AT16537U1 - Length-adjustable connecting rod with tolerance compensation - Google Patents

Abstract

The invention relates to a length-adjustable connecting rod (6.1) for an internal combustion engine with a first connecting rod part (18.1) in which a first connecting rod eye (9.1) is formed, a second connecting rod part (19.1) in which a second connecting rod eye (8.1) is formed, and at least one cylinder-piston unit (31.1) in order to adjust the first connecting rod part (18.1) relative to the second connecting rod part (19.1), the cylinder-piston unit (31.1) comprises a cylinder bore (22.1), one in the cylinder bore ( 22.1) longitudinally movable adjusting piston (21.1) and at least one pressure chamber (24.1, 25.1) provided in the cylinder bore (22.1). It is an object of the present invention to compensate for differences in length of the total length of the connecting rod (6.1) which may occur during production, which can result from the addition of the individual part tolerances. For this purpose, it is provided according to the invention that an eccentric insert is arranged in one of the connecting rod eyes (9.1, 8.1) so that it cannot rotate, such that a defined length of the connecting rod (6.1) is set. The invention also relates to a method for setting a defined length of a connecting rod (6.1).

Description

patent office

description

LENGTH ADJUSTABLE CONNECTING ROD WITH TOLERANCE COMPENSATION The present invention relates to a length adjustable connecting rod for an internal combustion engine having a first connecting rod part in which a first connecting rod eye is formed, a second connecting rod part in which a second connecting rod eye is formed and at least one cylinder-piston unit In order to adjust the first connecting rod part relative to the second connecting rod part, the cylinder-piston unit comprises a cylinder bore, an adjustment piston arranged to be longitudinally movable in the cylinder bore and at least one pressure chamber provided in the cylinder bore.

The invention further relates to a method for setting a defined length of a connecting rod.

The thermal efficiency of an internal combustion engine, especially gasoline engines, depends on the compression ratio ε, ie the ratio of the total volume before compression to the compression volume (ε = (stroke volume V _h + compression volume V _c ) / compression volume V _c ). The thermal efficiency increases as the compression ratio increases. The increase in thermal efficiency via the compression ratio is degressive, but is still relatively pronounced in the range of today's values.

In practice, the compression ratio can not be increased arbitrarily, since too high a compression ratio leads to an unintended self-ignition of the combustion mixture by pressure and temperature increase. This premature combustion not only leads to restless running and knocking in gasoline engines, but can also lead to component damage to the engine. In the partial load range, the risk of spontaneous combustion is lower, which depends not only on the influence of the ambient temperature and pressure, but also on the operating point of the engine. Accordingly, a higher compression ratio is possible in the partial load range. In the development of modern internal combustion engines, there are therefore efforts to adapt the compression ratio to the respective operating point of the engine and thus to implement a variable compression ratio.

For the implementation of a variable compression ratio (VOR - variable compression ratio) there are different solutions with which the position of the crank pin of the crankshaft or the piston pin of the engine piston is changed or the effective length of the connecting rod is varied. There are solutions for continuous and discontinuous adjustment of the components. Continuous adjustment enables an optimal reduction of CO ₂ emissions and consumption due to a compression ratio that can be set for each operating point. In contrast, a discontinuous adjustment with two stages designed as end stops of the adjustment movement offers constructive and operational advantages and still enables significant savings in consumption and CO ₂ emissions compared to a conventional crank drive.

WO 2015/055582 A2 shows that the compression ratio in the internal combustion engine is adjusted by the connecting rod length. The connecting rod length influences the compression volume in the combustion chamber, the stroke volume being determined by the position of the crankshaft journal and the cylinder bore. A short connecting rod therefore leads to a lower compression ratio than a long connecting rod with otherwise the same geometric dimensions, e.g. Piston, cylinder head, crankshaft, valve control, etc. In the known length-adjustable connecting rods, the connecting rod length is hydraulically varied between two positions. The entire connecting rod is designed in several parts, the length change being carried out by a telescopic mechanism which is adjustable by means of a double-acting hydraulic cylinder. The small connecting rod eye, usually for receiving the piston pin, is connected to a piston rod (telescopic rod part). The associated adjusting piston is guided axially displaceably in a cylinder which is arranged in the connecting rod part with the large connecting rod eye, usually for receiving the crankshaft journal. The Verstellkol

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AT 16 537 U1 2019-12-15 Austrian patent office ben separates the cylinder into two pressure chambers, an upper and a lower pressure chamber. These two pressure chambers are supplied with engine oil via a hydraulic adjustment mechanism, the engine oil being supplied via the lubrication of the connecting rod bearing.

