AT524689B1 - axis - Google Patents

Abstract

The invention relates to a gearwheel arrangement comprising an axle (21) and a gearwheel which is rotatably mounted on the axle (21), the axle (21) having a longitudinal extension along a longitudinal central axis (22) and a first end region (23) and a second end area (24) which lie opposite one another along the longitudinal central axis (22), and the first end area (23) forms a bearing area for the axle (21), and with at least one bearing (27, 28) for a gear wheel (6, 7 ), which is arranged or formed at a distance from the first end region (23). Gear teeth are provided with a coating that can be rubbed off during operation of the gear wheel. The first end area (23) has an eccentricity (31) in relation to the longitudinal central axis (22).

Description

The invention also relates to a gear drive comprising a first gear wheel with a first toothing, a second gear wheel with a second toothing and an intermediate wheel with an intermediate wheel toothing, the intermediate wheel being in meshing engagement with the first and the second gear wheel and the first and/or the second gear is rotatably mounted on an axis.

In addition, the invention relates to an engine with a plurality of rows of cylinders, in particular a V engine, in which a plurality of reciprocating pistons are arranged, the reciprocating pistons being connected to a gear drive via crankshafts.

In addition, the invention relates to a method for adjusting the backlash of meshing gears of a gear drive, wherein the gear drive has a first gear with a first toothing, a second gear with a second toothing and an intermediate gear with an intermediate gear toothing, and the intermediate gear in meshing engagement with the

first and the second gear, comprising the steps of: coating the

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at least partially rubs off.

In the case of meshing gears, tooth flank play is necessary, for example to compensate for thermal expansion, to be able to introduce lubricant and to compensate for possible tolerances caused by installation inaccuracies. A wide variety of methods are known for adjusting the backlash. Among other things, DE 199 55 474 C1 describes a method for setting backlash in a gear transmission, in which at least one first gear wheel, which can rotate about an axis fixed to the housing, is supplied with a second gear wheel that can be moved parallel to the axis during assembly with setting backlash, and for setting the tooth flank play, an intermediate layer arranged in a removable manner between tooth flanks of meshing teeth of the meshing gears is used, with a support covering the tooth flanks of predetermined teeth and fixed on the selected gear being arranged as an intermediate layer at least in one of the gears before its assembly, and the gear wheel with a fixed arranged support or Intermediate layer is brought into play-free engagement during assembly with a predetermined force with corresponding tooth flanks of the other gear, the intermediate layer after backlash adjustment of the gears by running-related abrasion of the support or by a e targeted mechanical removal is removed.

From DE 100 62 241 C?2 a method for achieving a desired backlash in a transmission with at least two meshing gears is known, according to which the game adjustment relative to each other by means of a removable coating made of a polymer and a filler at least

one of the gears can be adjusted.

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can be adjusted, this can possibly lead to problems.

JP 2002/317644 A provides an auxiliary machine drive gear device capable of reducing labor for changing the auxiliary machine drive gear device from a normal rotation mode (right rotation) to a reverse rotation mode (left rotation). An idler gear is disposed on an idler shaft between the drive gear and the auxiliary machine drive gear. The idler shaft has a support portion with which the idler shaft is supported in a housing, and a bearing portion on which the idler gear is rotatably supported. The support section is formed eccentrically to the bearing section. Depending on the direction of rotation of the idler gear, the support portion is rotated rightward or leftward, so that the idler gear selectively meshes with a right-hand gear or a left-hand gear of the auxiliary machine drive gear train.

JP 2006/183623 A describes reducing the size of an engine by reducing a center-to-center distance between a crankshaft and an idler shaft pivotally supporting an idler gear in a cam drive device of the engine for transmitting power from a drive sprocket rotating in unison. An inner primary drive gear, which transmits the power of the engine to a transmission, and an outer idler drive gear, which has a smaller diameter than the primary drive gear, are mounted on the crankshaft. An idler gear meshing with the idler drive gear is rotatably supported on an idler shaft supported on an engine body. Drive sprockets facing the primary drive gear at least on part thereof are coaxially attached to the idler gear on its axial inner side. The idler shaft has an eccentric shaft section in its middle section and the same axis as that of

is offset from the axis of the eccentric shaft portion, and is a support shaft,

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DE 322963 C describes a gearwheel fastening on magnetoelectric ignition devices for internal combustion engines, in which two shafts are coupled to one another by a simple gearwheel transmission, the axis of at least one of the two gearwheels being lockable in an eccentric which can be adjusted as required

is stored.

