EP0980466B1 - Vorrichtung zum verstellen des hubvolumens und/oder des effektiven verdichtungsverhältnisses einer brennkraftmaschine während des betriebs - Google Patents

Vorrichtung zum verstellen des hubvolumens und/oder des effektiven verdichtungsverhältnisses einer brennkraftmaschine während des betriebs Download PDF

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Publication number
EP0980466B1
EP0980466B1 EP98924396A EP98924396A EP0980466B1 EP 0980466 B1 EP0980466 B1 EP 0980466B1 EP 98924396 A EP98924396 A EP 98924396A EP 98924396 A EP98924396 A EP 98924396A EP 0980466 B1 EP0980466 B1 EP 0980466B1
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EP
European Patent Office
Prior art keywords
piston
actuator
engine
valve
cylinder
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EP98924396A
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English (en)
French (fr)
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EP0980466A1 (de
Inventor
Vianney Rabhi
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Individual
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Priority claimed from FR9705943A external-priority patent/FR2763096B1/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
    • F02B75/00—Other engines
    • F02B75/04—Engines with variable distances between pistons at top dead-centre positions and cylinder heads
    • 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
    • F02B75/04—Engines with variable distances between pistons at top dead-centre positions and cylinder heads
    • F02B75/045—Engines with variable distances between pistons at top dead-centre positions and cylinder heads by means of a variable connecting rod length
    • 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
    • F01B9/00—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups
    • F01B9/04—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with rotary main shaft other than crankshaft
    • F01B9/047—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with rotary main shaft other than crankshaft with rack and pinion
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/348—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear by means acting on timing belts or chains

Definitions

  • the present invention relates to a device for varying the displacement and / or effective displacement ratio of a piston engine during its operation.
  • the displacement of an engine usually designates the geometric characteristics of said motor defined by the stroke and the bore.
  • volumetric ratio is also, according to the usual language, a relation existing between the chamber volume and the volume defined by the stroke multiplied by the bore. We will retain here the volumetric ratio workforce determined by the effective compression ratio of fresh gases.
  • large displacement engines In use at low power, for example during urban journeys, at even work, large displacement engines consume more energy than large displacement engines, due to a greater distance from their operating conditions generating maximum efficiency.
  • the disadvantages of large displacement engines can become an advantage when conditions of use requiring high power, for example on highway at high speed.
  • the engine power is adjusted mainly by acting on their diet through a box of speeds, and on their load through the throttle valve which controls the inlet pressure by rolling and changes the filling rate of the cylinder (s) and the average effective engine cycle pressure.
  • volumetric ratio This is defined by the relationship between the volume of the cylinder and the volume of the explosion chamber. This ratio is fixed, it is calculated taking into account the maximum load conditions of the motor and of the fuel used, however, at partial load or when the cylinder is insufficiently filled at high speeds, this ratio could be significantly increased to increase engine efficiency.
  • the device according to the invention provides in particular that:
  • the engine cycle exploits a longer expansion stroke than the stroke used to compress the gases, the expansion diagram being then truncated later than on an engine of the same displacement as defined according to prior art.
  • its operation requires one or more low-power servo means making it possible to act on the longitudinal position of the control rod relative to the cylinder body, holding account of the engine operating requirements.
  • the device according to the present invention comprises a second device to control the effective displacement of the engine consisting of a valve additional intake and a device that controls its opening / closing and which allows you to modify the angular offset of the closing point and opening of said valve relative to the crankshaft.
  • the device according to the present invention comprises a second device to control the effective displacement of the engine without valve additional intake consisting of a device that controls the opening and closing of the inlet valve known per se and which makes it possible to modify the angular offset of the point of closure and opening of said valve by compared to the crankshaft.
  • the device according to the present invention comprises a device controlling opening and closing the additional intake valve which is a camshaft controlled by a device which controls its angular offset by compared to the engine crankshaft.
  • the device according to the present invention comprises a device controlling opening and closing of the inlet valve known per se which is consisting of an additional camshaft controlled by a device which controls its angular offset from the engine crankshaft, said camshaft additional actuating said valve via a mechanical connection in addition to the movement imparted to said valve by its camshaft.