In addition to the telescope solutions, there are also other adjustment mechanisms that can be used. For example, from DE 10 2005 055199 A1 a piston-operated adjustment mechanism is known which uses an eccentric device to adjust the piston stroke. Further adjustment mechanisms are known from DE 19835146 A1 and from GB 2161580 and DE 4226361 A1.

Characterized in that the connecting rod is designed as a telescopic system with several interacting components, the addition of the tolerances of the individual components can lead to a considerable spread in the total length of different connecting rods. The different overall lengths of the connecting rods can lead to different compression ratios when used in an internal combustion engine.

It is therefore the object of the present invention to provide a length-adjustable connecting rod with exact dimensions. In particular, it must be possible to correct large tolerance deviations.

For this purpose, it is provided according to the invention that an eccentric insert is arranged so that it cannot rotate in one of the connecting rod eyes in such a way that a defined length of the connecting rod is set. This configuration of the connecting rod provides a system by means of which the center distance of the connecting rod eyes of a length-adjustable connecting rod can be precisely adjusted at the end of the production chain. This ensures exact dimensions so that different compression ratios can be avoided. This can be achieved with just a single eccentric insert by inserting and fixing the eccentric insert in a specific angular position in the respective connecting rod eye, so that the desired length is set. On the one hand, tolerances resulting from the assembly of the connecting rod according to the invention can be compensated for. On the other hand, it is possible to implement different connecting rod lengths, which are required by users of such connecting rods, with a single connecting rod constructed in a modular manner. A prefabricated connecting rod can therefore be adapted to different engine needs by adapting the eccentric insert.

In a particularly simple embodiment it can be provided that the eccentric insert is designed as an eccentric bushing arranged in one of the connecting rod eyes.

Advantageously, one of the connecting rod eyes is designed as a small connecting rod eye for receiving a piston pin and the eccentric bushing is arranged in this small connecting rod eye. The eccentric bushing can be attached particularly easily in the small connecting rod eye.

[0013] Alternatively, it could also be provided that the eccentric insert is formed by eccentric bearing shells arranged in one of the connecting rod eyes. This also enables a simple configuration.

Advantageously, one of the connecting rod eyes is designed as a large connecting rod eye for receiving a crankshaft journal and the eccentric bearing shells are arranged in this large connecting rod eye. The large connecting rod eye for receiving the crankshaft journal is usually made of several parts, so that the eccentric bearing shells can be easily attached during assembly.

[0015] In a particularly simple embodiment, two eccentric bearing shells can be provided. Then only two different components need to be kept in stock to correct the length tolerances.

Advantageously, the two eccentric bearing shells have a different thickness. Depending on which bearing shell is used at the top or bottom, different length deviations can be compensated for.

In yet another embodiment it can be provided that the abutting surfaces

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AT 16 537 U1 2019-12-15 Austrian patent office for the eccentric bearing cups are designed according to the Poka-Yoke principle. The transitions between the eccentric bearing shells must be kept very smooth. It is therefore important that bearing shells that belong together in pairs are always installed. If the abutting surfaces of the eccentric bearing shells are designed according to the Poka-Yoke principle, it is ensured that only the correct bearing shells are installed together.

[0018] It can advantageously be provided that the abutting surfaces of the eccentric bearing shells interlock positively. The form fit is designed so that only the correct bearing shells fit in pairs. By "correct" it is meant that the matching bearing shells are designed in such a way that a very smooth transition is achieved at the abutting surfaces of these eccentric bearing surfaces. Other bearing shells have a different shape and cannot be installed with a positive fit. For example, teeth can be provided on the abutting surfaces of the mating eccentric bearing shells.

[0019] Alternatively, it can also be provided that eccentric bearing shells belonging to one another are identified by a color code. The installer recognizes from the color code that he is installing the correct bearing shells together. Errors can also be avoided in this way.

In a further embodiment it can be provided that corresponding locking elements are provided on the outside of the eccentric insert facing the connecting rod eye and in the connecting rod eye. This allows the eccentric insert to be positioned in the connecting rod eye in a permanently non-rotating manner. Interlocking devices, press fit arrangements or the like can be provided as locking elements in a form-fitting and / or non-positive manner. In a variant of the invention, the locking elements are designed as interlocking teeth. This achieves a defined position that only allows discrete angular positions. In addition, the interlocking gears provide protection against rotation.

