EP1520970B1 - Hydraulische Betätigungsvorrichtung für eine Brennkraftmaschine - Google Patents

Hydraulische Betätigungsvorrichtung für eine Brennkraftmaschine Download PDF

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Publication number
EP1520970B1
EP1520970B1 EP04292347A EP04292347A EP1520970B1 EP 1520970 B1 EP1520970 B1 EP 1520970B1 EP 04292347 A EP04292347 A EP 04292347A EP 04292347 A EP04292347 A EP 04292347A EP 1520970 B1 EP1520970 B1 EP 1520970B1
Authority
EP
European Patent Office
Prior art keywords
piston
passage
valve
rod
fluid
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.)
Not-in-force
Application number
EP04292347A
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English (en)
French (fr)
Other versions
EP1520970A1 (de
Inventor
Aurélien Huss
Olivier Venuti
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.)
PSA Automobiles SA
Original Assignee
Peugeot Citroen Automobiles SA
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Publication of EP1520970A1 publication Critical patent/EP1520970A1/de
Application granted granted Critical
Publication of EP1520970B1 publication Critical patent/EP1520970B1/de
Not-in-force legal-status Critical Current
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D15/00—Varying compression ratio
    • F02D15/02—Varying compression ratio by alteration or displacement of piston stroke
    • 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
    • F02B75/048—Engines with variable distances between pistons at top dead-centre positions and cylinder heads by means of a variable crank stroke length

