WO2020007418A1 - Moteur à pistons axiaux et procédé permettant de faire fonctionner un moteur à pistons axiaux - Google Patents

Moteur à pistons axiaux et procédé permettant de faire fonctionner un moteur à pistons axiaux Download PDF

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Publication number
WO2020007418A1
WO2020007418A1 PCT/DE2019/100625 DE2019100625W WO2020007418A1 WO 2020007418 A1 WO2020007418 A1 WO 2020007418A1 DE 2019100625 W DE2019100625 W DE 2019100625W WO 2020007418 A1 WO2020007418 A1 WO 2020007418A1
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WO
WIPO (PCT)
Prior art keywords
combustion chamber
working
axial piston
movable
flame
Prior art date
Application number
PCT/DE2019/100625
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German (de)
English (en)
Inventor
Ulrich Rohs
Original Assignee
GETAS GESELLSCHAFT FüR THERMODYNAMISCHE 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.)
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Publication of WO2020007418A1 publication Critical patent/WO2020007418A1/fr

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Classifications

    • 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
    • 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

Definitions

  • the invention relates to an axial piston motor with an internal continuous
  • Such axial piston motors generally have a continuously operating combustion chamber, a number of working cylinders with working pistons running back and forth in these and an output contraction, the combustion chamber and the output contraction coaxial with one another on a central axis and the working cylinders around the central axis are arranged and wherein the combustion chamber is connected to the working cylinders via openable and closable firing channels.
  • Corresponding axial piston motors with internal continuous combustion can be found, for example, in EP 1 035 310 A2, EP 2 711 499 A2, WO 2011/009455 A2, WO 2012/107013 A2 and in German patent application DE 10 2016 119 889 A1, whereby there slide valves, be they rotary slide valves or slide pistons, are used to open or close the firing channels.
  • DE 10 2017 124 411 A1 discloses the use of poppet valves for opening and closing the shot channels.
  • an axial piston motor with internal continuous combustion comprising a continuously operating combustion chamber which generates a working gas stream via a continuous working flame fed with fuel and combustion air, can have a number of Working cylinders back and forth in these running working pistons in which the working gas does work, and an output shaft operatively connected to the working piston, the working cylinders being arranged around a central axis, the combustion chamber having at least one combustion chamber outlet, through which the working gas flow leaves the combustion chamber in at least one protective direction, and wherein the combustion chamber outlet, seen in the firing direction, is connected to the working cylinders via at least one openable and closable cover valve, characterized in that the combustion chamber outlet is designed to be movable with the combustion chamber or a firing channel downstream of the combustion chamber outlet in the firing direction and can optionally be directed towards the cover valves.
  • the cover valves enable relatively high shutter speeds, so that the working pistons can be filled precisely even at high speeds.
  • the movable combustion chamber, the movable combustion chamber outlet or the movable firing channel can, with a suitable design or process control, ensure that the working gas is fired at the working cylinders in a targeted manner and only in the required periods.
  • Valve cover which can open and close the respective protective channel in conjunction with an associated valve set.
  • the cover valves include, in particular, poppet valves in which the valve cover is carried by a valve stem, so that in particular a pressure acting on the valve cover from the valve stem side can counteract a pressure acting on the valve cover from the opposite side.
  • the cover valves also include pot valves in which the valve cover is ultimately formed by the bottom of the pot, the pot wall then representing the valve stem and being able to serve as a guide or a drive.
  • Lid valves are among the shut-off devices. A distinction must be made
  • Lid valves and therefore in particular plate and pot valves, in particular of slides, taps or flaps, which are also to be counted as shut-off devices. While the direction of movement of the shut-off assemblies is largely perpendicular to the flow direction through the respective shut-off device in the case of valves, taps or flaps, the direction of motion of the shut-off assembly, i.e. in particular the valve cover, is against and against the valve seat of valves, especially for deck valves away, directed essentially parallel to the direction of flow through the valve.
  • cover valves in particular poppet valves or pot valves
  • non-generic crankshaft motors and not in axial piston motors
  • cover valves in particular poppet valves or pot valves
  • internal continuous combustion since 1910 from US 972,504 or since 1971 from US 3,577,729 or since 1976 from US 3,973,393 known.
  • the long shot channels provided there between the combustion chamber and the working cylinder do not suggest high efficiency in any way.
  • the differences in the length of the firing channels or in the flow paths leading to the firing channels due to the type of construction do not lead to the expectation of uniform work and therefore a uniform efficiency of these crankshaft motors.
  • the combustion chamber outlet can be designed to be movable independently of the combustion chamber for the rest or together with the rest of the combustion chamber. Both configurations make it possible, just like the movable firing channel, to direct the working gas flow specifically to the cover valves. It has been found that this then enables the cover valves to be relieved, since they are only thermally stressed for a short time, namely as long as the working gas flow is directed at the respective cover valve.
  • valves Compared to slides and other shut-off devices, valves, and in particular cover valves or plate or pot valves, have a relatively linear response behavior and can in particular open and close relatively quickly. This then enables corresponding fast shutter speeds compared to axial piston motors in which slides are used.
  • the movable combustion chamber outlet or the movable firing channel enables targeted alignment of the respective cover valve when it is to be opened, so that the cover valve can then be thermally relieved and cooled.
  • the movable combustion chamber, the movable combustion chamber outlet or the movable firing channel can preferably rotate. In this way, a the simplest possible implementation of the movement of the combustion chamber outlet or the weft channel and a synchronization of this movement with the movement of the deck valves and / or the working pistons can be achieved.
  • the phase can be adapted to different requirements if necessary by offsetting the rotational speed.