  • the device comprises a device controlling the angular offset of the camshaft controlling the opening of the valve additional intake which consists of an intermediate pulley whose position defines the length of the timing belt or chain included between the camshaft pulley of the intake and exhaust valves of the engine and the camshaft pulley which controls the opening of the additional intake valve.
  • the device according to the present invention comprises a device controlling the position of the control rack which consists of a hydraulic cylinder which acts on said rack by means of a mechanical connection.
  • the device according to the present invention comprises a device which controls the position of the intermediate pulley consisting of a hydraulic cylinder.
  • the device according to the present invention comprises a gear having a truncated profile so as to keep only the teeth useful for the transmission of movement between the piston and the connecting rod.
  • the device according to the present invention comprises rolling surfaces which are fitted respectively on the gear and the racks ensuring the permanent centering of said gear between said racks, while the point of contact between said rolling surfaces is permanently positioned at the level of the gear primitive.
  • the device according to the present invention comprises a piston, the part of which cylindrical is of sufficient height to accommodate segments, but does not has no skirt ensuring its longitudinal guidance.
  • the device according to the present invention comprises a control device which comprises a cylinder piston provided with a cavity on its cylindrical surface in look with the orifice of the hydraulic fluid inlet duct opening into the central part of the cylinder body, said cavity being at least a height equivalent to the maximum stroke of said cylinder piston and being connected to the conduit placed longitudinally and eccentrically arranged in the mass of said cylinder piston connecting the lower and upper circular surfaces of said piston cylinder, by a connecting channel.
  • the device according to the present invention comprises a control device which includes a non-return valve made up of a ball held on a surface by a spring and closing a hole.
  • the device according to the present invention comprises a control device which includes a hydraulic fluid inlet conduit, one of the ports opens into the central part of the cylinder body and which is connected to the circuit hydraulic under pressure ensuring the lubrication of the displacement engine variable.
  • the device according to the present invention comprises a control device which has sealing elements made of rubber O-rings.
  • the device according to the present invention comprises a control device whose the shoulder ensures the centering of the control rod in the duct placed longitudinally and eccentrically arranged in the mass of said piston cylinder, said shoulder having grooves or grooves allowing the circulation of hydraulic fluid through said conduit.
  • the device according to the invention is inserted in an environment well known from the prior art: piston engines.
  • FIGS. 1 to 4 an engine has been shown comprising a piston 1, a cylinder 2, valves 3, 4, 15 or 22, an engine block 5, a cylinder head 6, a crankshaft 7, a spark plug 8 and an explosion chamber 9.
  • the device according to the invention essentially comprises a rack 10 integral with the lower part of the piston 1, a control rack 11 mounted in a cavity or on a guide, arranged in the engine block 5, a device 12 which controls the position of said control rack by report to the engine block. It also includes a connecting rod 13 mounted freely on the crankshaft 7 of the engine and which comprises in its upper part a gear 14 free mounted.
  • cylindrical part of the piston 1 is of sufficient height to accommodate segments, but does not have a skirt ensuring its guidance longitudinal (Figure 5).
  • the gear 14 may have a truncated profile so as to retain only the teeth useful for the transmission of movement between the piston 1 and the connecting rod 13 (Figure 5). It can be seen that the rolling surfaces are arranged respectively on the gear 14 and the racks 10, 11 ensuring the permanent centering of said gear between said racks, while the point of contact between said rolling surfaces is permanently positioned at the level of the primitive of gear 14 ( Figure 5).
  • the device according to the invention further comprises an intake valve additional 15 whose camshaft 16 controlling its opening is controlled to a device 17 which controls its angular offset relative to the crankshaft 7 of the engine.
  • the function fulfilled by the additional intake valve 15 can be assumed by the inlet valve 22 as defined according to art anterior as shown in Figure 3.
  • the additional device then makes it possible to modify the angular offset of the point closing and opening the valve 22 relative to the crankshaft 7.
  • the additional device may include an additional camshaft 21 slaved to a device not shown which controls its angular offset relative to the engine crankshaft. Additional camshaft 21 actuates the valve intake 22 via a mechanical link 23 in addition to movement imparted to said valve by its camshaft 24 as defined according to the prior art.
