Heat engine comprising a system for varying the compression ratio

Abstract

A heat engine includes a system for varying the compression ratio of the engine. The compression ratio varying system comprises: at least one eccentric part rotatably mounted on a crank pin. The eccentric part has an eccentric outer face that co-operates with one end of a rod, as well as at least one ring gear. A device for controlling the angular position of the eccentric part, includes an actuating pinion mounted on an actuating shaft. The control device also comprises at least one stepped intermediate pinion having at least first and second steps each formed by a pinion, the pinion of the first step meshing with the actuating pinion and the pinion of the second step meshing with the gear of the eccentric part.

Claims

1. A heat engine including a system configured to vary a compression ratio of said engine, said system comprising: a crankshaft having a crankshaft crankpin supported on a crank arm, at least an eccentric part which is rotatably mounted on the crankshaft crankpin, wherein said eccentric part comprises an external face including an eccentric shape which is intended to cooperate with an end of a connecting rod, as well as at least a gear, a control device configured to control a rotational position of said eccentric part which comprises an actuating pinion which is mounted on an actuating shaft that passes through the crank arm, wherein said control device further comprises at least a stepped intermediate pinion, which comprises at least a first and a second stage that are each formed by a pinion, wherein the pinion of said first stage meshes with said actuating pinion and the pinion of said second stage meshes with said gear of the eccentric part.

2. The heat engine according to claim 1 and wherein the pinions of the first and second stages are located at a same side of the crank arm.

3. The heat engine according to claim 1 and wherein the pinion of said first stage has a diameter which is smaller than a diameter of the pinion of said second stage.

4. The heat engine according to claim 1 wherein the pinion of said first stage comprises less teeth than the pinion of said second stage.

5. The heat engine according to claim 1 wherein said pinions of said first and second stages have substantially a same axial thickness with respect to each other.

6. The heat engine according to claim 1 wherein said pinions of said first and second stages are assembled together by shrinking.

7. The heat engine according to claim 1 wherein said pinions of said first and second stages are located at either side of a support plate.

8. The heat engine according to claim 7 wherein said support plate comprises a fastener configured to attach the support plate on a crankshaft flange.

9. The heat engine according to claim 7, wherein said pinions of said first and second stages are rotationally guided with respect to said support plate via a bearing.

10. The heat engine according to claim 7 wherein said actuating pinion is rotationally mounted on a pin projecting from said support plate.

11. The heat engine according to claim 7 wherein a gear ratio between said actuating pinion and said gear of the eccentric part is substantially equal to 0.5.

12. The heat engine according to claim 1 wherein said pinions of said first and second stages are assembled together by screwing.

13. The heat engine according to claim 1 wherein said pinions of said first and second stages are assembled together by welding.

14. The heat engine according to claim 1 wherein said pinions of said first and second stages are assembled together by shrinking and/or screwing and/or welding and/or gluing and/or snapping and/or put in cooperation with splines of said pinions.

15. The heat engine according to claim 1 wherein said pinions of said first and second stages are assembled together by gluing.

16. The heat engine according to claim 1 wherein said pinions of said first and second stages are assembled together by snapping.

17. The heat engine according to claim 1 wherein said pinions of said first and second stages are assembled together by being put in cooperation with splines of said pinions.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

(1) Aspects of the invention will be better understood on reading the following description and on examining the accompanying figures. These figures are only given for illustrative reasons, but they are not limiting the invention.

(2) FIG. 1, as already described, is a perspective view of intermediate pinions according to the prior art, each having two meshing planes with the actuating pinion and the gear of the eccentric part, respectively, while FIG. 1a is an end view of a crankshaft according to the prior art;

(3) FIG. 2 is a side view illustrating the integration of the system for varying the compression ratio of a heat engine along the entire length of the crankshaft;

(4) FIG. 3 is a perspective view of the system for varying the compression ratio of a heat engine without the crankshaft;

(5) FIG. 4 is a perspective view of the portion of the system for varying the compression ratio incorporating a stepped intermediate gear, while FIG. 4a is an end view of a crankshaft;

(6) FIG. 5 is an exploded view of a stepped intermediate gear;

(7) FIG. 6 is a schematic front view of a system for varying the compression ratio of a heat engine made according to a variant of the present invention;

(8) FIGS. 7a and 7b are perspective views illustrating the mounting of a stepped intermediate gear on a support plate;

(9) FIGS. 8a and 8b are a perspective view and a perspective partial sectional view, respectively, illustrating mounting of the support plate of FIGS. 7a and 7b on a flange of the crankshaft.

