EP1282766B1 - Moteur a piston libre - Google Patents

Moteur a piston libre Download PDF

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Publication number
EP1282766B1
EP1282766B1 EP01944926A EP01944926A EP1282766B1 EP 1282766 B1 EP1282766 B1 EP 1282766B1 EP 01944926 A EP01944926 A EP 01944926A EP 01944926 A EP01944926 A EP 01944926A EP 1282766 B1 EP1282766 B1 EP 1282766B1
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EP
European Patent Office
Prior art keywords
piston
pressure
valve
engine
free
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
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EP01944926A
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German (de)
English (en)
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EP1282766A1 (fr
Inventor
Rudolf SCHÄFFER
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Bosch Rexroth AG
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Bosch Rexroth AG
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Priority claimed from DE10120196A external-priority patent/DE10120196A1/de
Application filed by Bosch Rexroth AG filed Critical Bosch Rexroth AG
Publication of EP1282766A1 publication Critical patent/EP1282766A1/fr
Application granted granted Critical
Publication of EP1282766B1 publication Critical patent/EP1282766B1/fr
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    • 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

Definitions

  • the invention relates to a free-piston engine according to the preamble of claim 1.
  • a free-piston engine is basically a 2-stroke process working internal combustion engine, in which instead of a crank mechanism with a hydraulic circuit Piston pump is connected downstream as a drive train. To the engine piston is connected to a hydraulic cylinder, over which the generated during a motor working cycle translational energy without the classic detour About the rotation of a crank mechanism directly to hydraulic working fluid is supplied.
  • the downstream, storable hydraulic circuit is such designed to caching the delivered work and depending on the power requirements of a hydraulic Output unit, for example an axial piston machine supplies.
  • a free-piston engine is the described generic type, which also as Brandl free piston engine is known. This concept is done the compression movement of the engine piston by interaction with a hydraulic piston via a 2/3-way diverter valve with a high-pressure accumulator or a Low pressure accumulator is connectable. At the beginning of the compression stroke an acceleration of the engine piston takes place by applying the hydraulic cylinder with the Pressure in the high-pressure accumulator. Upon reaching a predetermined Engine piston speed is the hydraulic cylinder via the changeover valve with the low-pressure accumulator connected, so that the further compression stroke of the Engine piston against the effective force from the compression pressure of the working gas.
  • the working gas After reaching of the outer dead center (AT), the working gas is ignited and the engine piston toward the inner dead center (IT) accelerates.
  • IT inner dead center
  • the connection to the High-pressure accumulator controlled so that the engine piston braked and its kinetic energy in potential converted to hydraulic energy and the High-pressure accumulator is loaded.
  • the switching times of the changeover valve are in the millisecond range, arise when connecting and controlling the connection to High-pressure accumulator in the switching valve throttling losses, the on the order of 10% of the engine power can.
  • This INNAS free-piston engine is the hydraulic piston designed as a stepped piston and has two active surfaces, of which the first larger in a compression cylinder is arranged while the second smaller limits a pump work space or working cylinder. The larger area becomes with the pressure in a compression cylinder acted upon while the working cylinder via check valves with a high-pressure accumulator or a low pressure accumulator is connectable.
  • This INNAS free piston engine has one opposite the Brandl free piston engine much more complex structure, so that the device technology Effort is relatively high.
  • the invention is based on the object to develop the generic free-piston engine in such a way that minimizes the device complexity is.
  • the free-piston engine according to the invention has a stepped Piston, whose larger face in the compression cylinder and its smaller end face in the working cylinder is guided. Both the working cylinder and the compression cylinder are to initiate the compression stroke or for charging during the expansion stroke connectable to a common high-pressure accumulator.
  • this variant has the advantage that only two Accumulator, i. a low pressure accumulator and a High-pressure accumulator sufficient to operate while the generic INNAS free-piston engine three pressure accumulator must be present with the associated lines.
  • the System can thus be much more compact with less be built device technical effort, so that the cost of the free-piston engine over the initially described solutions are reduced.
