阅读说明：本技术 用于往复活塞式机器的曲柄传动机构及具有这种曲柄传动机构的往复活塞式机器 (Crank drive for a reciprocating piston machine and reciprocating piston machine having such a crank drive ) 是由 U·古特泽 于 2018-04-20 设计创作，主要内容包括：本发明涉及一种用于往复活塞式机器的曲柄传动机构(1),包括：曲轴(2),其具有至少一个曲柄销(6)；至少一个以能旋转的方式设置在曲柄销(6)上的偏心部(7),借助偏心部,至少一个连杆以能旋转的方式能支承在曲柄销(6)上,活塞通过连杆能铰接地与曲轴(2)耦合,活塞以能平移运动的方式能设置在往复活塞式机器的具有可变压缩比的气缸中；至少一个与曲轴(2)同轴地设置的调节轴(9),通过调节轴,通过驱动调节轴(9),偏心部(7)能相对于曲柄销(6)扭转,由此可调节气缸的压缩比；调整环节(10),借助调整环节能驱动调节轴(9),调整环节(10)设置在曲轴(2)的端部(13)上且沿曲轴(2)的轴向方向连接到曲轴上。(The invention relates to a crank drive (1) for a reciprocating piston machine, comprising: a crankshaft (2) having at least one crank pin (6); at least one eccentric (7) arranged rotatably on the crank pin (6), by means of which at least one connecting rod can be mounted rotatably on the crank pin (6), by means of which connecting rod a piston can be coupled in an articulated manner to the crankshaft (2), which piston can be arranged in a cylinder of a reciprocating piston machine with variable compression ratio in a translatory manner; at least one adjusting shaft (9) arranged coaxially to the crankshaft (2), by means of which the eccentric (7) can be twisted relative to the crank pin (6) by driving the adjusting shaft (9), whereby the compression ratio of the cylinder can be adjusted; the adjusting link (10) drives the adjusting shaft (9) by means of the adjusting ring in an energy-saving manner, and the adjusting link (10) is arranged on the end part (13) of the crankshaft (2) and is connected to the crankshaft along the axial direction of the crankshaft (2).)

1. Crank drive (1) for a reciprocating piston machine, comprising: a crankshaft (2) having at least one crank pin (6); at least one eccentric (7) arranged rotatably on the crank pin (6), by means of which at least one connecting rod is supported rotatably on the crank pin (6), by means of which connecting rod a piston can be coupled in an articulated manner to the crankshaft (2), which piston can be arranged in a translatory manner in a cylinder of the reciprocating piston machine with variable compression ratio; at least one adjusting shaft (9) arranged coaxially to the crankshaft (2), by means of which the eccentric (7) can be rotated relative to the crank pin (6) by driving the adjusting shaft (9), whereby the compression ratio of the cylinder can be adjusted; and an adjusting element (10) by means of which the adjusting shaft (9) can be driven, characterized in that the adjusting element (10) is arranged at an end (13) of the crankshaft (2) and is connected to the crankshaft (2) in the axial direction thereof.

2. Crank drive (1) according to claim 1, characterized in that the adjusting shaft (9) passes completely through at least one main journal (3") of the crankshaft (2) in the axial direction of the crankshaft (2).

3. Crank-drive mechanism (1) according to claim 2, characterized in that the at least one main journal (3") is the last main journal (3") of the crankshaft (2) in the axial direction of the crankshaft (2).

4. Crank drive (1) according to one of the preceding claims, characterized in that the adjustment link (10) is arranged coaxially to the crankshaft (2).

5. Crank drive (1) according to one of the preceding claims, characterized in that the adjusting element (10) can be rotated about a rotational axis (20), in particular relative to the crankshaft (2), for driving the adjusting shaft (9).

6. Crank drive (1) according to claims 4 and 5, characterized in that the axis of rotation (20) of the adjustment link (10) coincides with the crankshaft axis of rotation (4), about which the crankshaft (2) can rotate during operation of the reciprocating piston machine, in particular relative to the crankcase.

7. Crank drive (1) according to claim 5 or 6, characterized in that the adjustment link (10) rotates permanently around the axis of rotation (20) together with the crankshaft (2) during the rotation of the crankshaft (2) around its crankshaft rotation axis (4) and no adjustment of the compression ratio takes place.

8. A crank-drive (1) according to claim 7, characterized in that the adjusting element (10) rotates permanently with the crankshaft (2) about the axis of rotation (20) at a fixed rotational speed ratio relative to the crankshaft (2) during the rotation of the crankshaft (2) about its crankshaft axis of rotation (4), and no adjustment of the compression ratio takes place.

9. A crank gear (1) according to claim 5 or 6, characterized in that during the rotation of the crankshaft (2) about its crankshaft rotation axis (4), no rotation of the adjustment link (10) about the rotation axis (20) takes place and no adjustment of the compression ratio takes place.

