Transmission device of an engine, particularly for an engine with variable compression rate and/or variable displacement

Abstract

A transmission device, particularly for an engine with variable compression rate and/or variable displacement, includes, in a cylinder housing: a combustion piston capable of moving in a combustion cylinder of the engine and secured to a transmission member; a gear engaging with a first rack of the transmission member and providing transmission of the movement between the combustion piston and a crankshaft of the engine; a connecting rod engaging, at a first end, with the gear and, at a second end, with the crankshaft; and a control member engaging with the gear and secured to a control piston. The combustion piston and the transmission member are slidably linked with the cylinder housing in a main direction.

Claims

1. A transmission device for an engine with a variable compression rate and/or a variable displacement, the transmission device comprising, in a cylinder housing: a combustion piston capable of moving along a main direction in a combustion cylinder of the engine and secured to a transmission member, the transmission member being engaged with a first connecting device supported by a wall of the cylinder housing configured to block any movement of the transmission member other than a translation in the main direction; a gear engaged with a first rack of the transmission member and with a rack of a control member secured to a control piston, the gear having a central hole wherein a bore opens for positioning a connecting rod head; wherein the gear presents a spacing between inner surfaces of the central hole and side faces of the connecting rod allowing for the translation in a longitudinal direction of the connecting rod head; and a connecting rod engaged, at a first end, in the central hole of the gear and linked, at a second end, with a crankshaft of the engine, the crankshaft defining a longitudinal direction; wherein the gear, the transmission member and the connecting rod are maintained in alignment with each other while the connecting rod head may translate in a longitudinal direction relative to the gear to make it possible to hold the connecting rod parallel to the main direction even when the connecting rod head is moved as a result of differential expansion of a crank shaft relative to the cylinder housing; and wherein the cylinder housing is provided by a body comprising a spherical portion in contact with a matching hole of the cylinder housing, with the body having, on the side opposite the spherical portion, a tab or a groove respectively engaging with a groove or a tab of the control member.

2. The transmission device according to claim 1, wherein the first connecting device is provided by a roller bearing on a plate of the cylinder housing and on the transmission member.

3. The transmission device according to claim 2, wherein the transmission member and the cylinder housing comprises a rib and a guide groove adapted to receive the rib, with one being arranged on the roller and the other one being arranged on the transmission member.

4. The transmission device according to claim 1, wherein the connecting rod head has a rod eye bore allowing for swiveling of the connecting rod in the central hole of the gear.

5. The transmission device according to claim 1, wherein a roll band of the gear is in contact with a raceway of the transmission member, bulging and U-shapes of which are engaged one in the other.

6. The transmission device according to claim 1, wherein a roll band of the gear is in contact with a raceway of the control member, bulging and U-shapes of which are engaged one in the other.

7. The transmission device according to claim 1, wherein a bearing surface of the control member contacts a surface of the cylinder housing, with one being cylindrical with a longitudinal axis, and the other one being flat.

8. The transmission device according to claim 1, wherein the cylinder housing is provided with a pressing device for compensating running clearances.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

(1) The invention will be better understood when reading the following description of a particular and not restrictive embodiment while referring to the appended figures among which:

(2) FIGS. 1A and 1B schematically and, respectively, show the design position and a position of equilibrium of some mobile members of an engine of the prior art.

(3) FIG. 2 shows a principle sectional view of an engine with variable compression rate.

(4) FIGS. 3A and 3B show perspective and exploded views of some elements of the transmission device according to a specific exemplary implementation of the invention.

(5) FIG. 3C shows a side view of some elements of the transmission device according to a particular exemplary implementation of the invention.

(6) FIG. 3D shows a section along the axis F of FIG. 3c of some elements of the transmission device according to a particular exemplary implementation of the invention.

(7) FIGS. 4 and 5 show perspective and exploded views of the gear in a particular exemplary implementation of the invention.

(8) FIG. 6 shows a perspective view of the connecting rod in a particular exemplary implementation of the invention.

(9) FIGS. 7A and 7B show cross-sections of the control member and the control piston according to two particular exemplary implementations of the invention.

(10) FIG. 8 schematically shows a position of equilibrium of some mobile elements of an engine according to the invention.

DETAILED DESCRIPTION

(11) In the following description and while referring to the figures, the following definitions will be used, by convention: the longitudinal direction is the direction defined by the major axis of the crankshaft 9; the main direction is the direction defined by the major axis of the combustion piston 2; the transverse direction is the direction defined by the direction perpendicular to the previous two directions.