It is known from JP 2011/122555 A to facilitate machining of a surface to provide an idler shaft including an idler plate provided on one side of a cylinder head outer wall, the idler plate having a diameter larger than the shaft diameter and to the side is eccentric to a cylinder head bottom surface. The idler shaft and idler plate are fixed to a bulkhead by a bolt, and the idler plate is fitted into a hole formed in the cylinder head outer wall. The machining surface can be machined prior to installing the idler shaft by inserting a tool through the hole

becomes.

US 2014/083220 A1 describes a lash adjuster of a camshaft drive mechanism, wherein a rotational driving force of a crankshaft is transmitted to a valve gear of an internal combustion engine through the camshaft driving mechanism, in which a driving gear and a driven gear for transmitting the driving force are arranged by meshing with each other therebetween, an eccentric support shaft, which rotatably supports at least one of the drive gear and the driven gear on an outer periphery of the eccentric support shaft, and has a center axis which is eccentric with respect to the center of a rotation axis of the rotatably supported drive gear or the driven gear, is arranged in the internal combustion engine so as to be on a certain To be able to be fixed rotational angular position about the central axis, and adjusts a distance amount between a pair of the drive gear and the driven gear, the eccentric support shaft over

a base shaft attached to the internal combustion engine is attached, so that the

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means bolted to the base shaft on the axis of the base shaft.

DE 10 2004 018 263 A1 discloses a device for backlash adjustment, in particular for a camshaft drive of an internal combustion engine comprising gears, with camshafts mounted in the cylinder head with drive gears and an intermediate gear which corresponds to these and can be driven by the crankshaft and which is located in a structurally separate intermediate gear.

house is stored.

The object of the invention is a way to adjust the tooth flank

games of at least three meshing gears to create.

The object of the invention is achieved with the gear arrangement mentioned at the outset, in which the first end region of the axis relative to the longitudinal central axis

has an eccentricity.

In addition, the object is achieved with the gear drive mentioned at the outset, in which the first and/or the second gear is designed as a gear arrangement according to the invention.

The object of the invention is also achieved with the motor mentioned at the outset,

which has a gear drive according to the invention.

Finally, the object of the invention is also achieved with the method mentioned at the beginning, according to which a gearwheel arrangement according to the invention is formed by arranging the second gearwheel on the axle, the meshing engagement of the second toothing of the second gearwheel with the intermediate wheel toothing is produced and the backlash between the intermediate wheel teeth -

tion and the second toothing to a predefined value by twisting

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is detected.

The advantage here is that the gear can be delivered to the idler gear on a cam track. This is made possible by changing the center distance in the area where the gear is located, caused by changing the relative position of the eccentricity. This means that it is no longer necessary to move the third gear wheel parallel to the axis, which means that the meshing of the toothings with one another can be produced more gently. This avoids the rubbing off of a coating on one of the toothings before the gear drive is put into operation. This in turn prevents the teeth from coming too close to the gearing and incorrect setting of the backlash, which also means that readjustments can be avoided. The backlash of three gears meshing with one another can therefore be achieved with the axle according to the invention

be adjusted more precisely.

According to one embodiment of the invention, it can be provided that the bearing for the gear wheel is designed as a slide bearing in the form of a coating on the surface of the axle. Compared to other types of bearings, the space required for the gear wheel bearing can be reduced, which means that the axis can be made more robust and therefore less sensitive to vibrations. This in turn has a positive effect with regard to a little fluctuating backlash.

For easier assembly and locking of the axle after the tooth flank play has been set, it can be provided according to a further embodiment of the invention that an assembly element is arranged on the axle.

According to one embodiment variant of the invention, it can also be provided that an axial sliding bearing is formed on the mounting element in order to be able to reduce the overall length of the axle.

