EP3469203A1 - Heat engine provided with an improved system for varying the compression ratio - Google Patents

Heat engine provided with an improved system for varying the compression ratio

Info

Publication number
EP3469203A1
EP3469203A1 EP17726657.4A EP17726657A EP3469203A1 EP 3469203 A1 EP3469203 A1 EP 3469203A1 EP 17726657 A EP17726657 A EP 17726657A EP 3469203 A1 EP3469203 A1 EP 3469203A1
Authority
EP
European Patent Office
Prior art keywords
pinion
heat engine
eccentric part
crankshaft
shaft
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.)
Withdrawn
Application number
EP17726657.4A
Other languages
German (de)
French (fr)
Inventor
Matthieu POGAM
Julien Berger
Lambertus Hendrik De Gooijer
Willem-Constant Wagenvoort
Sander Wagenaar
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.)
Gomecsys BV
Original Assignee
Gomecsys BV
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 Gomecsys BV filed Critical Gomecsys BV
Publication of EP3469203A1 publication Critical patent/EP3469203A1/en
Withdrawn legal-status Critical Current

Links

Classifications

    • 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
    • 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
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C23/00—Bearings for exclusively rotary movement adjustable for aligning or positioning
    • F16C23/10—Bearings, parts of which are eccentrically adjustable with respect to each other
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C3/00—Shafts; Axles; Cranks; Eccentrics
    • F16C3/04—Crankshafts, eccentric-shafts; Cranks, eccentrics
    • F16C3/22—Cranks; Eccentrics
    • F16C3/28—Adjustable cranks or eccentrics
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H21/00—Gearings comprising primarily only links or levers, with or without slides
    • F16H21/10—Gearings comprising primarily only links or levers, with or without slides all movement being in, or parallel to, a single plane
    • F16H21/16—Gearings comprising primarily only links or levers, with or without slides all movement being in, or parallel to, a single plane for interconverting rotary motion and reciprocating motion
    • F16H21/18—Crank gearings; Eccentric gearings
    • F16H21/22—Crank gearings; Eccentric gearings with one connecting-rod and one guided slide to each crank or eccentric
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • F16H37/12—Gearings comprising primarily toothed or friction gearing, links or levers, and cams, or members of at least two of these types
    • F16H37/124—Gearings comprising primarily toothed or friction gearing, links or levers, and cams, or members of at least two of these types for interconverting rotary motion and reciprocating motion