10. Crank drive (1) according to one of the preceding claims, wherein the adjustment element (10) is designed as a ring gear (21) of a planetary gear (22) having a ring gear (21), a sun gear (23), a planet gear carrier (24) and at least one planet gear (25) which meshes with the sun gear (23) and with the ring gear (21) and is mounted on the planet gear carrier (24) in a rotatable manner.

11. Crank drive (1) according to claim 10, characterized in that the planet carrier (24) is connected to the crankshaft (2) in a rotationally fixed manner.

12. Crank drive (1) according to claim 10 or 11, wherein the sun gear (23) is connected to the adjusting shaft (9) in a rotationally fixed manner.

13. Crank drive (1) according to one of claims 10 to 12, characterized in that a worm drive (27) is provided, by means of which the ring gear (21) can be driven and thus rotated, whereby the adjusting shaft (9) can be driven.

14. Reciprocating piston machine for a motor vehicle, comprising at least one cylinder with a variable compression ratio, comprising a crankcase and comprising a crank drive (1) having:

-at least one piston received in the cylinder in a translatory motion;

-at least one connecting rod hingedly coupled to the piston;

-a crankshaft (2) comprising at least one crank pin (6) and at least one main journal (3) by means of which the crankshaft (2) is supported on a crankcase in a manner rotatable relative thereto about a crankshaft axis of rotation (4);

-at least one eccentric (7) arranged rotatably on a crank pin (6), by means of which the connecting rod is supported rotatably on the crank pin (6), whereby the piston is coupled hingedly with the crankshaft (2);

-at least one adjusting shaft (9) arranged coaxially with the crankshaft (2), by means of which adjusting shaft the eccentric (7) can be twisted relative to the crankpin (6) by driving the adjusting shaft (9), whereby the compression ratio of the cylinder can be adjusted; and

an adjusting element (10) by means of which the adjusting shaft (9) can be driven,

characterized in that the adjustment link (10) is arranged at an end (13) of the crankshaft (2) and is connected to the crankshaft (2) in the axial direction of the crankshaft.

Technical Field

The present invention relates to a crank drive for a reciprocating-piston machine, in particular for a motor vehicle, according to the preamble of claim 1, and to a reciprocating-piston machine, in particular for a motor vehicle, having such a crank drive according to the preamble of claim 14.

Background

Such a crank drive for a reciprocating piston machine, in particular for a motor vehicle, and a reciprocating piston machine, in particular for a motor vehicle, having such a crank drive are known, for example, from DE 102011018166 a 1. The reciprocating piston machine has at least one combustion chamber with a variable compression ratio in the form of a cylinder and a crankcase. The crank mechanism has at least one piston which is received in a cylinder in a translatory manner. This means that the piston can be moved to and fro in a translatory manner in the cylinder, so that the piston can be moved in an oscillating manner in the cylinder. The crank mechanism furthermore has at least one connecting rod which is coupled to the piston in an articulated manner, for example by means of a piston pin. The crank mechanism also has a crankshaft, which is the output shaft of a reciprocating piston engine, which is designed, for example, as an internal combustion engine. By means of the crankshaft, the reciprocating piston machine can provide a torque, in particular for driving a motor vehicle. The crankshaft has at least one crank pin and at least one main journal, by means of which the crankshaft is mounted on the crankcase so as to be rotatable about a crankshaft axis of rotation relative to the crankcase. The crankshaft axis of rotation is also referred to as the crankshaft axis, wherein the crankpin is arranged eccentrically with respect to the crankshaft axis.

The crank drive also has at least one eccentric portion arranged rotatably on the crank pin, which eccentric portion is thus rotatable relative to the crank pin. By means of the eccentric, the connecting rod is mounted on the crank pin in a rotatable manner, whereby the piston is coupled in an articulated manner to the crankshaft. By this articulated coupling of the piston with the crankshaft, the translational movement of the piston in the cylinder is converted into a rotational movement of the crankshaft about its crankshaft axis of rotation.

Furthermore, at least one adjusting shaft is provided, which is arranged coaxially to the crankshaft and by means of which the eccentric can be rotated relative to the crank pin by driving the adjusting shaft. Thereby, the compression ratio of the cylinder can be adjusted. Furthermore, the crank mechanism has an adjusting element, which is also referred to as an adjusting element. In this case, by means of the adjustment element, the adjustment shaft can be driven and, as a result, the compression ratio can be adjusted or changed.

Disclosure of Invention

The object of the present invention is to provide a crank mechanism and a reciprocating piston machine of the type mentioned above, so that particularly advantageous operation of the reciprocating piston machine can be achieved.

According to the invention, this object is achieved by a crank drive having the features of claim 1 and by a reciprocating piston machine having the features of claim 14. Advantageous embodiments of the invention are the subject matter of the dependent claims.

