 (fr)

Families Citing this family (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7397049B2 (en) * 2006-03-22 2008-07-08 Varian Semiconductor Equipment Associates, Inc. Determining ion beam parallelism using refraction method
DE112010003062A5 (de) 2009-07-24 2012-08-02 GETAS GESELLSCHAFT FüR THERMODYNAMISCHE ANTRIEBSSYSTEME MBH Axialkolbenmotor, verfahren zum betrieb eines axialkolbenmotors sowie verfahren zur herstellung eines wärmeübertragers eines axialkolbenmotors
WO2011009454A2 (fr) * 2009-07-24 2011-01-27 GETAS GESELLSCHAFT FüR THERMODYNAMISCHE ANTRIEBSSYSTEME MBH Moteur à pistons axiaux, procédé pour faire fonctionner un moteur à piston axiaux et procédé pour réaliser un échangeur thermique d'un moteur à pistons axiaux
US10119398B2 (en) 2009-07-24 2018-11-06 GETAS Gesellschaft fuer termodynamische Antriebssysteme mbH Axial-piston engine, method for operating an axial-piston engine, and method for producing a heat exchanger of an axial-piston engine
US20120118249A1 (en) * 2009-07-24 2012-05-17 Getas Gesellschaft Fuer Thermodynamische Antriebssysteme Mbh Axial-piston engine, method for operating an axial-piston engine, and method for producing a heat exchanger of an axial-piston engine
CN106917676A (zh) * 2009-07-24 2017-07-04 热力驱动系统有限责任公司 轴向活塞发动机、其操作方法和制造它的热交换器的方法
US9188000B2 (en) * 2009-07-24 2015-11-17 Getas Gesellschaft Fuer Thermodynamische Antriebssysteme Mbh Axial-piston motor with continuously working combustion chamber having two combustion air inputs
DE102011018846A1 (de) * 2011-01-19 2012-07-19 GETAS GESELLSCHAFT FüR THERMODYNAMISCHE ANTRIEBSSYSTEME MBH Axialkolbenmotor sowie Verfahren zum Betrieb eines Axialkolbenmotors
RU2679952C2 (ru) * 2013-10-22 2019-02-14 Крис Киараш МОНТЕБЕЛЛО Роторно-поршневой двигатель с внешней камерой сгорания-расширения
DE102015108542A1 (de) 2015-05-29 2016-12-01 GETAS GESELLSCHAFT FüR THERMODYNAMISCHE ANTRIEBSSYSTEME MBH Axialkolbenmotor
DE102015118239A1 (de) * 2015-10-26 2017-04-27 GETAS GESELLSCHAFT FüR THERMODYNAMISCHE ANTRIEBSSYSTEME MBH Axialkolbenmotor und Verfahren zum Betrieb eines Axialkolbenmotors
DE102016100439A1 (de) 2016-01-12 2017-07-13 GETAS GESELLSCHAFT FüR THERMODYNAMISCHE ANTRIEBSSYSTEME MBH Verfahren zum Betrieb eines Axialkolbenmotors sowie Axialkolbenmotor
RU2628831C2 (ru) * 2016-10-20 2017-08-22 Погуляев Юрий Дмитриевич Способ управления аксиально-поршневым двигателем и аксиально-поршневой двигатель
RU2634974C2 (ru) * 2016-10-20 2017-11-08 Погуляев Юрий Дмитриевич Способ управления аксиально-поршневым двигателем и аксиально-поршневой двигатель
DE102017124411A1 (de) 2016-11-07 2018-05-09 GETAS GESELLSCHAFT FüR THERMODYNAMISCHE ANTRIEBSSYSTEME MBH Axialkolbenmotor
WO2019149297A1 (fr) 2018-01-31 2019-08-08 GETAS GESELLSCHAFT FüR THERMODYNAMISCHE ANTRIEBSSYSTEME MBH Moteur à piston axial
WO2020007419A1 (fr) 2018-07-04 2020-01-09 GETAS GESELLSCHAFT FüR THERMODYNAMISCHE ANTRIEBSSYSTEME MBH Moteur à pistons axiaux

