EP3402973B1 - Procédé permettant de faire fonctionner un moteur à pistons axiaux et moteur à pistons axiaux - Google Patents

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

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Publication number
EP3402973B1
EP3402973B1 EP17703309.9A EP17703309A EP3402973B1 EP 3402973 B1 EP3402973 B1 EP 3402973B1 EP 17703309 A EP17703309 A EP 17703309A EP 3402973 B1 EP3402973 B1 EP 3402973B1
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EP
European Patent Office
Prior art keywords
compressor
axial piston
valve
piston motor
compressor outlet
Prior art date
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Application number
EP17703309.9A
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German (de)
English (en)
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EP3402973A1 (fr
Inventor
Ulrich Rohs
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GETAS Gesellschaft fuer Themodynamische Antriebssysteme mbH
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GETAS Gesellschaft fuer Themodynamische Antriebssysteme mbH
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Classifications

    • 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
    • F02B33/00—Engines characterised by provision of pumps for charging or scavenging
    • F02B33/02—Engines with reciprocating-piston pumps; Engines with crankcase pumps
    • F02B33/06—Engines with reciprocating-piston pumps; Engines with crankcase pumps with reciprocating-piston pumps other than simple crankcase pumps
    • 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
    • F02B33/00—Engines characterised by provision of pumps for charging or scavenging
    • F02B33/02—Engines with reciprocating-piston pumps; Engines with crankcase pumps
    • F02B33/28—Component parts, details or accessories of crankcase pumps, not provided for in, or of interest apart from, subgroups F02B33/02 - F02B33/26
    • F02B33/30—Control of inlet or outlet ports
    • 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
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines
    • F02B75/28—Engines with two or more pistons reciprocating within same cylinder or within essentially coaxial cylinders
    • 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
    • F02B75/28—Engines with two or more pistons reciprocating within same cylinder or within essentially coaxial cylinders
    • F02B75/282—Engines with two or more pistons reciprocating within same cylinder or within essentially coaxial cylinders the pistons having equal strokes