(12) In addition, in the present application, “disturbances” will mean the phenomena tending to place the mobile members, when the engine is running, in a position of equilibrium different from the design position. It may be, for example, and not exhaustively, wear or the manufacturing tolerance of the members leading to dimensions that deviate from their exact design dimensions, or movements related to the differentiated expansion between such members, to the deformation under load thereof or to the presence of excessive running clearances.

(13) In FIG. 2, which shows a principle section view of an engine with variable compression rate and/or variable displacement, a cylinder housing 100 includes at least one combustion cylinder 110 wherein a combustion piston 2 moves in a guided translation causing the rotation of a crankshaft 9 through a transmission device 1.

(14) The transmission device 1 comprises a transmission member 3 secured to the combustion piston 2 and first engaging with a first connecting device 4 supported by a wall of the cylinder housing 100 and, on the other hand, with a first side of a gear 5.

(15) The transmission member 3 is provided, on one of its faces, with a large rack, the teeth of which are engaged with those of the gear 5.

(16) The gear 5 is connected, via a transmission shaft 62, to a first end of a connecting rod 6. The second end of the connecting rod 6 is connected to a crankshaft 9, so as to execute the transmission of the movement.

(17) The gear 5 engages on a second side, opposite the transmission member 3, with a rack of a control member 7 capable of moving in the main direction in engagement with a second connecting device 4′.

(18) The control member 7 is controlled by a control device comprising a cylinder consisting of a control piston 12 guided in a control cylinder 112 of the cylinder housing 100. The control device ensures the translational movement of the control member 7 in the main direction.

(19) In operation, the translational movement of the combustion piston 2 and of the transmission member 3 integral therewith, is initiated and maintained by the combustion of the mixture in the combustion cylinder 110. Such movement is guided by the existing link between the combustion piston 2 and the combustion cylinder 110, and the connecting device 4. The movement is transmitted to the assembly formed by the gear 5 and the connecting rod 6 to move the crankshaft 9 in rotation. The position of the control member 7 is adjusted in the main direction by the control device. The movement thereof is guided by the second connecting device 4′ in this direction. The movement of the control member 7 causes the pivoting of the gear 5, which results in moving the end of the stroke of the combustion piston 2 in the combustion cylinder 110. The engine compression rate and/or capacity thus varies.

(20) According to the invention, the nature of the links between some mobile members that have just been listed is so determined as to control the operating position occupied by such members, when the transmission device 1 is subjected to disturbances.

(21) “Controlling the operating position” means that the degrees of freedom and the degrees of blocking defining the nature of the links facilitate a movement of the parts of the mobile members relative to their ideal locations of design toward a position, which does not lead to excessive operating friction. Within the scope of this application, a degree of freedom or such movement will be considered as “locked” to the extent that this degree of freedom or this movement cannot exceed the required minimum clearance. For example, in order to stop a translational movement between two components having a mutually different degree of functional freedom, a maximum clearance of 0.04 mm to 0.2 mm is allowed in the direction of translation to be locked.

(22) It should be noted that such an analysis is not easy, since not only should each link be studied, but also the interactions between each link, too, for each one of the degrees of freedom and/or of blocking in order to determine the most favorable combination. It should also be noted that the multiple blocking of some degrees may lead to the development of constraints in parts, thus, promoting wear thereof, and that, on the contrary, excessive (relative to the expected functionality of each member) degrees of freedom can lead to the malfunction of the device when it is subjected to disturbances, as has been stated in the introduction of this application.

(23) The prototypes and thorough studies conducted by the inventors of this application have thus shown that some main links of the transmission device 1, which has just been described should be precisely determined, among which: the link between the assembly formed by the combustion piston 2 and the transmission member 3, and the cylinder housing 100. the link between the gear 5 and the connecting rod 6. the link between the gear 5 and the transmission member 3. the link between the gear 5 and the control member 7.

(24) The exact nature of each of these links is disclosed in detail in the following paragraphs of the present description.

(25) For example, links A between the assembly may be formed by the combustion piston 2 and the transmission member 3, and the cylinder housing 100.

(26) According to the invention, the assembly of the combustion piston 2 and the transmission member 3 is slidably linked A with the cylinder housing 100 in a main direction.

(27) As is known per se, the sliding link provides five degrees of blocking and allows a single translational movement.