Family Cites Families (34)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3007462A (en) * 1957-08-26 1961-11-07 Vernon W Balzer Reciprocating machine
US4024703A (en) 1971-10-14 1977-05-24 Hudson Perry D Combustion in combustion products pressure generator intermittent burner type and engines
SE366092B (fr) * 1973-01-02 1974-04-08 T Airas
DE2321060A1 (de) * 1973-04-26 1974-11-14 Volkswagenwerk Ag Hubkolben-brennkraftmaschine mit innerer kontinuierlicher verbrennung
DE2331706A1 (de) * 1973-06-22 1975-01-16 Volkswagenwerk Ag Mit kontinuierlicher verbrennung arbeitende hubkolben-brennkraftmaschine
US3895614A (en) * 1973-12-03 1975-07-22 Henry E Bailey Split piston two-stroke four cycle internal combustion engine
US3985111A (en) * 1973-12-17 1976-10-12 Eaton Corporation Article for defining an auxiliary compartment for an engine combustion chamber
DE2826932A1 (de) * 1978-06-20 1980-01-24 Maschf Augsburg Nuernberg Ag Axialkolben-brennkraftmaschine
FR2442336A1 (fr) 1978-11-24 1980-06-20 Townsend Engineering Co Procede pour proteger les organes d'etancheite d'un piston de moteur a combustion interne contre la chaleur de combustion
SU799556A1 (ru) 1979-01-02 1986-03-30 Предприятие П/Я М-5536 Двигатель внутреннего сгорани с воспламенением от сжати
US4448154A (en) * 1979-04-30 1984-05-15 Paradox International, Incorporated Internal combustion engine
US4343282A (en) * 1979-07-16 1982-08-10 Glenn Joseph G Liquid tower carburetor
NL8200333A (nl) * 1981-02-27 1982-09-16 Westinghouse Electric Corp Verbrandingsinrichting voor gasturbine.
FR2608212A1 (fr) 1985-12-19 1988-06-17 Pellerin Jacques Moteur thermique en barillet dont pistons et chemises sont refroidis par une circulation dirigee de fluide, circulation obtenue par des turbines interieures au moteur
JPS62267520A (ja) 1986-05-14 1987-11-20 Isuzu Motors Ltd デイーゼル機関
JP2644745B2 (ja) 1987-03-06 1997-08-25 株式会社日立製作所 ガスタービン用燃焼器
WO1989005399A1 (fr) 1987-12-02 1989-06-15 Wagner-Polybau Szolgáltató Kft. Agencement servant a faciliter l'exploitation d'un moteur a combustion interne par prechauffage du carburant du moteur
SU1740762A1 (ru) * 1987-12-07 1992-06-15 А.И. Устимов Способ работы двухтактного форкамерного двигател внутреннего сгорани и двухтактный форкамерный двигатель внутреннего сгорани
JPH0289916A (ja) * 1988-09-26 1990-03-29 Toshiba Corp ガスタービン燃焼器
SU1751374A1 (ru) * 1990-08-06 1992-07-30 Уральский Автомоторный Завод Производственного Объединения "Зил" Двигатель внутреннего сгорани
EP0554325B1 (fr) 1990-10-23 1995-07-26 ROLLS-ROYCE plc Chambre de combustion pour moteur a turbine a gaz et mode de fonctionnement de ladite chambre
US5203298A (en) * 1992-05-29 1993-04-20 John Manolis Pre-combustion chamber for internal combustion engine
JP2950720B2 (ja) 1994-02-24 1999-09-20 株式会社東芝 ガスタービン燃焼装置およびその燃焼制御方法
US5964087A (en) * 1994-08-08 1999-10-12 Tort-Oropeza; Alejandro External combustion engine
US5549032A (en) 1995-04-25 1996-08-27 Long; Otto V. Low-pollution high-power external combustion engine
US6951211B2 (en) * 1996-07-17 2005-10-04 Bryant Clyde C Cold air super-charged internal combustion engine, working cycle and method
US5904044A (en) 1997-02-19 1999-05-18 White; William M. Fluid expander
DE19909689B4 (de) 1999-03-05 2009-07-23 Rohs, Ulrich, Dr.-Ing. Kolbenmotor mit kontinuierlicher Verbrennung
US6536207B1 (en) * 2000-03-02 2003-03-25 New Power Concepts Llc Auxiliary power unit
JP3712947B2 (ja) * 2001-03-02 2005-11-02 川崎重工業株式会社 ガスタービンエンジン用の液体燃料焚き低ｎｏｘ燃焼器
SE526379C2 (sv) * 2004-01-22 2005-09-06 Cargine Engineering Ab Metod och system för styrning av en anordning för kompression
US20080193886A1 (en) * 2004-02-10 2008-08-14 Ebara Corporation Combustion Apparatus
US7677210B2 (en) * 2005-12-14 2010-03-16 Chasin Lawrence C Rotating barrel type internal combustion engine
US20070256658A1 (en) * 2006-03-06 2007-11-08 Andersson Per G E Combined variable compression ratio and passive ignition system