  • the hydraulic piston or the engine piston has a dead center position, self-acting due to pressure conditions established. At high pressure in the high pressure accumulator must the Engine pistons during the expansion stroke against this working high pressure, so that due to the balance of forces the expansion stroke earlier than at a lower one Pressure in the high-pressure accumulator is terminated. by virtue of this shifted dead center is in the next cycle the available during the compression stroke Acceleration distance correspondingly shorter. Because the pressure in the high-pressure accumulator during the compression stroke the larger end face acts, this shorter acceleration distance balanced by the higher pressure, so that the engine piston is about the same Speed is accelerated, as at a lower speed Pressure with a longer acceleration distance. The the Motor piston supplied energy remains about the same that energy, that at a lower one Pressure of the high-pressure accumulator and a longer one for it Acceleration distance is supplied.
  • Another significant advantage of the invention Solution is that the suction of pressure medium during the return movement of the hydraulic piston of his Dead center practically over the entire path of the hydraulic piston takes place while at the beginning described Brandl free-piston engine, the suction of the pressure medium the low pressure accumulator only after reaching a predetermined acceleration of the hydraulic piston took place.
  • the pressure fluid out of the cylinder to the High-pressure accumulator returned - the compression direction effective piston area thus corresponds to the Difference surface between the larger face and the Ring surface of preferably designed as a differential piston Piston.
  • a version with differential piston builds significantly shorter than the INNAS free piston engine, as in the inventive solution of the compression cylinder both for pressurization during the compression stroke as well as to load the high-pressure accumulator is used.
  • a differential cylinder can also be Pistons are used with a piston collar whose Piston rod in the working cylinder and its piston section with larger diameter in the compression cylinder is guided.
  • To initiate the compression stroke is the annular end face of the stepped piston with the high-pressure accumulator connected, taking on the smaller end face the piston rod has the pressure in the low-pressure accumulator, so that the compression stroke by the suction of the pressure medium is supported from the low-pressure storage.
  • the stepped piston provided with a control edge over which during the compression stroke a connection to the high-pressure accumulator is alsêtbar, so that after a predetermined Acceleration section of the hydraulic piston pressure medium bypassing the start valve directly from the high-pressure accumulator fed into the compression cylinder becomes. Since thus the main pressure medium flow does not have the Start valve must be able to throttle losses be lowered further.
  • a directional control valve via which one the start valve surrounding start line can be opened, so that a large area cross-section provided is to close the free piston when starting the engine accelerate. This directional valve remains during the Operation of the free-piston engine open.
  • the directional control valve as a logic valve with a graduated logic piston is executed.
  • a smaller area cross section of the Logic piston is via an upstream release valve with the pressure in the high-pressure accumulator acted upon while the larger area cross section of the logic piston with the pressure in the compression cylinder is applied.
  • the release valve is preferably as a 3/2-way valve executed, over which the smaller area cross section optionally with the pressure in the high-pressure accumulator or with the Tank pressure can be acted upon.
  • the piston retraction assembly has a check valve, in the opening position of the working cylinder with the Compression cylinder is connected.
  • the piston retraction assembly further has a piston return valve, about the the compression cylinder with the tank is connectable.
  • the check valve is in the hydraulic piston integrated.
  • This solution has the advantage that due the short communication paths between the compression cylinder and the working cylinder, the throttle losses are minimal. Furthermore, this arrangement is very compact constructed, since in the housing no own recordings for the piston retraction assembly must be provided. The Compactness can be further improved, although that Check valve is integrated in the hydraulic piston.
  • the stepped piston can be active in a fault Move towards the outer dead center when its in Direction outer dead center effective ring end face with the pressure in the high-pressure accumulator can be acted upon, wherein at least one of the counteracting surfaces of the Stepped piston is relieved of pressure.
  • the return is particularly easy if the engine piston-side annular end face with a larger area than the one in the direction internal dead center effective annular face of the stepped piston is executed.
  • bypass line can be provided over the local check valve is bypassed. These Bypass line can be shut off via a metering valve.
  • Fig. 1 shows a schematic representation of a first Embodiment of a free-piston engine 1.
  • This has a motor housing 2, in the combustion cylinder 4 a Engine piston 6 is guided.
  • This is in active connection with a coaxially arranged hydraulic piston 8, the in an axial bore 10 is guided.
  • An annular end face 12 of the hydraulic piston 8 limits a working cylinder 14, while the larger end face 16 of the hydraulic piston 8 limits a compression cylinder 18.
  • a pressure channel 20 and a low pressure channel 22 In the working cylinder 14 open a pressure channel 20 and a low pressure channel 22. The latter is with a low pressure accumulator 24 connected, wherein a pressure medium flow from the working cylinder 14 to the low pressure accumulator 24th is prevented by a check valve 26.