(28) According to the invention, any movement of the transmission member 3 other than a translation in a main direction should thus be locked. In other words, the connecting device 4 is so configured as to block any movement of the transmission member 3 other than a translation in a main direction. This more particularly relates to the blocking of a swiveling movement in the combustion cylinder 110 of the transmission member 3 and the combustion piston 2, which would induce friction on the inner walls of this cylinder.

(29) In order to minimize friction between the parts of the link, such sliding link A is preferably broken down into: an annular linear link A1 between the combustion piston 2 and the combustion cylinder 110, the center of which is formed by the combustion piston 2 in the main direction. a straight linear link A21 in the longitudinal direction is combined with a punctual link A22 in the longitudinal direction between the transmission member 3 and the cylinder housing 100.

(30) The annular linear link A1 opposes the two translations in the longitudinal and transverse directions of the combustion piston 2, with all the other movements being free. This ensures minimum friction between the contact surfaces of the combustion piston 2 with that of the combustion cylinder 110.

(31) The straight linear link A21 opposes the translation of the transmission member 3 in the transverse direction and the rotation thereof along the main axis of the combustion cylinder 110.

(32) Eventually, the punctual link A22 provides the fifth degree of blocking of the sliding link that opposes the translation of the transmission member 3 in the longitudinal direction.

(33) This ensures that the translational movement in the main direction of the assembly formed by the combustion piston 2 and the transmission member 3 relative to the cylinder housing 100 only remains free. Friction at the skirt of the combustion piston and the cylinder is thus prevented, or limited. The other five possible degrees of freedom of such member are blocked, thus avoiding any strain to the parts that might cause situations that could cause excessive friction and/or noise operation, or the wear thereof.

(34) Link C Between the Gear 5 and the Transmission Member 3

(35) It should be reminded that the gear 5 engages with a large rack formed on the transmission member 3. In this respect, the link C between the gear 5 and the transmission member 3 comprises a first rack and pinion link.

(36) This rack and pinion link can be defined as a straight linear link, wherein the gear toothing is represented by a line substantially parallel to the axis of the gear passing through the pitch circle of the toothing and the rack toothing is represented by a plane oriented along the pressure angle of the teeth, commonly 20°. This link has: two degrees of freedom in translation in the plane which defines same, two degrees of freedom in rotation, one for the axis defined by the direction of the line, with the other one being defined by the normal to the plane characterizing the link.

(37) According to the invention, the link C between the gear 5 and the transmission member 3 further includes an annular linear link in the main direction.

(38) This combination of links results in the blocking of the relative translational movement in the longitudinal and transverse directions between the gear 5 and the transmission member 3, and in allowing the rotational movements along the longitudinal and main axes of the gear 5 relative to the transmission member 3 and the translation movement along the main axis.

(39) According to the invention, the gear 5 has to be maintained centered on the large rack of the transmission member 3, without thereby inducing significant constraints on the gear 5 or on the control member 7. The gear 5 and/or the transmission member 3 are so configured as to be maintained centered relative to one another.

(40) It should be noted that, in the solutions known from the art, the sliding longitudinal movement of the gear 5 on the transmission member 3 was possible. For this purpose, the width of the teeth of the gear 5 was so reduced as to enable this sliding movement.

(41) According to the present invention, the blocking of this translational movement by the link C makes it possible to optimize the width of the teeth of the gear 5 and thus to maximize the load that can be transmitted by the transmission device 1. The engine performances are thus improved for unchanged overall dimensions of the components (best engine torque and higher rating).

(42) Link D Between the Gear 5 and the Control Member 7

(43) The transmission device 1 (FIG. 3A) also comprises a control member 7 for adjusting the end of the piston stroke in the combustion cylinder 110.

(44) The link D between the gear 5 and the control member 7 includes an annular linear link in the main direction. The control member 7 is provided with a large rack engaging with the gear 5, and the link also includes a rack and pinion link.

(45) The location of this link is thus perfectly similar to the link C seen above. And, the gear 5 and/or the control member 7 are accordingly so configured as to be maintained centered with respect to one another, too.

(46) This combination of links, therefore, leads to block the relative translational movements in the longitudinal and transverse directions between the gear 5 and the control member 7 and enable the rotational movements along the longitudinal and main axes of the gear 5 relative to the transmission member 3 and the translational movement along the main axis.

(47) The issue is thus to prevent constraints from applying to the gear 5 and leading to moving same from the plane in which the previous links hold same.