Definitions

  • the invention relates to a method for operating an axial piston motor, in which fuel and compressed fuel burned continuously to working fluid in a combustion chamber and successively working cylinders is fed, in which working piston back and forth, which in turn drive an output and compressor pistons, which in compressor cylinders out and run here, in which the combustion medium is compressed, wherein the fuel medium is sucked in via compressor inlet valves and the compressed fuel medium is supplied via compressor outlet valves of the compressor cylinders of the combustion chamber.
  • the invention relates to an axial piston motor with a continuous compressed combustion medium and fuel combustion medium combustion chamber, with working cylinders, which are connected by means of cyclically openable and closable weft connections with the combustion chamber and in which working piston reciprocate, with compressor cylinders, in which compressor piston out and at least one combustion medium supply line leading from compressor discharge valves of the compressor cylinders to the combustion chamber, at least one of the compressor discharge valves having a closure member opening away from the compressor cylinder and cooperating with a valvetrain.
  • Such operating methods or axial piston motors are for example from the EP 1 035 310 A2 or from the WO 2011/00943 A2 known.
  • the outlet valve remains closed as long as the pressure in the compressor piston is below the pressure in the pressure chamber or under the pressure of the corresponding Brennmediumzutechnisch.
  • the closure part of the compressor outlet valve formed by the ceramic ball opens and strikes against an adjusting screw. This opens the way into the pressure chamber.
  • WO 2011/009453 A2 discloses such a passive control of the compressor outlet valve with a valve cover designed as a hemisphere, which interacts with a Ventildeckelantikfeder, so ultimately also this compressor outlet valve on the pressure difference between the compressor cylinder and Brennmediumzutechnisch is controlled, the spring force of the Ventildeckelantikfeder ultimately acts only parallel to this pressure difference.
  • the DE 602 25 683 T2 discloses a desmodromic valve control in which a valve is forcibly opened and closed.
  • the most effective possible compression in a generic method for operating an axial piston motor if this is characterized in that at least one of the compressor exhaust valves positively controlled closed and opened via a built-up in the respective compressor cylinder compressor pressure.
  • the combustion medium from the compressor cylinder is supplied to the combustion chamber, and in the compressor cylinder is sufficient to find compressor pressure, while it can be ensured via the positively controlled closure that no fuel medium flows back into the compressor cylinder, which would accordingly lead to losses.
  • the closing operation of the at least one of the compressor discharge valves is initiated before the associated compressor piston reaches its top dead center. Although compressed at this time then still compressed fuel medium from the compressor cylinder to the combustion chamber. In the vicinity of the upper Tonas but this is done only with a relatively low volume mass flow, so that by the closing compressor outlet valve due smaller valve throughput is not critical and the flow impeded only slightly.
  • the closing operation of the at least one of the compressor outlet valves is initiated at the latest 5 °, preferably at the latest 7 °, before the associated compressor piston reaches its top dead center.
  • the closure part of the compressor outlet valve has to accelerate and travel a certain distance until finally the compressor outlet valve is closed.
  • the closing process is initiated in time, it can be ensured that the corresponding compressor outlet valve is closed in good time, especially taking into account tolerances.
  • the forced or positively controlled closing after the closing operation is initiated, under certain circumstances by the moving mass of one of the compressor exhaust valves ultimately made, which in particular allows compliance with any tolerances, especially since the compressor outlet is kept closed by the pressure difference, and the associated Compressor piston has reached its top dead center.
  • the corresponding compressor outlet valve is actively pressed down to the point at which it is tightly closed or is in contact with a pressure system.
  • the at least one of the compressor outlet valves is closed when the associated compressor piston reaches its top dead center.
  • any possible backflow of combustion medium from the combustion medium supply line which - as already indicated above - can also be interrupted by a second compressor stage, can be prevented in the respective compressor cylinder.
  • a loss of compressed fuel medium can be reduced to a minimum or avoided altogether.
  • the at least one of the compressor outlet valves is released before the compression process in the respective compressor cylinder. This can happen, for example, already during the suction. In particular, this can already be done at the latest 12 °, preferably at the latest 10 °, after the associated compressor piston has reached its top dead center, since in the end the pressure difference between the fuel supply line and the compressor cylinder ensures that the corresponding compressor outlet valve remains tightly closed.