Definitions

  • the present invention relates to a heat engine with a system of variation of the improved compression ratio.
  • the invention finds a particularly advantageous, but not exclusive, application in the field of motor vehicles.
  • Variation of the compression ratio is known as a function of the operating conditions of the engine.
  • These compression ratio variation systems comprise a set of eccentric parts mounted on the crankshaft crank pins so as to cooperate each with a connecting rod end.
  • a control device makes it possible to adjust the position of the eccentric pieces.
  • the control device comprises an actuating shaft and a cascade of sprockets constituted by an actuating pinion integral with the actuating shaft, and intermediate pinions meshing on the one hand with the actuating pinion. and on the other hand with a toothed ring integral with the eccentric piece.
  • each eccentric piece rotates at half the speed of the crankshaft.
  • a meshing triplet is used between actuating gears, intermediate gears, and eccentric parts.
  • the number of teeth of the drive pinion being half as small as that of the eccentric parts, it allows a rotation of the first eccentric part located on the side of the half-speed actuation of that of the crankshaft fixed rate.
  • the assembly of the pinions and transfer shafts at the crankshaft journals allows, step by step, to retranscribe the kinematics of the first eccentric part located on the actuating side to the other eccentric parts.
  • the gear triplet of the actuating pinion, the intermediate gear, and the eccentric piece extends in different planes. This requires digging locally the arm of the crankshaft to integrate the intermediate gear. Such a configuration has the disadvantage of mechanically weaken the crankshaft.
  • a second known configuration is distinguished by the fact that the gear triplet of the drive pinion, the intermediate gear, and the eccentric piece extends in the same plane. A compromise between functional, crankshaft holding, crank radius, and teeth holds may allow that the sum of the head radius of the teeth of the drive pinion and the eccentric piece is smaller than the crank radius of the crankshaft. This can improve the crankshaft holding, as there is no need to dig the crankshaft arm for integration of the whole.
  • the resistance of the teeth is, however, reduced compared to the first configuration mentioned above.
  • the invention aims to effectively overcome the disadvantages of existing systems by providing a thermal engine, including a motor vehicle, comprising a system for varying a compression ratio of the engine, the compression ratio variation system comprising:
  • crankshaft comprising at least one crank pin and at least one arm
  • the eccentric part rotatably mounted on the crankpin, the eccentric part comprising an external face of eccentric shape intended to cooperate with an end of a connecting rod, as well as at least one ring gear, and
  • At least one intermediate shaft passing axially through a journal and the crankshaft arm by a corresponding bore, the intermediate shaft being provided with a first intermediate gear meshing with the actuating pinion and a second intermediate gear meshing with an eccentric piece.
  • the heat engine comprises two intermediate shafts each provided with a first intermediate gear meshing with the actuating pinion. and a second intermediate gear meshing with an eccentric piece. This makes it possible to distribute the torque transmitted by the intermediate shafts.
  • the actuating shaft being coaxial with the crankshaft, the two intermediate shafts are positioned on either side of the actuating shaft.
  • at least one bearing is interposed radially between an intermediate shaft and a face of a corresponding bore.
  • the heat engine comprises a housing in which are inserted at least partly the intermediate shaft or trees.
  • the housing comprises at least one bearing housing for rotational mounting of an end of a corresponding intermediate shaft.
  • the housing includes a pinion at the outer periphery.
  • a pulley is fixed on an axial end face of the housing.
  • each first intermediate gear is integrated with a corresponding intermediate shaft.
  • a speed ratio between the rotational speed of the eccentric piece divided by the speed of rotation of the actuating pinion is equal to 0.5.
  • FIG. 1 is an overall view of a variation system of the compression ratio according to the present invention integrated in a crankshaft of a heat engine;
  • Figure 2 is a longitudinal sectional view of the crankshaft and the compression ratio variation system according to the present invention
  • Figure 3 is a perspective view of the compression ratio variation system according to the present invention without the crankshaft
  • Figure 4 is an exploded perspective view of the actuating device of the compression ratio variation system according to the present invention
  • Figure 5 is a longitudinal sectional view illustrating an alternative embodiment of the compression ratio variation system according to the present invention
  • Figure 6 is a perspective view of the end of the crankshaft incorporating the actuating device according to the present invention
  • Figures 7a, 7b, and 7c are schematic representations illustrating different gear combinations for obtaining a reduction ratio of 0.5 between the drive pinion and the eccentric piece. Identical elements, similar, or the like, retain the same reference from one figure to another.
  • Figure 1 shows a crankshaft 12 incorporating a 1 1 system of variation of the compression ratio to vary the compression ratio according to the operating conditions of the engine.
  • the system 1 1 thus makes it possible to operate an internal combustion engine at a high compression ratio under low load conditions in order to improve its efficiency. Under high load operating conditions, the compression ratio can be decreased to avoid jolts.
  • crankshaft 12 X axis is intended to be rotatably mounted on a motor housing by means of bearings.
  • the crankshaft 12 comprises a plurality of crank pins 13 and journals 14 cooperating with the crankcase bearings.
  • the crank pins 13 and the pins 14 are separated by arms 17 extending substantially perpendicular to the axis X.
  • the crankshaft 12 further has a front end intended to be rotatably connected with a pulley 18.
  • a steering wheel inertia (not shown) is rotatably connected to the rear end of the crankshaft 12.
  • Eccentric pieces 21 are rotatably mounted on the crank pins 13 via a through opening 22 made in each eccentric part 21.