  • the movable combustion chamber, the movable combustion chamber outlet or the movable firing channel rotate around the central axis of the axial piston motor, so that a coupling with the movement of the driven contraction appears to be possible without further ado.
  • the movable combustion chamber, the movable combustion chamber outlet or the movable firing channel are preferably arranged in a rotating body, which enables a simple and precise construction.
  • the rotating body advantageously carries a combustion chamber floor, so that a movable combustion chamber outlet, which is arranged in the combustion chamber floor, can be implemented in a structurally simple manner.
  • a movable combustion chamber outlet which is arranged in the combustion chamber floor
  • Combustion chamber outlet or the rotating body are arranged in a pressure chamber pressurized with combustion chamber pressure or with Ver.
  • This arrangement places lower demands on a possibly provided seal, in particular in the area of the cover valves or also of the rotating body, when the working gas is shot at the cover valves.
  • the compressor pressure can be easily provided, for example, by supplying combustion air from the compressor, in particular if this combustion air is still used to cool the assemblies in the area of the cover valves or the rotating body or the combustion chamber base and is then used by the pressure chamber to supply the working flame
  • Combustion chamber pressure can be provided particularly easily in this area, for example by specifically using leakage currents from the combustion chamber or from the combustion chamber outlet.
  • the pressure chamber is preferably divided by at least one pressure chamber seal in a valve pressure chamber, in which the cover valves are also arranged or from which they also lead out, and an upper chamber, since this allows a flow direction in the overall system to be easily defined by the seal.
  • the valve pressure chamber is preferably subjected to combustion chamber pressure, while the upper chamber, for example with compressor pressure, which is naturally higher than the combustion chamber pressure, since the flow path is shorter and does not still run over the combustion chamber.
  • the pressure chamber seal comprises a labyrinth seal.
  • the labyrinth seal comprises a piston ring, since this is very inexpensive in itself and allows sealing conditions that are controllable per se.
  • the pressure chamber can surround the movable combustion chamber.
  • the pressure chamber can open into the combustion chamber, so that air can be fed from the pressure chamber to the combustion chamber. Both arrangements, however, together make it possible for air to be supplied from the pressure chamber to the movable combustion chamber in any operating position by surrounding it on all sides. The air supplied from the pressure chamber of the combustion chamber can then be used directly as combustion air.
  • the upper space advantageously opens into the combustion chamber, so that a flow direction to the combustion chamber can be ensured in a structurally simple manner.
  • the pressure chamber can supply the combustion chamber with compressed air, either directly if the pressure chamber opens into the combustion chamber or if there are further assemblies between the pressure chamber and combustion chamber are provided, can be done indirectly.
  • a structurally simple supply is possible, in particular, if the upper space feeds the movable combustion chamber with compressed air, which is correspondingly particularly advantageous since here short paths to a burner providing the working flame and reaching into the combustion chamber are to be expected.
  • the air in the pressure chamber cools the combustion chamber.
  • the implementation of the cooling system is structurally particularly simple, and the energy of the cooling system can be recovered with a suitable design if the air used for cooling is supplied from the pressure or upper space of the combustion chamber and is additionally available there as thermal energy.
  • good cooling can be achieved in that the combustion chamber bears cooling fins towards the pressure space or towards the upper space.
  • the cooling fins with one component can extend perpendicular to the direction of movement of the air with respect to the combustion chamber on the combustion chamber.
  • the pressure chamber can have air swirling structures pointing towards the combustion chamber in order to achieve the same advantage mentioned.
  • the movable combustion chamber advantageously includes a fuel supply which can follow the movement of the movable combustion chamber. It is particularly advantageous if the fuel supply includes a rotating union. In this way, a reliable fuel supply can be ensured during the movement of the combustion chamber, which is particularly advantageous in a rotating combustion chamber, in particular in conjunction with the rotating union.
  • the cover valve can also preferably not see the working flame through the combustion chamber outlet. Alternatively or cumulatively, this may be the case
  • Lid valve does not see the working flame even through the movable firing channel.
  • Both of the above-mentioned designs have the advantage that the cover valve is shielded from direct radiation and is therefore thermally relieved, possibly while accepting the disadvantage of a more complex or longer flow path.
  • the working gas can be directed directly or, if possible, directly to the cover valve and thus in the direction of firing or in the direction of the working cylinder, while accepting the disadvantage of a greater thermal radiation exposure, which, however, with suitable motion control of the combustion chamber, the combustion chamber floor or the firing channel can be minimized. Accordingly, it can be advantageous for the cover valve to see the working flame through the combustion chamber outlet and / or through the movable firing channel, which then enables a correspondingly direct flow path.
  • the movable combustion chamber can also be combined with the movable one
  • the ignition device can comprise, for example, a spark plug or a start burner, which does not necessarily have to be moved when they can conduct their ignition energy to the combustion chamber via the moving ignition energy transport.
  • the ignition device for example a spark plug, can rotate with the combustion chamber and in the vicinity of the working or main nozzle, with which
  • Fuel is placed in the combustion chamber before it is brought into contact with combustion air to be able to ignite the working flame.
  • the ignition device can then be found on the one hand constantly in a thermally loaded and fueled area, which then loads the ignition device accordingly.
  • the combustion chamber is running, there will generally be no air available in these areas, so that the fuel cannot be ignited there either.
  • it can be advantageous to have the ignition device continuously ignited. Electrical energy for the ignition device can then be provided in a contactless manner, if necessary, via sliding contacts or via a skipping spark, possibly also at regular intervals and even several times during one revolution.
  • the combustion chamber can comprise a fuel preparation, by means of which the fuel generating the working flame is processed before it comes into contact with the combustion air.