  • the at least one of the compressor outlet valves can be driven mechanically, which allows a particularly precise and structurally simple to implement drive form.
  • the at least one of the compressor outlet valves is driven in synchronism with the output of the axial piston motor, it being understood that, depending on the respective operating state, the phases between the output of the axial piston motor and the drive of the compressor outlet valve may be adapted.
  • valve train is mechanically formed, which allows a simple and precise control of the closure part.
  • valve train may have a pressure system which acts on the closure part, whereby a valve gear which acts only against the opening direction of the closure member, structurally particularly simple can be provided.
  • valve train can be released in the opening direction, that the pressure application is removed from the closure part.
  • the pressure system and the limiting system can be located on a common control module, so that displaced by shifting the control module, the pressure system or the limiting system in a corresponding position and in this way the corresponding compressor outlet valve can be controlled.
  • the pressure system and the limiting system on the control module are integrally formed with each other, which requires a structurally particularly simple design.
  • control assembly may be displaceable between a load position and a release position, wherein in the load position preferably the pressure system and in the unloading position, preferably the limiting system are each positioned so that they can interact with the closure part.
  • the pressure application device acts on the closure part in a corresponding pressing manner
  • relief position only the limiting system limits the valve travel in the opening direction.
  • a corresponding shift can for example take place in that the control module is subjected to a corresponding sliding movement.
  • a tilting or rotational movement for example, a rocker arm or the like may be provided, through which the control module between the loading position and the unloading position changes and each offers the pressure system or the limiting system the closure part for interaction.
  • the pressure system and the limiting system can also be designed identically, which can be realized in particular for example in An horrstkovn, anchors or rocker arms.
  • the pressure system, the limiting system and / or the control module are sprung.
  • the forces acting on the closure member can be minimized, so that its life is increased, which is particularly advantageous if the closure part in lightweight construction, for example, made of very light materials or hollow inside.
  • this also ensures a safe closing of the valve, regardless of unavoidable manufacturing tolerances.
  • the closure part may also have a suspension, which is effective for the pressure system, the limiting system or the control module, in order to ensure a corresponding discharge in this way.
  • a suspension can serve as a tolerance compensation if the pressure system presses on the same even when the valve is closed and rests against this.
  • the pressure system can be spaced from the closure part with the compressor outlet valve closed, in order to allow a tolerance compensation in this way. This is possible in particular if it is ensured in another way that the compressor outlet valve is reliably closed, which can be ensured, for example, by the inherent mass of the compressor outlet valve and / or the pressure difference via the compressor outlet valve or with other measures, such as by means of magnetic forces , The above-mentioned suspension can then still be used for material-relieving purposes.
  • the combustion chamber can, as is well known from the prior art, be effective in two stages and a preburner, which essentially serves to thermally treat the main part of the fuel, before this in a main combustion chamber with the combustion medium, which is usually air represents, is brought into contact. It is understood that differently configured combustion chambers can be readily used in corresponding axial piston engines.
  • the Brennmediumzutechnisch can also be constructed relatively complex.
  • the Brennmediumzutechnisch has a plurality of parallel lines, which then for example, extend separately from individual compressor cylinders to the combustion chamber.
  • the Brennmediumzutechnisch also, As already indicated above, comprise further compressor stages and thus first open into another compressor cylinder, and then to lead from the compressor outlet valve or compressor outlet valves to the combustion chamber.
  • pressure chambers may be provided as constituents of the combustion medium supply line, in which the combustion medium provided by the compressor cylinders is first collected and then fed into one or more supply lines to the combustion chamber.
  • the combustion medium supply line may also comprise one or more heat exchangers with which the combustion medium is heated prior to entry into the combustion chamber, wherein the exhaust gas from the working cylinders or its thermal energy is preferably used here, as already known from the prior art.
