EP1232335B1 - Moteur a pistons libres - Google Patents

Moteur a pistons libres Download PDF

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Publication number
EP1232335B1
EP1232335B1 EP00981162A EP00981162A EP1232335B1 EP 1232335 B1 EP1232335 B1 EP 1232335B1 EP 00981162 A EP00981162 A EP 00981162A EP 00981162 A EP00981162 A EP 00981162A EP 1232335 B1 EP1232335 B1 EP 1232335B1
Authority
EP
European Patent Office
Prior art keywords
piston
pressure
control
free
engine
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.)
Expired - Lifetime
Application number
EP00981162A
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German (de)
English (en)
Other versions
EP1232335A1 (fr
Inventor
Rudolf SCHÄFFER
Jörg Dantlgraber
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.)
Bosch Rexroth AG
Original Assignee
Bosch Rexroth AG
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
Priority claimed from DE10026728A external-priority patent/DE10026728A1/de
Application filed by Bosch Rexroth AG filed Critical Bosch Rexroth AG
Publication of EP1232335A1 publication Critical patent/EP1232335A1/fr
Application granted granted Critical
Publication of EP1232335B1 publication Critical patent/EP1232335B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F01B11/00—Reciprocating-piston machines or engines without rotary main shaft, e.g. of free-piston type
    • F01B11/007—Reciprocating-piston machines or engines without rotary main shaft, e.g. of free-piston type in which the movement in only one direction is obtained by a single acting piston motor, e.g. with actuation in the other direction by spring means
    • 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
    • F02B71/00—Free-piston engines; Engines without rotary main shaft
    • F02B71/04—Adaptations of such engines for special use; Combinations of such engines with apparatus driven thereby
    • F02B71/045—Adaptations of such engines for special use; Combinations of such engines with apparatus driven thereby with hydrostatic transmission
    • 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
    • F02B75/02—Engines characterised by their cycles, e.g. six-stroke
    • F02B2075/022—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle
    • F02B2075/025—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle two