  • Each eccentric part 21 has an outer face 25 of eccentric shape with respect to the axis of the opening 22 and thus the corresponding crankpin 13.
  • the outer face 25 is intended to cooperate with a large end of a connecting rod (not shown), which has its small end is connected in rotation with a piston of the engine.
  • Each room eccentric 21 also comprises two toothed rings 28 positioned on either side of the outer face 25.
  • the eccentric parts 21 may be monobloc parts.
  • the crankshaft 12 is subdivided into several parts to allow assembly of the assembly.
  • the crankshaft 12 is monoblock, while the eccentric parts 21 are formed of two half-shells mounted around each crankpin 13.
  • a control device 31 makes it possible to adjust the angular position of the eccentric parts 21, as shown in FIGS. 3 and 4.
  • the control device 31 comprises an actuating shaft 32 provided with an actuating pinion 33, the other end being provided with a pinion 33 'intended to cooperate with an actuating device regulating the angular position of the eccentric pieces 21.
  • two intermediate shafts 40 pass axially through a trunnion 14 and an arm 17 of the crankshaft 12 by a corresponding bore 43.
  • Each intermediate shaft 40 is provided with a first intermediate gear 41 meshing with the actuating gear 33 and a second intermediate gear 41 'meshing with an eccentric part 21.
  • the drive gear 33 and the eccentric part 21 are positioned on either side of the arm 17 of the crankshaft 12.
  • the actuating shaft 32 is advantageously coaxial with the crankshaft 12, while the two intermediate shafts 40 are positioned on either side of the actuating shaft 32.
  • a bearing 44 for example of the needle type, is interposed radially between each intermediate shaft 40 and a face of the corresponding bore 43.
  • the first pinions 41 are integrated at one end of a corresponding intermediate shaft 40.
  • the pinions 41 may be obtained by machining or forging the intermediate shaft 40.
  • the second pinion 41 ' can be fitted on the side of the opposite end of the corresponding shaft 40.
  • the control system 31 comprises a housing 47, shown in Figures 4 and 6, wherein are inserted at least partially the intermediate shafts 40.
  • the housing 47 comprises two housing 49 each forming a bearing for rotatably mounting one end of a corresponding intermediate shaft 40.
  • Bearings 55 for example needle-type, may be interposed radially between the inner face of the housing 49 and the corresponding intermediate shaft 40.
  • the housing 47 may incorporate a pinion 50 at the outer periphery.
  • This pinion 50 may for example be used by the oil circuit.
  • teeth 52 for the transmission chain visible in Figures 5 and 6. These teeth 52 are interposed axially between the housing 47 and the pin 14 of the crankshaft 12. The teeth 52 may be made in one piece or reported relative to the journal 14.
  • the pulley 18 is fixed on an axial end face of the housing 47.
  • the pulley 18 may for example be fixed to the housing 47 by means of a set of screws 54 passing through a transverse wall of the pulley 18 to cooperate with threaded openings made in the housing 47, as shown in Figure 5.
  • Other fastening systems of the pulley 18 on the housing 47 are, however, conceivable.
  • control device comprises a single intermediate shaft 40.
  • the use of two intermediate shafts 40 or more makes it possible to reduce the torque supported by each intermediate shaft 40.
  • a speed ratio between the rotational speed of the eccentric part 21 divided by the speed of rotation of the actuating pinion 33 is equal to 0.5. As shown in FIGS. 7a, this ratio may for example be obtained directly between the eccentric part 21 and the second intermediate gear 41 'meshing with each other.
  • an actuating gear 33 having 15 teeth with a module of 1, a first and a second intermediate gear 41, 41 'respectively comprising 15 teeth with a module of 1 and 22 teeth with a module 1 .5, and an eccentric part 21 having 44 teeth with a module of 1 .5.
  • the transfer gear 59 comprises for example 15 teeth with a module of 1, 5 and the corresponding eccentric part 21 has 44 teeth with a module of 1, 5.
  • Figures 7b and 7c have the same configuration on the side of the actuation but the crank radius, corresponding to the distance between the center of the crankpin 13 and the center of the pin 14, being shorter for the configuration of the figure 7c, the transfer gears 59 are smaller for the configuration of Figure 7c than for the configuration of Figure 7b.
  • an actuating gear 33 having 22 teeth with a module of 1, intermediate gears 41, 41 'having 15 teeth, and an eccentric part 21 having 44 teeth are used.
  • FIG. 5 In the embodiment of FIG.
  • the transfer gear 59 comprises, for example, 19 teeth with a module of 1, 5 and the corresponding eccentric part 21 has 44 teeth with a module of 1, 5.
  • the transfer gear 59 comprises for example 15 teeth with a module of 1, 5 and the eccentric part 21 has 44 teeth with a module of 1, 5.
  • Other configurations of intermediate gears 41, 41 'and eccentric parts 21 are of course conceivable to obtain the desired reduction ratios of the system.
  • the system 1 1 In operation and when the actuating shaft 32 is fixed in rotation relative to the frame, the system 1 1 has a fixed compression ratio configuration. In transient rate, the angular position of the eccentric piece 21 located on the side of the pulley 18 is controlled by the angular position of the actuating shaft 32 and thus pass to a new compression ratio point.
  • the shaft 32 may be actuated for example by means of the actuating device, such as a wheel and worm gear or any other means for moving the adapted shaft.
  • shafts 58 and sprockets 59 called transfer transmit the same kinematics of the eccentric part 21 on the side of the actuating shaft 32 from near to all other eccentric parts 21 of the crankshaft 12.
  • the pinions 59 mounted on the shafts 58 meshing with the ring gear 28 of the other eccentric parts 21.
  • the invention thus facilitates the integration of the system 1 1 of variation of the compression ratio by the embodiment of through bore 43 in the crank arm 12 and not radial recesses difficult to machine, as was the case. in the first configuration.
  • the invention also improves the rigidity of the assembly.
  • the stresses applied to the teeth are less than in the second configuration, which makes it possible to maximize the torque transmitted by the control system 31.