In order to enable a precise setting without too much manufacturing effort, it can be provided that the toothing has angular steps of approximately 15 °.

In a still further embodiment it can be provided that the maximum eccentricity of the eccentric insert is approximately 1 mm. In this way, the desired tolerance compensation can be made possible, excessive changes in length are avoided.

In order to enable a simple and secure attachment of the eccentric insert in the desired angular position in the connecting rod eye, it can be provided that the eccentric insert is pressed in the connecting rod eye.

In yet another embodiment it can be provided that the maximum and the minimum eccentricity of the eccentric insert come to rest on the central axis of the connecting rod. This ensures that the connecting rod center axis is not shifted. Different inserts with different eccentricities must then be kept in stock, which are selected for tolerance compensation depending on the desired or required length. The inserts are then installed with the maximum and minimum eccentricity on the connecting rod center axis and inclining up or down.

The object of the invention is also achieved by a method mentioned at the outset for setting a defined length of a connecting rod with a first connecting rod part in which a first connecting rod eye is formed, a second connecting rod part in which a second connecting rod eye is formed, and at least one cylinder Piston unit in order to adjust the first connecting rod part relative to the second connecting rod part, wherein the cylinder-piston unit comprises a cylinder bore, an adjusting piston arranged to be longitudinally movable in the cylinder bore and at least one pressure chamber provided in the cylinder bore, solved according to the invention in that at least one of the connecting rod eyes is provided with an eccentric insert which can be moved in the connecting rod eyes and can be fixed in its movement and the following steps are carried out:

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AT 16 537 U1 2019-12-15 Austrian Patent Office [0026] a. Determining a current length of the connecting rod;

B. Comparison of the current length of the connecting rod with a defined length;

[0028] c. If the current length deviates from the defined length, the eccentric insert is rotated in at least one connecting rod eye until the current length of the connecting rod matches the defined length;

[0029] d. The eccentric inserts arranged in the connecting rod eyes are secured against rotation.

In this way, a simple tolerance compensation or a quick adjustment of the length of the connecting rod to developer needs can be achieved without the production processes having to be changed or large rejects having to be tolerated due to tolerance deviations.

In the following, the invention is explained in more detail with reference to non-restrictive exemplary embodiments which are shown in the drawings. Show it:

1 shows a schematic cross section through an internal combustion engine, [0033] FIG. 2 shows a schematic illustration of an embodiment of a length-adjustable connecting rod from FIG. 1 in a partially sectioned illustration with an eccentric insert used in a connecting rod eye, [0034] FIG. 3 2 shows an enlargement of the connecting rod eye with the eccentric insert from FIG. 2, FIG. 4 shows a side view of the eccentric insert from FIGS. 2 and 3 in section, FIGS. 5a-5c [0037] FIG. 6 [ Fig. 7 Fig. 8 is a side view of the eccentric insert of Fig. 2, 3 and 4 in section in different installation positions.

1 shows a schematic representation of a further embodiment of a length-adjustable connecting rod from FIG. 1 in a partially sectioned illustration with an eccentric insert inserted in a connecting rod eye, an embodiment of an eccentric insert in the form of eccentric bearing shells, and the eccentric bearing shells from FIG. 7 in a different installation position.

In Fig. 1, an internal combustion engine (gasoline engine) 1 is shown in a schematic representation. The internal combustion engine 1 has three cylinders 2.1, 2.2 and 2.3, in each of which a reciprocating piston 3.1, 3.2, 3.3 moves up and down. Furthermore, the internal combustion engine 1 comprises a crankshaft 4 which is rotatably supported by means of crankshaft bearings 5.1, 5.2, 5.3 and 5.4. The crankshaft 4 is connected to the associated reciprocating pistons 3.1, 3.2 and 3.3 by means of the connecting rods 6.1, 6.2 and 6.3. For each connecting rod 6.1, 6.2 and 6.3, the crankshaft 4 has an eccentrically arranged crankshaft journal 7.1, 7.2 and 7.3. The large connecting rod eyes 8.1, 8.2 and 8.3 are each mounted on the associated crankshaft journal 7.1, 7.2 and 7.3. The small connecting rod eye 9.1, 9.2 and 9.3 are each mounted on a piston pin 10.1, 10.2 and 10.3 and thus pivotally connected to the associated piston 3.1, 3.2 and 3.3. The terms small connecting rod eye 9.1, 9.2 and 9.3 and large connecting rod eye 8.1, 8.2 and 8.3 show neither an absolute nor a relative size assignment, but only serve to differentiate the components and assign them to the internal combustion engine shown in FIG. 1. Accordingly, the dimensions of the diameter of the small connecting rod eyes 9.1, 9.2 and 9.3 can be smaller, the same size or larger than the dimensions of the diameter of the large connecting rod eyes 8.1, 8.2 and 8.3.