Also Published As

Publication number Publication date
RU2490488C2 (ru) 2013-08-20
JP2011503412A (ja) 2011-01-27
RU2010118716A (ru) 2011-12-20
CN103334833A (zh) 2013-10-02
KR20100093554A (ko) 2010-08-25
CN101932792B (zh) 2013-05-08
EP2711499A2 (fr) 2014-03-26
EP2220341A2 (fr) 2010-08-25
JP5598763B2 (ja) 2014-10-01
EP2220341B1 (fr) 2019-01-09
BRPI0817366A2 (pt) 2015-03-31
CN101932792A (zh) 2010-12-29
DE112008003003A5 (de) 2010-08-05
CN103334833B (zh) 2019-04-05
WO2009062473A3 (fr) 2009-11-26
US20100258065A1 (en) 2010-10-14
KR101514859B1 (ko) 2015-04-23
EP2711500A3 (fr) 2015-01-21
EP2711500A2 (fr) 2014-03-26
US20180128204A1 (en) 2018-05-10
WO2009062473A2 (fr) 2009-05-22
US9879635B2 (en) 2018-01-30
EP2711499A3 (fr) 2015-05-06
ES2711318T3 (es) 2019-05-03
EP2711499A8 (fr) 2014-05-28

Similar Documents

Publication Publication Date Title
EP2711500B1 (fr) Moteur à pistons axiaux
DE102015221286B4 (de) Verfahren zum Betreiben einer Brennkraftmaschine mit einer Spüleinrichtung
EP0102507A2 (fr) Dispositif destiné à l'injection du combustible dans les chambres de combustion des moteurs à combustion interne du type à auto-allumage
DE102006018973A1 (de) Laserzündung in einer Vorkammer
DE112014004695T5 (de) Brennstoffeinspritzvorrichtung für eine Gasturbine
DE102009055038A1 (de) Laserzündeinrichtung
DE2110182A1 (de) Zusatzheizung für ein Kraftfahrzeug mit wassergekühltem Motor
DE102017201275B4 (de) Verbrennungskraftmaschine mit kraftstoff-einspritzsüde mit zusätzlicher zuführung eines verbrennungsfördernden mediums in den brennraum
DE102012016673B4 (de) Antriebseinrichtung mit einer Brennkraftmaschine und einer Heizvorrichtung zum Beheizen eines Katalysators
WO2011009452A2 (fr) Moteur à pistons axiaux et procédé pour faire fonctionner un moteur à pistons axiaux
EP0148837B1 (fr) Dispositif d'injection de carburant dans un ecoulement secondaire d'air de combustion d'une chambre de combustion
DE4215763A1 (de) Brenner
DE4244400C2 (de) Brenner zur Heißgaserzeugung
DE102022002118B3 (de) Brenner für ein Kraftfahrzeug sowie Kraftfahrzeug mit wenigstens einem solchen Brenner
EP3048244B1 (fr) Moteur a pistons axiaux
AT524226B1 (de) Verbrennungsmotor und Verfahren zum Betreiben eines Verbrennungsmotors
AT500024B1 (de) Verfahren zum betreiben einer mit gasförmigem kraftstoff betriebenen brennkraftmaschine
DE2301865A1 (de) Brennkraftmaschine mit aeusserer verbrennung
AT523836B1 (de) Verfahren zum Betreiben eines Hubkolbenmotors sowie Hubkolbenmotor
DE102022206552B3 (de) Verfahren zum Betreiben einer Antriebseinrichtung sowie entsprechende Antriebseinrichtung
DE19802626C1 (de) Verfahren zum Betreiben einer Brennkraftmaschine
DE102016212084B4 (de) Brennkraftmaschine mit im Zylinderrohr angeordneter Einspritzvorrichtung und Verfahren zum Betreiben einer derartigen Brennkraftmaschine
DE102010037743B4 (de) Betriebsverfahren für einen Zweitaktmotor
DE3507669A1 (de) Mischblock fuer ein brennbares gasgemisch
DE102005037551A1 (de) Brennkraftmaschine, sowie Verfahren zum Betreiben einer solchen Brennkraftmaschine

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AC Divisional application: reference to earlier application

Ref document number: 2220341

Country of ref document: EP

Kind code of ref document: P

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MT NL NO PL PT RO SE SI SK TR

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Kind code of ref document: A3

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MT NL NO PL PT RO SE SI SK TR

RIC1 Information provided on ipc code assigned before grant

Ipc: F01B 3/04 20060101ALI20141216BHEP

Ipc: F02G 3/02 20060101ALI20141216BHEP

Ipc: F01B 3/00 20060101AFI20141216BHEP

Ipc: F02B 75/26 20060101ALI20141216BHEP

17P Request for examination filed

Effective date: 20150603

RBV Designated contracting states (corrected)

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MT NL NO PL PT RO SE SI SK TR

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

INTG Intention to grant announced

Effective date: 20150828