  • the one of the Kompressaulaulassventile a poppet valve whose valve cover is the closure member and acts on the Ventilschafft the valve gear.
  • a corresponding axial piston motor structurally simple and accurate implement.
  • a ball of a ball valve or also a corresponding hemisphere can optionally be used as the closure part, as long as a corresponding valve drive is also provided here.
  • the valve drive may in particular have a cam disk or camshaft that is synchronized with an output of the axial piston motor.
  • a corresponding synchronization structurally simple and precise realize, in which case it is particularly possible to drive the closure member mechanically or via a mechanically designed valve train.
  • an electrical, hydraulic or pneumatic signal can be generated, which can then be used in accordance with the synchronization of the valve train.
  • valve train also drives further compressor outlet valves or compressor inlet valves, which requires a correspondingly effective design or a very low structural complexity.
  • the directions of movement of the pistons in the compressor and working cylinders are aligned parallel to the output shaft and the output.
  • the combustion chamber is arranged centrally to the working cylinders, so that to each of the working cylinder an identical or very similar distance is covered and the axial piston motor works very uniformly.
  • compressor cylinder head 17 may be in the in FIGS. 3 and 4 shown axial piston motor 10 are used and has at least one Brennmediumeinlass 46 and a Brennmediumauslass 47 to compressor cylinders 40.
  • the compressed in the compressor cylinders 40 by reciprocating compressor piston 45 compressed combustion medium is collected in a manifold 48, in which the Brennmediumauslässe 47 of the individual compressor cylinder 40 open.
  • a multi-part Brennmediumzutechnisch 56 which is formed in this embodiment in three parts corresponding to a number of heat exchangers 55, through the heat exchanger 55 to a combustion chamber 20, wherein the manifold 48 is to count the Brennmediumzutechnisch 56.
  • the Brennmediumzu effet 56 may be simpler or more complex and, for example, still lead to other compressor stages or be interrupted by other compressor stages, which may also have these appropriate valves and Brennmediumeinlässe and / or -auslässe.
  • shot connections 25 each extend to working cylinders 30 which are represented by firing channels 26 which can be opened and closed periodically between the combustion chamber 20 and the respective working cylinders 30.
  • this can be realized for example by rotating around the working cylinder Burt McCullumn slide, by control piston or by coaxial with the combustion chamber 20 arranged rotary rotary valve or the like.
  • working piston 35 reciprocate, each connected via a connecting rod 51, each with a compressor piston 45, wherein the connecting rods 51 interact with a cam 52 of an output 50, which is arranged on an output shaft 53.
  • the connecting rod 51 interacts with the cam 52 of the output 50 via a connecting rod bearing 57 (see FIG. 7 ).
  • the compressor cylinder 40, compressor piston 45, working cylinder 30, working piston 35 and connecting rod 51 are arranged in a star shape coaxially around the combustion chamber 20 and the output shaft 53.
  • the axial piston motor 10 comprises a housing 16, which has a working cylinder head 15 with the shot channels 26 and lines for exhaust gas 36 and not shown in detail but well known exhaust valves to one side.
  • the housing 16 carries the compressor cylinder head 17th
  • the exhaust gas 36 is passed into the heat exchanger 55 and its thermal energy is fed into the heat exchanger 55 to the located in the Brennmediumzutechnisch 56, compressed combustion medium before it is used in the combustion chamber 20, which operates continuously, for burning fuel.
  • the schematic representation of FIGS. 3 and 4 merely indicated a single-stage combustion chamber. It is understood that here also a multi-stage combustion, in particular with a preburner for the preparation of the fuel, can be provided.
  • the Brennmediumauslass 47 provided in the compressor cylinder head 17 can be opened and closed by means of a compressor outlet valve 42.
  • the compressor outlet valve 42 designed as a poppet valve 80 comprises as valve 70 a closure part 71, which is formed by a valve cover 81 of the poppet valve 80, and an opposite 75, which is formed by the compressor cylinder head 17 itself and represents the valve seat 83 of the poppet valve 80.
  • the poppet valve 80 further includes a valve stem 82 which is guided by a valve guide 89 so that the valve 70 can be safely opened and closed. In this case, the valve guide 89 is seated in the compressor cylinder head 17th
  • valve train 60 As a valve train 60 is a control assembly 65 which is mounted on a sleeve-like control assembly guide 88 in the compressor cylinder head 17 radially displaceable relative to the output shaft 53 and is pressed by a pressure spring 87 against a cam 61, wherein the control assembly 65 carries a cam follower ball 85 which to reduce friction losses on the cam 61 runs.
  • the pressure spring 87 is supported, on the one hand, on the control assembly guide 88 and, on the other hand, on a sleeve 84 in which the control assembly 65 is fastened, so that the control assembly 65 is actuated via the cam disk 61 synchronously with the rotation of the output shaft 53, since the cam disk 61 acts on the Output shaft 53 is placed.