DETAILED DESCRIPTION

(10) FIGS. 1a and 4a show views of the crankshaft with the non-stepped intermediate pinions without step according to the prior art shown in FIG. 1, and with the stepped gears according to the invention shown in FIG. 4, respectively.

(11) In FIGS. 2 to 8, identical, similar, or analogous elements, retain the same reference from one figure to another.

(12) FIG. 2 is a side view of a crankshaft 12 incorporating a system 11 for varying the compression ratio to vary the compression ratio as a function of the operating conditions of the engine. This makes the system 11 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.

(13) More specifically, the engine crankshaft 12 with axis X is intended to be rotatably mounted on a crankcase by means of bearings. The crankshaft 12 comprises a plurality of crankpins 13, and journals 14, separated by flanges 17 extending substantially perpendicular to the axis X. The crankshaft 12 further has a front end intended to be attached in rotational direction with a pulley 18. A flywheel (not shown) is attached in rotatable direction to the rear end of the crankshaft 12.

(14) Eccentric parts 21 are rotatably mounted on the crankpins 13 via a through-hole 22 made in each eccentric part 21. As can be seen more clearly in FIG. 4, each eccentric part 21 comprises an external face 25 of eccentric shape with respect to the axis of the hole 22 and therefore to the corresponding crankpin 13. The outer face 25 is intended to cooperate with a big end of a connecting rod 26, which has its small end rotatably connected to a piston 27 of the engine. Each eccentric part 21 also comprises two gears 28 located at either side of the outer face 25.

(15) A control device 31 which is clearly visible in FIG. 3 makes it possible to adjust the angular position of the eccentric parts 21. For this purpose, the control device 31 comprises an actuating shaft 32 and a cascade of pinions constituted by an actuating pinion 33 mounted on the actuating shaft 32, and a stepped intermediate pinion 36. This intermediate pinion 36 comprises a first and a second stage, each formed by a pinion 37, 38, respectively. The pinion 37 of the first stage meshes with the actuating pinion 33 and the pinion 38 of the second stage meshes with a gear 28. The pinions 37 and 38 are coaxial. It is also possible to use two or more intermediate pinions. It depends on the application.

(16) In order to allow a reduction in the diameter of the actuating pinion 33 and thus a reduction in the size of the assembly, the pinion 37 of the first stage has a smaller diameter than the diameter of the pinion 38 of the second stage. In addition, the pinion 37 of the first stage has less teeth than the pinion 38 of the second stage.

(17) The pinions 37, 38 of the first and second stages have substantially the same axial thickness with respect to each other. This thickness corresponds substantially to half the thickness of an intermediate pinion of the prior art.

(18) As can be seen in FIG. 5, to ensure assembly of the pinions 37, 38 together, one of the two pinions, here the pinion 37 comprises a sleeve 41 including a central hole to allow passage of a shaft. This sleeve 41 projects in axial direction from an end face of the annular portion that carries the teeth of the pinion 37.

(19) The two sprockets 37, 38 may be assembled by shrinking and/or screwing between the external axial cylindrical face 42 of the sleeve 41 and the internal axial cylindrical face 43 of the annular toothed portion of the pinion 38. The faces 42, 43 may also be welded or glued together by a welding zone and/or gluing zone extending continuously along the entire periphery or via a few points of equidistant welds. It is also possible to provide grooves (fretted or not) of complementary shape arranged in the faces 42, 43 of the pinions 37, 38. A snap-fit assembly of the pinions 37, 38 is also conceivable. Alternatively, the assembly is reversed, that is to say that the pinion 38 comprises the sleeve 41 that penetrates inside the central opening of the pinion 37.