(48) The combination of links A, C and D makes it possible to position the transmission member 3, the gear 5 and the control member 7 in alignment and in a position determined relative to the cylinder housing 100.

(49) Link B Between the Gear 5 and the Connecting Rod 6

(50) According to the invention, the link B between the gear 5 and the connecting rod 6 comprises an annular linear link in the longitudinal direction.

(51) As seen previously, an annular linear link opposes two translational movements. In this case, the issue is opposing the translation in the main and cross directions of the connecting rod 6 relative to the gear 5. All the other movements are free.

(52) The rotation of the connecting rod 6 relative to the gear 5 is required to transform the translational movement in the main direction of the axis of the gear 5 into a rotational movement of the crankshaft 9 along the longitudinal axis.

(53) The translation of a connecting rod eye 61 in a longitudinal direction relative to the gear 5 makes it possible to hold the connecting rod 6 parallel to the axis of the combustion cylinder 110 even when a rod head 64 is moved, as a result of the differential expansion of the crankshaft 9 relative to the cylinder housing 100. The position of equilibrium of the connecting rod 6 in the transmission device 1 also makes it possible to prevent or limit wear of the connecting rod bearings 65, and ensures a maximum power transmission.

(54) The link B enables free rotational movements between the connecting rod 6 and the gear 5 about the longitudinal axis, the transverse axis and about the main axis. These last two rotations (about the transverse axis and about the main axis) make up for the perpendicularity defects that may exist, for example, between the combustion cylinder 110 and the crankshaft 9, and in this case also, reduce friction that occurs in the transmission device 1.

(55) Generally, the annular linear link B between the gear 5 and the connecting rod 6 makes it possible to dissociate the positioning, in a first plane, of the “high” mobile members of the transmission device 1 (the combustion piston 2, the transmission member 3, the gear 5 and the control member 7), from the positioning in a second plane different, from the first one, and substantially parallel thereto, of the “low” mobile member of the device (the connecting rod 6, the crankshaft 9).

(56) The combination of links A, B, C and D, which have just been listed, lead to promote when the engine is running and is independent of the disturbances that it is subjected to, as well as the alignment of the gear 5 with the transmission member 3 and the control member 7. The link between the gear 5 and the connecting rod 6 is free enough, as seen above, to prevent the gear 5 from being driven by the movement of the crankshaft 9 along the longitudinal axis.

(57) In other words, the mobile members of the transmission device 1, which have just been described, are all positioned along the longitudinal axis in relation to the walls of the cylinder housing 100 and not, as was the case in the described solutions of the prior art, relative to the position of the crankshaft 9, through the connecting rod.

(58) Link E Between the Control Member 7 and the Cylinder Housing 100

(59) The link E between the control member 7 and the cylinder housing 100 comprises, in the lower part thereof, a straight linear link E1 in the longitudinal direction. The connecting device 4′ is so configured as to provide this link.

(60) This link has two degrees of blocking that enable it on the one hand to maintain the control member 7 against the cylinder housing 100 and, on the other hand, to prevent the rotation of this member about its main axis, i.e., in the main direction defined above.

(61) This link also makes it possible to keep free the translational movement required to operate the engine in the main direction of the transmission member 3.

(62) To absorb the geometrical defects, which may exist between the mobile members in the transverse direction, the link E1 can be supported by a running clearance compensating system, as described, for example, in EP1740810, EP1979591 or in the application FR14/59791 dated Mar. 10, 2014.

(63) As seen above, the control member 7 is secured to a control piston 12 guided in the control cylinder 112. The link E also comprises a link E2 between the control piston 12 and the control cylinder 112 having an annular linear nature and having a center formed by the control piston 12 in the main direction.

(64) However, for a given rate adjustment, i.e., when the position of the control piston 12 is fixed in the control cylinder 112, this link E2 has a degree of freedom in translation in the main direction blocked, which reduces it to a simple ball joint.

(65) In this configuration, the rotational movement of the control member 7 relative to the cylinder housing 100, about an axis of rotation passing through its apex and in the transverse direction, is preserved. This movement makes it possible to absorb the disturbances that develop in the transmission device during the operation thereof, which could reduce its mechanical efficiency.

(66) The combination of the links E1 and E2, in combination with the links A, C and D that have just been disclosed, ensures a sliding link between the assembly formed by the control member 7 and the control piston 12 and the cylinder housing 100.