  • the compression cylinder 18 is via a high pressure passage 28 connected to a high-pressure accumulator 30, wherein the high pressure passage 28 via a designed as a 2/2-way valve Start valve 32 on or is zuu Kunststoffbar.
  • a high pressure passage 28 connected to a high-pressure accumulator 30, wherein the high pressure passage 28 via a designed as a 2/2-way valve Start valve 32 on or is zuu Kunststoffbar.
  • the Pressure channel 20 opens into the high pressure passage 28 a.
  • another check valve 34 is a flow of Pressure medium from the high-pressure accumulator 30 in the working cylinder 14 prevented.
  • the combustion cylinder 4 is provided with an outlet channel Provided 36, via the exhaust gas from the engine piston. 6 limited combustion chamber 38 can be dissipated.
  • the hydraulic piston 8 facing the back of the Engine piston 6 defines an inlet space 40, which in the shown inner dead center of the engine piston. 6 has its minimum volume.
  • the inlet space 40 is through an overflow channel 42 with the combustion chamber 38th connected.
  • the fresh air can during the compression stroke of the Engine piston 6 via an inlet channel 44 with an inlet valve 46 are supplied.
  • the ignition of the free-piston engine is done by injecting fuel over an injection valve 48 opening in the combustion cylinder.
  • the start valve 32 open, so that the high-pressure accumulator 30 with the compression cylinder 18 is connected.
  • the pressure medium located in the working cylinder 14 is via the check valve 34 and the pressure line 20 back into the pressure channel 28 promoted. that is, the end face 16 and the annular end face 12 of the hydraulic piston 8 are with the pressure in the high-pressure accumulator 30th acted upon, so that the surface of the piston rod corresponding end face in the direction of the outer dead center (AT) is effective.
  • the connection to the low-pressure accumulator 24 is locked by the check valve 26.
  • FIG. 4 shows a free-piston engine during the compression stroke, the above-described embodiment by a device for dosing the compression energy is supplemented.
  • This device has a bypass line 50, through which the check valve 26 in the low-pressure channel 22 is bypassed.
  • the bypass line 50 is a designed as a 2/2-way valve metering valve 52nd provided that in its blocking position, the bypass line 50 locks.
  • shut off metering valve 52 corresponds to in Figure 4 illustrated embodiment of that the above drawings.
  • the working space 14 directly to the low-pressure accumulator 24th be connected so that the annular end face 12 with the Pressure in the low pressure accumulator 24 is acted upon.
  • the hydraulic piston 8 must during the compression stroke not accelerated against the pressure in the high-pressure accumulator 30 so that, for example, to the beginning of the compression stroke the supplied compression energy increases can be.
  • FIG. 6 shows an exemplary embodiment of a free-piston engine 1, in which the hydraulic piston 8 as a stepped piston with two piston rods 56, 58 and a collar 60 is executed.
  • the Working cylinder 14 through the end face 62 of FIG 6 right piston rod 56 limited.
  • the compression cylinder 18 is facing through the piston rod 56 Ring end face 64 of the annular collar 60 limited.
  • the piston rod 58 and the left annular surface 66 of the hydraulic piston 8 define a ring cylinder 68 of the hydraulic piston 8 receiving axial bore 10.
  • the low-pressure accumulator 24 is like the embodiment described above via a low pressure channel 22 and a Check valve 26 with the adjacent to the piston rod 56 Working cylinder 14 connected. In this working cylinder 14 also opens with the high-pressure accumulator 30 connected pressure channel 20 with the check valve 30th
  • the high pressure accumulator 30 is further on the High-pressure channel 28 with the right through the annular end face 64 limited compression cylinder 18 connected.
  • the start valve 32 is arranged in the high pressure passage 28, the start valve 32 is arranged.
  • the start valve 32 can be bypassed via a bypass channel 72, in which a check valve 70 is arranged, the one Backflow from the pressure medium from the compression cylinder 18 to the high-pressure accumulator 30 allows.
  • a pressure line 74 can be opened, the downstream of the check valve 70 in the High-pressure channel 28 opens.
  • the start valve 32 To initiate the compression stroke, the start valve 32 from its locked position into its passage position brought so that the high-pressure accumulator 30 via the pressure channel 28 is connected to the compression cylinder 18 is.