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According to one embodiment variant of the invention, it can be provided that a lubricant channel for supplying lubricant to the plain bearing is arranged in the axis. In particular for the design of the bearing as a coating, the service life of the plain bearing can be extended, whereby the positive effects of this bearing on the backlash can be maintained longer.

Also to reduce vibrations and thus to reduce backlash changes can be provided according to an embodiment of the invention that the second end area as a further bearing area of the axle

is trained.

According to another embodiment variant of the invention, it can be provided that the mounting element for fastening the axle to an engine block has only one bore or a plurality of bores. It is therefore dispensed with elongated holes to provide the adjustability of the axis, with which the axis can be mounted more precisely and this position over a longer period

period can be retained.

According to one embodiment, it can be provided that a receiving element for a fastener is arranged in at least one of the bores. It is thus possible to improve the anti-twist mounting of the axle on an engine block. In addition, this recording element can also take on other tasks. For example, the receiving element can also have the function of a spacer or vibration damping

or a decoupled assembly, etc.

Provision is made for teeth of the gear wheel to be provided with a coating that can be rubbed off during operation of the gear wheel. The gear assembly has so

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According to one variant of the gear drive, it can also be provided that the first toothing of the first gear and/or the second toothing of the second gear and/or the intermediate wheel toothing of the intermediate wheel is/are provided with a coating that can be abraded during operation of the intermediate wheel. In comparison to the layer thickness of the abradable coating on only one of the gears, the layer thickness of the abradable coating on the gear teeth can be reduced, e.g. halved. This can improve the stability of the coating for handling the gears during assembly.

be enough.

For a better understanding of the invention, this is based on the following

Figures explained in more detail.

They each show in a greatly simplified, schematic representation:

1 shows a section of a gear drive of a motor in a front view; FIG. 2 shows a first gear wheel of the gear drive according to FIG. 1 in an oblique view; FIG. FIG. 3 shows a second gear wheel of the gear drive according to FIG. 1 in an oblique view; FIG. 4 shows an axis in longitudinal section;

FIG. 5 shows the axle according to FIG. 4 in a first end view; FIG.

FIG. 6 shows the axle according to FIG. 4 in a second end view;

7 shows an embodiment variant of a mounting element in an oblique view;

8 shows a section through a detail from the mounting element according to FIG.

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In Fig. 1, a motor 1 is indicated (only an outline of the housing is indicated). The engine 1 comprises two or generally several rows of cylinders 2 (of essentially the same design) (also referred to as cylinder banks), in which reciprocating pistons (not shown in detail) are arranged. In the particular arrangement shown, these banks are arranged in a V configuration relative to each other, resulting in a so-called V-type engine. However, the several rows of cylinders 2 can also be arranged differently to one another, for example parallel next to one another or in the same plane.

The number of cylinders 2 can vary depending on the desired performance.

At least one camshaft for controlling the valves is assigned to the cylinders 2 . In the specifically illustrated embodiment of the engine 1, two (overhead) camshafts are arranged per row of cylinders, at each end of which a gear wheel 3 is arranged. The camshafts are arranged in cylinder heads 4. A cylinder head 4 is provided for each row of cylinders.

The gears 3 are part of belt drives 5, in particular chain drives. A belt drive 5 is provided for each cylinder head 4 . One of the belt drives 5 has a first gear wheel 6 , the other belt drive 5 has a second gear wheel 7 . The first and the second gear wheel 6, 7 are designed with at least two tracks, as can also be seen in particular from FIGS. A gear wheel track 8, 9 is provided for the engagement of the traction means, such as a belt, in particular a chain 10 (can also be referred to as a timing chain in the embodiment variant shown).

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The second gear wheel track 9 is intended for engagement with an intermediate wheel 11 . The intermediate wheel 11 is arranged in particular on the crankshaft of the engine 1, so it can also be referred to as a crankshaft wheel. The intermediate gear 11, together with the first gear 6 and the second gear 7, is part of a gear drive 12.