  • the device according to the invention can also include various accessories not represented such as probes transmitting various parameters of engine operation, one or more computers or devices performing the processing of information from said probes and a system for securing the device 12 which controls the position of the rack control 11 relative to the engine block 5 and the device 17 which controls the angular offset of the additional intake valve 15 to the result of the processing of information from said probes.
  • various accessories not represented such as probes transmitting various parameters of engine operation, one or more computers or devices performing the processing of information from said probes and a system for securing the device 12 which controls the position of the rack control 11 relative to the engine block 5 and the device 17 which controls the angular offset of the additional intake valve 15 to the result of the processing of information from said probes.
  • Modifying the effective displacement of the engine while keeping a report adequate volumetric is effected by the combined action of devices allowing to control during its operation the volumetric ratio of the engine of a part and the effective displacement of said motor on the other hand.
  • the engine's volumetric ratio is checked by position control origin of the stroke of the piston 1 relative to the cylinder 2, without modifying the length of said stroke.
  • the control device 12 of the rack 11 receives the order to move said control rack 11.
  • This order is materialized, for example, by the introduction into a hydraulic cylinder 25 of a certain volume of oil under pressure from a pump (not shown).
  • the volume introduced is calculated beforehand by the device (s) (not represented) processing information from probes parametric parameters of the engine (not shown).
  • the action of the control system 12 on the control rack 11 via a link mechanical 20 has the effect of printing on said control rack 11 a translational movement parallel to its longitudinal axis.
  • the control rack 11 constitutes a gear system with the gear 14 mounted freely in the upper part of the connecting rod 13 and the rack 10 secured to the lower part of the piston 1.
  • the displacement of the control rack 11 implies a modification of the point of origin of the stroke of piston 1 relative to cylinder 2. Changing the point of origin of the effect of the stroke is to modify the volume of the explosion chamber 9, the length of said stroke being unchanged, the volumetric ratio of the engine is amended.
  • the device 17 which controls the angular offset of the camshaft 16 which controls the opening of the additional intake valve 15 receives the order delay or advance the closing of said intake valve additional 15.
  • This order is materialized according to a particular embodiment of the device 17 by the introduction into a hydraulic cylinder 26 of a certain volume pressurized oil from a pump (not shown).
  • the volume introduced is calculated beforehand by the device (s) not represented performing the processing of information from probes parametric parameters of the engine (not shown).
  • the hydraulic cylinder 26 can act on the position of an intermediate pulley 18 which modifies the length of timing belt 27 or chain between the pulley 28 of the camshaft 24 of the intake 3 and exhaust 4 valves of the engine, and the pulley 29 of the camshaft 16 which controls the opening of the additional intake valve 15.
  • a delay calculated at the closing of the intake valve additional 15 has the effect of allowing the piston 1 to flow back into the tubing intake 19 a certain quantity of fresh gas admitted in excess on the one hand, and to use only part of the length of the stroke of the piston 1 for compress the gases on the other hand.
  • fresh gases being pumped into the intake manifold 19 can be re-aspirated by a neighboring cylinder during the intake phase.
  • the device according to the invention provides that the ratio between the volume of the explosion chamber defined by the system which controls the volumetric ratio and the length of the piston stroke used to compress the fresh gases may not not remain constant, this in order to allow the engine to work according to the highest possible effective volume ratio authorized by the conditions of operation of said engine.
  • the effective displacement of the engine and its ratio effective volumetric are permanently subject to optimization requirements engine performance.
  • FIGS. 5 to 7 show an alternative embodiment of the device 12 which controls the position of the control rack 11 relative to the block motor 5.
  • the control device 12 essentially comprises a cylinder body 45 mounted fixed relative to the engine block 5 parallel to the control rack 11, a jack cover 46 mounted fixed relative to the jack body 45, a cylinder piston 47, cylinder axis 48 and cylinder axis extension 49 assembled with the control rack 11, which constitute the upper guide of said control rack 11 and which can be move longitudinally with respect to the cylinder body 45.
  • control means 42 which consist of a control rod 50 provided with a shoulder 51 and able to move longitudinally.