A first aspect of the invention relates to a crank drive for a reciprocating piston machine, in particular for a motor vehicle (e.g. a motor vehicle). The reciprocating piston machine is preferably designed as an internal combustion engine or as an internal combustion engine, wherein, for example, a motor vehicle, in particular designed as a passenger vehicle, can be driven by means of the reciprocating piston machine. The crank mechanism has a crankshaft, which is the output shaft of the reciprocating piston engine. The reciprocating piston machine can provide a torque, in particular for driving a motor vehicle, for example via a crankshaft. The crankshaft has at least one crank pin, which is arranged eccentrically, for example, with respect to a main journal of the crankshaft. The main journal, for example, the crankshaft is mounted on a crankcase of the reciprocating piston machine in a rotatable manner, so that the crankshaft can rotate about a crankshaft axis of rotation, also referred to as crankshaft axis, relative to the crankcase, in particular during operation and in this case in particular during operation of the ignition of the reciprocating piston machine.

The crank mechanism furthermore has at least one eccentric part, which is arranged on the crank pin in a rotatable manner. This means that the eccentric can rotate relative to the crank pin. By means of the eccentric, at least one connecting rod is rotatably mounted or is to be mounted on the crank pin. The piston of the reciprocating piston machine is coupled or can be coupled to the crankshaft in an articulated manner by means of a connecting rod, wherein the piston is arranged in a translatory manner or can be arranged in a cylinder of the reciprocating piston machine with a variable compression ratio. In the finished state of the reciprocating piston machine, the piston can be translationally oscillated in the cylinder. In other words, the piston can be moved back and forth in a translatory manner, wherein the piston is connected, for example, hingedly to a connecting rod. The piston is thereby connected in an articulated manner to the crank pin and thus to the crankshaft as a whole via a connecting rod, whereby a translational movement of the piston in the cylinder is converted into a rotational movement of the crankshaft about the crankshaft axis of rotation.

During the preceding ignition operation, a combustion process is carried out in the cylinder, in the region of which the respective fuel-air mixture is combusted. Thereby, the piston is driven, whereby the piston moves translationally in the cylinder. By the articulated coupling of the piston with the crankshaft, the crankshaft is rotated about its crankshaft axis of rotation relative to the crankcase by driving the piston.

The crank mechanism furthermore has at least one adjusting shaft, which is arranged coaxially to the crankshaft and is also referred to as a synchronizing shaft, for example. By means of the adjusting shaft, the eccentric can be twisted relative to the crank pin by driving the adjusting shaft, whereby the compression ratio of the cylinder can be adjusted or adjustable. In other words, if the actuating shaft is driven by means of an actuating element, also referred to as an actuating element, the actuating shaft rotates or twists, for example, about an actuating shaft rotation axis, in particular, relative to the crankshaft. By rotating, in particular at least indirectly, the adjusting shaft about the adjusting shaft rotational axis, the eccentric rotates or twists relative to the crank pin, in particular about the eccentric rotational axis. Since the eccentric portion, in particular the side surface of the outer peripheral side thereof, is eccentric to an eccentric rotation axis that coincides with the central axis of the crank pin, for example, the connecting rod is moved relative thereto in the radial direction of the crank pin by the rotation of the eccentric portion relative to the crank pin about the eccentric rotation axis, whereby the compression ratio is changed. In particular, the stroke height of the piston can be changed by the twisting of the eccentric portion relative to the crank pin about the eccentric rotation axis, which is accompanied by a change in the compression ratio.

In order to now achieve a particularly advantageous and, in particular, low-emission and energy-consuming operation of the reciprocating piston engine, it is provided according to the invention that the actuating element is arranged at one end of the crankshaft and is connected to the crankshaft or to the one end in the axial direction of the crankshaft. The invention is based on the object of providing an adjustment element which is, as is conventional, either in the center or at the edge of the engine and which interacts at least indirectly with or with the eccentric. This is to be understood in particular in that the actuating element is not usually connected to the crankshaft substantially in the axial direction of the crankshaft and is therefore not arranged at the end of the crankshaft, but rather the actuating element is usually arranged in a plane which is intersected by the crankshaft. In order to be able to vary the compression ratio, a structure is required in the installation space, which is usually provided for the crankshaft, in particular in the case of reciprocating piston machines without a variable compression ratio. This leads to a weakening of the crankshaft, especially when the reciprocating piston machine is to be held constant in its basic dimensions compared to the reciprocating piston machine without a variable compression ratio. Furthermore, such a design can lead to a loss of efficiency, which can now be avoided with the crank mechanism according to the invention. In other words, by adjusting the arrangement of the link on the one end of the crankshaft, weakening of the crankshaft can be avoided, so that a particularly efficient and therefore low-emission and energy-consuming, in particular low-fuel-consuming operation of the reciprocating piston engine, preferably designed as an internal combustion engine, can be achieved as a result.