The crankshaft 4 is provided with a crankshaft sprocket 11 and coupled to a camshaft sprocket 13 by means of a timing chain 12. The camshaft sprocket 13 drives a camshaft 14 with its associated cams for actuating the inlet and outlet

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AT 16 537 U1 2019-12-15 Austrian patent office valves (not shown in detail) of each cylinder 2.1, 2.2 and 2.3. The empty strand of the control chain 12 is tensioned by means of a pivotably arranged tensioning rail 15 which is pressed onto it by means of a chain tensioner 16. The tension strand of the control chain 12 can slide along a guide rail. The essential functioning of this internal combustion engine, including fuel injection and ignition by means of a spark plug, is not explained in more detail and is assumed to be known. The eccentricity of the crankshaft journals 7.1, 7.2 and 7.3 essentially determines the stroke distance H _K , especially if, as in the present case, the crankshaft 4 is arranged exactly centrally under the cylinders 2.1, 2.2 and 2.3. The reciprocating piston 3.1 is shown in its lowest position in FIG. 1, while the reciprocating piston 3.2 is shown in its uppermost position. In the present case, the difference results in the stroke H _K. The remaining height H _c (see cylinder 2.2) gives the remaining compression height in cylinder 2.2. In conjunction with the diameter of the lifting piston 3.1, 3.2 or 3.3 or the associated cylinders 2.1, 2.2 and 2.3, the stroke volume V _h results from the stroke distance H _K and the compression volume V _{c is} calculated from the remaining compression height H _c . Of course, the compression volume V _c largely depends on the design of the cylinder cover. The compression ratio ε results from these volumes V _h and V _c . In detail, the compression ratio ε is calculated from the sum of the stroke volume V _h and the compression volume V _c divided by the compression volume V _c . Today's values for gasoline engines are between 10 and 14 for ε.

So that depending on the operating point (speed n, temperature T, throttle valve position) of the internal combustion engine 1, the compression ratio ε can be adjusted, the connecting rods 6.1, 6.2 and 6.3 are designed to be adjustable in length. As a result, a higher compression ratio can be used in the partial load range than in the full load range.

In Fig. 2, the length-adjustable connecting rod 6.1 is shown as an example, which is identical to the connecting rods 6.2 and 6.3. The description therefore applies accordingly to all connecting rods. The connecting rod 6.1 has a first connecting rod part 18.1 with a connecting rod head 17.1 and a second connecting rod part 19.1. The small connecting rod eye 9.1 is formed in the connecting rod head 17.1. The first connecting rod part 18.1 is telescopically guided in the second connecting rod part 19.1. The relative movement of the first connecting rod part 18.1 in the longitudinal direction to the second connecting rod part 19.1 takes place by means of a cylinder-piston unit 31.1 with an adjusting piston

21.1. and a cylinder bore 22.1. On the second connecting rod part 19.1 there is a lower bearing shell

20.1 arranged which, together with the lower region of the second connecting rod part 19.1, surrounds the large connecting rod eye 8.1. The lower bearing shell 20.1 and the second connecting rod part 19.1 are connected to one another in the usual way by means of fastening means. The lower end of the first connecting rod part 18.1 is connected to the adjusting piston 21.1, which is in the cylinder bore

22.1 of the second connecting rod part 19.1 is slidably guided. At the upper end, the second connecting rod part 19.1 has a cover 23.1, through which the first connecting rod part 18.1 is guided and sealed. The cover 23.1 thus seals the cylinder bore 22.1 overall. A first pressure chamber 24.1 of circular cross section is formed below the adjusting piston 21.1 and above the adjusting piston 21.1 is an annular second pressure chamber

25.1 formed. The adjusting piston 21.1 and the piston bore 22.1 are part of the adjusting mechanism for changing the length of the connecting rod. The adjusting mechanism also includes a hydraulic circuit 26.1, which accordingly ensures that the hydraulic fluid flows in or out of the pressure chambers 24.1 and 25.1 and thus moves or locks the adjusting piston 21.1.

