EP1520970A1 - Hydraulische Betätigungsvorrichtung für eine Brennkraftmaschine - Google Patents

Hydraulische Betätigungsvorrichtung für eine Brennkraftmaschine Download PDF

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Publication number
EP1520970A1
EP1520970A1 EP04292347A EP04292347A EP1520970A1 EP 1520970 A1 EP1520970 A1 EP 1520970A1 EP 04292347 A EP04292347 A EP 04292347A EP 04292347 A EP04292347 A EP 04292347A EP 1520970 A1 EP1520970 A1 EP 1520970A1
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.)
Granted
Application number
EP04292347A
Other languages
English (en)
French (fr)
Other versions
EP1520970B1 (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
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
Application filed by Peugeot Citroen Automobiles SA filed Critical Peugeot Citroen Automobiles SA
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
Anticipated expiration legal-status Critical

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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 a 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 the bottom dead center and top dead center, the choice of the volumetric ratio is a compromise between the low-end and low-load performance, ie at a low power demand, and the occurrence of rattling under conditions more loaded.
  • a motor to internal combustion, variable volumetric ratio and variable displacement which includes at least one cylinder in which a piston can move between a neutral position top and a bottom dead center.
  • This engine also includes means for varying the position of the top dead center between predetermined limits, in order to vary simultaneously the piston stroke, the position of the bottom dead center and correlatively the volumetric ratio and the displacement according to the conditions of use of the engine.
  • These means comprise a rod articulated on the one hand on the engine piston and secondly on a main rod that turns on a crankshaft and which is also articulated on a connecting rod forming a balance, associated with a member for adjusting the position of said connecting rod controlling the positions of the top and bottom dead spots.
  • the purpose of the invention is to propose a hydraulic actuator associated with this set of articulated rods and which allows to vary quickly the position of the top dead center and the bottom dead center position as well than keeping these dead spots up and down at a fixed position, while consuming a minimum of energy.
  • the subject of the invention is therefore a hydraulic actuator for 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 delimiting in said body a lower room and a superior room filled with fluid and means 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 set of connecting rods, the active surface of the piston in the lower chamber being lower than the active surface of said piston in the superior room.
  • the invention also relates to a combustion engine internal, comprising at least one cylinder in which a piston can move between a top dead center and a bottom dead center and means to vary the position of the top dead center between predetermined limits in order to vary simultaneously the piston stroke, 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 previously mentioned, connected to said piston by a set of articulated rods.
  • FIG. 1 schematically shows a cylinder 1 of a 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 connecting rod main 4 which turns 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 adjusting the position of this rod 7 and which comprises an actuator referred to as a whole by reference 20.
  • the connecting rod 7 forming a pendulum 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 turn 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 connecting rod 3
  • the long arm 4b provides the connection between the crankpin 10 and the axis 6 articulation on the connecting rod 7 forming a balance.
  • the set of connecting rods 3, 4 and 7 as well as the hydraulic actuator 20 are housed in a cylinder housing 12.
  • the actuator 20 must make it possible to maintain the point of articulation 9 of the rod 7 forming a rocker at a fixed position as well as to move this point hinge 9 quickly to a predetermined set point in both meaning, ie up or down, and in a partial stroke or total and a dynamic less than one second.
  • a predetermined set point in both meaning, ie up or down, and in a partial stroke or total and a dynamic less than one second.
  • At each position of the point articulation 9 controlled by the actuator 20 corresponds to a position of the connecting rod 7 forming balance wheel, main link 4, crankshaft 5, connecting rod 3 and piston 2.
  • Figs. 2 and 3 illustrate the extreme positions of the piston 2 for a strong compression ratio and a weak stroke.
  • Fig. 2 shows the state of the set of rods 3, 4 and 7 and the piston 2 at top dead center and
  • FIG. 3 shows the same elements at the bottom dead center of this piston 2.
  • Figs. 4 and 5 respectively illustrate the extreme positions of the piston 2 for a low compression ratio and a strong stroke of the piston 2.
  • Fig. 4 shows the state of the assembly of rods 3, 4 and 7 and the piston 2 at the point dead high 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 is mounted movable in translation a piston 22 connected to the rod 7 forming a rocker by the hinge point 9.
  • the piston 22 is provided at its periphery with a seal 23 and delimits within the body 21 a lower chamber 24 and an upper chamber 25 which are filled of a fluid.
  • the active surface 22a of the piston 22 in the lower chamber 24 is less 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 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 valve rated 31.
  • These means also include a second passage 32 arranged 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 comprises a second end 32b opening into the first passage 30 between the first end 30a and the valve 31.
  • the means comprise also control devices for the flow of fluid between chambers 24 and 25 by the valves 31 and 33 and which are designated by the reference General 40.
  • the control members 40 are formed by a first rod 41 disposed in the first passage 30 and whose outer diameter corresponds substantially at the diameter of said passage 30.
  • This first rod 41 has a axial channel 42 for passage of the fluid from the lower chamber 24 to the chamber greater than 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 a system actuator, not shown, and on the other hand, a pusher 44 arranged 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 this second rod 43 to move it vertically upwards or downwards is constituted by any system appropriate, such as a rack and pinion system, controlled by an electric motor.
  • the valve 31 of the first passage 30 is maintained 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 superior room 25.
  • the valve 33 of the second passage 32 is maintained 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 for maintain 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 articulation point 9 or displaces this point of articulation 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 connecting rods 3, 4 and 7 in two opposite directions, this articulation 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 stem 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 entrance to the channel 42.
  • the flap 31 is pressed onto its seat 36 under the effect of the compression spring 37.
  • valve 31 remains plated 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 virtually continuously and acts as a pre-charge spring.
  • valve 31 is kept pressed on its seat 36 by the pressure of the fluid in the chamber 25 so that 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 circulates 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 said piston with the set of rods, or to vary the position of this piston and the position of this articulation point towards a set point determined according to a dynamic less than one second in order to vary the position of the point dead piston top of the internal combustion engine between limits predetermined and therefore to vary simultaneously the race of this piston, the position of the bottom dead point 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 efforts and more particularly to any engine architecture.