The eccentric portion is designed, for example, as an eccentric bearing shell, which can be rotated relative to the crank pin for adjusting or changing the compression ratio. The change or adjustment of the compression ratio is also referred to as compression adjustment. If, for example, a plurality of cylinders and, therefore, a plurality of crankpins and a plurality of eccentrics are provided, for example, at least one synchronizing shaft is used for at least two of the eccentrics, by means of which the eccentrics provided for the respective cylinders are coupled to one another. The respective eccentric is usually rotated by a non-rotating, rotatable shaft, whereby the phase angle of the eccentric is adjusted. An unrotatable, rotatable shaft is to be understood in particular to mean that the shaft can be rotated about an adjustment axis of rotation, in particular relative to the crankshaft, in order to adjust or change the compression ratio as a result, but that during the rotation of the crankshaft about the crankshaft axis of rotation the shaft does not rotate and no adjustment of the compression ratio takes place, i.e. the compression ratio remains constant. In contrast, in the crank mechanism according to the invention, the adjusting shaft can be designed as a rotating adjusting or synchronizing shaft, which rotates permanently together with the crankshaft about its adjusting shaft axis of rotation during the rotation of the crankshaft about its crankshaft axis of rotation and no adjustment of the compression ratio takes place, i.e. the compression ratio is at least substantially kept constant.

In an advantageous embodiment of the invention, the adjusting shaft passes completely through at least one main journal of the crankshaft in the axial direction of the crankshaft. In this case, the adjusting shaft preferably extends in the center of the main journal, so that weakening of the crankshaft can be avoided.

In this case, it is preferably provided that the at least one main journal is the last main journal of the crankshaft in the axial direction of the crankshaft. In this way, a particularly space-saving arrangement of the adjustment element can be achieved, so that an undesired weakening of the crankshaft can be avoided.

In a further advantageous embodiment of the invention, the adjustment element is arranged coaxially with the crankshaft, as a result of which a particularly efficient operation can be achieved.

It is particularly advantageous to show that the adjusting ring can be rotated about a rotational axis, in particular relative to the crankshaft, in order to drive the adjusting shaft. In this case, it is preferably provided that the axis of rotation of the adjustment element coincides with the previously described axis of rotation of the adjustment shaft.

In a particularly advantageous embodiment of the invention, the axis of rotation of the adjustment element coincides with the axis of rotation of the crankshaft, about which the crankshaft can rotate during operation of the reciprocating piston engine, in particular relative to the crankcase.

Furthermore, it is shown as particularly advantageous that during the rotation of the crankshaft about its crankshaft axis of rotation, the actuating element is permanently rotated about the axis of rotation together with the crankshaft, and no adjustment of the compression ratio takes place, that is to say the compression ratio is constant. In other words, it is provided that the adjusting element rotates permanently or always together with the crankshaft about its axis of rotation when the crankshaft rotates about its crankshaft axis of rotation and no adjustment of the compression ratio takes place. The adjusting element is therefore preferably designed as a rotary adjusting element, by means of whose rotational speed the phase angle of the eccentric, which is preferably designed as a bearing shell, relative to the crank pin can be adjusted. Thereby, the compression ratio can be finally adjusted.

In this case, it is particularly advantageous to show that the rotating adjustment element rotates with the crankshaft at a fixed rotational speed ratio relative to the crankshaft at a constant compression ratio. In this case, for example, energy flows to the control element, which can thus be operated, for example, in the manner of a generator. In this case, the actuating element is driven by the crankshaft via an actuating shaft, for example. In this case, it is conceivable for the actuating element to be operated as a generator, by means of which the mechanical energy provided by the actuating shaft, for example, can be converted into electrical energy. The electrical energy can be provided, for example, wherein the provided electrical energy is at least substantially directly supplied to at least one electrical consumer and/or can be stored in an energy store.

Furthermore, it is conceivable to achieve a throughflow from the actuating element, in particular to the actuating shaft, wherein the actuating element then operates, for example, in the form of a motor. This is provided, for example, for adjusting or regulating the compression ratio. Thus, for example, the actuating element can be operated as a motor in order to drive the actuating shaft. In particular, a diverse control, in particular control, is possible in the rotational actuating element, whereas the controlled rotational speed ratio between the rotational actuating element and the crankshaft and the overall system (in particular with respect to the plain bearing) should be compatible.

Furthermore, it is conceivable for the adjustment element to be designed as an unrotated, rotatable adjustment element. This means that during the rotation of the crankshaft about its crankshaft axis of rotation, no rotation of the adjustment element about its axis of rotation takes place and no adjustment of the compression ratio takes place. However, in order to change the compression ratio, the actuating element rotates about its axis of rotation, in particular relative to the crankshaft.

In order to achieve particularly efficient operation and to be able to adjust the compression ratio particularly as required and precisely, it is preferably provided that the adjustment element is designed as a ring gear of the planetary gear. The planetary gear set has a ring gear, a sun gear, a planet gear carrier and at least one planet gear, which meshes with the sun gear and with the ring gear and is mounted on the planet gear carrier in a rotatable manner. The planet carrier is also referred to as planet carrier, for example.