As described above, the connecting rod is constructed as a telescope system with several components. Each of these individual components, i.e. the first connecting rod part 18.1 with the small connecting rod eye 9.1 and the adjusting piston 21.1 and the second connecting rod part 19.1 with the large connecting rod eye 8.1 and the cylinder bore 22.1 have individual tolerances, whereby the addition of the individual tolerances can result in a considerable spread of the total length of the connecting rod 6.1. The use of several connecting rods with different overall lengths would result in different compression ratios. This is understandably not him

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AT 16 537 U1 2019-12-15 Austrian patent office wishes. Therefore, in the embodiment shown in FIG. 2, an eccentric insert in the form of an eccentric bushing 27.1 is inserted in the small connecting rod eye 9.1 in a manner that prevents it from rotating. The eccentric bushing 27.1 is inserted in the small connecting rod eye 9.1 in such a way that its eccentricity compensates for the differences in length that occur. This allows the center distance of the connecting rod eyes to be adjusted exactly. This is explained in more detail below.

3 shows an enlargement of the upper area of the first connecting rod part 18.1. As already described, an eccentric bushing 27.1 is inserted in the small connecting rod eye 9.1. The eccentric bushing 27.1 has a circular cross section, the diameter of which corresponds approximately to the diameter of the small connecting rod eye 9.1. A circular or cylindrical opening 28.1 for receiving the piston pin 10.1 is formed in the eccentric bushing 27.1 eccentrically to the center of the circumferential circle. Depending on the angular position of the eccentric bushing 27.1 in the small connecting rod eye 9.1, the eccentricity E ^ E ₂ running along the central rod axis has a different value. This changes the overall length of the connecting rod 6.1 and compensates for the tolerances that occur. A toothing 29.1 can be formed on the circumference of the connecting rod eye 9.1. The eccentric bushing

27.1 also has a toothing 30.1 on its outer circumference, which interacts with the toothing 29.1 in the connecting rod eye 9.1 and thus enables a defined position of the eccentric bushing 27.1 in the connecting rod eye 9.1. The teeth only allow discrete angular positions. In addition, the eccentric bushing 27.1 is prevented from rotating in the small connecting rod eye 9.1. The toothing preferably has angular steps of approximately 15 °.

The toothing thus serves as a lock with corresponding locking elements on the inner circumference of the connecting rod eye 9.1 and on the outer circumference of the eccentric bushing

27.1.

In addition to this design of the locking elements, other embodiments are also possible which allow permanent rotation protection of the eccentric insert designed as an eccentric bushing 27.1 in the connecting rod eye 9.1.

To compensate for different tolerances that occur, only one embodiment of the eccentric bushing is necessary, which only has to be used with respect to the correct angular position in the connecting rod eye. It can also be provided that the eccentric bushing is pressed in the connecting rod eye in order to prevent rotation. In Figure 3, two possible different positions of the eccentric bushing 27.1 are shown. In the first angular position shown, the receptacle 28.1 for the piston pin 10.1 is drawn in solid lines. In this angular position, the eccentricity Et of the eccentric bushing 27.1 facing the large connecting rod eye is relatively large, as a result of which a too short length of the connecting rod can be compensated for. In the second angular position shown, the receptacle 28.1 for the piston pin 10.1 is drawn in dashed lines. In this second angular position, the eccentricity E _{2 of} the eccentric bushing 27.1 facing the large connecting rod eye is small, as a result of which a too long length of the connecting rod can be compensated for. Depending on the design of the eccentric bushing, for example whether external teeth are provided or not, many other angular positions of the eccentric bushing 27.1 can be set. It can also be provided that a large number of different eccentric bushings are provided, which have different maximum and minimum eccentricities. An eccentric bushing is then selected, the maximum or minimum eccentricity of which corresponds to the length of the connecting rod 6.1 to be compensated. This eccentric bushing is then fastened in the small connecting rod eye 9.1, for example by pressing or by the toothing provided on the circumference, in such a way that the center of the circular receptacle 28.1 of the eccentric bushing 27.1 comes to lie on the central axis M of the connecting rod. The minimum and maximum eccentricity of the eccentric bushing 27.1 then also lie on the central axis M of the connecting rod. This prevents the connecting rod center axis from shifting.

While only the arrangement of an eccentric insert in the small connecting rod eye 9.1 has been described above, eccentric inserts can also be provided according to the invention, both in the small 9.1 and in the large connecting rod eye 8.1, which can be adjusted accordingly

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AT 16 537 U1 2019-12-15 Austrian patent office. This provides an even greater adjustment range for the defined length of the connecting rod 6.1.