Only for the sake of completeness it should be mentioned that the first and/or the second gear 6, 7 can have more than two gear tracks 8, 9. For example, the first gear wheel 6 can have a third gear wheel track 13, so that it can be connected to another gear wheel 14, which belongs to an auxiliary unit, for example, via a further belt drive, in particular a chain.

such as a pump to be connected.

Instead of multi-track gears 6, 7, individual gears can also be used per track, which rotate (directly or indirectly via another component).

are firmly connected.

It should also be mentioned that the gear drive 12 can also be designed differently in terms of geometry or can also be used for a different application than that described. For example, one of the gears 6, 7 can be part of a mass balance.

The first gear 6 has a first set of teeth 15 with first teeth 16 . The second gear 7 has a second set of teeth 17 with second teeth 18 . The intermediate wheel 11 has an intermediate wheel toothing 19 with intermediate wheel teeth 20 . The intermediate wheel teeth 20 of the intermediate wheel toothing 19 are in meshing engagement with the first teeth 16 of the first toothing 15 and at the same time with the second teeth 18 of the second toothing 17. Thus the first gear wheel 6, the second gear wheel 7 and the intermediate gear wheel 11 of the gear train 12 are in mesh in meshing engagement with each other.

Among other things, for the reasons mentioned above, there is backlash between the tooth flanks of the first teeth 16, the second teeth 18 and the intermediate gear teeth 20, in particular a backlash (torsional backlash) that

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refers to the arc (pitch circle) around which one wheel can rotate around the fixed other.

A coating that can be rubbed off during operation is used to produce or adjust the tooth flank clearance. Abradable coatings for this purpose are known. The term “coating” is to be understood broadly within the meaning of this description, including adhesive films or strips in general, in particular

self-adhesive strips fall under this term.

Preferably, however, an abradable coating based on a polymer, in particular a polyamideimide, optionally with the addition of at least one additive, such as a filler and/or a solid lubricant, in particular graphite and/or molybdenum disulphide, is used. Reference is made to the aforementioned DE 199 55 474 C1 and DE 100 62 241 C2, or to AT 519887 A1.

The coating can be applied to all tooth flanks or only to part of the tooth flanks, for example only in an angular range of less than 360°, in one direction of rotation or in both directions of rotation. There is also the possibility that the intermediate gear teeth 20 of the intermediate gear 11 and/or the first teeth 16 of the first gear 6 and/or the second teeth 18 of the second gear 7 are provided with the abradable coating. In the event that two gears meshing directly with each other have a coating, the layer thickness of the coating per gear can be reduced

will.

The layer thickness of the coating itself depends on the desired size of the tooth flank play. For example, the (total) layer thickness of the abradable coating can be between 30 μm and 120 μm, in particular between 50 μm and 80 μm.

The total layer thickness here means that layer thickness of the abradable coating that is present between two gears when they are on tooth flanks.

kenspiel are set to zero.

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In addition to the abradable coating, the total backlash, as the backlash in the chain first gear 6 - intermediate gear 11 - second gear 7 via an axle 21 (possibly also referred to as an axle stub), as shown in Figs. 4 to 6 as an exemplary embodiment, set. In this case, the gear of the gear drive 12, which is arranged on the axle 21, can optionally also have an abradable coating. However, this gear wheel can also be designed without a coating that can be rubbed off, for example if the intermediate wheel teeth 20 of the intermediate wheel 11 have a coating that can be rubbed off and has the appropriate layer thickness.

The axis 21 is preferably used in the gear drive 12 for the rotatable mounting of the first gear 6 and/or the second gear 7, in particular when the intermediate gear 11 is a crankshaft gear.

The axis 21 has a longitudinal extent along a longitudinal central axis 22 and is delimited by a first end area 23 and a second end area 24 . The length of the end areas 23, 24 depends, among other things, on the geometric conditions and the mechanical load capacity of the axle 21. The two end areas 23, 24 form the two ends of the axle 21. In the embodiment variant shown, the axle 21 also has a mounting element 25, which protrudes beyond the axis 21 in the radial direction. This mounting element 25 can also be designed in one piece with the axle 21 . In the embodiment variant shown, the first end region 23 with the mounting element 25 extends from the end of the axle 21 to this mounting element 25 over a length 26 in the direction of the longitudinal central axis 22. The axle 21 is attached to this first end region 23 in a corresponding holder, for example a Recess of the motor housing or an opening through the motor housing, recorded or held in a form-fitting manner. In particular, the axis 21 is accommodated in this recess or this opening over the entire length 26 . However, this should only be understood as a clarification of the term “end area”.