Definitions

  • the invention relates to a free-piston engine according to the preamble of claim 1.
  • a free-piston engine is a 2-stroke process working internal combustion engine, in which instead of a crank mechanism a hydraulic circuit with a piston pump is connected downstream as a drive train is.
  • the engine piston with a hydraulic cylinder connected, via which the generated during an engine cycle translational energy without the classic detour via the rotational movement of a crank drive directly to the hydraulic working medium is fed.
  • the downstream, storable hydraulic circuit is designed to take up the work cached and depending on the power requirement of a hydraulic Output unit, for example an axial piston machine.
  • the invention has for its object the generic To further develop the free-piston engine in such a way that the throttle losses reduced with a minimal expenditure on device technology are.
  • a hydraulic piston receiving Hydraulic cylinder and a switch valve to choose from hydraulic connection of the hydraulic cylinder with a high-pressure storage device or a low-pressure accumulator a valve arrangement switched with a control piston, via which the hydraulic piston with one from the outlet pressure at the changeover valve or from the pressure in the High-pressure accumulator-dependent pressure force can be applied.
  • the switching valve can be essential for one lower flow rate than in the prior art, so that short switching times can be achieved with minimal throttle losses are.
  • control piston is designed with a control edge, via which a connection to the high-pressure accumulator can be controlled is.
  • the control piston thus gets its switching energy via its own control edge from the high pressure storage device, so that the Quantity of pressure medium flowing through the changeover valve only for initiation the opening movement of the control piston is required and is minimal.
  • valve arrangement By interposing the valve arrangement according to the invention can minimize the amount of pressure medium flowing through the changeover valve so that the pressure drops when opening and closing the connection to the high pressure accumulator is minimal.
  • the cross-sectional area of the control piston becomes more advantageous Formed larger than that of the hydraulic piston, so that a comparative due to the chosen gear ratio small stroke of the control piston is sufficient for sufficient acceleration of the engine piston.
  • the opening movement of the control piston is limited by a stop. After emergence of the control piston on this stop there is no further pressure build-up in the hydraulic cylinder, so that no further acceleration of the Engine piston takes place. That is, according to the present invention, Technically required closing of the changeover valve by opening of the control piston replaced on the stop, so that when Closing the changeover valve throttle losses practically cannot occur.
  • This stop can be made adjustable to adjust the maximum speed of the engine piston can.
  • the charging of the high-pressure storage device during the combustion stroke of the engine piston takes place via a high pressure channel, in a check valve is provided.
  • This high pressure channel can in one embodiment of the free-piston engine according to the invention Opened or closed via a further control edge of the control piston be so that the loading process from the position of the spool is dependent.
  • a directional control valve can be provided via one the bypass line provided in the check valve can be controlled or controlled.
  • the hydraulic piston can be operated by this directional control valve during the compression stroke directly with the pressure in the High-pressure storage device are acted upon during the control piston initially remains in its closed position. After the Hydraulic piston a predetermined acceleration or The bypass line is activated, so that the further movement of the hydraulic piston in the above Is determined by the control piston.
  • the directional control valve can optionally be provided with a switch position in which the high-pressure duct can be connected to the tank, so that the free piston practically without counter pressure in the direction of its inner Dead center is mobile.
  • control piston is designed as a stepped piston, the in the opening direction effective ring area via the low pressure channel with a Check valve is connected to the low pressure accumulator.
  • the ring face of the control piston becomes the closing direction with the pressure in the hydraulic cylinder of the hydraulic piston and through the force of the control spring is applied.
  • pressure medium during the entire opening movement of the control piston sucked out of the low pressure accumulator.
  • the annular space of the stepped piston is connected via a pressure channel connected to the high pressure accumulator, so that when the Control piston charging the high pressure storage device takes place.
  • the rear peripheral edge of the larger face of the step-like trained control piston is preferably designed such that this shortly before the control piston hits its valve seat opens the high pressure channel, so that the kinetic Energy of the engine or hydraulic piston for loading the high-pressure storage device is exploited.
  • the High-pressure storage device with a medium-pressure accumulator and one Execute high-pressure accumulator the one required for the compression stroke Energy is taken from the medium pressure accumulator. This is to the high-pressure accumulator via a suitable valve device connected and kept at a pressure level that is below the minimum level of the high-pressure accumulator. If exceeded a limit pressure can be the pressure in the medium pressure storage to the low pressure storage be dismantled.
  • the hydraulic piston is designed as a differential piston, whereby an annular space delimited by the differential piston during the expansion stroke and the annulus of a stepped spool during the compression stroke connectable to the low pressure accumulator are.
  • the free-piston engine according to the invention can be particularly compact train when the transmission valve assembly is coaxial with the engine piston axis is executed.
  • the valve arrangement is preferably used as a logic valve or Slide valve executed.
  • Figure 1 shows a highly simplified, schematic representation of a free-piston engine 1 according to the invention.
  • This has a motor housing 2, through which at least one combustion cylinder 4 (right of the dash-dotted line in FIG. 1) and a hydraulic cylinder 6 (to the left of the dash-dotted vertical line).