In this case, the planet carrier is connected to the crankshaft in a rotationally fixed manner, as is shown to be particularly advantageous. Thereby, a particularly efficient operation may be presented.

It is also particularly advantageous to show that the sun gear is connected to the adjusting shaft in a rotationally fixed manner. The compression ratio can thereby be adjusted particularly advantageously, in particular by twisting the ring gear (in particular with respect to the crankshaft). By twisting the ring gear (in particular via the planet gears), the sun gear is twisted and the adjusting shaft is twisted together with the sun gear, whereby the compression ratio can be adjusted as desired and precisely.

Finally, it is particularly advantageous to provide a worm gear, by means of which the ring gear can be driven and thus rotated, whereby the adjusting shaft can be driven. The worm drive is also referred to as a worm gear and preferably has a self-locking, so that, for example, when it is desired not to change the compression ratio but to keep it constant, the ring gear is fixed or secured against rotation about the axis of rotation of the adjustment element by the worm drive, in particular by its self-locking. Thus, no additional actuators, such as brakes or clutches, are required in order to avoid undesired rotation of the adjusting member (ring gear) and thus undesired adjustment of the compression ratio, but rather this is done by the worm drive and in particular by self-locking thereof. The number of components, the weight and the installation space requirement of the crank mechanism can thereby be kept particularly low, so that a particularly efficient operation can be achieved.

A second aspect of the invention relates to a reciprocating-piston machine for a motor vehicle, preferably configured as an internal combustion engine, comprising: at least one cylinder having a variable compression ratio; a crankcase; and a crank drive, in particular according to the first aspect of the invention.

The crank mechanism of the second aspect of the invention has at least one piston accommodated in a cylinder in a translatory manner and at least one connecting rod coupled to the piston in an articulated manner. The crank mechanism furthermore has a crankshaft, which comprises at least one crank pin and at least one main journal, by means of which the crankshaft is mounted on the crankcase so as to be rotatable relative to the crankcase about a crankshaft axis of rotation. The crank mechanism furthermore has at least one eccentric which is arranged on the crank pin in a rotatable manner and by means of which the connecting rod is mounted on the crank pin in a rotatable manner, whereby the piston is coupled in an articulated manner to the crankshaft. As a result, a translational movement of the piston in the cylinder may be converted into a rotational movement of the crankshaft about its crankshaft rotational axis. The crank mechanism furthermore has at least one adjusting shaft arranged coaxially to the crankshaft, by means of which the eccentric can be rotated relative to the crank pin by driving the adjusting shaft, whereby the compression ratio of the cylinder can be adjusted or adjustable or variable. The crank drive furthermore has an adjusting element, by means of which the adjusting shaft can be driven.

In order to now make possible a particularly efficient operation and therefore low emissions and energy consumption, it is provided according to the invention that the actuating element is arranged at the end of the crankshaft and is connected to the crankshaft in the axial direction of the crankshaft. The advantages and advantageous embodiments of the first aspect of the invention are to be regarded as advantages and advantageous embodiments of the second aspect of the invention and vice versa.

Drawings

Further details of the invention emerge from the following description of a preferred embodiment with the aid of the attached drawings. In the drawings:

fig. 1 shows a schematic side view of a crank drive according to the invention for a reciprocating piston machine according to a first embodiment; and

fig. 2 shows a schematic side view of a crank drive according to a second embodiment.

Detailed Description

In the figures, identical or functionally identical elements are provided with the same reference numerals.

Fig. 1 shows a schematic side view of a first embodiment of a crank drive 1 for a reciprocating piston engine, in particular for a motor vehicle. The motor vehicle is designed, for example, as a motor vehicle, in particular as a passenger vehicle, and can be driven by means of a reciprocating piston machine. The reciprocating piston machine is designed as an internal combustion engine or as an internal combustion engine and has at least one combustion chamber designed as a cylinder. In particular, reciprocating piston machines have a plurality of cylinders. Furthermore, the reciprocating piston machine has a crankcase, which is designed for example as a cylinder crankcase, by means of which for example cylinders are formed. As is explained in more detail below, the respective cylinder has a variable compression ratio, the value of which can be varied and is therefore adjustable. Each cylinder of the crank gear 1 has, for example, a piston, not shown in the drawing, which is received in the respective cylinder in a translatorily movable manner and which is reciprocable in the cylinder in a translatorily movable manner. During ignition operation of the reciprocating piston machine, the respective cylinder is supplied with fuel, in particular liquid fuel, for operating the reciprocating piston machine and with air, so that a fuel-air mixture is produced in the respective cylinder. The respective fuel-air mixture is ignited and thereby burnt, whereby the respective cylinder is driven, that is to say moves in translation relative to the crankcase.

In this case, each piston of the crank mechanism 1 has a connecting rod, which is coupled to the respective piston in an articulated manner and is not shown in the figures, for example by means of a piston pin. Thereby, the translational movement of the piston can be transferred to the respective connecting rod.