  • the fuel preparation preferably comprises a preparation flame or a preparation burner, as a result of which it is possible to work particularly precisely and, if necessary, the fuel preparation can be regulated.
  • the fuel preparation includes a hot gas and / or flame return, which enables a structurally simple and reliable design. In particular, it is advantageous if the fuel preparation moves with the combustion chamber, in particular rotates with it.
  • the movable firing channel has a firing channel opening on the combustion chamber side facing the combustion chamber or the combustion chamber outlet and a firing channel opening on the valve side facing the cover valves.
  • the connections both to the combustion chamber and in the direction of the cover valves can easily be provided. Accordingly, this then also enables simple guidance of the working gas flow from the combustion chamber to the respective cover valve.
  • it is particularly advantageous if the fuel which generates the working flame is fed to a working nozzle which is aligned in the direction of a mixing tube in which the fuel comes into contact with the combustion air.
  • the working nozzle is aligned with a component directed radially to the central axis on the mixing tube and the mixing tube is further away from the central axis than the working nozzle in order to support the fuel transport to the mixing tube with the centrifugal force of the movement.
  • speed-dependent effects can be used here.
  • both the mixing tube and the movable combustion chamber outlet or the firing chamber-side firing channel opening are each arranged at an angle to the central axis, the angle of the mixing tube being smaller than the angle of the moveable combustion chamber outlet or the firing chamber-side firing channel opening or that the mixing tube is directed to an area next to the movable combustion chamber outlet or the firing channel opening on the combustion chamber side.
  • the area is preferably arranged radially between the central axis on the one hand and the movable combustion chamber outlet or the firing channel opening on the other hand.
  • an operating method for operating an axial piston engine in which a working flame is continuously fed with fuel and combustion air and generates a working gas stream, whereby the working gas flow is shot through openable and closable cover valves in the working cylinder, characterized by the fact that the working flame or the working gas flow is optionally directed towards the cover valves and the cover valves are opened and closed synchronously for this purpose.
  • the working flame or the working gas flow is preferably directed successively onto the cover valves.
  • the cover valves are arranged around a central axis and the working flame or the working gas stream are rotated past the cover valves.
  • the working flame burns in a moving combustion chamber, which leads to a structurally simple provision of a stable working flame.
  • the combustion air advantageously cools the moving combustion chamber before it enters the combustion chamber.
  • This provides a structurally simple to implement cooling system, the energy of which can be recovered with a suitable design, in particular if the air is supplied from the pressure or top space to the combustion chamber.
  • the stationary ignition device can comprise, for example, a spark plug or a start burner.
  • a circulation flow of working flame and working gas circulates, this circulation flow having colder and warmer, and thus denser and less dense, areas in the flow cross section and the circulation being oriented such that the direction of the working flame or Forces of the working gas flow support circulation by taking advantage of the different effects of centrifugal force on the denser and less dense areas.
  • the centrifugal force can support the formation and stabilization of a circulation in the combustion chamber which stabilizes the working flame, in particular also for hot gas or working flame return.
  • a fuel flow is preferably combined with the partial flow of the circulation flow or the common circulation flow for the preparation, since this combination can be implemented simply and stably in the course of the process.
  • At least one of the cover valves is a poppet valve, which is particularly stable and inexpensive.
  • at least one of the cover valves is a pot valve, since it is particularly easy to cool the inside.
  • Figure 2 shows the axial piston motor of Figure 1 in section along the line II-II of Fig. 1.
  • FIG. 3 shows an enlargement of the part of FIG. 2 that represents the combustion chamber
  • FIGS. 2 and 3 shows the combustion chamber according to FIGS. 2 and 3 in perspective view
  • FIGS. 2 and 3 shows the supply of air under compressor pressure to the combustion chamber according to FIGS. 2 and 3;
  • FIGS. 1 to 5 are identical to Figure 6 in FIGS. 1 to 5 alternative arrangement
  • FIG. 7 shows a schematic section along the line VII-VII in FIG. 8 through one of the exemplary embodiments according to FIGS. 1 to 6 alternative arrangement of cylinder head and combustion chamber;
  • FIG. 8 shows a section along the line VIII-VIII in FIG. 7 through the arrangement according to FIG
  • Figure 9 is an enlargement of Fig. 7;
  • FIG. 10 shows a perspective illustration of the arrangement according to FIGS. 7 to 9;
  • FIG. 11 shows a perspective representation of the arrangement according to FIGS. 7 to 10 including valve actuation
  • FIG. 12 shows a section along the line XII-XII from FIG. 13 through an alternative
  • Cylinder head in a representation similar to that of FIGS. 7 and 9;
  • Figure 13 is a plan view of the arrangement of Fig. 12;
  • FIG. 14 shows a perspective view of a further alternative cylinder head
  • FIG. 15 shows the arrangement according to FIG. 14 in section along the line XV -XV in FIG. 16;
  • FIG. 16 is a top view of the arrangement according to FIGS. 14 and 15;
  • FIG. 17 shows a section through the closed pot valve of the arrangement according to FIGS. 14 to 16 along the line XVII-XVII in Fig. 16;
  • FIGS. 14 to 18 shows a section through the open pot valve of the arrangement according to FIGS. 14 to
  • FIG. 19 shows a section corresponding to FIG. 17 through a to the arrangement according to
  • FIGS. 17 and 18 alternative closed lid valve in a similar Dar position as Fig. 17;
  • FIG. 20 shows a section corresponding to FIG. 18 through the opened cover valve
  • FIG. 21 shows the FIGS. 18 and 20 corresponding section through a to the arrangements according to FIGS. 17 to 20 alternative open cover valve in a similar representation to that shown in FIGS. 18 and 20;
  • FIG. 22 shows the FIGS. 18 and 20 corresponding section through the closed
  • the axial piston motor 10 shown in the figures each have a continuously operating combustion chamber 20 and six working cylinders 30 and six compressor cylinders 40 and an output fan 50. It is understood that in different Embodiments easily other numbers of cylinder 30 and Verêtrzy cylinder 40 can be provided.