  • a Engine piston 10 out through which the cylinder bore 8 into a combustion chamber 16 and an inlet space 18 is divided.
  • the Engine piston 10 In the illustrated Waiting position of the free piston engine 1 is the Engine piston 10 at its inner dead center (IT), with an exhaust port 14 is turned on, so that combustion gases from the combustion chamber 16 can flow.
  • Fresh gas is supplied via an inlet channel opening into the rear inlet space 18 20 with inlet valve.
  • the inlet space 18 and the combustion space 16 are connected to one another by means of an overflow channel 22.
  • the injection of the fuel into the combustion chamber 16 takes place via an injection valve 24 in the cylinder head of the combustion cylinder 4.
  • the free-piston engine 1 corresponds to a conventional two-stroke engine, so that further explanations are unnecessary.
  • the engine piston 10 carries a hydraulic piston 26, the Diameter significantly smaller than that of the engine piston 10 is. This hydraulic piston 26 dips into a stepped axial bore 28 of the hydraulic cylinder 6 a.
  • a radial opens in the axial bore 28 of the hydraulic cylinder arranged high pressure channel 30, which with a check valve 32 a high pressure accumulator 34 is connected.
  • a low pressure accumulator 36 for example a pressure medium tank, via a low pressure channel 38 and a check valve 40 with the connected by the axial bore 28 limited space.
  • the check valve 40 prevents a backflow of the in the axial bore 28th received pressure medium to the low pressure accumulator 36, while the Check valve 32 a backflow of the high pressure accumulator 34th Prevented pressure medium in the axial bore 28 prevented.
  • the hydraulic piston 26 passes through the axial bore 28 and plunges into a control room 42, in which one designed as a logic piston Control piston 44 is guided. This is by means of a control spring 46 biased against a valve seat 48.
  • Control room 42 opens a pressure channel 50 which on the one hand with the High pressure accumulator 34 and on the other hand with an input port P a changeover valve 52 is connected.
  • a pilot space adjoining the end face of the control piston 44 54 is via a control channel 56 with an output or Working port A of the switching valve 52 connected.
  • This is as electrically or electrohydraulically controlled 3/2-way valve, that can be controlled via the motor control, not shown is.
  • P the changeover valve 52 also has a tank connection T, which is connected to a tank or the low pressure accumulator 36.
  • the control piston 44 sits in the basic position of the free-piston engine 1 on the valve seat 48 so that the pilot chamber 54 and the Control room 42 are locked against each other.
  • the control piston 44 of the logic valve by the force of the control spring 46 and by the pressure in the axial bore 28 and thus in the back Control chamber 42 acts in the closing direction while it is in the opening direction is acted upon by the pressure in the pilot control chamber 54.
  • the changeover valve 52 is over the engine control is brought into a second switching position in which according to Figure 2, the pressure port P connected to the working port A. are so that pressure medium from the high pressure accumulator 34 via the Pressure channel 50 and the control channel 56 fed into the pilot space 54 becomes. That is, the end face of the control piston 44 is with High pressure applied while low pressure is still in the control room 42 is effective. Due to the pressure difference, the control piston 44 of its valve seat 48 is lifted and over by the peripheral edge of the control piston 44 formed control edge 58 the connection between the pilot room 54 and the pressure channel 50 turned on.
  • the control piston thus gets its acceleration energy in dependence from the control edge opening, through which the end face of the control piston 44 acted upon directly by the pressure in the high-pressure accumulator 34 becomes. Due to the resulting axial movement of the Control piston 44, the hydraulic piston 26 is accelerated and corresponding to the engine piston 10 in the illustration according to FIG moved to the right - the outlet channel 14 and the overflow channel 22 are controlled by the engine piston 10 in the combustion chamber 16 existing fresh gas is compressed.
  • the check valve 40 prevents that during the Control piston movement pressure medium from the axial bore 28 in the low pressure accumulator 36 flows out.
  • the control piston 44 runs after a predetermined Route D to a stop 60 in the control room 42.
  • the on its maximum speed accelerated engine piston 10 moves due to its inertia further towards the AT, whereby by the negative pressure arising in the axial bore 28 from pressure medium the low pressure accumulator 36 via the check valve 40 and the low pressure channel 38 is sucked in.
  • the position of the stopper 60 is chosen so that the kinetic energy of the engine piston 10 at the time of the control piston 44 reaching the stop 60 is sufficient, around the engine piston 10 against the polytropically increasing compression pressure of the fresh gas in the combustion chamber 16 towards the AT move.
  • the engine piston 10 is affected by the compression pressure slowed down and comes to a standstill in the AT.
  • Logic valve can of course also be used a slide valve can be used.
  • the axis is of the logic valve coaxial with the axis of the combustion cylinder.
  • other relative positions can also be implemented, where the hydraulic connection to the hydraulic cylinder 6 is guaranteed.
  • FIG. 8 shows an embodiment of a free-piston engine shown, in which the hydraulic or working piston 26 via a Directional valve 70 can be acted upon directly with the high pressure in the high pressure accumulator 34 is.
  • the basic structure of the free-piston engine shown in FIG. 8 corresponds to that shown in FIG. 1 Embodiment, so that only the newly added in the following Components are described.
  • the check valve 32 are bypassed via a bypass line 72 into which the directional valve 70 is switched.
  • the directional control valve is designed with three switching positions, whereby in the switching position a, the bypass line 72 is open and a connection locked to the tank. In the basic position 0 is both the connection to the tank and the bypass line 72 are blocked.
  • In the switching position marked with b can be the area of the high pressure duct 30 upstream of the check valve 32 with the tank are connected so that the pressure in the axial bore 28 to the tank is degradable.
  • the switching valve 52 in the Working position brought so that the left end face of the control piston 44 is acted upon by the pressure in the high-pressure accumulator 34.