Abstract

The invention relates to a heat engine, including a system (11) for varying a compression ratio, which comprises: a crankshaft (12) including at least one crank pin (13) and at least one arm (17); at least one eccentric part (21) rotatably mounted on said crank pin (13), said eccentric part (21) including an eccentric outer surface (25) intended for engaging with one end of a connecting rod, as well as at least one toothed ring gear (28); a control device (31) for controlling the angular position of said eccentric part (21), characterised in that said control device (31) includes: an actuating shaft (32) provided with an actuating pinion (33); at least one intermediate shaft (40) passing axially, from side to side, through a journal (14) and said arm (17) of said crankshaft (12) via a corresponding bore, said intermediate shaft (40) being provided with a first intermediate pinion (41) meshing with said actuating pinion (33) and a second intermediate pinion (41') meshing with an eccentric part (21).

Description

MOTEUR THERMIQUE MUNI D'UN SYSTEME DE VARIATION DU TAUX DE COMPRESSION AMÉLIORÉ  THERMAL MOTOR WITH ENHANCED COMPRESSION RATE CHANGE SYSTEM
[0001 ] La présente invention porte sur un moteur thermique muni d'un système de variation du taux de compression amélioré. L'invention trouve une application particulièrement avantageuse, mais non exclusive, dans le domaine des véhicules automobiles. The present invention relates to a heat engine with a system of variation of the improved compression ratio. The invention finds a particularly advantageous, but not exclusive, application in the field of motor vehicles.
[0002] On connaît des systèmes de variation du taux de compression en fonction des conditions de fonctionnement du moteur. Ces systèmes de variation du taux de compression comportent un ensemble de pièces excentriques montées sur les manetons du vilebrequin de manière à coopérer chacune avec une extrémité de bielle. [0002] Variation of the compression ratio is known as a function of the operating conditions of the engine. These compression ratio variation systems comprise a set of eccentric parts mounted on the crankshaft crank pins so as to cooperate each with a connecting rod end.
[0003] Un dispositif de commande permet de régler la position des pièces excentriques. A cet effet, le dispositif de commande comporte un arbre d'actionnement et une cascade de pignons constituée par un pignon d'actionnement solidaire de l'arbre d'actionnement, et des pignons intermédiaires engrenant d'une part avec le pignon d'actionnement et d'autre part avec une couronne dentée solidaire de la pièce excentrique. [0003] A control device makes it possible to adjust the position of the eccentric pieces. For this purpose, the control device comprises an actuating shaft and a cascade of sprockets constituted by an actuating pinion integral with the actuating shaft, and intermediate pinions meshing on the one hand with the actuating pinion. and on the other hand with a toothed ring integral with the eccentric piece.
[0004] A taux fixe ou arbre d'actionnement fixe par rapport au carter-cylindres, chaque pièce excentrique tourne à la moitié de la vitesse du vilebrequin. A cet effet, on utilise une triplette d'engrènements entre pignons d'actionnement, pignons intermédiaires, et pièces excentriques. Le nombre de dents du pignon d'actionnement étant deux fois moindre que celui des pièces excentriques, cela permet une rotation de la première pièce excentrique situé du côté de l'actionnement à demi-vitesse de celle du vilebrequin en taux fixe. L'assemblage des pignons et des arbres de transfert au niveau des tourillons du vilebrequin permet, de proche en proche, de retranscrire la cinématique de la première pièce excentrique situé du côté de l'actionnement aux autres pièces excentriques. [0005] Suivant une première configuration décrite dans le document WO20131 10700, la triplette d'engrenages du pignon d'actionnement, du pignon intermédiaire, et de la pièce excentrique s'étend suivant des plans différents. Cela oblige à creuser localement le bras du vilebrequin pour intégrer le pignon intermédiaire. Une telle configuration présente l'inconvénient de fragiliser mécaniquement le vilebrequin. [0006] Une deuxième configuration connue se distingue par le fait que la triplette d'engrenages du pignon d'actionnement, du pignon intermédiaire, et de la pièce excentrique s'étend suivant le même plan. Un compromis entre fonctionnel, tenue du vilebrequin, rayon de manivelle, et tenues des dentures peut permettre que la somme du rayon de tête des dents du pignon d'actionnement et de la pièce excentrique soit plus petite que le rayon de manivelle du vilebrequin. Cela peut améliorer la tenue du vilebrequin, dans la mesure où il n'y a pas besoin de creuser le bras du vilebrequin pour l'intégration de l'ensemble. La tenue des dentures est toutefois réduite par rapport à la première configuration précitée. [0007] L'invention vise à remédier efficacement aux inconvénients des systèmes existants en proposant un moteur thermique, notamment de véhicule automobile, comportant un système de variation d'un taux de compression du moteur, le système de variation du taux de compression comprenant: At fixed rate or actuating shaft fixed relative to the crankcase, each eccentric piece rotates at half the speed of the crankshaft. For this purpose, a meshing triplet is used between actuating gears, intermediate gears, and eccentric parts. The number of teeth of the drive pinion being half as small as that of the eccentric parts, it allows a rotation of the first eccentric part located on the side of the half-speed actuation of that of the crankshaft fixed rate. The assembly of the pinions and transfer shafts at the crankshaft journals allows, step by step, to retranscribe the kinematics of the first eccentric part located on the actuating side to the other eccentric parts. According to a first configuration described in WO20131 10700, the gear triplet of the actuating pinion, the intermediate gear, and the eccentric piece extends in different planes. This requires digging locally the arm of the crankshaft to integrate the intermediate gear. Such a configuration has the disadvantage of mechanically weaken the crankshaft. A second known configuration is distinguished by the fact that the gear triplet of the drive pinion, the intermediate gear, and the eccentric piece extends in the same plane. A compromise between functional, crankshaft holding, crank radius, and teeth holds may allow that the sum of the head radius of the teeth of the drive pinion and the eccentric piece is smaller than the crank radius of the crankshaft. This can improve the crankshaft holding, as there is no need to dig the crankshaft arm for integration of the whole. The resistance of the teeth is, however, reduced compared to the first configuration mentioned above. The invention aims to effectively overcome the disadvantages of existing systems by providing a thermal engine, including a motor vehicle, comprising a system for varying a compression ratio of the engine, the compression ratio variation system comprising:
- un vilebrequin comportant, au moins un maneton et au moins un bras,  a crankshaft comprising at least one crank pin and at least one arm,
- au moins une pièce excentrique montée rotative sur le maneton, la pièce excentrique comportant une face externe de forme excentrique destinée à coopérer avec une extrémité d'une bielle, ainsi qu'au moins une couronne dentée, et at least one eccentric part rotatably mounted on the crankpin, the eccentric part comprising an external face of eccentric shape intended to cooperate with an end of a connecting rod, as well as at least one ring gear, and
- un dispositif de commande de la position angulaire de la pièce excentrique,  a device for controlling the angular position of the eccentric part,
caractérisé en ce que le dispositif de commande comporte: characterized in that the control device comprises:
- un arbre d'actionnement muni d'un pignon d'actionnement, et an actuating shaft provided with an actuating gear, and