  • Pressure of the hydraulic piston 8 By acting on the annular end face 64 Pressure of the hydraulic piston 8 is accelerated, the engine piston 6 moved to his AT and those in the combustion cylinder 38 existing fresh air compressed.
  • the peripheral edge of the annular end surface 64 controls the Pressure line 74, so that the pressure medium directly under Bypassing of the starting valve 32 in the compression cylinder 18 can occur. This allows the throttle loss minimize over the start valve 32, since the pressure medium only at the beginning of the compression stroke, the start valve 32nd flows through.
  • the compression stroke is pressure medium from the low pressure accumulator 24 via the low pressure channel 22 and the opening check valve 26 in the Working cylinder 14 sucked.
  • the engine piston 6 is by the increasing compression pressure in the combustion chamber 38 braked in the AT.
  • the start valve 32 is closed and via the injection valve 48 fuel injected and thereby ignited the resulting mixture.
  • the engine piston 6 and the hydraulic piston 8 are accelerated from AT to IT, being at the return movement of the hydraulic piston 8, the pressure line 74 controlled becomes.
  • the expansion movement takes place against the pressure in the working cylinder 14 and in the compression cylinder 18, so that when open check valve 34 of the high-pressure accumulator 30 via the pressure channel 20 and via the high-pressure channel 28 is loaded.
  • FIG. 7 shows a variant of that shown in FIG Free-piston engine with a stepped piston Hydraulic piston 8, this with a piston retraction system is equipped, over that in case of a fault the engine piston 6 and the hydraulic piston 8 in their IT position are traceable.
  • the piston retraction system has a the high pressure accumulator 30 connected return channel 76, the in the annular cylinder 68 opens.
  • the connection between the ring cylinder 68 and the high-pressure accumulator 30 can via a designed as a 2/2-way valve switching valve 78th be shut off or opened.
  • the pressure in the working cylinder 14 can via a Working cylinder 14 with the downstream of the check valve 26 arranged part of the low-pressure channel 22nd connecting discharge channel 80 are degraded. This is on a control valve 82 up or zuu Kunststoffbar. that is, at the initiation of the piston retraction becomes the control valve 82 brought into its open position, so that the Pressure fluid during the return movement of the hydraulic piston. 8 from the working cylinder 14 via the discharge channel 80 in the low-pressure accumulator 24 is fed.
  • the annular end face 66 of the hydraulic piston 8 can furthermore via a channel 84 with another switching valve 86 with the discharge channel 80 and thus be connected directly to the low-pressure accumulator 24, so that, for example, during the compression stroke the Rear of the hydraulic piston 8 with a lower Pressure can be applied.
  • the control valve 82nd brought into its locked position.
  • Figure 8 shows a schematic representation of that Range of a free-piston engine 1, in which the hydraulic piston 8 for driving the not shown Engine piston is arranged.
  • Embodiment is - similar to the Embodiment according to Figure 4 - the low-pressure accumulator 24 via a check valve 26 with the annular Working space of the working cylinder 14 connected.
  • the check valve 26 can via a bypass line 50 with Dosing valve 52 are bypassed, so that at the beginning of the Compression stroke supplied compression energy through direct intrusion of the low-pressure accumulator 24 influenced can be.
  • the high pressure accumulator 30 is above the high pressure passage 28 and the start valve 32 and the pressure channel 20 with the Compression cylinder 18 connected.
  • the free piston engine has a piston retraction assembly 84, which, however, in the illustrated solution formed by a check valve 86 and a retraction valve 88 is.
  • the check valve 86 is also in the hydraulic piston 8 integrated.
  • the retraction valve 88 is a 2/2-way valve executed in his spring-loaded Basic position a between a tank channel 90 and the pressure channel 20 extending channel 92 shuts off and in its switching position opens this connection.
  • the high pressure passage 28 is bypassing the starting valve 32 via a directional control valve 94 directly to the compression cylinder 18 connectable, in the motor housing. 2 the free-piston engine 1 is integrated.
  • the directional control valve 94th as a logic valve (2/2-way valve) with graduated Logic piston 96 is formed.
  • the face of the logic piston 96 with a larger area cross-section 98 is against a valve seat 100 biased.