  • the directional control valve 70 is brought into the switching position shown a is bypassed in the check valve 32 so that the pressure in the hydraulic accumulator 34 also in the axial bore 28 and thus on the Rear of the control piston 44 acts. Because of the hydraulic The balance of forces then becomes the control piston 44 by the force the control spring 46 biased into its closed position.
  • the hydraulic piston 26 accelerates and thus the compression stroke of the engine piston 10 initiated.
  • the directional control valve 70 is in its 0 marked Brought locking position, so that the bypass line 72 is blocked and the pressure medium supply from the high pressure accumulator 34 into the axial bore 28 is prevented.
  • the control piston 44 then lifts from its Valve seat 48 from, so that the further movement of the engine piston 10 is determined by the axial movement of the control piston 44.
  • This variable Initial speed may vary depending on the operating conditions and the opening stroke and the opening time by activation of the directional control valve 70 can be adapted.
  • the directional control valve 70 must be of a correspondingly large size Nominal size.
  • the directional control valve 70 can be made very small, so that due to the low Pressure fluid flows a fast switching and low losses occur in the area of the directional control valve 70.
  • switch position b is the axial bore 28 is relieved of pressure so that the hydraulic piston 26 or the engine piston 10 in the event of a misfire after switching can be moved further to the inner dead center (IT).
  • control piston 44 as a stepped piston is formed, with a radially widened collar 74 in a correspondingly enlarged section 76 of the control piston 44 receiving control room 78 is formed.
  • the high pressure channel 30 opens in the closed position of the control piston 44 in that of the larger end face of the control piston 44 limited space 78, while another pressure channel 80 in the of the Annular end face of the stepped piston 44 delimits the annular space 82.
  • This pressure channel 80 is connected to the high pressure accumulator 84, whereby a check valve 84 flows from the high pressure accumulator 34 in the annular space 82 similar to that arranged in the high-pressure duct 30 Check valve 32 prevented.
  • this can Check valve 32 are bypassed via a bypass line 72 in which is connected to a metering valve 86, its function in principle corresponds to the directional control valve 70 from the exemplary embodiment described above.
  • the low-pressure duct that connects to the low-pressure accumulator 36 38 also opens into the annular space 32, so that the Control piston 44 by the pressure in the low-pressure accumulator 36 in the opening direction is acted upon.
  • the force of the control spring 46 must are accordingly designed such that they control spool 44 in the Basic position against the pressure in the low-pressure accumulator 36 against the Valve seat 48 presses.
  • the changeover valve 52 is used to initiate the compression stroke brought into the working position so that the control piston 44 from Valve seat 48 lifts off and the hydraulic piston 26 and the engine piston 10 are accelerated.
  • the control piston 44 is pressure medium from the low pressure accumulator 36 from the beginning sucked in via the low-pressure duct 38, so that the opening movement is supported by the pressure in the low pressure accumulator 36.
  • the stop is 60 formed at such an axial distance from the control piston 44, that this has no effect. That is, when operating the free-piston engine 1, the control piston 44 is in its opening direction seen end position by a balance of forces and not by a Accumulated on a stop stopped. This end position of the control piston 44 is reached when the engine piston 10 its outer Dead center reached.
  • FIG. 10 shows a variant of the embodiment shown in FIG. 9, in which the working or hydraulic piston 26 as a differential piston is executed, the radially recessed part is oriented towards the engine piston 10.
  • the radially reset Part of the hydraulic piston 26 forms one with the axial bore 28 another annular space 88, which via a low pressure line 90 and a Check valve 92 with the low pressure accumulator 36 and a Connection channel 94 and a check valve 96 with that of the larger End face of the control piston 44 limited space 78 connected is.
  • this will be in the wider annulus 88 located pressure medium via the connecting channel 94 and that Check valve 96 displaced to room 78.
  • FIG 11 is an embodiment shown, that with regard to the basic structure that shown in Figure 7 Embodiment corresponds.
  • the one shown in FIG Variant is next to the high pressure accumulator 34 and the low pressure accumulator 36 a further medium pressure accumulator 98 is provided which is connected to the pressure channel 50, so that the pressure in FIG left end face of the control piston 44 by the pressure in the medium pressure accumulator 98 is acted upon when the holding valve 52 is in its Working position is brought.
  • the medium pressure accumulator 98 is over a line 100 with a control valve 102 with the downstream of the Check valve 32 located part of the high pressure channel 30 connected.
  • the medium pressure reservoir 98 is a further line 104 and a further control valve 106 with connected to the low pressure accumulator 36.
  • the pressure level of the medium pressure accumulator 98 lies between that of the high pressure accumulator 34 and the low pressure accumulator 36.
  • the two control valves 102 and 106 are closed, so that when switching the switching valve 52 in its Working position the end face of the control piston 44 with the pressure is acted upon in the medium pressure accumulator 98. That is, the acceleration of the engine piston 10 is essentially from the pressure in the medium pressure accumulator 98 dependent.
  • This pressure can be controlled appropriately of control valves 102, 106 maintained at a constant level become.
  • control valve 102 When the pressure in the medium pressure accumulator 98 drops below predetermined level, the control valve 102 is opened so that the medium pressure accumulator 98 is charged via the high pressure accumulator 34 becomes. If the predetermined pressure level is exceeded, the other becomes Control valve 106 opened so that pressure to Low pressure accumulator 36 can be dismantled.
  • a free-piston engine whose engine piston is in the compression direction Power can be applied via a hydraulic cylinder is. This can be done via a changeover valve with the pressure in a high pressure storage device or in a low pressure storage device get connected.
  • a valve arrangement with a control piston provided, through the control edge a connection to High-pressure storage device is controllable.