(67) The Link E′ Between the Control Member 7 and the Cylinder Housing 100

(68) According to a variant of the preferred embodiment for implementing the invention, the link E′ between the control member 7 and the cylinder housing 100 comprises, in its lower part, an annular linear link E′l in the main direction. The connecting device 4 is so configured, in this embodiment, as to provide such a link.

(69) This link has two degrees of blocking that enable same, on the one hand, to maintain the control member 7 against the cylinder housing 100 and, on the other hand, to prevent the translation of the lower part of the control member 7 in a longitudinal direction.

(70) This link also makes it possible to maintain free the translational movement required to operate the engine in the main direction of the control member 7, as well as the rotation of the control member 7 about the main axis.

(71) Similarly to the variant E, the link E′l can be supported by a running clearance compensating system.

(72) The link E′ also comprises a link E′2 between the control piston 12 and the control cylinder 112 having an annular linear nature and a center formed by the control piston 12 in the main direction.

(73) However, and similarly to the variant E, for a given rate adjustment, this link E′2 has a degree of freedom in translation in the main direction blocked, which reduces it to a simple ball joint.

(74) In this configuration, the rotational movement of the control member 7 relative to the cylinder housing 100, about an axis of rotation passing through its apex in the main direction, is preserved. This movement makes it possible to absorb the disturbances that could reduce its mechanical efficiency.

(75) The combination of the links E′l, E′2, in combination with the links A, C and D, which have just been disclosed, ensures a sliding link between the assembly formed by the control member 7 and the control piston 12 and the cylinder housing 100.

(76) Exemplary Implementation of the Invention.

(77) FIGS. 3A, 3B, 3C and 3D show a particular exemplary implementation of the transmission device 1, according to the invention.

(78) The combustion piston 2 is provided with a guide skirt 23. When, as is the case, the guide skirt 23 has a low height relative to the diameter of the combustion cylinder 110 (FIG. 2), the link between the combustion piston 2 and the combustion cylinder 110 forms the annular linear link A1 between same.

(79) The combustion piston 2 can be made of a thick disc provided with grooves receiving the top compression rings, the compression rings, and the scraper rings, as is well known per se.

(80) The quality of this link can be improved by giving the guide skirt 23 a slightly bulging shape thereby limiting the intensity of friction, which occurs at the contact surfaces.

(81) The link between the transmission member 3 and a wall of the cylinder housing 100 (FIG. 2) is provided by the connecting device 4. The latter provides, in a preferred embodiment, for the straight linear link A21 and the punctual link A22.

(82) The connecting device 4 includes a roller 40 consisting of a cylindrical body and whereon the respective surfaces 48, 38 of a plate 41 are supported, secured to the cylinder housing 100 and to the transmission member 3. The roller 40 provides for a straight linear link A21 in the longitudinal direction. In order to synchronize the movement of the combustion piston 2 and of the roller 40, the latter may be provided with gears 44 at each of its ends, engaging with racks 46 associated with the plate 41, on the vertical edges thereof. The first and/or the second gear 44 of the roller 40 may also engage with a rack 37 of the transmission member 3. The punctual link A22 may be formed by providing a cylindrical body 42 of the roller 40 with a guide rib 43. This guide rib 43 may be placed in the middle of the cylindrical body between the gears 44. The guide rib 43 is so designed as to be accommodated, on the one hand, in a first vertical groove 49 formed on the plate 41, and in a second vertical groove 31 formed on the surface 38 of the transmission member 3.

(83) In an alternative embodiment, it can be provided so that the guide rib 43 of the roller 40 will be replaced by a groove, and that the grooves 49, 31 will be replaced by two guide ribs.

(84) The gear 5, shown in greater detail in FIGS. 4 and 5, may consist of two half gears RI and R2 assembled in one piece. They have a central hole 53 into which a bore 50 for positioning the connecting rod eye 61 (FIG. 3D) by means of a transmission shaft 62 (FIG. 3D) opening.

(85) The annular linear link B between the gear 5 and the connecting rod 6 (FIG. 2) is provided by a spacing between the inner surfaces of the central hole 53 and the side faces of the connecting rod eye 61 enabling the translational movement of the connecting rod 6 on the transmission shaft 62.

(86) It is also provided by giving a rounded profile to the bore 63 of the connecting rod eye 61, which receives the transmission shaft 62. This profile enables the swiveling of the connecting rod 6 along the main and transverse rotation axes. The connecting rod 6 is shown in FIG. 6.