- au moins un arbre intermédiaire traversant axialement de part en part un tourillon et le bras du vilebrequin par un alésage correspondant, l'arbre intermédiaire étant muni d'un premier pignon intermédiaire engrenant avec le pignon d'actionnement et d'un deuxième pignon intermédiaire engrenant avec une pièce excentrique. [0008] L'invention permet ainsi de faciliter l'intégration du système de variation du taux de compression par la réalisation d'alésage traversant dans le bras de vilebrequin et non de creusures radiales difficilement usinables, comme cela était le cas dans la première configuration. L'invention améliore également la rigidité de l'ensemble. En outre, les contraintes appliquées sur les dentures sont moindres que dans la deuxième configuration, ce qui permet de maximiser le couple transmis par le système de commande.  - At least one intermediate shaft passing axially through a journal and the crankshaft arm by a corresponding bore, the intermediate shaft being provided with a first intermediate gear meshing with the actuating pinion and a second intermediate gear meshing with an eccentric piece. The invention thus facilitates the integration of the compression ratio variation system by producing through bore in the crank arm and not radial recesses difficult to machinable, as was the case in the first configuration . The invention also improves the rigidity of the assembly. In addition, the stresses applied to the teeth are less than in the second configuration, which maximizes the torque transmitted by the control system.
[0009] Selon une réalisation, le moteur thermique comporte deux arbres intermédiaires munis chacun d'un premier pignon intermédiaire engrenant avec le pignon d'actionnement et d'un deuxième pignon intermédiaire engrenant avec une pièce excentrique. Cela permet de répartir le couple transmis par les arbres intermédiaires. According to one embodiment, the heat engine comprises two intermediate shafts each provided with a first intermediate gear meshing with the actuating pinion. and a second intermediate gear meshing with an eccentric piece. This makes it possible to distribute the torque transmitted by the intermediate shafts.
[0010] Selon une réalisation, l'arbre d'actionnement étant coaxial avec le vilebrequin, les deux arbres intermédiaires sont positionnés de part et d'autre de l'arbre d'actionnement. [001 1 ] Selon une réalisation, au moins un roulement est interposé radialement entre un arbre intermédiaire et une face d'un alésage correspondant. In one embodiment, the actuating shaft being coaxial with the crankshaft, the two intermediate shafts are positioned on either side of the actuating shaft. [001 1] In one embodiment, at least one bearing is interposed radially between an intermediate shaft and a face of a corresponding bore.
[0012] Selon une réalisation, le moteur thermique comporte un boîtier dans lequel sont insérés au moins en partie le ou les arbres intermédiaires. According to one embodiment, the heat engine comprises a housing in which are inserted at least partly the intermediate shaft or trees.
[0013] Selon une réalisation, le boîtier comporte au moins un logement formant palier pour le montage en rotation d'une extrémité d'un arbre intermédiaire correspondant. According to one embodiment, the housing comprises at least one bearing housing for rotational mounting of an end of a corresponding intermediate shaft.
[0014] Selon une réalisation, le boîtier intègre un pignon en périphérie externe. In one embodiment, the housing includes a pinion at the outer periphery.
[0015] Selon une réalisation, une poulie est fixée sur une face d'extrémité axiale du boîtier. In one embodiment, a pulley is fixed on an axial end face of the housing.
[0016] Selon une réalisation, chaque premier pignon intermédiaire est intégré à un arbre intermédiaire correspondant. According to one embodiment, each first intermediate gear is integrated with a corresponding intermediate shaft.
[0017] Selon une réalisation, un ratio de vitesse entre la vitesse de rotation de la pièce excentrique divisée par la vitesse de rotation du pignon d'actionnement est égal à 0.5. According to one embodiment, a speed ratio between the rotational speed of the eccentric piece divided by the speed of rotation of the actuating pinion is equal to 0.5.
[0018] L'invention sera mieux comprise à la lecture de la description qui suit et à l'examen des figures qui l'accompagnent. Ces figures ne sont données qu'à titre illustratif mais nullement limitatif de l'invention. The invention will be better understood on reading the description which follows and the examination of the figures that accompany it. These figures are given for illustrative but not limiting of the invention.
[0019] La figures 1 est une vue d'ensemble d'un système de variation du taux de compression selon la présente invention intégré dans un vilebrequin de moteur thermique; FIG. 1 is an overall view of a variation system of the compression ratio according to the present invention integrated in a crankshaft of a heat engine;
[0020] La figure 2 est une vue en coupe longitudinale du vilebrequin et du système de variation du taux de compression selon la présente invention; [0021 ] La figure 3 est une vue en perspective du système de variation du taux de compression selon la présente invention sans le vilebrequin; [0022] La figure 4 est une vue en perspective éclatée du dispositif d'actionnement du système de variation du taux de compression selon la présente invention; Figure 2 is a longitudinal sectional view of the crankshaft and the compression ratio variation system according to the present invention; Figure 3 is a perspective view of the compression ratio variation system according to the present invention without the crankshaft; Figure 4 is an exploded perspective view of the actuating device of the compression ratio variation system according to the present invention;
[0023] La figure 5 est une vue en coupe longitudinale illustrant une variante de réalisation du système de variation du taux de compression selon la présente invention; [0024] La figure 6 est une vue en perspective de l'extrémité du vilebrequin intégrant le dispositif d'actionnement selon la présente invention; Figure 5 is a longitudinal sectional view illustrating an alternative embodiment of the compression ratio variation system according to the present invention; Figure 6 is a perspective view of the end of the crankshaft incorporating the actuating device according to the present invention;
[0025] Les figures 7a, 7b, et 7c sont des représentations schématiques illustrant différentes combinaisons d'engrenage permettant d'obtenir un ratio de réduction de 0.5 entre le pignon d'actionnement et la pièce excentrique. [0026] Les éléments identiques, similaires, ou analogues, conservent la même référence d'une figure à l'autre. Figures 7a, 7b, and 7c are schematic representations illustrating different gear combinations for obtaining a reduction ratio of 0.5 between the drive pinion and the eccentric piece. Identical elements, similar, or the like, retain the same reference from one figure to another.
[0027] La figure 1 montre un vilebrequin 12 intégrant un système 1 1 de variation du taux de compression pour faire varier le taux de compression en fonction des conditions de fonctionnement du moteur. Le système 1 1 permet ainsi de faire fonctionner un moteur à combustion interne à un taux de compression élevé dans des conditions de faible charge afin d'améliorer son rendement. Dans des conditions de fonctionnement à fortes charges, le taux de compression peut être diminué afin d'éviter les à-coups. [0027] Figure 1 shows a crankshaft 12 incorporating a 1 1 system of variation of the compression ratio to vary the compression ratio according to the operating conditions of the engine. The system 1 1 thus makes it possible to operate an internal combustion engine at a high compression ratio under low load conditions in order to improve its efficiency. Under high load operating conditions, the compression ratio can be decreased to avoid jolts.