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AC Divisional application: reference to earlier application

Ref document number: 2220341

Country of ref document: EP

Kind code of ref document: P

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MT NL NO PL PT RO SE SI SK TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: AT

Ref legal event code: REF

Ref document number: 774756

Country of ref document: AT

Kind code of ref document: T

Effective date: 20160215

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: GERMAN

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 502008013826

Country of ref document: DE

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG4D

REG Reference to a national code

Ref country code: NL

Ref legal event code: MP

Effective date: 20160210

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: HR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160210

Ref country code: NO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160510

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160511

Ref country code: IT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160210

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160210

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160210

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160610

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160210

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160210

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160210

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160210

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160210

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160613

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160210

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160210

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502008013826

Country of ref document: DE

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 9

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160210

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160210

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160210

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20161111

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160210

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20161130

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160510

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20161110

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20161130

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20161130

REG Reference to a national code

Ref country code: IE

Ref legal event code: MM4A

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20161130

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 10

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20161110

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20161110

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 774756

Country of ref document: AT

Kind code of ref document: T

Effective date: 20161110

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20161110

REG Reference to a national code

Ref country code: BE

Ref legal event code: MM

Effective date: 20161130

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO

Effective date: 20081110

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160210

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MC

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160210

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160210

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: TR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160210

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20181123

Year of fee payment: 11

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20191127

Year of fee payment: 12

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20191130

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 502008013826

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20210601