  • the control rod 50 is positioned parallel to the cylinder axis 48 and goes right through the cylinder cover 46, the cylinder body 45 and the piston actuator 47 by means of conduits arranged in said actuator covers 46, cylinder body 45 and cylinder piston 47.
  • the control means 42 also consist of valves 52, 53 housed in a conduit 54 arranged in the mass of the cylinder piston 47.
  • the valves 52, 53 allow to authorize or prohibit the circulation of the fluid hydraulic between the upper 40 and lower 41 chambers of the jack such as defined by the position of the cylinder piston 47 relative to the cylinder body 45.
  • the valves 52, 53 consist of rings which can slide around the stem check 50. The inside diameter of the rings is expected to be less than the diameter of the shoulder 51 of the control rod 50 so that it is possible to keep open thanks to the shoulder 51.
  • the valves 52, 53 do not are not kept open by the shoulder 51, they are kept on their seat by springs 55, 56.
  • the control means 42 consist of a non-return valve 43 housed in a hydraulic fluid inlet pipe 57, one of the orifices of which opens out in the central part of the cylinder body 45.
  • the non-return valve 43 authorizes the entry of hydraulic fluid into the cylinder body 45, but prohibits the exit.
  • the valve 43 may consist, according to a particular embodiment, of a ball 58 held on a seat by a spring 59 in order to close an orifice 44.
  • the control means 42 of the device 12 provide that the cylinder piston 47 has a cavity 30 on its cylindrical surface facing the conduit inlet 57 provided in the central part of the cylinder body 45.
  • the cavity 30 is of a height at least equivalent to the maximum stroke of the cylinder piston 47.
  • the cavity 30 communicates with the conduit 54 placed longitudinally and so eccentric to connect the upper and lower circular surfaces of the cylinder piston 47, via a connecting channel 31.
  • control means 42 also provide that on the elements in movement 49, 48, 47, 50, 52, 53 are respectively provided elements sealing which may consist of rubber O-rings 32, 33, 34, 35, 36, 37, 38, 39.
  • the position of the control rack 11 is checked by through the control rod 50 whose position determines the position of the cylinder piston 47 thanks to the action of the two valves 52, 53.
  • Valves 52, 53 make it possible to control the volume of trapped oil respectively in the upper 40 and lower 41 chamber of the jack hydraulic.
  • the position of the control rod 50 therefore conditions in permanently the position of the control rack 11 relative to the block engine 5, and therefore the volume of the engine's explosion chamber 9. It is so possible to control the engine chamber volume with a device very low power servo control (not shown).

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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)
  • Output Control And Ontrol Of Special Type Engine (AREA)
  • Actuator (AREA)
  • Vehicle Body Suspensions (AREA)
  • Forklifts And Lifting Vehicles (AREA)
  • Characterised By The Charging Evacuation (AREA)
  • Pistons, Piston Rings, And Cylinders (AREA)

Claims (19)

  1. Vorrichtung, die es ermöglicht, den Hubraum und/oder das effektive Kompressionsverhältnis eines Kolbenmotors während seines Betriebs zu verändern, dadurch gekennzeichnet, daß sie folgendes umfaßt:
    eine erste Vorrichtung, die es ermöglicht, das Kompressionsverhältnis des Motors zu steuern, indem sie durch Modifikation des Ausgangspunkts des Hubs des Kolbens (1) relativ zum Zylinder (2) wirksam wird, ohne die Länge des Hubs zu modifizieren;
    und eine zweite Vorrichtung, die es ermöglicht, den effektiven Hubraum des Motors zu steuern, indem sie durch Verdrängung der überschüssig zugeführten Gase in dem Zylinder (2) das Motors in das Einlaßrohr (19) und durch Einstellung der Länge des Aufwärtshubs des zum Komprimieren der Gase eingesetzten Kolbens tätig wird.