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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)

Claims (15)

  1. Moteur à piston libre, comportant un piston (10) du moteur et un piston hydraulique (26) qui coopère avec ce dernier et peut être chargé, par l'intermédiaire d'une soupape de commutation (52), avec la pression régnant dans un dispositif à accumulateur à haute pression (34) ou dans un accumulateur à basse pression (36), caractérisé en ce qu'entre le piston hydraulique (26) et la soupape de commutation (52) est disposé un dispositif à soupapes (44, 46, 48) comportant un piston de commande (44), et dans lequel une liaison avec le dispositif à accumulateur à haute pression (34) peut être commandée par l'intermédiaire d'une arête de commande (58) du piston de commande (44), et le piston de commande (44) est chargé dans le sens de la fermeture par la pression dans le cylindre hydraulique (6) et par la force d'un ressort de commande (46) et, dans le sens de l'ouverture, par la pression de sortie de la soupape de commutation (52) ou par la pression du dispositif à accumulateur à haute pression (34).
  2. Moteur à piston libre selon la revendication 1, dans lequel la surface du piston de commande (44) est supérieure à la surface en coupe transversale, active du point de vue hydraulique, du piston hydraulique (26).
  3. Moteur à piston libre selon la revendication 1 ou 2, dans lequel la course du piston de commande dans le sens de l'ouverture est limitée, avant la fin de la course du piston hydraulique (26), par une butée (60).
  4. Moteur à piston libre selon la revendication 3, dans lequel la butée (60) est réglable.
  5. Moteur à piston libre selon l'une des revendications précédentes, dans lequel le cylindre hydraulique (6) peut être relié par l'intermédiaire d'un canal à haute pression (30) au dispositif à accumulateur à haute pression (34) et par l'intermédiaire d'un canal à basse pression (38) à l'accumulateur à basse pression (36), et une soupape antiretour respective (32, 34) empêchant un reflux depuis l'accumulateur à haute pression (34) ou dans l'accumulateur à basse pression (36).
  6. Moteur à piston libre selon la revendication 5, dans lequel la soupape antiretour (32) disposée dans le canal à haute pression peut être contournée au moyen d'une canalisation de by-pass (72) qui peut être contournée ou bloquée au moyen d'une soupape droite (70, 86).
  7. Moteur à piston libre selon la revendication 6, dans lequel la soupape droite (70) possède une position de commutation (b), dans laquelle la canalisation de by-pass (72) peut être reliée au réservoir.
  8. Moteur à piston libre selon l'une des revendications 5 à 7, dans lequel le canal haute pression (30) peut être commandé par l'intermédiaire d'une seconde arête de commande (62) du piston de commande (44).
  9. Moteur à piston libre selon l'une des revendications 5 à 8, dans lequel le piston de commande (44) est un piston étagé et l'espace annulaire (82) délimité par une face frontale annulaire du piston de commande (44) peut être relié aussi bien à l'accumulateur à basse pression (36) qu'au dispositif à accumulateur à basse pression (34).
  10. Moteur à piston libre selon la revendication 9, dans lequel le canal de pression (4) débouche dans une chambre (78) délimitée par la surface frontale plus étendue du piston de commande (44).
  11. Moteur à piston libre selon l'une des revendications précédentes, dans lequel le dispositif à accumulateur à haute pression (34, 98) comporte un accumulateur moyenne pression (98) et un accumulateur à haute pression (34), qui peuvent être reliés entre eux au moyen d'une canalisation (100) et d'une soupape de commande (102), la surface frontale, qui agit dans le sens de l'ouverture, du piston de commande (44) pouvant être chargée par la pression régnant dans l'accumulateur à moyenne pression (34).
  12. Moteur à piston libre selon la revendication 11, dans lequel l'accumulateur à moyenne pression (94) peut être relié à l'accumulateur à basse pression (86) par l'intermédiaire d'une autre canalisation de liaison (104) et d'une autre soupape de commande (106).
  13. Moteur à piston libre selon les revendications 5 et 11 ou 12, dans lequel le canal à haute pression (30) est relié à l'accumulateur à haute pression (34).
  14. Moteur à piston libre selon l'une des revendications précédentes, caractérisé en ce que le dispositif à soupapes de transmission (44, 46, 48) est monté coaxialement à l'axe du piston du moteur.
  15. Moteur à piston libre selon l'une des revendications précédentes, caractérisé en ce que le dispositif à soupapes de transmission (44, 46, 48) est agencé sous la forme d'une soupape logique ou d'une soupape à tiroir.
EP00981162A 1999-11-24 2000-11-06 Moteur a pistons libres Expired - Lifetime EP1232335B1 (fr)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
DE19956547 1999-11-24
DE19956547 1999-11-24
DE10026728 2000-05-30
DE10026728A DE10026728A1 (de) 1999-11-24 2000-05-30 Freikolbenmotor
PCT/DE2000/003886 WO2001038706A1 (fr) 1999-11-24 2000-11-06 Moteur a pistons libres