(20) In the embodiment of FIGS. 7a to 8b, the pinions 37 and 38 are located on either side of a support plate 46. The support plate 46 comprises fixing means 47 to be fixed on a flange 17 of the crankshaft, so that at least a portion of at least one of the gears, in this case the pinion 37 (see FIG. 8b) and a portion of the plate 46 is housed in a recess in the flange 17. In this case, these fixing means 47 comprise two screws 48 passing through holes made in a flange 49 of the plate 46 intended to cooperate with corresponding threaded bores formed in the thickness of the flange 17 (see FIG. 8a), such that a third screw 48 passes through an opening made on the side of an opposite end of the plate 46 and intended to cooperate with a threaded bore made in a transverse face of the flange 17. Alternatively, the screws 48 may be replaced by rivets or pins, or any other means of attachment adapted to the application.

(21) The pinions 37 and 38 are rotationally guided with respect to the support plate 46 via a bearing 52, such as a needle-type bearing which is visible in FIG. 8b. For this purpose, the needle bearing 52 is mounted on a shaft 53 which passes through an opening made in the support plate 46.

(22) As shown in FIG. 7b, the actuating pinion 33 is rotatably mounted on a pin 56 projecting from the support plate 46. The pin 56 may be attached to or made of one material with the support plate 46. This ensures guiding of the shaft 32 and the actuating pinion 33. The actuating pinion 33 meshes with the pinion 37 on one side of the support plate 46, while the pinion 38 meshes with the gear 28 of an eccentric part 21 on the other side of the support plate 46 (see FIGS. 7b and 8a).

(23) In operation and when the actuating shaft 32 is rotationally fixed with respect to the crankcase, the system has a configuration of fixed compression ratio. Upon changing compression ratio, the angular position of the eccentric part 21 located on the side of the pulley 18 is controlled by the angular position of the actuating shaft 32 so as to change to a new compression ratio. For this purpose, the actuating shaft 32 may be actuated for example by means of a wheel and worm gear 57 (see FIG. 3), or any other means for moving the adapted shaft.

(24) A gear ratio between the actuating pinion 33 and the gear 28 of the eccentric part is substantially equal to 0.5. This ensures a rotation of the eccentric part 21 at half speed with respect to the rotational speed of the crankshaft.

(25) In addition, as illustrated in FIG. 3, through the journals 14 of the crankshaft 12, shafts 58 and so-called transfer pinions 59 transmit the same kinematics of the eccentric part located on the side of the actuating shaft 32 step by step on all the other eccentric parts of the crankshaft 12. To this end, the pinions 59 mounted on the shafts 58 mesh with the gears 28 of the other eccentric parts.

(26) In a variant, as illustrated by FIG. 6, the invention may also be implemented in a so-called cassette epicyclic gear arrangement integrated inside or in the vicinity of the accessory crankshaft pulley 18. In this case, an assembly of stepped intermediate pinions 36 each mesh with the actuating pinion 33, on the one hand, and with a satellite pinion 61 reversing the direction of rotation, on the other hand. Each satellite pinion 61 also meshes with a transfer pinion 59.

(27) FIGS. 1a and 4a demonstrate an important advantage provided by the invention:FIG. 1a shows, according to the prior art, the crankshaft V in which is dug a pocket P which houses the non-stepped intermediate pinion. This pocket is close to the crankpin M.in FIG. 4a, according to the invention, the crankshaft has a pocket P which has smaller dimensions, because of the stepping of the intermediate pinion. In addition, it is noted that this pocket is further away from the crankpin: not only the pocket P (the cavity) is smaller, but in addition it is further away from the region of vicinity of the crankpin, which is an important region in terms of mechanical strength, where it is important to keep a sufficient thickness to precisely ensure the mechanical strength of the part.

(28) Due to the stepping of the intermediate pinion in two new intermediate pinions 36, 37, it is possible to reduce the number of teeth of the actuating pinion 33. For example: the intermediate pinion 36 meshes with the eccentric by 28 teeth and the intermediate pinion 37 meshes with the actuating pinion by 20 teeth: only 15 teeth are required for the actuating pinion 33 in order to make the kinematics of ratio 0.5 between actuation and eccentric. The number of teeth of the intermediate pinion does not have any impact on the kinematics, the actuating pinion is thus reduced in size (diameter), the pocket on the crankshaft is also reduced, which limits the impact on the strength of this crank arm.

(29) In the case of the comparative example without stepping (FIGS. 1 and 1a), for example if the eccentric 2 has 42 teeth, with a non-stepped intermediate pinion 5, the actuating pinion 4 must, on the contrary, necessarily have 21 teeth so as to have a ratio of 0.5 between actuation and eccentric.