Definitions

  • the present invention relates to a hydraulic actuator for internal combustion engine with variable volumetric ratio and variable displacement and an internal combustion engine equipped with at least one such hydraulic actuator.
  • volumetric ratio of an internal combustion engine being defined as the ratio between the combustion chamber volumes of a cylinder at low dead point and top dead center, the choice of the volumetric ratio is a compromise between the low-end efficiency and low load, ie at a low demand power, and the occurrence of rattling under more loaded operating conditions.
  • FR-A-2 807 105 discloses an internal combustion engine with variable volumetric ratio and variable displacement, which comprises at least one cylinder in which a piston can move between a top dead center and a neutral position. low.
  • This engine also comprises means for varying the position of the top dead center between predetermined limits, in order to simultaneously vary the stroke of the piston, the position of the bottom dead center and correlatively the volumetric ratio and the displacement according to the conditions of the engine. use of the engine.
  • These means comprise a rod articulated on the one hand on the piston of the engine and on the other hand on a main connecting rod which rotates on a crankshaft and which is also articulated on a connecting rod forming a balance, associated with a member of adjustment of the position of said connecting rod controlling the positions of the dead centers up and down.
  • JP 62041970 discloses an actuator or the position of the piston is adjusted during a force exerted on the piston by all the connecting rods.
  • the object of the invention is to propose a hydraulic actuator associated with this set of articulated connecting rods, which makes it possible to rapidly vary the position of the top dead center and the position of the bottom dead center, as well as to maintain these top and bottom dead spots at a minimum. fixed position, while consuming a minimum of energy.
  • the subject of the invention is therefore a hydraulic actuator for an internal combustion engine with variable volumetric ratio and variable displacement, characterized in that it comprises, in a body, a piston connected to a set of rods articulated to a piston of the engine and defining in said body a lower chamber and an upper chamber filled with fluid and means for holding the piston at a fixed position or adjusting the position of this piston in the body by selective passage of the fluid between the two chambers under the effect the pressure difference in said chambers during a force exerted on the piston of this actuator by the assembly of connecting rods, the active surface of the piston in the lower chamber being less than the active surface of said piston in the upper chamber.
  • the invention also relates to an internal combustion engine, comprising at least one cylinder in which a piston can move between a top dead center and a bottom dead center and means for varying the position of the top dead center between limits. predetermined in order to simultaneously vary the stroke of the piston, the position of the bottom dead center and correlatively the volumetric ratio and the displacement according to the conditions of use of the engine, characterized in that said means comprise a hydraulic actuator as mentioned above, connected to said piston by a set of articulated links.
  • FIG. 1 schematically shows a cylinder 1 of an internal combustion engine in which a piston 2 can run races between a top dead center and a bottom dead center.
  • the piston 2 is connected to a connecting rod 3 said slave rod, articulated on the one hand on the piston 2 and on the other hand on a main connecting rod 4 which rotates on a crankshaft 5.
  • the main rod 4 is also articulated by an axis 6 on a connecting rod 7 forming a balance, associated with a device for adjusting the position of this rod 7 and which comprises a hydraulic actuator designated as a whole by the reference 20.
  • the connecting rod 7 forming a rocker is connected to the hydraulic actuator 20 by a hinge 9.
  • the main rod 4 comprises a short arm 4a and a long arm 4b integral with a tubular body 4c which can rotate on a crankpin 10 forming an integral part of the crankshaft 5.
  • the short arm 4a provides the connection between the crankpin 10 and the axis 11 of the rod 3, while the long arm 4b provides the connection between the crankpin 10 and the articulation axis 6 on the connecting rod 7 forming a balance.
  • the set of rods 3, 4 and 7 and the hydraulic actuator 20 are housed in a cylinder casing 12.
  • the actuator 20 must make it possible to maintain the articulation point 9 of the link rod 7 forming a rocker arm at a fixed position as well as to move this articulation point 9 rapidly towards a predetermined set point in both directions, ie say up or down, and in a partial or full stroke and a dynamic less than one second.
  • Figs. 2 and 3 illustrate the extreme positions of the piston 2 for a high compression ratio and a low stroke.
  • Fig. 2 shows the state of the assembly of rods 3, 4 and 7 and the piston 2 at the top dead center
  • FIG. 3 shows the same elements at the bottom dead center of this piston 2.
  • FIG. 4 shows the state of the assembly of rods 3, 4 and 7 and piston 2 at the top dead center and FIG. 5 shows the same elements at the bottom dead center of this piston 2.
  • This hydraulic actuator 20 is formed by a body 21 inside which a piston 22 connected to the connecting rod 7 forming a rocker arm by means of the d-point is mounted to move in translation. 9.
  • the piston 22 is provided at its periphery with a seal 23 and defines within the body 21 a lower chamber 24 and an upper chamber 25 which are filled with a fluid.