Landscapes

  • 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)
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 true EP1520970A1 (de) 2005-04-06
EP1520970B1 EP1520970B1 (de) 2006-05-17

Family

ID=34307368

Family Applications (1)

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)

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

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2011107131A1 (de) * 2010-03-02 2011-09-09 Daimler Ag Hubkolbenmaschine
EP2022959A3 (de) * 2007-08-10 2014-06-18 Nissan Motor Company Limited Variable Druckverhältnisvorrichtung für einen Verbrennungsmotor

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009006633A1 (de) * 2009-01-29 2010-08-05 Audi Ag Brennkraftmaschine mit verlängertem Expansionshub und verstellbarem Verdichtungsverhältnis
AT521676B1 (de) * 2018-10-08 2020-04-15 Avl List Gmbh Längenverstellbare Pleuelstange mit mechanisch betätigbarem Ventil

Citations (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
US6202623B1 (en) * 1997-09-12 2001-03-20 Preservation Holdings Limited Internal combustion engines

Patent Citations (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
US6202623B1 (en) * 1997-09-12 2001-03-20 Preservation Holdings Limited Internal combustion engines

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 011, no. 228 (M - 610) 24 July 1987 (1987-07-24) *

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2022959A3 (de) * 2007-08-10 2014-06-18 Nissan Motor Company Limited Variable Druckverhältnisvorrichtung für einen Verbrennungsmotor
WO2011107131A1 (de) * 2010-03-02 2011-09-09 Daimler Ag Hubkolbenmaschine

Also Published As

Publication number Publication date
FR2860551B1 (fr) 2007-05-11
DE602004000901D1 (de) 2006-06-22
DE602004000901T2 (de) 2006-11-30
FR2860551A1 (fr) 2005-04-08
EP1520970B1 (de) 2006-05-17
ATE326623T1 (de) 2006-06-15
ES2264098T3 (es) 2006-12-16

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