The crank gear 1 furthermore has a crankshaft 2 with a plurality of main journals 3, 3' and 3 ″ which are spaced apart from one another in the axial direction of the crankshaft 2 and are arranged one behind the other. The crankshaft 2 is mounted on the crankcase in a rotatable manner via the main journals 3, 3' and 3 ″ so that the crankshaft 2 can rotate relative to the crankcase about a crankshaft rotation axis 4. The rotatability of the crankshaft 2 about the crankshaft axis of rotation 4 relative to the crankcase is illustrated in fig. 1 by means of an arrow 5.

Furthermore, the crankshaft 2, in particular each cylinder, has a crankpin 6 or 6' which is arranged eccentrically with respect to the crankshaft axis of rotation 4 and thus executes a reciprocating stroke when the crankshaft 2 rotates about the crankshaft axis of rotation 4 relative to the crankcase. In this case, an eccentric portion 7 or 7 'is mounted or arranged on the respective crank pin 6 or 6' in a rotatable manner, so that the respective eccentric portion 7 or 7 'can be rotated about an eccentric axis of rotation 8 relative to the respective crank pin 6 or 6'. As can be seen particularly well in fig. 1, the eccentric rotational axis 8 extends at least substantially parallel to the crankshaft rotational axis 4 and is spaced apart from or axially offset from the crankshaft rotational axis 4.

By means of the respective eccentric 7 or 7', the respective connecting rod is rotatably supported on the respective crankpin 6 or 6', whereby the piston is coupled in an articulated manner via a piston pin, the connecting rod and the respective eccentric 7 or 7 'with the respective crankpin 6 or 6' and thus with the crankshaft 2 as a whole. By this articulated coupling of the respective piston to the crankshaft 2, a respective translational movement of the respective piston can be converted into a rotational movement of the crankshaft 2 about the crankshaft rotation axis 4. The result is therefore that the crankshaft 2 is driven and thus rotates about the crankshaft axis of rotation 4 relative to the crankcase if the respective piston is driven as explained before. In this way, the reciprocating piston engine can provide a torque for driving the motor vehicle via the crankshaft 2 during the ignition mode.

The crank mechanism 1 furthermore has at least one adjusting shaft 9, which is arranged coaxially with the crankshaft 2 or with the crankshaft axis of rotation 4 and by means of which the respective eccentric 7 or 7 'can be rotated relative to the respective crank pin 6 or 6' by driving the adjusting shaft 9. Thereby, the compression ratio of the corresponding cylinder can be adjusted. Furthermore, at least one adjusting element 10, also referred to as an adjusting element, is provided, by means of which the adjusting shaft 9 can be driven. By driving the adjusting shaft 9, it rotates about an adjusting shaft rotational axis 11, in particular relative to the crankshaft 2 and relative to the crankcase, wherein the adjusting shaft rotational axis 11 coincides with the crankshaft rotational axis 4. By rotation of the adjusting shaft 9 about the adjusting shaft axis of rotation 11, the respective eccentric 7 or 7 'is twisted about the eccentric axis of rotation 8 relative to the respective crank pin 6 or 6', thereby changing the compression ratio of the respective cylinder. The compression ratio is varied in such a way that the respective eccentric section 7 or 7', in particular the side face on the outer circumference side thereof, is formed eccentrically with respect to the eccentric axis of rotation 8. The eccentric axis of rotation 8 coincides here, for example, with the center axis of the respective crank pin 6 or 6'. If the respective eccentric section 7 or 7 'is thus rotated about the eccentric axis of rotation 8 relative to the respective crank pin 6 or 6', the respective connecting rod and thus the respective piston are thereby moved in the radial direction of the respective crank pin 6 or 6 'relative to the respective crank pin 6 or 6', thereby for example adjusting or varying the stroke height of the piston and thus the respective compression ratio of the respective cylinder.

The respective eccentric section 7 or 7 'is designed, for example, in the form of an eccentric bushing, by means of which the respective connecting rod is rotatably mounted on the respective crank pin 6 or 6'. As can be seen in particular from fig. 1, the main journals 3, 3 'and 3 ″ are connected to the crank pins 6 and 6' via respective crank arms 14. In order to be able to turn the respective eccentric section 7 or 7 'relative to the crank pin 6 or 6', the respective eccentric section 7 or 7 'has a toothing 12 or 12', which is configured, for example, in the manner of an external toothing, the function of which is explained in more detail below.

In order to now avoid excessive weakening of the crankshaft 2 as a result of the use of a variable compression ratio and as a result to enable particularly efficient and therefore emission-and fuel-efficient operation of the reciprocating piston engine, the adjusting element 10 is arranged at an end 13 of the crankshaft 2 and is connected in the axial direction of the crankshaft 2 to the crankshaft 2, in particular to said end 13. The axial direction of the crankshaft 2 coincides with the crankshaft rotation axis 4.