It can also be provided that the toothing in the connecting rod eye 9.1 and on the circumference of the eccentric bushing 27.1 is designed such that incorrect installation of the eccentric bushing 27.1 in the connecting rod eye 9.1 is impossible (fail-safe principle or poka yoke).

4, the eccentric bushing 27.1 is partially shown in section. The eccentric bushing 27.1 has inside the cylindrical opening 28.1 for receiving the piston pin 10.1. As already described, the eccentric bushing 27.1 has a circular cross section transverse to its longitudinal direction L. The circular opening 28.1 is arranged eccentrically to the center of the circular cross section of the eccentric bushing 27.1. Depending on the angular position of the eccentric bushing 27.1 in the small connecting rod eye 9.1, the distance from the center of the circular opening 28.1 and thus the central axis of the piston pin 10.1 to the center of the large connecting rod eye 8.1 increases and decreases, and thus the total length of the connecting rod 6.1. Tolerances that occur in the individual connecting rod components 6.1, which can add up, are thus compensated for.

5a to 5c, an eccentric bushing 27.1 is shown in three different angular positions. 5a shows the eccentric bushing 27.1 in a neutral position. This means that the upper eccentricity E _o , ie the thickness of the eccentric bushing 27.1 in the upper region, ie pointing towards the reciprocating piston along the central axis of the connecting rod, is the same as the lower eccentricity Eu. The lower eccentricity Eu is the thickness of the eccentric bush

27.1 in the lower area of the eccentric bushing, pointing towards the large connecting rod eye 8.1.

Fig. 5b shows the eccentric bushing 27.1 in an angular position in which a too short overall length of the connecting rod 6.1 must be compensated. In this case the upper eccentricity E _{o is} smaller than the lower eccentricity Eu.

5c shows the eccentric bushing 27.1 in an angular position in which an excessively long overall length of the connecting rod 6.1 must be compensated for. In this case the upper eccentricity E _{o is} greater than the lower eccentricity Eu.

Fig. 6 shows the lower region of the connecting rod 6.1, in which the large connecting rod eye 8.1 is designed to receive the crankshaft journal. For this purpose, the second connecting rod part 19.1 is connected to a lower bearing shell 20.1. This can be done, for example, using conventional fasteners such as screws. The second connecting rod part 19.1 forms, together with the lower bearing shell 20.1, the large connecting rod eye 8.1. Two associated eccentric bearing shells 32.1, 33.1 are arranged in the large connecting rod eye 8.1. The two eccentric bearing shells 32.1, 33.1 together form a circular cylindrical receptacle 36.1 for a crankshaft journal. The two bearing shells 32.1, 33.1 abut on a first abutment surface 34.1 and a second abutment surface 35.1. In order to enable smooth operation of the connecting rod 6.1, the transition at these abutting surfaces 34.1, 35.1 must be kept very smooth. It is therefore important that two matching eccentric bearing shells 32.1, 33.1 are always used together. For this purpose, it can be provided that the matching bearing shells 32.1, 33.1 are formed on their abutting surfaces 34.1, 35.1 in such a way that they form a positive fit. Here, for example, a toothing would be conceivable. Alternatively, it can be provided that matching bearing shells 32.1, 33.1 have a color code, on the basis of which it becomes clear that only these bearing shells may be installed together.

7a and 7b show an example of a pair of associated eccentric bearing shells 32.1, 33.1 which are inserted into the large connecting rod eye 8.1 in such a way that they compensate for a length of the connecting rod 6.1 which is too long. The eccentric bearing shell 32.1 with the maximum eccentricity E _max is arranged in the lower region of the large connecting rod eye 8.1, ie on the lower bearing shell 20.1 and thus pointing the way from the upper connecting rod eye 9.1. The other eccentric bearing shell 33.1 with the minimal eccentricity E _min is accordingly arranged in the upper region of the large connecting rod eye 8.1 at the foot of the second connecting rod part 19.1

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AT 16 537 U1 2019-12-15 austrian patent office net. The center point M _E l of the receptacle 36.1 for the crankshaft journal formed by the eccentric bearing shells 32.1, 33.1 is therefore shifted upward with respect to the center point M _{PL of} the large connecting rod eye 8.1 and thus the effective length of the connecting rod

6.1 shortened.

7b shows the two eccentric bearing shells 32.1, 33.1 in the pulled-apart state. Here the abutting surfaces 34.1, 35.1 are clearly visible.