  • a radial port 102 In the area of this Valve seat 100 is formed a radial port 102, the via a bypass line 104 with the high-pressure channel 28 is connected. That is, when resting on the valve seat 100 Logic piston 96 is the connection between the Bypass line 104 and the compression chamber 18 shut off.
  • the other end portion of the logic piston 96 with smaller Area cross section 106 is in a control room 108th guided, via a control channel 110 and a release valve 112 with the tank channel 90 or the high-pressure channel 28 is connectable.
  • the release valve 112 is shown in the Embodiment designed as a 3/2-way valve, that in its spring-biased home position the High pressure channel 28 connects to the control channel 110. In the switching position is the connection to the high-pressure channel 28 shut off and the control channel 110 with the tank channel 90 connected.
  • the release valve is used to start the free-piston engine 112 brought into its switching position, so that the smaller area cross-section 106 is applied to the tank pressure is.
  • the spring 113 is designed so that the Control piston when starting the engine initially against the valve seat 100 is biased.
  • the start valve 32 is opened, so that the compression cylinder 18 with the Pressure is applied in the high-pressure accumulator - the hydraulic piston 8 is due to the increasing pressure accelerated.
  • This increases the on the larger area cross-section 98 of the logic piston 96 acting pressure, so that this opens, lifts off the valve seat 100 and the Radial connection 102 and thus the connection to the high-pressure accumulator 30 is turned on - the logic valve 94 opens completely.
  • An advantage of this variant is that the logic piston 96 its energy to open on its own control edge receives, so that no pilot valve required is. The opening movement is very fast, so that the pressure in the compression cylinder 18 with high dynamics can be increased. During operation of the free-piston engine 1, the logic piston 96 remains in its open position.
  • the free-piston engine 1 To stop the free-piston engine is the start valve 32 closed and the release valve 112 in his Switched home position, so that the smaller area cross section 106 of the logic piston 96 with the pressure in High-pressure accumulator is acted upon. The free-piston engine 1 then comes with closed start valve 32 and closed Logic valve 94 to a stop. That is, in the above-described Solution, the logic valve 94 also acts as Check valve, over which the connection from the compression cylinder 18 can be opened to the high-pressure accumulator 30.
  • the check valve 86 is in the closing direction by the force of a closing spring 114 and in Opening direction by the pressure in the compression cylinder 18 charged.
  • open check valve 86 is the Working cylinder 14 via the check valve 34 with the Compression cylinder 18 connected. Consequently, at above-described pressure buildup in the compression cylinder 18th brought the check valve 86 in its open position, so that during the compression stroke in the working cylinder 14 constructive pressure on the check valve 34th and the high pressure passage 28 for charging the high pressure accumulator 30 can be exploited.
  • Figure 9 shows a possible constructive solution to Integration of the check valve 84 and the check valve 86 in the hydraulic piston 8. Accordingly, this as split piston with a collar 116 and one opposite reduced the outer diameter of the collar 116 in diameter Piston rod 118 executed.
  • the covenant 116 and the Kobenstange 118 are via a sliding sleeve 120th connected with each other.
  • the piston rod 118 has an enlarged diameter End piece 122, which is inside the sliding sleeve 120 is arranged.
  • In the illustrated stop position is a rear stop surface 124 on a stop ring 126 of the sliding sleeve 120 at.
  • the tail 122 is designed with a guide bore 128 in the axially displaceable closing body 130 is guided.
  • the closing body 130 thus forms a seat 136 for the Covenant 116.
  • the closing body 130 has compensation bores 138, about the pressure fluid from the working cylinder 18 may enter a spring chamber 140.
  • the closing body 130 has a guide pin 142, the sealing in one Axial bore 144 of the piston rod 118 is immersed.
  • the Force of the compression spring 132 and the area difference between the left seat-side face and the right spring chamber-side annular end face is chosen so that the Closing body 130 at a pressure in the working cylinder 18, which is below the pressure in the low-pressure accumulator 24, is still biased in its closed position.
  • the Closing member 130 against the force of the compression spring 132 Upon reaching a higher pressure in the working cylinder 18 is the Closing member 130 against the force of the compression spring 132 after moved to the right until it runs onto a stop shoulder 146.
  • the closing body 130 with the compression spring 132 acts practically as a check valve, which increases when pressure increases in the compression cylinder 18 in its open position is brought.