  2. Vorrichtung nach Anspruch 1, dadurch gekennzeichnet, daß die erste Vorrichtung, die es ermöglicht, das Kompressionsverhältnis des Motors zu steuern, aus einem Verzahnungssystem besteht, das folgendes umfaßt:
    eine Zahnstange (10), die fest mit dem Unterteil des Kolbens (1) verbunden ist und die in einem Führungssystem gehalten wird, das der Zahnstange eine Translationsbewegung in Längsrichtung gestattet,
    eine Steuerzahnstange (11), die in dem Motorblock (5) translationsbeweglich in Längsrichtung geführt wird;
    eine Vorrichtung (12), die es ermöglicht die Position der Steuerzahnstange (11) zu steuern,
    und ein Zahnrad (14), das frei auf einer Pleuelstange (13) montiert ist, die ebenfalls frei auf einer Kurbelwelle (7) montiert ist, so daß das Zahnrad (14) zwischen den zwei Zahnstangen (10, 11) angeordnet ist, um das Element zur Übertragung der Bewegung zwischen dem Kolben (1) und der Pleuelstange (13) zu bilden.
  3. Vorrichtung nach Anspruch 1, dadurch gekennzeichnet, daß die zweite Vorrichtung, die es ermöglicht, den effektiven Hubraum des Motors zu steuern, aus einem zusätzlichen Einlaßventil (15) und einer Vorrichtung (16, 17) besteht, die sein Öffnen/Schließen steuert und die es ermöglicht, die Winkelverschiebung des öffnungsund Schließpunktes des Ventils in Bezug zur Kurbelwelle (7) zu modifizieren.
  4. Vorrichtung nach Anspruch 1, dadurch gekennzeichnet, daß die zweite Vorrichtung, die es gestattet, den effektiven Hubraum des Motors zu steuern, ohne zusätzliches Einlaßventil (15) ist und aus einer Vorrichtung (21) besteht, die das Öffnen und Schließen eines an sich bekannten Einlaßventils (22) steuert und die es ermöglicht, die Winkelverschiebung des Öffnungsund Schließpunktes des Ventils in Bezug zur Kurbelwelle (7) zu modifizieren.
  5. Vorrichtung nach Anspruch 3, dadurch gekennzeichnet, daß die Vorrichtung, die das Öffnen und Schließen des zusätzlichen Einlaßventils (15) steuert, eine Nockenwelle (16) ist, die mit einer Vorrichtung (17) gesteuert wird, die seine Winkelverschiebung in Bezug zur Kurbelwelle (7) des Motors steuert.
  6. Vorrichtung nach Anspruch 4, dadurch gekennzeichnet, daß die Vorrichtung, die das Öffnen und Schließen des an sich bekannten Einlaßventils (22) steuert, aus einer zusätzlichen Nockenwelle (21) besteht, die mit einer Vorrichtung gesteuert wird, die seine Winkelverschiebung in Bezug zur Kurbelwelle (7) des Motors steuert, wobei die zusätzliche Nockenwelle (21) das Ventil über eine mechanische Verbindung (23) betätigt, in Ergänzung zu der Bewegung, die dem Ventil durch seine Nockenwelle (24) eingeprägt wird.
  7. Vorrichtung nach Anspruch 5, dadurch gekennzeichnet, daß die Vorrichtung (17), die die Winkelverschiebung der Nockenwelle (16) steuert, die das Öffnen des zusätzlichen Einlaßventils (15) realisiert, aus einer Zwischenscheibe (18) besteht, deren Position die Treibriemen- oder Kettenlänge bestimmt, die zwischen der Scheibe (28) der Nockenwelle (24) des Einlaß- (3) und Auslaßventils (4) des Motors und der Scheibe (29) der Nockenwelle (16) liegt, die das Öffnen des zusätzlichen Einlaßventils (15) realisiert.
  8. Vorrichtung nach Anspruch 2, dadurch gekennzeichnet, daß die Vorrichtung (12), die die Position der Steuerzahnstange (11) steuert, aus einem hydraulischen Druckzylinder (25) besteht, der über eine mechanische Verbindung (20) auf die Zahnstange einwirkt.
  9. Vorrichtung nach Anspruch 7, dadurch gekennzeichnet, daß die Vorrichtung (17), die die Position der Zwischenscheibe (18) steuert, aus einem hydraulischen Druckzylinder (26) besteht.
  10. Vorrichtung nach Anspruch 2, dadurch gekennzeichnet, daß das Zahnrad (14) ein beschnittenes Profil aufweist, so daß nur die Zahnungen, die für die Übertragung der Bewegung zwischen dem Kolben (1) und der Pleuelstange (13) nützlich sind, erhalten sind.