  • the active surface 22a of the piston 22 in the lower chamber 24 is smaller than the active surface 22b of said piston 22 in the upper chamber 25 (Fig. 6).
  • the hydraulic actuator 20 comprises means for holding the piston 22 at a fixed position or for adjusting the position of this piston 22 in the body 21 by selective passage of the fluid between the two chambers 24 and 25 under the effect of the pressure difference in said chambers 24 and 25 during a force exerted on the piston 22 of this actuator 20 by the set of rods 3, 4 and 7.
  • the means comprise a first passage 30 formed in the piston 22 and which has a first end 30a opening into the lower chamber 24 and a second end 30b opening into the upper chamber 25. This second end 30b is provided with a calibrated valve 31.
  • These means also comprise a second passage 32 formed in the piston 22 and which has a first end 32a opening into the lower chamber 24 and provided with a calibrated valve 33.
  • This passage 32 has a second end 32b opening into the first passage 30 between the first end 30a and the valve 31.
  • the means also comprise control members of the flow of the fluid between the chambers 24 and 25 by the valves 31 and 33 and which are designated by the general reference 40.
  • the control members 40 are formed by a first rod 41 disposed in the first passage 30 and whose outer diameter substantially corresponds to the diameter of said passage 30.
  • This first rod 41 comprises a axial channel 42 for passage of the fluid from the lower chamber 24 to the upper chamber 25, as will be seen later.
  • the first rod 41 is intended to act on the valve 31.
  • the control members 40 comprise, on the one hand, a second rod 43 disposed in the axis of the first rod 41 and connected to an actuation system, not shown, and, on the other hand, a pusher 44 disposed between the rods 41 and 43 and which is movable against return springs 35 and 46 by said second rod 43 between a closed position of the channel 42 of the first rod 41 and an open position of this channel 42.
  • the second rod 43 is guided in an orifice 45 formed in the body 21 and the actuating system of the second rod 43 to move it vertically upwards or downwards is constituted by any suitable system, such as a pinion and rack, controlled by an electric motor.
  • the valve 31 of the first passage 30 is held pressed against a seat 36 formed in the first passage 30 by a compression spring 37 to control the flow of fluid from the lower chamber 24 to the upper chamber 25.
  • the valve 33 of the second passage 32 is held pressed against a seat 47 formed in the second passage 32 by a compression spring 48 to control the flow of fluid from the upper chamber 25 to the lower chamber 24.
  • the return springs associated with the pusher 44 comprise a first spring 35 interposed between the face 22a of the piston 22 and this pusher 44 to hold said pusher 44 against the end of the second rod 43 and a second spring 46 interposed between the bottom of the channel 42 and the pusher 44 so as to maintain the upper end of the rod 41 against the valve 31.
  • the lower chamber 24 is connected to a fluid-feeding pump 50 of this lower chamber 24.
  • the actuator 20 maintains the hinge point 9 or moves this hinge point 9 and thus the position of the top dead center and the position of the bottom dead center of the piston 2 in the cylinder 1 via the set of rods 3, 4 and 7 in two opposite directions, this hinge point 9 being subjected to a highly asymmetrical alternating force by said assembly.
  • the actuation system raises the second rod 43 which itself raises the first rod 41 via the pusher 44 which closes the axial channel 42 as shown in FIG. 8.
  • This first rod 41 opens the valve 31 which lifts from its seat 36.
  • the piston 22 remains in its position.
  • the actuation system descends the second rod 43, which has the effect of releasing the pusher 44 and the inlet of the channel 42.
  • the valve 31 is pressed on its seat 36 under the effect of the compression spring 37.
  • valve 31 When the force exerted by the assembly of rods 3, 4 and 7 on the piston 22 is positive, that is to say directed upwards, the valve 31 remains pressed on its seat 36 because the pressure in the upper chamber 25 is greater than that prevailing in the lower chamber 24. The piston 22 does not move.
  • the booster pump 50 operates substantially continuously and acts as a pre-charge spring.
  • valve 31 is held pressed against its seat 36 by the pressure of the fluid in the upper chamber 25 if although no fluid passes between the chambers 24 and 25 and the piston 22 remains in the same position.
  • valve 33 When the force exerted on the piston 22 is directed downwards, the valve 33 is held pressed against its seat 47 by the pressure of the fluid in the lower chamber 24 and the pusher 44 closes the axial channel 42 of the first rod 41 and in this case also no fluid flows between the chambers 24 and 25 and the piston 22 remains in the same position.
  • the hydraulic actuator according to the invention makes it possible to maintain the piston of this actuator in a fixed position, and thus the point of articulation of said piston with the set of connecting rods, or to vary the position of this piston and the position of this articulation point towards a set point determined with a dynamic less than one second in order to vary the position of the top dead center of the piston of the internal combustion engine between predetermined limits and consequently to vary the stroke simultaneously of this piston, the position of the bottom dead center and correlatively the volumetric ratio and the displacement according to the conditions of use of the engine.
  • the hydraulic actuator according to the invention can be applied to any mechanical system undergoing the same type of effort and more particularly to any engine architecture.