  • This check valve closes only when the pressure in the compression cylinder 18 is lower than that Pressure in the low-pressure accumulator 24 is. Such a smaller one Pressure is then adjusted when the free piston targeted to be moved back to its starting position.
  • a free-piston engine with an engine piston the drivable via a stepped hydraulic piston is.
  • the larger diameter of the hydraulic piston is in a compression cylinder, while the smaller Diameter is arranged in a working cylinder.
  • the compression stroke is the compression cylinder with a high-pressure accumulator and the working cylinder with a low pressure accumulator or a high pressure accumulator connected.
  • the High-pressure accumulator displaced by the out of the cylinder chambers Pressure medium loaded.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)
  • Valve Device For Special Equipments (AREA)

Claims (14)

  1. Moteur à pistons libres avec un piston moteur (6) d'un moteur à combustion qui est entraíné par l'intermédiaire d'un piston hydraulique (8) à gradins, dont la surface frontale la plus petite (12 ; 62) est disposée dans un cylindre moteur (14), et dont la surface frontale la plus grande (16 ; 64) est disposée dans un cylindre de compression (18), dans lequel le cylindre moteur (14) est relié via un clapet anti-retour (34), en vue du rechargement, à un réservoir haute pression (30) et, pour l'admission ultérieure de pression via un autre clapet anti-retour, (26) à un réservoir basse pression (24), et dans lequel pendant la course de compression, le cylindre de compression (18) est alimenté en pression provenant du réservoir haute pression via une soupape de mise en marche (32), tandis que, lors de la course de détente, la pression est utilisée dans un des cylindres (14, 18) pour le rechargement du réservoir haute pression (30).
  2. Moteur à pistons libres selon la revendication 1, dans lequel le piston hydraulique (8) est un piston différentiel (8) avec une tige de piston (56) dirigée dans le cylindre moteur (14), dont la section de piston au diamètre supérieur (60) est dirigée dans le cylindre de compression (18).
  3. Moteur à pistons libres selon la revendication 2, avec une conduite d'alimentation (74) qui débouche d'une part dans une zone du canal haute pression (28) entre la soupape de mise en marche (32) et le réservoir haute pression (30), et d'autre part dans le cylindre de compression (18), et qui peut être réglée au maximum pendant la course de compression du piston hydraulique (8), la section du canal haute pression (28) disposée entre la soupape de mise en marche (32) et le cylindre de compression (18) pouvant être reliée à la conduite d'alimentation (74) via une conduite avec un clapet anti-retour (70).
  4. Moteur à pistons libres selon la revendication 2 ou 3, dans lequel un canal de rappel (76) avec un clapet anti-retour (78) est dérivé du canal haute pression (28), et débouche dans un cylindre annulaire (68) parcouru par une autre tige de piston (58), de sorte que, lorsque la soupape d'inversion (78) est actionnée, une surface annulaire (66) efficace dans le sens du point mort bas du piston moteur (8) peut être mise sous pression.
  5. Moteur à pistons libres selon la revendication 4, dans lequel la tige de piston (58) côté piston moteur présente un diamètre inférieur à celui de l'autre tige de piston (56).
  6. Moteur à pistons libres selon la revendication 1, avec un distributeur (94) par le piston (96) duquel un branchement en dérivation (104) contournant la soupape de mise en marche (32) peut être sélectionné.
  7. Moteur à pistons libres selon la revendication 6, dans lequel le distributeur (94) est une soupape logique dont le piston logique (96) est réalisé en gradins, sachant qu'une section de surface (106) plus petite est mise sous pression via une soupape de libération (112) avec la pression du réservoir haute pression (30), et dont la section de surface supérieure (98) est mise sous pression avec la pression du cylindre de compression (18).
  8. Moteur à pistons libres selon la revendication 7, dans lequel la soupape de libération (112) est un distributeur à 3/2 orifices qui comprime dans ses positions de commutation la section de surface la plus petite (106) avec la pression du réservoir haute pression (30), ou avec une pression du canal de réservoir (90).
  9. Moteur à pistons libres selon une des revendications précédentes, avec un ensemble de soupapes de retour de piston (54) par lequel le cylindre de compression peut être relié au réservoir (T) ou au réservoir haute pression (30).