  • a control ball 86 is provided between the valve stem 82 and the control assembly 65 to reduce friction losses.
  • the control assembly 65 has a limiting device 73 and a pressure system 74, which are provided at different positions of the control assembly 65 seen radially with respect to the output shaft 53. Depending on the curved path of the cam disk 61, the limiting system 73 or the pressing system 74 can then be brought into an interaction position with the control ball 86 by the cam disk 61.
  • the pressing system 74 is provided so close to the valve seat 83 that the valve cover 81 is pressed against the valve seat 83 and the compressor outlet valve 42 is closed when the pressing system 74 is disposed in its interaction position with respect to the control ball 86, as this in FIG. 1 is shown.
  • valve cover 81 can open from its valve seat 83 in an opening direction 72 when the gas pressure in the compressor cylinder 40 exceeds the gas pressure in the Brennmediumauslass 47, as this in FIG. 2 is shown as an example.
  • control assembly 65 and the valve train 60 releases the valve 70 in the opening direction 72 when the limiting system 73 is arranged in its interaction position with the control ball 86.
  • the valve can then open itself controlled by the gas pressure. If, on the other hand, the pressure drive 74 of the control assembly 65 is brought into the interaction position with the control ball 86 by the valve drive 60, the valve 70 is forcibly closed.
  • the limiting device 73 and the pressure device 74 are provided on a resilient arm of the control assembly 65, so that the control assembly 65 resiliently interacts with the closure member 71 of the valve 70. This relieves on the one hand the material of the valve 70 and on the other hand serves to ensure the closing of the valve 70 a secure fit of the closure member 71 on its opposite 75, especially taking into account unavoidable manufacturing tolerances.
  • the geometries between the pressure device 74 and the valve stem 82, the control ball 86 and the valve seat 83 are coordinated such that the pressure device 74, when brought in its position of interaction to the control ball 86, with closed compressor outlet valve 42 of the Control ball 86 remains spaced so as to take into account any tolerances in this way.
  • the compressor outlet valve 42 closes ballistically, ie by its own movement and mass, when it has been accelerated by the control assembly 65 in the closing direction accordingly.
  • the pressure difference across the compressor outlet valve 42 also acts valve-closing, and the top dead center of the corresponding compressor piston 45 has been reached. It is understood that in an alternative embodiment, if necessary, the pressure system 74 may rest against the control ball 86 in its interaction position, even when the compressor outlet valve 42 is closed, when the suspension is sufficiently matched to the tolerances.
  • a magnet 90 is used with an armature 91 as a valve drive 60, which also interact with a designed as a poppet valve 80 valve 70.
  • the valve guide 89 is embedded in an aluminum support 93, which on the side of the armature 91, which faces away from the magnet 90, carries a stop 94, against which springs 92 press the armature 91. If the magnet 90 is acted upon by a current, then the armature 91 is against the spring force of the springs 92 and against the opening direction 72 pulled against the magnet 90. If the magnet 90 is turned off, the springs 92 can push the armature 91 in the opening direction 72 against the stop 94 again.
  • the region of the compressor cylinder head 17 surrounding the aluminum carrier 93 has cooling ribs 95.
  • This arrangement also makes it possible for the closure part 71 of the valve 70 to open freely in the opening direction and only conditionally due to the gas pressure difference between the compressor cylinder 40 and the fuel medium vent 47, while it can be closed via the magnet 90.
  • the shaft of the armature 91 which comes into contact with the closure part 71 of the valve 70 serves both as a limiting device 73 and as a pressure system 74, whereby the compressor outlet valve 42 or the valve 70 is forcibly closed by tightening the armature 91 against the opening direction 72 of the valve 70 can be.
  • valve stem 81 and the valve seat 83 and the shaft of the armature 91 are matched in their geometries with one another such that the contact pressure system 74 rests against the valve stem 81 even when the compressor outlet valve 42 is closed.
  • a small gap between the armature 91 and magnet 90 can remain for tolerance compensation.
  • a ballistic closing of the compressor outlet valve 42 can also be provided here by the valve shaft 81 or the shaft of the armature 91 being correspondingly shorter, so that the pressure system 74 does not bear against the valve stem 81 when the compressor outlet valve 42 is closed.
  • FIGS. 7 and 8 arrangements shown show possible embodiments of compressor inlet valves 41, which are also controlled by the cam disk 61, which acts there as a camshaft 62, however.
  • the respective compressor inlet valve 41 is actuated via an actuating lever 99.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Compressor (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Portable Nailing Machines And Staplers (AREA)