  • the working cylinders 30 are each held by a cylinder carrier 36, which in turn is connected to a cylinder head 37, which then also carries the combustion chamber 20.
  • the combustion chamber 20 and the output shaft 50 are arranged coaxially to one another on a central axis 11, which represents a main axis of symmetry of the respective axial piston motor 10.
  • the working cylinder 30 and the compressor cylinder 40 are also around
  • a working piston 31 and a compressor piston 41 are connected to each other via a connecting rod 59, so that energy can be transferred directly from the respective working piston 31 to the respective compressor piston 41.
  • a connecting rod 59 so that energy can be transferred directly from the respective working piston 31 to the respective compressor piston 41.
  • the output shaft 50 carries a flywheel 53 with a cam track 54, which is comprised of rollers 58, which are each arranged on the connecting rod 59. In this way, the back and forth movement of the connecting rods 59 can be coupled with the rotary movement of the output shaft 50.
  • the axial piston motors 10 also have heat exchangers 70, through which, on the one hand, a feed line 71 from a compressor-side collecting space 74, which in this exemplary embodiment is designed as a collecting tube, to the combustion chamber 20 and, on the other hand, exhaust gas 75 from a working-piston side collecting tube 73, which via Derivatives 72 is connected to the working cylinders 30, leads. That way it can Exhaust gas 75 from the working cylinders 30 can be used to heat the compressed air from the compressor cylinders 40.
  • Valves connected to the compressor cylinders 40 Valves connected to the compressor cylinders 40.
  • a plurality of such feed lines 71 or such a heat exchanger 70 or only one such feed line 71 or only one such heat exchanger 70 can also be provided, with this in particular any losses via the working piston-side collecting space 73 in can be minimized in a known manner.
  • Such different arrangements are well known from the prior art.
  • outlet valves 32 are arranged, which are designed in a known manner as poppet valves.
  • the control of the outlet valves 32 is carried out hydraulically and via a suitable and closing pressure spring, wherein in different embodiments, a mechanical or pneumatic control can be easily provided. This is mechanically the case, for example, in the exemplary embodiments illustrated in FIGS. 7 to 22, the actuation of which will be explained in detail below.
  • stationary shot channels 21 are provided, which can be opened and closed via cover valves 60, so that hot working gas from the combustion chamber 20 can be supplied to the working cylinders 30 in a targeted manner and can perform its work there.
  • the working gas is then discharged via the outlet valves 32 from the working piston 31 and passes through the discharge lines 72 into the heat exchanger 70, where it releases a large part of its thermal energy to compressed air from the compressor cylinder 40 or from the compressor-side collecting space 74 and heats it ,
  • the compressed air is fed to the combustion chamber 20, and here, in a manner known per se, after the heat exchanger (s) 70, further heating can take place via a combustion chamber carrier 28 which is intended to be cooled by this air.
  • the axial piston motor 10 according to one of the exemplary embodiments 1 to 5 has a corresponding supply air 76, via which then the air heated in the heat exchanger 70 and compressed by the compressor cylinder 40 is supplied to the combustion chamber 20.
  • the compressed air is fed in at different points, it being possible to determine when the added fuel comes into contact with the air.
  • Processing nozzle 18A take place, in which a small part of the fuel is brought into contact with a corresponding part of compressed air and burned in order to then use the energy released in this way to process the remaining fuel, as is explained with reference to the exemplary embodiment shown in FIG.
  • the corresponding energy can also be provided by a hot gas and / or flame return 18B, by means of which hot gas and / or part of the flame from the combustion chamber 20 is brought into contact with the fuel to process it before it is brought into contact with air and then burned.
  • Combustion chamber 20 is fed on the one hand via a working or main burner 15 which has a working or main nozzle 17 for fuel and is fed with compressed air via a supply air funnel, which is not separately numbered and which opens into a mixing tube 124, so that the actual combustion in the combustion chamber 20 takes place.
  • a supply air funnel which is not separately numbered and which opens into a mixing tube 124, so that the actual combustion in the combustion chamber 20 takes place.
  • the fuel from the main nozzle 17 comes into contact with the compressed air in the mixing tube 124, it is thermally decomposed via the hot gas and / or flame return 18B.
  • the combustion chamber 20 is also fed on the one hand via a working or main burner 15 which has a working or main nozzle 17 for fuel and is fed with heated compressed air via lateral, not separately numbered oblique feed openings , so that the actual combustion takes place in the combustion chamber 20.
  • a decomposition or pre-burner 16 which in turn has a pre-nozzle 18 with a separate air supply (not separately numbered), is thermally disassembled.
  • the fuel is fed in via fuel feeds 19.
  • this can be one or two fuel feeds 19, it being understood that the two fuel feeds 19 can possibly also be brought together to form a common fuel feed line or can be fed from a common fuel feed line.
  • a movable combustion chamber outlet 24 or a movable firing channel 81 can be realized, for example, by a correspondingly movable combustion chamber 20 or by a corresponding body in which the firing channel 81 is arranged.
  • Such a movable combustion chamber is implemented in the exemplary embodiments according to FIGS. 1 to 6 and such a firing channel 81 located in a body is implemented in the exemplary embodiment according to FIG. 7.