  11. Vorrichtung nach Anspruch 2, dadurch gekennzeichnet, daß auf dem Zahnrad (14) beziehungsweise den Zahnstangen (10, 11) Laufflächen ausgebildet sind, die die permanente Zentrierung des Zahnrads zwischen den Zahnstangen gewährleistet, während der Kontaktpunkt zwischen den Laufflächen permanent auf Höhe der Basis des Zahnrads (14) positioniert ist.
  12. Vorrichtung nach Anspruch 2, dadurch gekennzeichnet, daß der zylindrische Teil des Kolbens (1) eine ausreichende Höhe hat, um Segmente aufzunehmen, aber keine Mantelfläche umfaßt, die seine Längsführung gewährleistet.
  13. Vorrichtung nach Anspruch 2, dadurch gekennzeichnet, daß die Steuervorrichtung (12) folgendes umfaßt:
    einen Hydraulikdruckzylinder mit Mitteln (49) zur Verlängerung seiner Achse (48), die es ermöglichen, ein in Abhängigkeit vom Hub des Druckzylinderkolbens verdrängtes Fluidvolumen zu bewahren, das für die obere (40) und untere (41) Kammer des Druckzylinders identisch ist,
    Steuermitteln (42), die es ermöglichen, die Achse (48) des Druckzylinders in Bezug auf den Körper des Druckzylinders (45) in eine vorbestimmte Position zu verschieben oder in einer vorbestimmten Position zu halten.
  14. Vorrichtung nach Anspruch 13, dadurch gekennzeichnet, daß die Steuervorrichtung (12) folgendes umfaßt:
    einen Druckzylinderkörper (45), der in Bezug zum Motorblock (5) parallel zur Steuerzahnstange (11) ortsfest angebracht ist, eine Druckzylinderabdeckung (46), die in Bezug zum Druckzylinderkörper (45) ortsfest angebracht ist, einen Druckzylinderkolben (47), eine Druckzylinderachse (48) und eine Druckzylinderachsverlängerung (49), die mit der Steuerzahnstange (11) verbunden ist, die ein oberes Führungssystem der Steuerzahnstange (11) bilden und die sich bezüglich des Druckzylinderkörpers (45) in Längsrichtung verschieben können,
    Steuermittel (42), die aus folgendem bestehen: einer Steuerstange (50), die einen Bund (51) aufweist und sich in Längsrichtung verschieben kann, wobei die Steuerstange (50)parallel zur Druckzylinderachse (48) positioniert ist und die Druckzylinderabdeckung (46), den Druckzylinderkörper (45) und den Druckzylinderkolben (47) mittels Öffnungen durchdringen, die in der Druckzylinderabdeckung (46), dem Druckzylinderkörper (45) und den Druckzylinderkolben (47) ausgebildet sind; Ventilen (52, 53), die in einem Kanal (54) untergebracht sind, der in Längsrichtung und exzentrisch versetzt im Volumen des Druckzylinderkolbens (47) ausgebildet ist, wobei die Ventile (52, 53) es ermöglichen das Fließen des Hydraulikfluids zwischen der oberen (40) und unteren (41) Kammer zu gestatten oder zu unterbinden, wie sie durch die Position des Druckzylinderkolbens (47) in Bezug zum Druckzylinderkörper (45) definiert sind, wobei die Ventile (52, 53) von Ringen gebildet werden, die um die Steuerstange (50) gleiten können und deren Innendurchmesser kleiner als der Durchmesser des Bundes (51) der Steuerstange (50) ist, so daß es möglich ist, sie mittels des Bundes (51) der Steuerstange (50) offen zu halten; und wenn die Ventile nicht von dem Bund (51) der Steuerstange (50) offen gehalten werden, werden sie durch Federn (55, 56) und ein Rückschlagventil (43), das in einem Einlaßkanal (57) für Hydraulikfluid untergebracht ist, dessen eine Öffnung in den Mittelteil des Druckzylinderkörper (45) mündet, in ihren Sitzen gehalten, wobei das Rückschlagventil (43) den Eintritt von Hydraulikfluid in den Druckzylinderkörper (45) gestattet, aber den Austritt unterbindet.