(87) The gear 51 comprises a first toothing engaging with the teeth 34 of the large rack 35 of the transmission member 3. It comprises a second toothing 52 engaging with the large rack 73 of the control member 7. This arrangement between the gear 5, and respectively, the control member 7 and the transmission member 3 forms the rack and pinion links disclosed above.

(88) According to the invention, such arrangement is also provided with an annular linear link C, D making it possible to keep the gear 5 centered on the large racks 35, 73. This additional link was not present in the known solutions of the prior art. Each toothing 51, 52 is provided, in the middle thereof, with a groove 54 coaxial with the pitch circle of the gear 5. Inside each groove 54, a roll band 55 with a bulging profile is fixed. It may, for example, be a toroidal-shaped roll band. The transmission member 3 and the control member 7 each have a raceway 30, 70, respectively, the U-shape of which matches that of the bulging portion of the roll band 55, designed to contact and receive this bulging part, as can be seen in FIG. 3D.

(89) In an alternative solution, the raceways 30, 70 of the transmission member 3 and the control member 7 may be bulging and the roll band 55 of the gear 5 have the matching U-shape.

(90) In FIGS. 4 and 5, the pivoting axis of the gear 5 located in the bore 50 is positioned at the center of the pitch circle of the gear 5. This configuration makes it possible to control the engine compression rate only via the control member 7. It is, however, possible, while remaining within the scope of the invention, to shift the pivoting axis of the center of the pitch circle of the gear 5 so as to vary the kinematics of the combustion piston 2 and thereby obtain a control of the engine displacement.

(91) As shown in FIGS. 7A and 7B, the control member 7 is secured to the control piston 12. The part of the control piston 12 in contact with the inner surfaces of the control cylinder 112, which can have a bulging profile, forms the annular linear link E2.

(92) In these figures, the cylinder housing 100 is also provided with a pressing device 90 making it possible to compensate for the running clearances, which may exist between the mobile members of the engine. Within the scope of the present invention, it will be assumed that the pressing device 90 is an integral part of the cylinder housing 100.

(93) The control member 7 is connected with the pressing device 90 of the cylinder housing 100.

(94) FIG. 7A, corresponding to the preferred solution of implementation of this link, shows an exemplary embodiment of the straight linear link E1 in the longitudinal direction. In this figure, the control member 7 has a cylindrical support surface along a longitudinal axis in contact with a flat surface of a piston of the pressing device 90. In an alternative solution not shown, the cylindrical surface along the longitudinal axis can be supported by the piston of the pressing device 90 and come into contact with a flat surface formed on the control member 7.

(95) FIG. 7B shows an exemplary embodiment of the annular linear link E1′ corresponding to the variant of the preferred solution of implementation of this link. A body 91 consisting of a spherical portion engages with a matching hole of the pressing device 90 in order to provide a ball joint, mobile in rotation along the three main, transverse and longitudinal axes. The control member 7, on its face opposite the large toothing, has a groove in which a tab of the body 91 can slide, on the side opposite the spherical portion thereof. This blocks the translation along the longitudinal axis, with the translation along the transverse axis being, of course, blocked by the control member 7 contacting the cylinder housing 100 of the pressing device 90. Of course, placing the groove on the body 91 and the tab on the control member 7, could be preferred.

(96) FIG. 8 schematically shows a position of equilibrium of some mobile members of the transmission device 1 (FIG. 3A), which has just been described as an example. It can be noted, contrary to the position taken by the elements shown in FIG. 1B in the case of an engine of the prior art, that, for each engine cylinder-assembly: the combustion pistons 2a, 2b and 2c and the transmission members 3a, 3b and 3c are oriented in a main direction, thus, limiting friction with the combustion cylinders 110; the gears 5a, 5b and 5c are centered on the transmission members 3a, 3b, 3c; the connecting rods 6a, 6b and 6c are also oriented in a main direction, thus providing an efficient transmission of forces and limiting wear on the connecting rod bearings.

(97) It can be seen in FIG. 8 that the members shown of the transmission device 1 keep an orientation determined relative to the cylinder housing 100 in spite of the disturbances caused by the displacements between the top mobile members and the low mobile members related to the expansion in this specific example.

(98) Of course, the invention is not limited to the examples described and variants can be applied to the embodiments thereof, without departing from the scope of the invention as defined in the claims.