  • the risk of incomplete combustion and in particular the risk of pollutants being formed can be reduced to a minimum, such two-stage combustion in various embodiments being already known from the prior art. It goes without saying that, in different embodiments, the present axial piston motor 10 and shown in the figures can be provided with alternative burner arrangements without thereby questioning the basic functionality and in particular the other advantages discussed here.
  • Types of combustion chambers can be used both as a movable or rotating combustion chamber 20 and as a stationary combustion chamber 20, and consequently in all embodiments.
  • the movable combustion chamber 20 as is shown by way of example in FIGS. 1 to 6, comprises a fuel supply 19 which can follow the movement of the movable combustion chamber 20, in particular the fuel supply 19 comprises a rotating union 19A.
  • the side wall 25 and a combustion chamber base 23 form a combustion chamber wall, which is not separately numbered, with here possibly also a combustion chamber cover, in which the main burner 15 and possibly also the oblique supply openings with heated compressed air and / or the hot gas and / or Flame return 18B are arranged to be added.
  • a combustion chamber insulation 26 is also provided, which in these exemplary embodiments is provided by one or more ceramic rings and in the exemplary embodiment illustrated in FIGS. 6 and 7 by a spacing spiral is shown.
  • the compressed air on the side wall 25 is fed to the burner by the distance which the spiral provides, via the oblique supply openings in the combustion chamber cover or via ventilation holes in the pre-nozzle 18, which on the one hand cools the side wall 25 and on the other hand a further pre-heating of the air can be achieved.
  • the combustion chamber support 28 and in particular also the combustion chamber base 23 are cooled with water via a water cooling 69.
  • valve carrier 68 which carries the cover valves 60, which are also referred to as thermal valves.
  • the water cooling of the combustion chamber support 28 takes place indirectly, in particular in the embodiment shown in FIG. 6 the water cooling 69 extends beyond the combustion chamber 20.
  • the cover valves 60 each have a valve stem 61 and a valve cover 63, which is seated in a valve seat 62 in the closed state.
  • valve spring 64 supported on the valve support 68 and a support 65 against which the valve spring 64 presses, in FIGS
  • the valve cover 63 is pulled against the valve seat 62, the cover valve 60 being designed as a poppet valve 60A which hangs in these exemplary embodiments.
  • a force acting in the direction of the valve cover 63 must be applied to the valve stem 61 in these exemplary embodiments, the poppet valve 60A being guided in a valve guide 66 for the associated movement, which is arranged in the valve carrier 68.
  • Control shaft 55 has a cam disk 52, through which lubricant can also reach the poppet valves 60A, in that it has openings which are not shown but are known per se.
  • a cam arm can be used, which can facilitate wetting with oil. In order to promote the latter, openings can also be provided in the cam disk 52.
  • the poppet valves 60 A are seated in the valve seat 62, which in turn is arranged on the combustion chamber floor 23 or between the combustion chamber 20 and the working cylinders 30, and ensure that the firing channels 21 can be opened and closed.
  • the poppet valves 60A can also be arranged in the side wall 25 of the combustion chamber, which, however, may be of a less compact design or else make more complex requirements with regard to the actuation of the poppet valves 60A.
  • the exemplary embodiment according to FIGS. 1 to 5 comprises a stationary ignition device 120 in the form of a spark plug, directly behind which a
  • Ignition energy transfer ring 122 is arranged. Starting from this, a moving ignition energy transport 121 takes place to a fuel inlet 123 in the combustion chamber 20. The ignition energy can be used there to ignite the continuous combustion. The distance between the spark plug and the ignition energy transfer ring 122 is very small, so that only a small energy loss occurs here and the essential ignition spark is then provided at the end of the moving ignition energy transport 121 facing the fuel inlet 123. Possibly. can, despite continuous combustion An ignition spark is regularly generated in order to minimize any deposits or corrosion in the area of the fuel inlet 123. If a processing nozzle 16 were used, its fuel input would be a correspondingly advantageous goal of transporting the ignition energy. [84] Alternatively, the exemplary embodiment shown in FIG. 6 has a stationary ignition device 120 designed as a nozzle, the funnel and the mixing tube 124 already explained above serving as moving ignition energy transport 121.
  • the working flame is ignited in the exemplary embodiments shown in FIGS. 1 to 6 by the stationary ignition device 120, the ignition energy being conducted from the stationary ignition device 120 to the supplied fuel by means of the ignition energy transport 121 moving with the moving combustion chamber.
  • the moving combustion chamber 20 of the exemplary embodiments shown in FIGS. 1 to 6 is arranged in a pressure chamber 82, which is divided by a pressure chamber seal 84 into a valve pressure chamber 85 and an upper chamber 86. In this way, in particular a pressure drop caused by longer distances in the air and bypassing the combustion chamber 20 can be counteracted.
  • the combustion chamber support 28 of the exemplary embodiment shown in FIGS. 1 to 5 carries cooling fins 29 towards the pressure chamber 82 and towards the upper chamber 86. These are partly inclined in order to ensure the best possible air swirling.
  • the pressure chamber 82 of this exemplary embodiment also has air-swirling structures 88 pointing towards the combustion chamber 20. This is used in particular for cooling and thermal insulation of the combustion chamber 20.
  • the water cooling 69 explained above is used in particular.
  • cooling fins and similar structures are dispensed with and the smallest possible distance is set between the combustion chamber support 28 and the outer wall of the pressure chamber 82, which in turn is correspondingly water-cooled in order to be able to transmit as much radiation energy as possible.
  • the movable firing channel 81 has a combustion chamber-side facing the combustion chamber 20 or the combustion chamber outlet 24 Shot channel opening 81 A and a valve-side shot channel opening 81B directed towards the cover valves 60.