8a and 8b show an example of a pair of associated eccentric bearing shells 32.1, 33.1, which are inserted into the large connecting rod eye 8.1 such that they compensate for a too short length of the connecting rod 6.1. Here is the eccentric bearing shell

32.1 with the maximum eccentricity E _max in the upper area of the large connecting rod eye 8.1, ie in contact with the second connecting rod part 19.1. The second eccentric bearing shell 33.1 with the minimal eccentricity E _min is arranged in the lower region of the large connecting rod eye 9.1, ie adjacent to the lower bearing shell 20.1. As a result, the center point M _{EL of} the receptacle 36.1 for the crankshaft pin formed by the eccentric bearing shells 32.1, 33.1 is shifted downward with respect to the center point M _{PL of} the large connecting rod eye 8.1, and thus the effective length of the connecting rod 6.1 is extended. 8b shows the two eccentric bearing shells 32.1, 33.1 in the pulled-apart state. Here again the abutting surfaces 34.1, 35.1 on which the two eccentric bearing shells 32.1, 33.1 abut one another are visible. As already described, the transition at these joints 34.1, 35.1 must be very smooth. This is only possible if only matching bearing shells are installed together. The abutting surfaces 34.1, 35.1 are therefore preferably designed according to the Poka-Yoke principle, so that only matching bearing shells can be installed together. This can take place, for example, in that mutually matching toothing is formed on the abutting surfaces 34.1, 35.1 or another interlocking form fit. Alternatively, a color code could also be used.

[0059] According to the invention, a method for setting a defined length of a connecting rod 6.1 comprises the following steps:

[0060] a. Determining a current length of the connecting rod 6.1;

B. Comparison of the current length of the connecting rod 6.1 with a defined length;

[0062] c. If the current length deviates from the defined length, the eccentric insert is rotated in at least one connecting rod eye 9.1, 8.1 until the current length of the connecting rod 6.1 matches the defined length;

[0063] d. The eccentric inserts arranged in the connecting rod eyes 9.1, 8.1 are secured against rotation.

The current length of the connecting rod 6.1 denotes the length after assembly or before installation in an internal combustion engine. The determination is carried out in the usual way.

The defined length is that length of the connecting rod 6.1 that is required for the intended use.

The connecting rod 6.1 is secured against rotation in the manner described above, in particular by providing and actuating the locking elements. In addition, permanent locking against rotation can also be achieved by gluing, welding or other known measures.

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LIST OF REFERENCE NUMBERS

1 internal combustion engine 2.1,2.2,2.3 cylinder 3.1,3.2,3.3 reciprocating 4 crankshaft 5.1,5.2,5.3,5.4 6.1,6.2,6.3 crankshaft bearings connecting rod 7.1,7.2,7.3 crankshaft journal 8.1.8.2.8.3 9.1.9.2.9.3 large connecting rod eye small connecting rod eye 10.1,10.2,10.3 piston pin 11 Kurbelwellenketterad 12 timing chain 13 camshaft sprocket 14 camshaft 15 tensioning rail 16 chain tensioner 17.1 big end 18.1 first connecting rod part 19.1 second connecting rod part 20.1 lower bearing shell 21.1 adjusting piston 22.1 piston bore 23.1 cover 24.1 first pressure chamber 25.1 second pressure chamber 26.1 hydraulic circuit 27.1 eccentric 28.1 circular opening eccentric bushing 29.1 Teeth small connecting rod eye 30.1 Toothing eccentric bushing 31.1 Cylinder-piston unit 32.1 first eccentric bearing shell 33.1 second eccentric bearing shell 34.1 first butt surface 35.1 second bump 36.1 Recording crankshaft journal

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AT 16 537 U1 2019-12-15 Austrian patent office

V _h displacement v _c compression volume He compression height H _K stroke Ei, E ₂ eccentricities E _o upper eccentricity eu lower eccentricity Emax maximum eccentricity Emin minimal eccentricity ε compression ratio n rotational speed T temperature M Central axis connecting rod Mp _A The center of the connecting rod eye m _el Center of eccentric cups

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Expectations

Claims (16)