  10. Moteur à pistons libres selon la revendication dans lequel l'ensemble de soupapes de retour de piston (54) comprend un clapet anti-retour (86) pour la connexion du cylindre moteur (14) au cylindre de compression (18), et une soupape de retour (88) pour la connexion du cylindre de compression (18) au réservoir (90), sachant que le clapet anti-retour (86) est intégré dans le piston hydraulique (8).
  11. Moteur à pistons libres selon la revendication 10, dans lequel le clapet anti-retour (34) attribué au réservoir haute pression (30) est également intégré dans le piston hydraulique (8).
  12. Moteur à pistons libres selon la revendication 11, dans lequel un bourrelet (160) formant un diamètre de piston plus grand du piston hydraulique (8) est relié via un soufflet de protection (120) à une tige de piston (118) qui peut être conduite par déplacement axial avec un embout (122) dans le soufflet de protection (120), le bourrelet (116) fermant dans une position de décalage une section de commande, de sorte qu'une connexion entre le cylindre de compression (14) et le cylindre moteur (18) est interrompue.
  13. Moteur à pistons libres selon la revendication 12, dans lequel un corps de fermeture (130) est dirigé dans l'embout (122), ce corps étant précontraint au moyen d'un ressort de pression (132) contre une ouverture au fond (134) du bourrelet (116), de sorte que la pression dans le cylindre de compression (18) est signalée via des orifices de compensation (138) du corps de fermeture (130) dans un espace des ressorts (140) pour le ressort de pression (132), et la surface efficace dans le sens de fermeture du corps de fermeture (130) est moins importante que la surface frontale efficace dans le sens d'ouverture du corps de fermeture (130).
  14. Moteur à pistons libres selon une des revendications précédentes, dans lequel une conduite de dérivation (50) dérivant le clapet anti-retour (26) est prévue dans un canal basse pression (22) entre le cylindre moteur (14) et le réservoir basse pression (24), laquelle peut être verrouillée par une soupape de réglage (52).
EP01944926A 2000-05-19 2001-05-15 Moteur a piston libre Expired - Lifetime EP1282766B1 (fr)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
DE10024737 2000-05-19
DE10024737 2000-05-19
DE10120196A DE10120196A1 (de) 2000-05-19 2001-04-24 Freikolbenmotor
DE10120196 2001-04-24
PCT/DE2001/001828 WO2001088352A1 (fr) 2000-05-19 2001-05-15 Moteur a piston libre

Publications (2)

Publication Number Publication Date
EP1282766A1 EP1282766A1 (fr) 2003-02-12
EP1282766B1 true EP1282766B1 (fr) 2005-07-27

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EP01944926A Expired - Lifetime EP1282766B1 (fr) 2000-05-19 2001-05-15 Moteur a piston libre

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US (1) US6931845B2 (fr)
EP (1) EP1282766B1 (fr)
CN (1) CN1214179C (fr)
AT (1) ATE300669T1 (fr)
ES (1) ES2245696T3 (fr)
WO (1) WO2001088352A1 (fr)

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US8986253B2 (en) 2008-01-25 2015-03-24 Tandem Diabetes Care, Inc. Two chamber pumps and related methods
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EP2334234A4 (fr) 2008-09-19 2013-03-20 Tandem Diabetes Care Inc Dispositif de mesure de la concentration d'un soluté et procédés associés
US8347832B2 (en) 2008-10-31 2013-01-08 Illinois Tool Works Inc. Fuel supply and combustion chamber systems for fastener-driving tools
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US9250106B2 (en) 2009-02-27 2016-02-02 Tandem Diabetes Care, Inc. Methods and devices for determination of flow reservoir volume
CA2753214C (fr) 2009-02-27 2017-07-25 Tandem Diabetes Care, Inc. Procedes et dispositifs pour la determination d'un volume de reservoir d'ecoulement
CN101655013A (zh) * 2009-04-25 2010-02-24 徐林波 双活塞串联直推式发动机及其应用
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JP4886873B2 (ja) * 2010-04-05 2012-02-29 隆逸 小林 リニア発電装置
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Publication number Publication date
ES2245696T3 (es) 2006-01-16
EP1282766A1 (fr) 2003-02-12
ATE300669T1 (de) 2005-08-15
CN1214179C (zh) 2005-08-10
WO2001088352A1 (fr) 2001-11-22
US20040065277A1 (en) 2004-04-08
US6931845B2 (en) 2005-08-23
CN1440489A (zh) 2003-09-03

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