Publications (2)

Publication Number Publication Date
EP1232335A1 EP1232335A1 (fr) 2002-08-21
EP1232335B1 true EP1232335B1 (fr) 2004-02-04

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EP00981162A Expired - Lifetime EP1232335B1 (fr) 1999-11-24 2000-11-06 Moteur a pistons libres

Country Status (3)

Country Link
EP (1) EP1232335B1 (fr)
JP (1) JP2003524727A (fr)
WO (1) WO2001038706A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102007040361A1 (de) 2007-08-27 2009-03-05 Muller, Katherina Freikolbenmotor mit variabler Verdichtung
CN104775901A (zh) * 2015-04-02 2015-07-15 吉林大学 基于内燃机和直线液压泵的动力装置

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6582204B2 (en) * 2001-09-06 2003-06-24 The United States Of America As Represented By The Administrator Of The U.S. Enviromental Protection Agency Fully-controlled, free-piston engine
DE102007016517A1 (de) 2007-04-05 2008-10-09 Muller, Katherina Hydrostatischer Fahrantrieb
US20130074960A1 (en) * 2011-09-22 2013-03-28 Gregory S. Sundheim Portable, refrigerant recovery unit
JP2013256886A (ja) * 2012-06-12 2013-12-26 Toyota Central R&D Labs Inc フリーピストン式発電機

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NL160632C (nl) * 1968-10-08 1979-11-15 Ir Theodorus Gerhardus Potma Vrije-zuigerpompinstallatie.
DE2715896C2 (de) * 1977-04-09 1984-01-19 Messerschmitt-Bölkow-Blohm GmbH, 8000 München Flüssigkeitspulskanone
AU531082B2 (en) * 1977-05-12 1983-08-11 SE. CA. societe ammyme SOCIETE D ENTERPRISES COMMERCIALES ET AERONAUTIQUES Opposed piston swash-plate motor/pump
US4166410A (en) * 1977-09-26 1979-09-04 Edward Bleiweiss Pneumatic motor
AT384658B (de) * 1981-11-16 1987-12-28 Brandl Dipl Ing Gerhard Einrichtung in einem drucksystem
DE4024591A1 (de) 1990-08-02 1992-02-06 Gerhard Brandl Freikolbenmotor
NL9101933A (nl) * 1991-11-19 1993-06-16 Innas Bv Vrije-zuigermotor met fluidumdrukaggregaat.

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102007040361A1 (de) 2007-08-27 2009-03-05 Muller, Katherina Freikolbenmotor mit variabler Verdichtung
CN104775901A (zh) * 2015-04-02 2015-07-15 吉林大学 基于内燃机和直线液压泵的动力装置

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EP1232335A1 (fr) 2002-08-21
JP2003524727A (ja) 2003-08-19
WO2001038706A1 (fr) 2001-05-31

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