As can be seen from fig. 1, the adjusting shaft 9 is connected in a rotationally fixed manner to a gear wheel 15, which meshes with the toothing 12 'and thus with the eccentric 7'. Thus, if the adjusting shaft 9 rotates about the adjusting shaft axis of rotation 11, in particular relative to the crankshaft 2, the eccentric 7 'is driven by the gear 15 and thereby twisted relative to the crank pin 6' about the eccentric axis of rotation 8.

The adjusting shaft 9 is also referred to as synchronizing shaft. The crank mechanism 1 has a further synchronizing shaft 16, also referred to as an adjusting shaft, which is connected in a rotationally fixed manner to the toothed wheels 17 and 18 and can rotate about the adjusting shaft axis of rotation 11, in particular relative to the crankshaft 2. Here, the synchronizing shaft 16 is also provided coaxially with the crankshaft 2. The gear 17 meshes with the toothing 12 'configured in the manner of an external toothing and thus with the eccentric portion 7', so that when the eccentric portion 7 'rotates about the eccentric rotation axis 8 relative to the crank pin 6', the gear 17 and the synchronizing shaft 16 rotate about the adjustment shaft rotation axis 11 relative to the crankshaft 2. In this case, the gear wheel 18 also rotates about the adjusting shaft axis of rotation 11 relative to the crankshaft 2, since the gear wheel 18 is connected in a rotationally fixed manner to the synchronizing shaft 16. The gear wheel 18 meshes here with the toothing 12, which is configured as an external toothing, and thus with the eccentric portion 7, so that the eccentric portion 7 is twisted about the eccentric axis of rotation 8 relative to the crank pin 6 by rotation of the gear wheel 18 about the adjustment shaft axis of rotation 11 relative to the crankshaft 2. The eccentrics 7 and 7' are therefore coupled, in particular torsionally fixed, to one another via the gears 17 and 18 and the synchronizing shaft 16, so that when the adjusting shaft 9 is rotated about the adjusting shaft axis of rotation 11, in particular relative to the crankshaft 2, by means of the adjusting element 10, the eccentrics 7 and 7' are simultaneously or synchronously rotated about the eccentric axis of rotation 8 relative to the crank pins 6 and 6 '. The adjusting shaft 9 is therefore a synchronizing shaft which is provided in addition to a synchronizing shaft 16 to which the adjusting element 10 provided at the end 13, also referred to as crankshaft end, is attached, in particular at least indirectly.

As can be seen from fig. 1, the adjusting shaft 9 extends in the center of the main journal 3 ″ and in this case passes completely through the main journal 3 ″ in the axial direction of the crankshaft 2. This means that the adjusting shaft 9 projects from the main journal 3 "or beyond it at both ends or on both sides in the axial direction of the crankshaft 2. Here, the main journal 3 ″ is the last main journal of the crankshaft 2 in the axial direction of the crankshaft 2, in particular on the end 13 side. At an end 19 of the crankshaft 2, which is opposite the end 13 in the axial direction of the crankshaft 2, the crankshaft has a main journal 3. The synchronizing shaft 16 is arranged in the center of the main journal 3' and passes completely through said main journal in the axial direction of the crankshaft 2. Thereby, an excessive weakening of the crankshaft 2 can be avoided.

Fig. 1 also shows that the actuating element 10 is arranged coaxially with the crankshaft 2 and can rotate about an axis of rotation 20, in particular relative to the crankshaft 2 and/or relative to the crankcase. The rotational axis 20 of the adjustment element 10 coincides with the crankshaft rotational axis 4, wherein the rotational axis 20 of the adjustment element 10 is also referred to as the adjustment element rotational axis. Overall, it can be seen that the crankshaft axis of rotation 4, the control shaft axis of rotation 11 and the axis of rotation 20 of the actuating element 10 coincide. In order to adjust the compression ratio and thus to rotate the eccentric parts 7 and 7', the adjusting element 10 is rotated about the axis of rotation 20 (adjusting element axis of rotation), in particular relative to the crankshaft 2 and/or relative to the crankcase.

In the first embodiment shown in fig. 1, the adjustment element is designed as an unrotatable, rotatable adjustment element, to be precise as a rotation or rotation about the axis of rotation 20, in order to change the compression ratio, whereas during the rotation of the crankshaft 2 about the crankshaft axis of rotation 4, no rotation of the adjustment element 10 about the axis of rotation 20 takes place and the compression ratio remains constant or no adjustment of the compression ratio takes place. Thus, for example, the adjusting element 10 is only rotated for rotating the eccentric parts 7 and 7', i.e. only for adjusting the compression ratio about the axis of rotation 20. In the design of the actuating element 10 as an unrotated actuating element, it can be advantageous to ensure that the correct relative rotational speed is maintained and that the actuating element 10 is at rest at a constant compression ratio.