[0028] Plus précisément, le vilebrequin 12 d'axe X est destiné à être monté rotatif sur un carter du moteur par l'intermédiaire de paliers. Le vilebrequin 12 comporte une pluralité de manetons 13 et de tourillons 14 coopérant avec les paliers du carter. Les manetons 13 et les tourillons 14 sont séparés par des bras 17 s'étendant sensiblement perpendiculairement par rapport à l'axe X. Le vilebrequin 12 présente en outre une extrémité avant destinée à être liée en rotation avec une poulie 18. Un volant d'inertie (non représenté) est lié en rotation à l'extrémité arrière du vilebrequin 12. [0029] Des pièces excentriques 21 sont montées de manière rotative sur les manetons 13 via une ouverture traversante 22 réalisée dans chaque pièce excentrique 21 . Chaque pièce excentrique 21 comporte une face externe 25 de forme excentrique par rapport à l'axe de l'ouverture 22 et donc du maneton 13 correspondant. La face externe 25 est destinée à coopérer avec une grande extrémité d'une bielle (non représentée), laquelle a sa petite extrémité est liée en rotation avec un piston du moteur. Chaque pièce excentrique 21 comporte également deux couronnes dentées 28 positionnées de part et d'autre de la face externe 25. More specifically, the crankshaft 12 X axis is intended to be rotatably mounted on a motor housing by means of bearings. The crankshaft 12 comprises a plurality of crank pins 13 and journals 14 cooperating with the crankcase bearings. The crank pins 13 and the pins 14 are separated by arms 17 extending substantially perpendicular to the axis X. The crankshaft 12 further has a front end intended to be rotatably connected with a pulley 18. A steering wheel inertia (not shown) is rotatably connected to the rear end of the crankshaft 12. Eccentric pieces 21 are rotatably mounted on the crank pins 13 via a through opening 22 made in each eccentric part 21. Each eccentric part 21 has an outer face 25 of eccentric shape with respect to the axis of the opening 22 and thus the corresponding crankpin 13. The outer face 25 is intended to cooperate with a large end of a connecting rod (not shown), which has its small end is connected in rotation with a piston of the engine. Each room eccentric 21 also comprises two toothed rings 28 positioned on either side of the outer face 25.
[0030] Les pièces excentriques 21 pourront être des pièces monoblocs. Dans ce cas, le vilebrequin 12 est subdivisé en plusieurs parties afin de permettre le montage de l'ensemble. Alternativement, le vilebrequin 12 est monobloc, tandis que les pièces excentriques 21 sont formées de deux demi-coquilles montées autour de chaque maneton 13. The eccentric parts 21 may be monobloc parts. In this case, the crankshaft 12 is subdivided into several parts to allow assembly of the assembly. Alternatively, the crankshaft 12 is monoblock, while the eccentric parts 21 are formed of two half-shells mounted around each crankpin 13.
[0031 ] Un dispositif de commande 31 permet de régler la position angulaire des pièces excentriques 21 , comme cela est représenté sur les figures 3 et 4. [0032] A cet effet, le dispositif de commande 31 comporte un arbre d'actionnement 32 muni d'un pignon d'actionnement 33, l'autre extrémité étant munie d'un pignon 33' destinée à coopérer avec un dispositif d'actionnement réglant la position angulaire des pièces excentrique 21 . A control device 31 makes it possible to adjust the angular position of the eccentric parts 21, as shown in FIGS. 3 and 4. [0032] For this purpose, the control device 31 comprises an actuating shaft 32 provided with an actuating pinion 33, the other end being provided with a pinion 33 'intended to cooperate with an actuating device regulating the angular position of the eccentric pieces 21.
[0033] En outre, deux arbres intermédiaires 40 traversent axialement de part en part un tourillon 14 et un bras 17 du vilebrequin 12 par un alésage 43 correspondant. Chaque arbre intermédiaire 40 est muni d'un premier pignon intermédiaire 41 engrenant avec le pignon d'actionnement 33 et d'un deuxième pignon intermédiaire 41 ' engrenant avec une pièce excentrique 21 . Le pignon d'actionnement 33 et la pièce excentrique 21 sont positionnés de part et d'autre du bras 17 du vilebrequin 12. [0034] L'arbre d'actionnement 32 est avantageusement coaxial avec le vilebrequin 12, tandis que les deux arbres intermédiaires 40 sont positionnés de part et d'autre de l'arbre d'actionnement 32. In addition, two intermediate shafts 40 pass axially through a trunnion 14 and an arm 17 of the crankshaft 12 by a corresponding bore 43. Each intermediate shaft 40 is provided with a first intermediate gear 41 meshing with the actuating gear 33 and a second intermediate gear 41 'meshing with an eccentric part 21. The drive gear 33 and the eccentric part 21 are positioned on either side of the arm 17 of the crankshaft 12. The actuating shaft 32 is advantageously coaxial with the crankshaft 12, while the two intermediate shafts 40 are positioned on either side of the actuating shaft 32.
[0035] Pour assurer un guidage en rotation des arbres intermédiaires 40 à l'intérieur du tourillon 14, un roulement 44, par exemple de type à aiguille, est interposé radialement entre chaque arbre intermédiaire 40 et une face de l'alésage 43 correspondant. To ensure a rotational guide of the intermediate shafts 40 inside the pin 14, a bearing 44, for example of the needle type, is interposed radially between each intermediate shaft 40 and a face of the corresponding bore 43.
[0036] Dans un exemple de réalisation, les premiers pignons 41 sont intégrés à une extrémité d'un arbre intermédiaire 40 correspondant. Les pignons 41 pourront être obtenus par usinage ou forgeage de l'arbre intermédiaire 40. Les deuxièmes pignons 41 ' pourront être emmanchés du côté de l'extrémité opposée de l'arbre 40 correspondant. [0037] Par ailleurs, le système de commande 31 comporte un boîtier 47, représenté sur les figures 4 et 6, dans lequel sont insérés au moins en partie les arbres intermédiaires 40. A cet effet, le boîtier 47 comporte deux logements 49 formant chacun un palier pour le montage en rotation d'une extrémité d'un arbre intermédiaire 40 correspondant. Des roulements 55, par exemple de type à aiguilles, pourront être interposés radialement entre la face interne du logement 49 et l'arbre intermédiaire 40 correspondant. In an exemplary embodiment, the first pinions 41 are integrated at one end of a corresponding intermediate shaft 40. The pinions 41 may be obtained by machining or forging the intermediate shaft 40. The second pinion 41 'can be fitted on the side of the opposite end of the corresponding shaft 40. Furthermore, the control system 31 comprises a housing 47, shown in Figures 4 and 6, wherein are inserted at least partially the intermediate shafts 40. For this purpose, the housing 47 comprises two housing 49 each forming a bearing for rotatably mounting one end of a corresponding intermediate shaft 40. Bearings 55, for example needle-type, may be interposed radially between the inner face of the housing 49 and the corresponding intermediate shaft 40.
[0038] Le boîtier 47 pourra intégrer un pignon 50 en périphérie externe. Ce pignon 50 pourra par exemple être utilisé par le circuit d'huile. Il sera possible de prévoir des dentures 52 pour la chaîne de transmission visibles sur les figures 5 et 6. Ces dentures 52 sont intercalées axialement entre le boîtier 47 et le tourillon 14 du vilebrequin 12. Les dentures 52 pourront être réalisées d'un seul tenant ou rapportées par rapport au tourillon 14. The housing 47 may incorporate a pinion 50 at the outer periphery. This pinion 50 may for example be used by the oil circuit. It will be possible to provide teeth 52 for the transmission chain visible in Figures 5 and 6. These teeth 52 are interposed axially between the housing 47 and the pin 14 of the crankshaft 12. The teeth 52 may be made in one piece or reported relative to the journal 14.
[0039] La poulie 18 est fixée sur une face d'extrémité axiale du boîtier 47. La poulie 18 pourra par exemple être fixée au boîtier 47 au moyen d'un ensemble de vis 54 traversant une paroi transversale de la poulie 18 pour coopérer avec des ouvertures taraudées réalisée dans le boîtier 47, comme cela est représenté sur la figure 5. D'autres systèmes de fixation de la poulie 18 sur le boîtier 47 sont toutefois envisageables. The pulley 18 is fixed on an axial end face of the housing 47. The pulley 18 may for example be fixed to the housing 47 by means of a set of screws 54 passing through a transverse wall of the pulley 18 to cooperate with threaded openings made in the housing 47, as shown in Figure 5. Other fastening systems of the pulley 18 on the housing 47 are, however, conceivable.