Claims (18)

  1. Procédé, destiné à faire fonctionner un moteur à pistons axiaux (10), lors duquel du carburant et un fluide combustible comprimé sont brûlés en continu en un fluide de travail dans une chambre de combustion (20) et amenés à des cylindres de travail (30) successifs, dans lesquels vont et viennent des pistons de travail (35) qui entraînent quant à eux une sortie (50) et des pistons de compresseur (45) qui vont et viennent dans des cylindres de compresseur (40) dans lesquels le milieu combustible est comprimé, le milieu combustible étant aspiré par l'intermédiaire de soupapes d'entrée de compresseur (41) et le milieu combustible étant amené par l'intermédiaire de soupapes de sortie de compresseur (42) des cylindres de compresseur (40) vers la chambre de combustion (20), caractérisé en ce qu'au moins l'une des soupapes de sortie de compresseur (42) se ferme par commande forcée et s'ouvre par l'intermédiaire d'une pression de compresseur qui s'établit dans le cylindre de compresseur (40) concerné.
  2. Procédé de fonctionnement selon la revendication 1, caractérisé en ce que le processus de fermeture de l'au moins une des soupapes de sortie de compresseur (42) est initié avant que le piston de compression (45) associé n'atteigne son point mort supérieur.
  3. Procédé de fonctionnement selon la revendication 2, caractérisé en ce que le processus de fermeture de l'au moins une des soupapes de sortie de compresseur (42) est initié au plus tard 5°, de préférence au plus tard 7° avant que le piston de compression (45) associé n'atteigne son point mort supérieur.
  4. Procédé de fonctionnement selon l'une quelconque des revendications 1 à 3, caractérisé en ce que l'au moins une des soupapes de sortie de compresseur (42) est fermée lorsque le piston de compression (45) associé atteint son point mort supérieur.
  5. Procédé de fonctionnement selon l'une quelconque des revendications 1 à 4, caractérisé en ce que l'au moins une des soupapes de sortie de compresseur (42) se ferme librement sous l'effet de sa propre masse, après l'initiation du processus de fermeture.
  6. Procédé de fonctionnement selon l'une quelconque des revendications 1 à 5, caractérisé en ce que l'au moins une des soupapes de sortie de compresseur (42) est libérée avant le processus de compression.
  7. Procédé de fonctionnement selon l'une quelconque des revendications 1 à 6, caractérisé en ce que l'au moins une des soupapes de sortie de compresseur (42) est entraînée mécaniquement.
  8. Procédé de fonctionnement selon l'une quelconque des revendications 1 à 7, caractérisé en ce que l'au moins une des soupapes de sortie de compresseur (42) est entraînée en synchronisation avec une (50) sortie du moteur à pistons axiaux (10).
  9. Moteur à pistons axiaux (10) comprenant une chambre de combustion (20) qui brûle un fluide combustible comprimé en continu et du carburant en un fluide de travail, pourvu de cylindres de travail (30), lesquels à l'aide de systèmes d'assemblage (25) à ouverture et fermeture cycliques sont reliés avec la chambre de combustion (20) et dans lesquels vont et viennent des pistons de travail (35), pourvu de cylindres de compresseur (40), dans lesquels vont et viennent des pistons de compresseur (45) qui sont entraînés par les pistons de travail (35) et pourvu d'au moins un conduit d'alimentation de fluide combustible (56), qui mène de soupapes de sortie de compresseur (42) des cylindres de compresseur (40) vers la chambre de combustion (20), au moins l'une des soupapes de sortie de compresseur (42) comportant une pièce de fermeture (71) qui s'ouvre en s'éloignant du cylindre de compresseur (40), caractérisé en ce que la pièce de fermeture (71) qui coopère avec une commande de soupape (60) s'ouvre contre un appui limiteur (73) et en ce que la commande de soupape (60) est libérable dans la direction d'ouverture (72) et/ou agit seulement à l'encontre de la direction d'ouverture (72) sur la pièce de fermeture (71).
  10. Moteur à pistons axiaux (10) selon la revendication 9, caractérisé en ce que la commande de soupape (60) est conçue en version mécanique.
  11. Moteur à pistons axiaux (10) selon la revendication 9 ou 10, caractérisé en ce que la commande de soupape (60) comporte un appui de pression (74) qui agit sur la pièce de fermeture (71).
  12. Moteur à pistons axiaux (10) selon la revendication 11, caractérisé en ce que lorsque la soupape de sortie de compresseur (42) est fermée, l'appui de pression (74) est écarté de la pièce de fermeture (71) de celle-ci.
  13. Moteur à pistons axiaux (10) selon la revendication 11 ou 12, caractérisé en ce que l'appui de pression (74) et l'appui limiteur (73) se trouvent sur un ensemble de commande (65) et sont conçus de préférence en monobloc l'un avec l'autre.
  14. Moteur à pistons axiaux (10) selon la revendication 13, caractérisé en ce que l'ensemble de commande (65) est déplaçable entre une position de charge et une position de décharge.
  15. Moteur à pistons axiaux (10) selon l'une quelconque des revendications 9 à 14, caractérisé en ce que l'appui de pression, l'appui limiteur et/ou l'ensemble de commande sont sur ressort.
  16. Moteur à pistons axiaux (10) selon l'une quelconque des revendications 9 à 15, caractérisé en ce que l'une des soupapes de sortie de compresseur (42) est une soupape champignon (80) dont le couvercle de soupape (81) est la pièce de fermeture (71) et sur la tige de soupape (82) de laquelle agit la commande de soupape (60) .
  17. Moteur à pistons axiaux (10) selon l'une quelconque des revendications 9 à 16, caractérisé en ce que la commande de soupape (60) comporte un disque à cames (61) ou un arbre à cames (62), qui sont synchronisés avec la sortie (50) du moteur à pistons axiaux (10).
  18. Moteur à pistons axiaux (10) selon l'une quelconque des revendications 9 à 17, caractérisé en ce que la commande de soupape (60) propulse également d'autres soupapes de sortie de compresseur (42) et/ou soupapes d'entrée de compresseur (41) t.
EP17703309.9A 2016-01-12 2017-01-09 Procédé permettant de faire fonctionner un moteur à pistons axiaux et moteur à pistons axiaux Active EP3402973B1 (fr)