Furthermore, in the first embodiment, the adjustment element 10 is designed as a ring gear 21 of a planetary gear 22. The planetary gear 22 has a ring gear 21 (adjustment element 10), a sun gear 23, a planet carrier 24, also referred to as planet carrier, and at least one or more planet gears 25, which are rotatably mounted on the planet carrier 24, are in engagement with the sun gear 23 and with the ring gear 21. The ring gear 21 has a first toothing in the form of an internal toothing 26, which meshes with the planet gears 25. In this case, the planet carrier 24 is fixedly connected to the crankshaft, i.e., is connected to the crankshaft 2 in a rotationally fixed manner. The sun gear 23 is connected to the adjusting shaft 9 in a rotationally fixed manner, so that by rotation of the sun gear 23 about the axis of rotation 20, the adjusting shaft 9 and therefore the gearwheel 15 rotate about the axis of rotation 20 or about the adjusting shaft axis of rotation 11, in particular relative to the crankshaft 2 and/or relative to the crankcase. Therefore, to adjust the compression ratio, the sun gear 23 rotates about the rotation axis 20. For this purpose, the ring gear 21 rotates again about the axis of rotation 20.

In order to rotate the ring gear 21 about the axis of rotation 20, a drive 27 is provided, by means of which the ring gear 21 can be driven and thus can rotate about the axis of rotation 20. In the first embodiment illustrated in fig. 1, the drive 27 is in the form of a worm gear with a so-called worm 28. The worm 28 is rotatable about a worm rotational axis 29 relative to the crankcase and in particular relative to the crankshaft 2, wherein the worm rotational axis 29 extends perpendicular to the imaginary plane and the rotational axis 20 lies in or extends parallel to the imaginary plane. The worm drive also has a worm wheel 30 which meshes with the worm 28 and is rotatable about the axis of rotation 20 by rotation of the worm 28 about the worm axis of rotation 29. Here, as can be seen from fig. 1, the worm wheel 30 is formed by the ring gear 21. For this purpose, the ring gear 21 has, for example, a second toothing in the form of an external toothing 31, which is designed, for example, as helical toothing. In this case, the worm 28 meshes or engages with the external toothing 31 in the external toothing 31, so that, as is generally known from worm gears or worm gear drives, if the worm 28 rotates about the worm rotation axis 29, the worm wheel 30 or the ring gear 21 rotates about the rotation axis 20. This is illustrated symbolically in fig. 1 by the double arrow 32.

For driving and thus rotating the worm 28 about the worm rotation axis 29, a motor, which is not visible in the figures, is provided, for example, and is configured as an electric motor. The use of a worm drive is advantageous in that the worm drive has a self-locking or enters into the self-locking when the worm 28 is not actively rotated about the worm rotation axis 29 by means of the motor. In this way, with a constant compression ratio, the ring gear 21 does not have to be secured against undesired rotation about the axis of rotation 20 by means of a worm drive by means of an additional and separate actuator or brake, so that undesired changes in the compression ratio can be avoided by self-locking of the worm drive and thus particularly inexpensively.

Fig. 2 shows a second embodiment of the crank mechanism 1. The second embodiment differs from the first embodiment in particular in that the actuating element 10 is not formed as a rotatable, non-rotating actuating element, but as a rotatable, rotating actuating element, as is illustrated in fig. 2 by the arrow 33. The rotatable, rotating adjustment element 10 is understood to mean that during the rotation of the crankshaft 2 about its crankshaft rotation axis 4, the adjustment element rotates together with the crankshaft 2, in particular at a fixed rotational speed ratio, permanently about the rotation axis 20 about the crankshaft 2, and no adjustment of the compression ratio takes place. In addition, relative rotation between the actuating element 10 and the crankshaft 2 does not occur here, for example. In order to change the compression ratio, the adjustment element 10 is twisted about the axis of rotation 20 relative to the crankshaft 2. However, if the compression ratio is kept constant, the adjustment link 10 rotates together with the crankshaft 2 about the rotation axis 20. This results in a multiplicity of control possibilities, but the corresponding, adjusted rotational speed ratio should be compatible with the overall mechanism, in particular with respect to the plain bearing.

List of reference numerals

1 crank drive mechanism

2 crankshaft

3. 3', 3' main journal

4 crankshaft axis of rotation

5 arrow head

6. 6' crank pin

7. 7' eccentric part

8 eccentric rotation axis

9 adjusting shaft

10 adjustment link

11 adjustment shaft axis of rotation

12. 12' external tooth part

13 end part

14 crank arm

15 Gear

16 synchronous shaft

17 Gear

18 gears

19 end part

20 axis of rotation

21 ring gear

22 planetary gear transmission device

23 Sun gear

24 planetary gear carrier

25 planetary gear

26 internal tooth part

27 drive device

28 Worm

29 axis of rotation of worm

30 worm wheel

31 external tooth part

32 double arrow

33 arrow head