1. Length-adjustable connecting rod (6.1) for an internal combustion engine with a first connecting rod part (18.1) in which a first connecting rod eye (9.1) is formed, a second connecting rod part (19.1) in which a second connecting rod eye (8.1) is formed, and at least one Cylinder-piston unit (31.1) to adjust the first connecting rod part (18.1) relative to the second connecting rod part (19.1), the cylinder-piston unit (31.1) comprises a cylinder bore (22.1), one in the cylinder bore (22.1) lengthways movably arranged adjusting piston (21.1) and at least one pressure chamber (24.1, 25.1) provided in the cylinder bore (22.1), characterized in that an eccentric insert is arranged in one of the connecting rod eyes (9.1, 8.1) in such a way that it cannot rotate, such that a defined length of the connecting rod (6.1) is set. 2. Length-adjustable connecting rod (6.1) according to claim 1, characterized in that the eccentric insert is designed as an eccentric bushing (27.1) arranged in one of the connecting rod eyes (9.1). 3. Length-adjustable connecting rod (6.1) according to claim 2, characterized in that one of the connecting rod eyes is designed as a small connecting rod eye (9.1) for receiving a piston pin and the eccentric bushing (27.1) is arranged in the small connecting rod eye (9.1). 4. Length-adjustable connecting rod (6.1) according to claim 1, characterized in that the eccentric insert in one of the connecting rod eyes (9.1, 8.1) comprises eccentric bearing shells (32.1, 33.1). 5. Length-adjustable connecting rod (6.1) according to claim 4, characterized in that one of the connecting rod eyes is designed as a large connecting rod eye (8.1) for receiving a crankshaft journal and the eccentric bearing shells (32.1, 33.1) are arranged in the large connecting rod eye (8.1). 6. Length-adjustable connecting rod (6.1) according to claim 4 or 5, characterized in that two eccentric bearing shells (32.1, 33.1) are provided. 7. Adjustable connecting rod according to one of claims 4-6, characterized in that the two bearing shells (32.1, 33.1) have a different thickness. 8. Length-adjustable connecting rod (6.1) according to any one of claims 4-7, characterized in that the abutting surfaces (34.1, 35.1) of the eccentric bearing shells (32.1, 33.1) are designed according to the poka-yoke principle. 9. Length-adjustable connecting rod (6.1) according to claim 8, characterized in that the abutting surfaces (34.1, 35.1) of the eccentric bearing shells (32.1, 33.1) interlock positively. 10. Length-adjustable connecting rod (6.1) according to one of claims 4 to 9, characterized in that associated eccentric bearing shells (32.1, 33.1) are identified by a color code. 11. Length-adjustable connecting rod (6.1) according to any one of claims 1-10, characterized in that corresponding locking elements are provided on the outside of the eccentric insert facing the connecting rod eye (8.1, 9.1) and in the connecting rod eye (9.1). 12. Length-adjustable connecting rod (6.1) according to claim 11, characterized in that the locking elements are designed as interlocking teeth (30.1, 29.1), wherein preferably the teeth (30.1, 29.1) have angular steps of approximately 15 °. 13. Length-adjustable connecting rod (6.1) according to any one of claims 1-12, characterized in that the maximum eccentricity of the eccentric insert is approximately 1 mm. 11/17 AT 16 537 U1 2019-12-15 Austrian patent office 14. Length-adjustable connecting rod (6.1) according to any one of claims 1-13, characterized in that the eccentric insert in the connecting rod eye (8.1, 9.1) is pressed. 15. Length-adjustable connecting rod (6.1) according to any one of claims 1-14, characterized in that the eccentric insert is arranged in the connecting rod eye (8.1, 9.1) such that the maximum and minimum eccentricity of the eccentric insert on the central axis (M) of the Connecting rod (6.1) come to rest. 16. Method for setting a defined length of a connecting rod (6.1) with a first connecting rod part (18.1) in which a first connecting rod eye (9.1) is formed, a second connecting rod part (19.1) in which a second connecting rod eye (8.1) is formed, and at least one cylinder-piston unit (31.1) to adjust the first connecting rod part (18.1) relative to the second connecting rod part (19.1), the cylinder-piston unit (31.1) having a cylinder bore (22.1), one in the cylinder bore ( 22.1) longitudinally movably arranged adjusting piston (21.1) and at least one pressure chamber (24.1, 25.1) provided in the cylinder bore (22.1), one in the connecting rod eyes (9.1, 8.1) moving and in at least one of the connecting rod eyes (9.1, 8.1) Eccentric insert that can be fixed in its movement is provided, characterized by the following steps: a. Determining a current length of the connecting rod (6.1); b. Comparison of the current length of the connecting rod (6.1) with a defined length; c. If the current length deviates from the defined length, turn the eccentric insert in at least one connecting rod eye (9.1, 8.1) until the current length of the connecting rod (6.1) matches the defined length; d. The eccentric inserts arranged in the connecting rod eyes (9.1, 8.1) are secured against rotation.