Applications Claiming Priority (2)

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DE102016100439.1A DE102016100439A1 (de) 2016-01-12 2016-01-12 Verfahren zum Betrieb eines Axialkolbenmotors sowie Axialkolbenmotor
PCT/DE2017/100010 WO2017121427A1 (fr) 2016-01-12 2017-01-09 Procédé permettant de faire fonctionner un moteur à pistons axiaux et moteur à pistons axiaux

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EP3402973B1 true EP3402973B1 (fr) 2019-09-11

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US (1) US10450945B2 (fr)
EP (1) EP3402973B1 (fr)
JP (1) JP2019505718A (fr)
KR (1) KR20180100628A (fr)
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DE (2) DE102016100439A1 (fr)
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WO2019149297A1 (fr) * 2018-01-31 2019-08-08 GETAS GESELLSCHAFT FüR THERMODYNAMISCHE ANTRIEBSSYSTEME MBH Moteur à piston axial
US10598089B1 (en) 2018-11-07 2020-03-24 Hts Llc Opposed piston engine with parallel combustion chambers
US11128197B2 (en) * 2019-09-20 2021-09-21 Hts Llc Linear electric device having reciprocating movement linked to rotational movement of a shaped cam

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DE19909689B4 (de) 1999-03-05 2009-07-23 Rohs, Ulrich, Dr.-Ing. Kolbenmotor mit kontinuierlicher Verbrennung
EP1214506B1 (fr) * 1999-08-31 2005-08-10 Richard Patton Moteur a combustion interne dote d'un regenerateur et d'un allumage a air chaud
EP1386061B1 (fr) * 2001-05-10 2008-03-19 Philippe Schmidt Dispositif de commande de la cinematique de soupapes
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DE10360920B3 (de) * 2003-12-23 2005-09-22 Meta Motoren- Und Energie-Technik Gmbh Hubkolbenverdichter
CA2679423A1 (fr) * 2007-02-27 2008-09-04 The Scuderi Group, Llc Moteur a cycle divise avec injection d'eau
EP2711500B1 (fr) 2007-11-12 2016-02-10 GETAS Gesellschaft für thermodynamische Antriebssysteme mbH Moteur à pistons axiaux
FR2947590B1 (fr) 2009-07-02 2011-07-15 Snecma Moyeu d'helice
EP2456955A2 (fr) * 2009-07-24 2012-05-30 GETAS Gesellschaft für thermodynamische Antriebssysteme mbH Moteur à pistons axiaux, procédé pour faire fonctionner un moteur à pistons axiaux et procédé de réalisation d'un échangeur thermique d'un moteur à pistons axiaux
DE102011018846A1 (de) 2011-01-19 2012-07-19 GETAS GESELLSCHAFT FüR THERMODYNAMISCHE ANTRIEBSSYSTEME MBH Axialkolbenmotor sowie Verfahren zum Betrieb eines Axialkolbenmotors

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US20190017432A1 (en) 2019-01-17
CN108463618A (zh) 2018-08-28
EP3402973A1 (fr) 2018-11-21
JP2019505718A (ja) 2019-02-28
WO2017121427A1 (fr) 2017-07-20
KR20180100628A (ko) 2018-09-11
US10450945B2 (en) 2019-10-22
DE112017000339A5 (de) 2018-09-20
DE102016100439A1 (de) 2017-07-13

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