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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)
  • Actuator (AREA)

Claims (8)

  1. Hydraulisches Stellglied für einen Verbrennungsmotor mit variablem Verdichtungsverhältnis und variablem Hubraum,
    dadurch gekennzeichnet, dass
    es in einem Körper (21) einen Kolben (22), der über eine Gabelpleueleinheit (3, 4, 7) mit einem Kolben (2) des Motors verbunden ist und in dem Körper (21) eine untere Kammer (24) und eine obere Kammer (25) begrenzt, die mit Flüssigkeit gefüllt sind, und Einrichtungen zum Halten des Kolbens (22) in einer feststehenden Lage oder zur Lageregelung dieses Kolbens (22) im Körper (21) durch selektiven Durchtritt der Flüssigkeit zwischen den beiden Kammern (24, 25) unter der Wirkung des Druckunterschieds in den Kammern (24, 25) bei einer auf den Kolben (22) dieses Stellglieds durch die Pleueleinheit (3, 4, 7) ausgeübten Kraft umfasst,
    wobei die Wirkfläche (22a) des Kolbens (22) in der unteren Kammer (24) kleiner ist als die Wirkfläche (22b) des Kolbens (22) in der oberen Kammer (25).
  2. Hydraulisches Stellglied nach Anspruch 1, dadurch gekennzeichnet, dass die Regeleinrichtungen umfassen:
    - einen ersten Durchgang (30), der im Kolben (22) ausgebildet ist und ein erstes Ende (30a) umfasst, das in die untere Kammer (24) mündet, und ein zweites Ende (30b), das in die obere Kammer (25) mündet und mit einem Sicherheitsventil (31) versehen ist,
    - einen zweiten Durchgang (32), der im Kolben (22) ausgebildet ist und ein erstes Ende (32a) umfasst, das in die untere Kammer (24) mündet und mit einem Sicherheitsventil (33) versehen ist, und ein zweites Ende (32b), das zwischen dem ersten Ende (30a) und dem Ventil (31) des ersten Durchgangs (30) in den ersten Durchgang (30) mündet, und
    - Einrichtungen (40) zum Steuern des Fließens der Flüssigkeit zwischen den Kammern (24, 25) mittels der Ventile (31, 33).
  3. Hydraulisches Stellglied nach Anspruch 2, dadurch gekennzeichnet, dass die Steuereinrichtungen (40) umfassen:
    - einen ersten Schaft (41), der im ersten Durchgang (30) angeordnet ist und auf das Ventil (31) dieses ersten Durchgangs (30) wirkt, wobei der erste Schaft (41) einen axialen Kanal (42) zum Durchgang der Flüssigkeit von der unteren Kammer (24) zur oberen Kammer (25) umfasst,
    - einen zweiten Schaft (43), der in der Achse des ersten Schafts (41) angeordnet und mit einem Stellsystem verbunden ist, und
    - einen Stößel (44), der zwischen den Schäften (41, 43) angeordnet und entgegen Rückstellfedern (35, 46) durch den zweiten Schaft (43) zwischen einer Verschließstellung des Kanals (42), in der das Ventil (31) des ersten Durchgangs (30) offen ist, und einer Öffnungsstellung dieses Kanals (42), in der das Ventil (31) des ersten Durchgangs geschlossen ist, verschiebbar ist.
  4. Hydraulisches Stellglied nach den Ansprüchen 2 und 3, dadurch gekennzeichnet, dass das Ventil (31) des ersten Durchgangs (30) von einer Druckfeder (37) gegen eine im ersten Durchgang (30) ausgebildete Auflage (36) gedrückt gehalten wird, um das Fließen der Flüssigkeit von der unteren Kammer (24) zur oberen Kammer (25) zu steuern.
  5. Hydraulisches Stellglied nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass das Ventil (33) des zweiten Durchgangs (32) von einer Druckfeder (48) gegen eine im zweiten Durchgang (32) ausgebildete Auflage (47) gedrückt gehalten wird, um das Fließen der Flüssigkeit von der oberen Kammer (25) zur unteren Kammer (24) zu steuern.
  6. Hydraulisches Stellglied nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die Rückstellfedern des Stößels (44) eine erste Feder (35) umfassen, die zwischen der Unterseite (22a) des Kolbens (22) und dem Stößel (44) eingesetzt ist, und eine zweite Feder (46), die zwischen dem Boden des Kanals (42) des Schafts (41) und dem Stößel (44) eingesetzt ist.
  7. Hydraulisches Stellglied nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die untere Kammer (24) an eine Flüssigkeitsüberdruckpumpe (50) angeschlossen ist.
  8. Verbrennungsmotor, der mindestens einen Zylinder (1), in dem sich ein Kolben (2) zwischen einem oberen Totpunkt und einem unteren Totpunkt verschieben kann, und Einrichtungen umfasst, um die Lage des oberen Totpunkts zwischen vorbestimmten Grenzen sich verändern zu lassen, um gleichzeitig den Lauf des Kolbens (2), die Lage des unteren Tiefpunkts und verhältnisgleich das Verdichtungsverhältnis und den Hubraum in Abhängigkeit von den Betriebsbedingungen des Motors sich verändern zu lassen, dadurch gekennzeichnet, dass die Einrichtungen ein hydraulisches Stellglied (20) nach einem der vorhergehenden Ansprüche umfassen, das über eine Gabelpleueleinheit (3, 4, 7) mit dem Kolben (2) verbunden ist.
EP04292347A 2003-10-02 2004-10-01 Hydraulische Betätigungsvorrichtung für eine Brennkraftmaschine Not-in-force EP1520970B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR0311566A FR2860551B1 (fr) 2003-10-02 2003-10-02 Actionneur hydraulique pour moteur a combustion interne et moteur a combustion interne comportant au moins un tel actionneur hydraulique
FR0311566 2003-10-02