  15. Vorrichtung nach Anspruch 14, dadurch gekennzeichnet, daß der Druckzylinderkolben (47) auf seiner Zylinderfläche gegenüber der Öffnung des Einlaßkanals (57) für Hydraulikfluid, die in den Mittelteil des Druckzylinderkörper (45) mündet, einen Hohlraum (30) umfaßt, wobei der Hohlraum (30) eine Höhe besitzt, die zumindest äquivalent zum maximalen Hub des Druckzylinderkolbens (47) ist, und durch einen Verbindungskanal (31) mit dem Kanal (54) verbunden ist, der in Längsrichtung und auf exzentrische Weise in dem Volumen des Druckzylinderkolbens (47) ausgebildet ist und die kreisförmige untere und obere Fläche des Druckzylinderkolbens (47) verbindet.
  16. Vorrichtung nach Anspruch 14, dadurch gekennzeichnet, daß das Rückschlagventil (43) von einer Kugel (58) gebildet wird, die von einer Feder (59) auf einer Auflagefläche gehalten wird und eine Öffnung (44) verschließt.
  17. Vorrichtung nach Anspruch 14, dadurch gekennzeichnet, daß die Zufuhrleitung (57) für Hydraulikfluid, deren eine Öffnung in den Mittelteil des Druckzylinderkörpers (45) mündet, mit der Hydraulikdruckleitung verbunden ist, die für die Schmierung des Motors mit veränderlichem Hubraum sorgt.
  18. Vorrichtung nach Anspruch 14, dadurch gekennzeichnet, daß sie Dichtungselemente umfaßt, die aus ringförmigen Kautschukdichtungen (32, 33, 34, 35, 36, 37, 38, 39) besteht.
  19. Vorrichtung nach Anspruch 14, dadurch gekennzeichnet, daß der Bund (51) der Steuerstange (50) für die Zentrierung der Steuerstange in dem Längskanal (54) sorgt, der exzentrisch in dem Volumen des Druckzylinderkolbens (47) angebracht ist, wobei der Bund Rillen oder Einschnitte umfaßt, die die Zirkulation des Fluids durch den Kanal gestatten.
EP98924396A 1997-05-09 1998-05-07 Vorrichtung zum verstellen des hubvolumens und/oder des effektiven verdichtungsverhältnisses einer brennkraftmaschine während des betriebs Expired - Lifetime EP0980466B1 (de)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
FR9705943A FR2763096B1 (fr) 1997-05-09 1997-05-09 Dispositif permettant de faire varier durant leur fonctionnement la cylindree et/ou le rapport volumetrique effectifs des moteurs a pistons
FR9705943 1997-05-09
FR9804601A FR2763097B1 (fr) 1997-05-09 1998-04-07 Dispositif permettant de controler la position de la cremaillere de commande d'un moteur a cylindree variable
FR9804601 1998-04-07
PCT/FR1998/000918 WO1998051911A1 (fr) 1997-05-09 1998-05-07 Dispositif permettant de faire varier la cylindree et/ou le rapport volumetrique effectifs d'un moteur a pistons pendant son fonctionnement

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EP0980466A1 EP0980466A1 (de) 2000-02-23
EP0980466B1 true EP0980466B1 (de) 2002-03-20

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KR100595778B1 (ko) 2006-07-03
FR2763097B1 (fr) 1999-09-03
DE69804297D1 (de) 2002-04-25
ES2174440T3 (es) 2002-11-01
DE69804297T2 (de) 2002-10-02
FR2763097A1 (fr) 1998-11-13
WO1998051911A1 (fr) 1998-11-19
JP4154622B2 (ja) 2008-09-24
JP2001525032A (ja) 2001-12-04
CA2289568C (fr) 2008-04-15
EP0980466A1 (de) 2000-02-23
ATE214784T1 (de) 2002-04-15
CA2289568A1 (fr) 1998-11-19
KR20010012405A (ko) 2001-02-15
AU723539B2 (en) 2000-08-31
AU7660998A (en) 1998-12-08
US6354252B1 (en) 2002-03-12

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