  • Both the mixing tube 124 and the movable combustion chamber outlet 24 or the firing channel opening 81 A of the exemplary embodiments shown in FIGS. 1 to 6 are each arranged at an angle to the central axis 11.
  • the angle 125 between the mixing tube 124 and the central axis 11 is smaller than the angle 126 between the movable combustion chamber outlet 24 or the firing chamber-side firing channel opening 81 A and the central axis 11.
  • the mixing tube 124 is exemplary of an area 127 in addition to the movable one Combustion chamber outlet 24 or the firing chamber opening 81 A directed.
  • the region 127 is arranged radially between the central axis 11 on the one hand and the movable combustion chamber outlet 24 or the firing channel opening 81 A on the other side. This promotes a corresponding circulation in the moving combustion chamber 20, so that as a result the flow to the working cylinders 30, but also to the hot gas and / or flame return 18B, if correspondingly provided for a specific implementation.
  • a cam disk 99 is also arranged on the combustion chamber carrier 28 on the fuel supply side as a valve train 90.
  • a cam arm can also be used here, for example, whereby wetting with oil can be facilitated.
  • openings can also be provided in the cam disk 99.
  • a hydraulic valve train 90 is provided at this point, which n is, however, sufficiently known from the prior art.
  • working cylinder ducts 22 are arranged in the exemplary embodiments shown in FIGS. 1 to 6, through which the working gas can get from the respective cover valves 60 into the associated working cylinder 30.
  • heat shields 27 are also arranged in the exemplary embodiments shown in FIGS. 1 to 6, which are designed as ceramic tubes in these exemplary embodiments and serve to minimize thermal losses and to relieve the assemblies surrounding them. It is understood that in alternative embodiments here other materials as well as other types of heat shields can be used. Possibly. it is also possible to dispense with such heat shields, as illustrated by way of example in FIGS. 7 to 22
  • the side wall 25 of the respective combustion chambers 20 is also in all
  • the combustion chamber 20 can also have a combustion chamber base 23 which is correspondingly ceramic in order to serve as the combustion chamber insulation 26.
  • several ceramic partial tubes can also be put together to form a tube, as this is shown by way of example in FIG. 6.
  • the cover valves 60 are seated in a cylinder wall 33 of the working cylinders 30, similar to the exhaust valves 32, on a side 34 facing away from the working piston 31 the working cylinder.
  • the cover valves 60 are designed to be vertical in order to minimize a possible dead space in the stationary firing channels.
  • the cylinder head 37 on the one hand forms the valve seats 62 of the cover valves 60 and also serves as a valve support 68 for the cover valves 60.
  • the combustion chamber base 23 of these exemplary embodiments is provided on a rotating body 80 which carries a movable, in particular a rotating, firing channel 81 and in a pressure chamber 82 is arranged, which on the one hand merges into the combustion chamber 20 and on the other hand is sealed by an outer seal 83 which seals it against atmospheric pressure with a relatively small diameter and a relatively cold area.
  • an outer seal 83 is also provided in the exemplary embodiments shown in FIGS. 1 to 6 for sealing the combustion chamber 20, pressure chamber 82 and the valve pressure chamber 85.
  • a seal between the pressure chamber 82 and the combustion chamber 20 can be dispensed with in the exemplary embodiments according to FIGS. 7 to 22 because of the long way around the rotating body 80, which enables a relatively uncomplicated construction, in particular at the high temperatures present.
  • a seal can also be provided there, for example a seal corresponding to the pressure chamber seal 84 of the embodiment examples according to FIGS. 1 to 6, it being understood that, if appropriate, also in the latter exemplary embodiments, the pressure chamber seal 84 can be dispensed with if the paths around the combustion chamber carrier 28 to the upper chamber 86 are long enough, in particular in the exemplary embodiment illustrated in FIG. 6.
  • the exemplary embodiments in FIGS. 7 to 13 also have a flash shield 87 for the rotating firing channel 81 in order to relieve the rotating body 80 as thermally as possible.
  • a flash shield is dispensed with in the exemplary embodiment according to FIG. 14, it being understood that if necessary a flash shield can also be provided there or the flash shield 87 can also be dispensed with in the exemplary embodiments illustrated in FIGS. 7 to 13 , [98]
  • the firing channel 81 and possibly its flash shield 87 the
  • Rotating body 80 of the exemplary embodiments in FIGS. 7 to 22 also has a balancing recess 89.
  • the exemplary embodiments in FIGS. 1 to 6 also have a balancing recess 89 in order to be able to compensate for any imbalances. Possibly.
  • a plurality of balancing recesses 89 can also be provided, whereby these can optionally also be individually designed for the respective fin.
  • the movable or rotating firing channel 81 or also the combustion chamber outlet 24 of the movable or rotating combustion chamber 20 can be dimensioned such that the cover valves 60 are each only at approximately 12% of the operating time with exhaust gas from the combustion chamber 20 can be charged directly. The remaining approximately 88% of the firing channel 81 is directed away from the cover valves 60.
  • the rotating shot channels 81 of the exemplary embodiments according to FIGS. 7 to 22 do not point directly from the flame in the combustion chamber 20 to the respective cover valves 60, so that the latter the flame through the shot channel 81 can't see. This contributes to further thermal relief. This is not the case in the exemplary embodiments according to FIGS. 1 to 6, since the cooling of the cover valves 60 appears sufficient here.