Publications (2)

Publication Number Publication Date
EP1520970A1 EP1520970A1 (de) 2005-04-06
EP1520970B1 true EP1520970B1 (de) 2006-05-17

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Application Number Title Priority Date Filing Date
EP04292347A Not-in-force EP1520970B1 (de) 2003-10-02 2004-10-01 Hydraulische Betätigungsvorrichtung für eine Brennkraftmaschine

Country Status (5)

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EP (1) EP1520970B1 (de)
AT (1) ATE326623T1 (de)
DE (1) DE602004000901T2 (de)
ES (1) ES2264098T3 (de)
FR (1) FR2860551B1 (de)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4882912B2 (ja) * 2007-08-10 2012-02-22 日産自動車株式会社 可変圧縮比内燃機関
DE102009006633A1 (de) * 2009-01-29 2010-08-05 Audi Ag Brennkraftmaschine mit verlängertem Expansionshub und verstellbarem Verdichtungsverhältnis
DE102010009909B3 (de) * 2010-03-02 2010-10-14 Daimler Ag Hubkolbenmaschine
AT521676B1 (de) * 2018-10-08 2020-04-15 Avl List Gmbh Längenverstellbare Pleuelstange mit mechanisch betätigbarem Ventil

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4131094A (en) * 1977-02-07 1978-12-26 Crise George W Variable displacement internal combustion engine having automatic piston stroke control
DE3148193A1 (de) * 1981-12-05 1983-06-09 Daimler-Benz Ag, 7000 Stuttgart "kolbenbrennkraftmaschine mit veraenderlichem verdichtungsverhaeltnis"
JPS6241970A (ja) * 1985-08-20 1987-02-23 Toyota Motor Corp ピストンストロ−ク可変機構
GB9719536D0 (en) * 1997-09-12 1997-11-19 Broadsuper Ltd Internal combustion engines

Also Published As

Publication number Publication date
FR2860551B1 (fr) 2007-05-11
DE602004000901D1 (de) 2006-06-22
DE602004000901T2 (de) 2006-11-30
EP1520970A1 (de) 2005-04-06
FR2860551A1 (fr) 2005-04-08
ATE326623T1 (de) 2006-06-15
ES2264098T3 (es) 2006-12-16

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