[0040] Suivant une variante de réalisation illustrée sur la figure 5, le dispositif de commande comporte un arbre intermédiaire 40 unique. Toutefois, l'utilisation de deux arbres intermédiaires 40 ou plus permet de diminuer le couple supporté par chaque arbre intermédiaire 40. According to an alternative embodiment illustrated in Figure 5, the control device comprises a single intermediate shaft 40. However, the use of two intermediate shafts 40 or more makes it possible to reduce the torque supported by each intermediate shaft 40.
[0041 ] Un ratio de vitesse entre la vitesse de rotation de la pièce excentrique 21 divisée par la vitesse de rotation du pignon d'actionnement 33 est égal à 0.5. Comme cela est représenté sur les figures 7a, ce ratio pourra par exemple être obtenu directement entre la pièce excentrique 21 et le deuxième pignon intermédiaire 41 ' engrenant l'un avec l'autre. A cet effet, il sera possible d'utiliser un pignon d'actionnement 33 ayant 15 dents avec un module de 1 , un premier et un deuxième pignons intermédiaires 41 , 41 ' comportant respectivement 15 dents avec un module de 1 et 22 dents avec un module de 1 .5, et une pièce excentrique 21 ayant 44 dents avec un module de 1 .5. Le pignon de transfert 59 comporte par exemple 15 dents avec un module de 1 ,5 et la pièce excentrique 21 correspondante comporte 44 dents avec un module de 1 ,5. [0042] Les figures 7b et 7c présentent une même configuration du côté de l'actionnement mais le rayon de manivelle, correspondant à la distance entre le centre du maneton 13 et le centre du tourillon 14, étant plus court pour la configuration de la figure 7c, les pignons de transfert 59 sont plus petits pour la configuration de la figure 7c que pour la configuration de la figure 7b. Dans un exemple de réalisation, on utilise un pignon d'actionnement 33 ayant 22 dents avec un module de 1 , des pignons intermédiaires 41 , 41 ' comportant 15 dents, et une pièce excentrique 21 comportant 44 dents. Dans ce cas, on prévoit un premier pignon intermédiaire 41 engrenant avec le pignon d'actionnement 33 ayant un module de 1 et un deuxième pignon intermédiaire 41 ' engrenant avec une pièce excentrique 21 ayant un module de 1 .5. Dans le mode de réalisation de la figure 7b, le pignon de transfert 59 comporte par exemple 19 dents avec un module de 1 ,5 et la pièce excentrique 21 correspondante comporte 44 dents avec un module de 1 ,5. Dans le mode de réalisation de la figure 7c, le pignon de transfert 59 comporte par exemple 15 dents avec un module de 1 ,5 et la pièce excentrique 21 comporte 44 dents avec un module de 1 ,5. D'autres configurations de pignons intermédiaires 41 , 41 ' et de pièces excentriques 21 sont bien entendu envisageables pour obtenir les rapports de réduction souhaités du système. A speed ratio between the rotational speed of the eccentric part 21 divided by the speed of rotation of the actuating pinion 33 is equal to 0.5. As shown in FIGS. 7a, this ratio may for example be obtained directly between the eccentric part 21 and the second intermediate gear 41 'meshing with each other. For this purpose, it will be possible to use an actuating gear 33 having 15 teeth with a module of 1, a first and a second intermediate gear 41, 41 'respectively comprising 15 teeth with a module of 1 and 22 teeth with a module 1 .5, and an eccentric part 21 having 44 teeth with a module of 1 .5. The transfer gear 59 comprises for example 15 teeth with a module of 1, 5 and the corresponding eccentric part 21 has 44 teeth with a module of 1, 5. Figures 7b and 7c have the same configuration on the side of the actuation but the crank radius, corresponding to the distance between the center of the crankpin 13 and the center of the pin 14, being shorter for the configuration of the figure 7c, the transfer gears 59 are smaller for the configuration of Figure 7c than for the configuration of Figure 7b. In an exemplary embodiment, an actuating gear 33 having 22 teeth with a module of 1, intermediate gears 41, 41 'having 15 teeth, and an eccentric part 21 having 44 teeth are used. In this case, there is provided a first intermediate gear 41 meshing with the actuating gear 33 having a module of 1 and a second intermediate gear 41 'meshing with an eccentric part 21 having a module of 1 .5. In the embodiment of FIG. 7b, the transfer gear 59 comprises, for example, 19 teeth with a module of 1, 5 and the corresponding eccentric part 21 has 44 teeth with a module of 1, 5. In the embodiment of FIG. 7c, the transfer gear 59 comprises for example 15 teeth with a module of 1, 5 and the eccentric part 21 has 44 teeth with a module of 1, 5. Other configurations of intermediate gears 41, 41 'and eccentric parts 21 are of course conceivable to obtain the desired reduction ratios of the system.
[0043] En fonctionnement et lorsque l'arbre d'actionnement 32 est fixe en rotation par rapport au bâti, le système 1 1 présente une configuration de taux de compression fixe. En transitoire de taux, la position angulaire de la pièce excentrique 21 située du côté de la poulie 18 est pilotée par la position angulaire de l'arbre d'actionnement 32 pour ainsi transiter vers un nouveau point de taux de compression. A cet effet, l'arbre 32 pourra être actionné par exemple au moyen du dispositif d'actionnement, tel qu'un engrenage à roue et vis sans fin ou tout autre moyen de déplacement de l'arbre adapté. [0044] En outre, comme cela est illustré sur les figures 2 et 4, à travers les tourillons 14 du vilebrequin 12, des arbres 58 et des pignons 59 dits de transfert transmettent la même cinématique de la pièce excentrique 21 située du côté de l'arbre d'actionnement 32 de proche en proche sur toutes les autres pièces excentriques 21 du vilebrequin 12. A cette fin, les pignons 59 montés sur les arbres 58 engrènent avec les couronnes dentées 28 des autres pièces excentriques 21 . In operation and when the actuating shaft 32 is fixed in rotation relative to the frame, the system 1 1 has a fixed compression ratio configuration. In transient rate, the angular position of the eccentric piece 21 located on the side of the pulley 18 is controlled by the angular position of the actuating shaft 32 and thus pass to a new compression ratio point. For this purpose, the shaft 32 may be actuated for example by means of the actuating device, such as a wheel and worm gear or any other means for moving the adapted shaft. In addition, as shown in Figures 2 and 4, through the journals 14 of the crankshaft 12, shafts 58 and sprockets 59 called transfer transmit the same kinematics of the eccentric part 21 on the side of the actuating shaft 32 from near to all other eccentric parts 21 of the crankshaft 12. To this end, the pinions 59 mounted on the shafts 58 meshing with the ring gear 28 of the other eccentric parts 21.
[0045] L'invention permet ainsi de faciliter l'intégration du système 1 1 de variation du taux de compression par la réalisation d'alésage traversant 43 dans le bras de vilebrequin 12 et non de creusures radiales difficilement usinables, comme cela était le cas dans la première configuration. L'invention améliore également la rigidité de l'ensemble. En outre, les contraintes appliquées sur les dentures sont moindres que dans la deuxième configuration, ce qui permet de maximiser le couple transmis par le système de commande 31 . The invention thus facilitates the integration of the system 1 1 of variation of the compression ratio by the embodiment of through bore 43 in the crank arm 12 and not radial recesses difficult to machine, as was the case. in the first configuration. The invention also improves the rigidity of the assembly. In addition, the stresses applied to the teeth are less than in the second configuration, which makes it possible to maximize the torque transmitted by the control system 31.