  • valve springs 64 of these exemplary embodiments are supported on molded parts of the valve stems 61 of these cover valves 60 on the one hand and on hold-down devices 118 (exemplary in FIGS. 17, 19 and 20)). Since the present axial piston engine 10 lacks high pressure peaks due to the continuous combustion, it seems sufficient to close the cover valves 60 of these exemplary embodiments only by spring force, the latter, since this does not enter into the energy balance, can be chosen to be relatively high. It goes without saying that alternative implementations are also possible here. In the alternative shown in FIGS. 21 and 22, on the other hand, this is called
  • the poppet valve 60A shown in Figures 21 and 22 is closed via a cam 96, wherein, in order to counteract the loads occurring here, between the valve stem 61 of these poppet valves 60A and the cam 96, a follower ball 115 is provided, which by a ball carrier 116 is held, which in turn is supported on the valve stem 61 via a play compensation spring 117.
  • a play compensation spring 117 not appearing to be necessary there.
  • the cover valves 60 are each opened via a rocker arm 111, which is tiltably attached to the valve carrier 68 by means of a lever bracket 112 and on which the cam 96 can engage.
  • a running ball 115 does not appear to be necessary to reduce friction, but may also be provided if necessary.
  • a calibration screw 114 is also provided on the rocker arms 111 in order to be able to ensure sufficient opening and reliable closing of the cover valves 60 shown in FIGS. 14 to 20, taking into account the inevitable tolerances.
  • a valve drive 90 driving the cover valves 60 comprises a royal contraction 93, which is not shown in detail per se, but per se via further contractions and gearwheels without further ado from the output shaft 50 can be driven and synchronized with this.
  • This Königswehe 93 drives camshafts 94 via bevel gears 95, for which purpose a bevel gear 95 is arranged on one of the driven camshafts 94, which meshes with a bevel gear 95 which is seated on the Königswehe 93.
  • the cams 94 driven by the royal contraction 93 are synchronized via a synchro ring 97, which rotates around the combustion chamber 20, in that the respective cam shafts 94 each carry synchro pinions 98, which mesh with the synchro ring 97.
  • the synchro pinion 98 and in particular also the synchro ring 97 each have a number of teeth which is an integral multiple of the number of working cylinders 30. In this way, the respective camshafts 94 can each be easily adapted to one another with respect to their time offset in accordance with their position in relation to the other camshafts.
  • valve drive 90 comprises a lever arrangement 91 driven by the control weir 55, which on the one hand drives both the outlet valves 32 and on the other hand the cover valves 60, each of which is driven by cam followers 92, which in turn are driven by one with the driven contraction 50 syn chronized cam disks 52 in a similar position as the cam disk 52 of the exemplary embodiment according to FIGS. 1 to 6 are driven.
  • FIGS. 7 to 13 are largely identical, with the exception that additional combustion chamber insulation 26 is provided in the embodiment shown in FIGS. 12 and 13.
  • Combustion chamber insulation 26 can, however, be used here, if necessary, on a conical body, as in the combustion chamber floor 23 of the exemplary embodiments according to FIGS. 1 to 6.
  • the working cylinder channels 22 of the exemplary embodiments shown in FIGS. 1 to 6 or the firing channels 21 of the exemplary embodiments shown in FIGS. 7 to 22 each have a kink, through which the path of the respective working cylinder or firing channel 22, 21 from the combustion chamber wall or is shaped by the combustion chamber floor 23 to the working cylinder 30.
  • This kink is seen from the combustion chamber 20 in the case of the exemplary embodiments shown in FIGS. 1 to 6 behind and in the exemplary embodiments shown in FIGS. 6 to 21 in front of the cover valves 60, so that the respective valve stem 61 can be designed in a straight line.
  • valve stems 61 can also be inclined at an angle of inclination, so that the kink can also be made weaker, as a result of which any reductions in the flow can be reduced to a minimum.
  • pot valves 60B are used as cover valves 60. Because of their relatively massive valve stem 61, which in alternative embodiments can also be made solid, so that the pot valves 60B can then be referred to as piston valves, such pot valves 60B can dissipate a lot of heat, so that they are not thermally stressed to the extent that such as poppet valves 60A at this point.
  • the relatively large stem diameter of the pot valves 60B but also of the piston valves means that the shot channels 21 have little residual volume in the area of the pot valves 60B or piston valves, so that, in particular if the rotating shot channel 81 does not point to a corresponding pot valve 60B , relatively little residual hot gas remains, which can still heat up the pot valve 60B. This also leads to further thermal relief.
  • the pot valves 60B are also provided with a cavity in which oil cooling 113 is sufficient, so that these pot valves 60B even are actively cooled.
  • oil cooling or similar cooling may be dispensed with.
  • Pot valves 60B of this type or the cover valves explained above can also be used in particular in the exemplary embodiments illustrated in FIGS. 1 to 6, in which case the control via the cam disk 52 and
  • Valve spring 64 should be adjusted accordingly.
  • the cover valves 60 are provided with conical valve seats 62. It has been found that this does not necessarily have to be the case, but that, in different embodiments, a differently designed valve seat can also be sufficient, which accordingly may require less adjustment effort.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Valve Device For Special Equipments (AREA)
  • Portable Nailing Machines And Staplers (AREA)

Abstract

L'invention concerne des moteurs à piston axiaux et un procédé permettant de faire fonctionner des moteurs à pistons axiaux et vise à atteindre un haut rendement, même à des vitesses de rotation élevées. À cet effet, un moteur à pistons axiaux à combustion interne continue comprend une chambre de combustion fonctionnant en continu qui produit un flux de gaz de travail par l'intermédiaire d'une flamme de travail alimentée en continu en carburant et en air de combustion, un certain nombre de cylindres de travail dans lesquels des pistons de travail effectuent un mouvement alternatif, et dans lesquels le gaz de travail effectue un travail, et un arbre de sortie en liaison fonctionnelle avec les pistons de travail, les cylindres étant agencés autour d'un axe central, la chambre de combustion présentant au moins une sortie de chambre de combustion par laquelle le flux de gaz de travail quitte la chambre de combustion dans au moins une direction de décharge, et la sortie de chambre de combustion étant, vue dans la direction de décharge, reliée aux cylindres de travail par une soupape à chapeau pouvant s'ouvrir et se fermer. Le moteur à pistons axiaux et le procédé permettant de faire fonctionner ledit moteur sont caractérisés en ce que la sortie de chambre de combustion et la chambre de combustion et/ou un canal de décharge placé en aval de la sortie de chambre de combustion dans la direction de décharge sont conçus pour être mobiles ou sélectivement orientés vers les soupapes à chapeau.