Claims

REVENDICATIONS
1. Moteur thermique, notamment de véhicule automobile, comportant un système (1 1 ) de variation d'un taux de compression dudit moteur, ledit système (1 1 ) de variation du taux de compression comprenant: 1. Heat engine, in particular a motor vehicle, comprising a system (1 1) for varying a compression ratio of said engine, said system (1 1) for varying the compression ratio comprising:
- un vilebrequin (12) comportant, au moins un maneton (13) et au moins un bras (17),- a crankshaft (12) comprising at least one crankpin (13) and at least one arm (17),
- au moins une pièce excentrique (21 ) montée rotative sur ledit maneton (13), ladite pièce excentrique (21 ) comportant une face externe (25) de forme excentrique destinée à coopérer avec une extrémité d'une bielle, ainsi qu'au moins une couronne dentée (28), et - at least one eccentric part (21) rotatably mounted on said crank pin (13), said eccentric part (21) comprising an external face (25) of eccentric shape intended to cooperate with one end of a connecting rod, as well as at least a toothed ring (28), and
- un dispositif de commande (31 ) de la position angulaire de ladite pièce excentrique (21 ), - a device (31) for controlling the angular position of said eccentric part (21),
caractérisé en ce que ledit dispositif de commande (31 ) comporte: characterized in that said control device (31) comprises:
- un arbre d'actionnement (32) muni d'un pignon d'actionnement (33), et - an actuation shaft (32) provided with an actuation pinion (33), and
- au moins un arbre intermédiaire (40) traversant axialement de part en part un tourillon (14) et ledit bras (17) dudit vilebrequin (12) par un alésage (43) correspondant, ledit arbre intermédiaire (40) étant muni d'un premier pignon intermédiaire (41 ) engrenant avec ledit pignon d'actionnement (33) et d'un deuxième pignon intermédiaire (41 ') engrenant avec une pièce excentrique (21 ). - at least one intermediate shaft (40) passing axially right through a journal (14) and said arm (17) of said crankshaft (12) through a corresponding bore (43), said intermediate shaft (40) being provided with a first intermediate gear (41) meshing with said actuating gear (33) and a second intermediate gear (41 ') meshing with an eccentric part (21).
2. Moteur thermique selon la revendication 1 , caractérisé en ce qu'il comporte deux arbres intermédiaires (40) munis chacun d'un premier pignon intermédiaire (41 ) engrenant avec ledit pignon d'actionnement (33) et d'un deuxième pignon intermédiaire (41 ') engrenant avec une pièce excentrique (21 ). 2. Heat engine according to claim 1, characterized in that it comprises two intermediate shafts (40) each provided with a first intermediate pinion (41) meshing with said actuating pinion (33) and a second intermediate pinion (41 ') meshing with an eccentric part (21).
3. Moteur thermique selon la revendication 2, caractérisé en ce que ledit arbre d'actionnement (32) étant coaxial avec ledit vilebrequin (12), lesdits deux arbres intermédiaires (40) sont positionnés de part et d'autre dudit arbre d'actionnement (32). 3. Heat engine according to claim 2, characterized in that said actuation shaft (32) being coaxial with said crankshaft (12), said two intermediate shafts (40) are positioned on either side of said actuation shaft (32).
4. Moteur thermique selon l'une quelconque des revendications 1 à 3, caractérisé en ce qu'au moins un roulement (44) est interposé radialement entre un arbre intermédiaire (40) et une face dudit alésage (43) correspondant. 4. Heat engine according to any one of claims 1 to 3, characterized in that at least one bearing (44) is interposed radially between an intermediate shaft (40) and one face of said corresponding bore (43).
5. Moteur thermique selon l'une quelconque des revendications 1 à 4, caractérisé en ce qu'il comporte un boîtier (47) dans lequel sont insérés au moins en partie ledit ou lesdits arbres intermédiaires (40). 5. Heat engine according to any one of claims 1 to 4, characterized in that it comprises a housing (47) in which said intermediate shaft(s) (40) are inserted at least in part.
6. Moteur thermique selon la revendication 5, caractérisé en ce que ledit boîtier (47) comporte au moins un logement (49) formant palier pour le montage en rotation d'une extrémité d'un arbre intermédiaire (40) correspondant. 6. Heat engine according to claim 5, characterized in that said housing (47) comprises at least one housing (49) forming a bearing for the rotational mounting of one end of a corresponding intermediate shaft (40).
7. Moteur thermique selon la revendication 5 ou 6, caractérisé en ce que ledit boîtier (47) intègre un pignon (50) en périphérie externe. 7. Heat engine according to claim 5 or 6, characterized in that said housing (47) integrates a pinion (50) on the external periphery.
8. Moteur thermique selon l'une quelconque des revendications 5 à 7, caractérisé en ce qu'une poulie (18) est fixée sur une face d'extrémité axiale dudit boîtier (47). 8. Heat engine according to any one of claims 5 to 7, characterized in that a pulley (18) is fixed on an axial end face of said housing (47).
9. Moteur selon l'une quelconque des revendications 1 à 8, caractérisé en ce que chaque premier pignon intermédiaire (41 ) est intégré à un arbre intermédiaire (40) correspondant. 9. Motor according to any one of claims 1 to 8, characterized in that each first intermediate pinion (41) is integrated into a corresponding intermediate shaft (40).
10. Moteur thermique selon l'une quelconque des revendications 1 à 9, caractérisé en ce qu'un ratio de vitesse entre la vitesse de rotation de ladite pièce excentrique (21 ) divisée par la vitesse de rotation dudit pignon d'actionnement (33) est égal à 0.5. 10. Heat engine according to any one of claims 1 to 9, characterized in that a speed ratio between the speed of rotation of said eccentric part (21) divided by the speed of rotation of said actuating pinion (33) is equal to 0.5.
EP17726657.4A 2016-06-09 2017-06-02 Heat engine provided with an improved system for varying the compression ratio Withdrawn EP3469203A1 (en)

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US10370970B1 (en) * 2018-06-16 2019-08-06 Anton Giger Engine crank and connecting rod mechanism

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WO2017211727A1 (en) 2017-12-14
CN109312672A (en) 2019-02-05
KR20190016519A (en) 2019-02-18
US20190376445A1 (en) 2019-12-12
FR3052495A1 (en) 2017-12-15
FR3052495B1 (en) 2020-01-10

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