PCT/DE2019/100625 2018-07-04 2019-07-04 Moteur à pistons axiaux et procédé permettant de faire fonctionner un moteur à pistons axiaux WO2020007418A1 (fr)

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DE102018116206 2018-07-04
DE102018116206.5 2018-07-04
DE102018129650 2018-11-25
DE102018129650.9 2018-11-25
DE102018129720.3 2018-11-26
DE102018129720 2018-11-26

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PCT/DE2019/100626 WO2020007419A1 (fr) 2018-07-04 2019-07-04 Moteur à pistons axiaux

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US972504A (en) 1908-03-23 1910-10-11 Walter F Brown Continuous-combustion heat-engine.
US3577729A (en) 1969-03-11 1971-05-04 Glenn B Warren Reciprocating internal combustion engine with constant pressure combustion
US3973393A (en) 1973-06-22 1976-08-10 Volkswagenwerk Aktiengesellschaft Reciprocating internal combustion engine with continuous combustion
US5285633A (en) * 1993-03-23 1994-02-15 The United States Of America As Represented By The Secretary Of The Navy Coolant subsystem for a torpedo propulsion system
EP1035310A2 (fr) 1999-03-05 2000-09-13 Rohs, Ulrich, Dr. Moteur à pistons à combustion continue
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
WO2011009455A2 (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
WO2012107013A2 (fr) 2011-01-19 2012-08-16 GETAS GESELLSCHAFT FüR THERMODYNAMISCHE ANTRIEBSSYSTEME MBH Moteur à pistons axiaux et procédé de fonctionnement d'un moteur à pistons axiaux
EP2711499A2 (fr) 2007-11-12 2014-03-26 GETAS Gesellschaft für thermodynamische Antriebssysteme mbH Moteur à pistons axiaux
DE102015118239A1 (de) * 2015-10-26 2017-04-27 GETAS GESELLSCHAFT FüR THERMODYNAMISCHE ANTRIEBSSYSTEME MBH Axialkolbenmotor und Verfahren zum Betrieb eines Axialkolbenmotors
DE102016119889A1 (de) 2015-10-26 2017-04-27 GETAS GESELLSCHAFT FüR THERMODYNAMISCHE ANTRIEBSSYSTEME MBH Axialkolbenmotor sowie Verfahren zum Betrieb eines Axialkolbenmotors
DE102017124411A1 (de) 2016-11-07 2018-05-09 GETAS GESELLSCHAFT FüR THERMODYNAMISCHE ANTRIEBSSYSTEME MBH Axialkolbenmotor

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2011009452A2 (fr) * 2009-07-24 2011-01-27 GETAS GESELLSCHAFT FüR THERMODYNAMISCHE ANTRIEBSSYSTEME MBH Moteur à pistons axiaux et procédé pour faire fonctionner un moteur à pistons axiaux
DE102015108542A1 (de) * 2015-05-29 2016-12-01 GETAS GESELLSCHAFT FüR THERMODYNAMISCHE ANTRIEBSSYSTEME MBH Axialkolbenmotor

Patent Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US972504A (en) 1908-03-23 1910-10-11 Walter F Brown Continuous-combustion heat-engine.
US3577729A (en) 1969-03-11 1971-05-04 Glenn B Warren Reciprocating internal combustion engine with constant pressure combustion
US3973393A (en) 1973-06-22 1976-08-10 Volkswagenwerk Aktiengesellschaft Reciprocating internal combustion engine with continuous combustion
US5285633A (en) * 1993-03-23 1994-02-15 The United States Of America As Represented By The Secretary Of The Navy Coolant subsystem for a torpedo propulsion system
EP1035310A2 (fr) 1999-03-05 2000-09-13 Rohs, Ulrich, Dr. Moteur à pistons à combustion continue
EP2711499A2 (fr) 2007-11-12 2014-03-26 GETAS Gesellschaft für thermodynamische Antriebssysteme mbH Moteur à pistons axiaux
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
WO2011009455A2 (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
WO2012107013A2 (fr) 2011-01-19 2012-08-16 GETAS GESELLSCHAFT FüR THERMODYNAMISCHE ANTRIEBSSYSTEME MBH Moteur à pistons axiaux et procédé de fonctionnement d'un moteur à pistons axiaux
DE102015118239A1 (de) * 2015-10-26 2017-04-27 GETAS GESELLSCHAFT FüR THERMODYNAMISCHE ANTRIEBSSYSTEME MBH Axialkolbenmotor und Verfahren zum Betrieb eines Axialkolbenmotors
DE102016119889A1 (de) 2015-10-26 2017-04-27 GETAS GESELLSCHAFT FüR THERMODYNAMISCHE ANTRIEBSSYSTEME MBH Axialkolbenmotor sowie Verfahren zum Betrieb eines Axialkolbenmotors
DE102017124411A1 (de) 2016-11-07 2018-05-09 GETAS GESELLSCHAFT FüR THERMODYNAMISCHE ANTRIEBSSYSTEME MBH Axialkolbenmotor

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