The first end area 23 thus forms a bearing for the axle 21, for example in a machine housing or a motor housing.

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At least one bearing for a gear wheel is arranged between the two end regions 23, 24, and preferably at a distance from the first end region 23. Specifically, the axle 21 shown has a first bearing 27 and a second bearing 28, which is arranged in particular at a distance from the first bearing 27, and is therefore provided for the arrangement of the second gear wheel 7, for example.

Instead of two separate bearings 27, 28, a continuous bearing can also be provided. Furthermore, more than two bearings 27, 28 can be arranged or formed.

The bearings 27, 28 are used to rotatably accommodate the second gear 7 or its individual gears for the desired number of tracks (or the first

Gear 6 with appropriate adjustment).

The at least one bearing 27, 28 can be a ball bearing or preferably a plain bearing, for example a plain bearing bush. Depending on the design, the bearing surface, in particular the sliding surface, can point in the direction of the respective gear wheel (if the at least one bearing 27, 28 is fixed on the axle 21) or in the direction of the axle 21 (if the at least one bearing 27, 28 fixed on the respective gear wheel). The sliding surface can thus form the radially outermost or the radially innermost surface of the plain bearing.

According to one embodiment of the invention, instead of a separate bearing element for the at least one bearing 27, 28, the axle 21 can be provided with a friction-reducing coating on an outer surface 29 or, alternatively, the bore in the gearwheel for receiving the axle 21, for example a metallic coating made of a Sliding material (in particular a plain bearing alloy for a sliding layer), or a polymer layer made from a conductive lacquer. Such sliding materials and bonded coatings are known from plain bearing technology, so that further discussions are unnecessary.

The friction-reducing coating can be made according to a wide variety of

ante also extend into the area of the assembly element 25 and thereby

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form all camps. However, the axial bearing can also be designed differently, for example as a thrust ring or as one that is independent of the at least one bearing 27 , 28

anti-friction coating.

The mounting element 25 can be plate-shaped and have a plurality of slot-like openings 30 spaced apart from one another and distributed in a circumferential direction, through which connecting means, such as screws in particular, can be inserted and the mounting element 25 can thus be fixed or locked, for example on a machine or motor housing. The openings 30 are arranged along a curved path (along a circle).

If one compares the illustrations of the axis 21 in FIG. 5 with those in FIG. 6, it is noticeable that the first region is designed with an eccentricity 31. The center point of the axis of rotation of the first end area 23 is thereby shifted in relation to the longitudinal center axis 22, so that a distance 33 in the x-direction and a distance 34 in the y-direction is formed between the longitudinal center axis 22 and the axis of rotation of the first end area 23. The size of these distances 32, 33 or the eccentricity 31 determines the size of the adjustability of the backlash. The axis of rotation of the first end region 23 is therefore not coaxial with the longitudinal central axis 22 . If the axle 21 is rotated, the eccentricity 31, which is positively accommodated in the corresponding receptacle, as has been explained above, causes the area of the axle 21 in which the at least one bearing 27, 28 is arranged or formed or In which the one or more gears are arranged and which is formed coaxially to the longitudinal central axis 22, an adjustment of the center distance in relation to the axis of the other gear. For example, the axis of rotation of the first gear wheel 6 is thus adjusted relative to the axis of rotation of the intermediate wheel 11 . The adjustment does not take place along a straight line, but along a curve. With this adjustment, the backlash is adjusted in addition to the setting by means of the abradable coating.

The adjustability of the axis 21 can, for example, in a rotation angle between

between 5° and 90°, in particular in a range of 10° and 30°.

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The change in the center distance can be between 0.1 mm and 1 mm. However, these values should only be used as examples and should not limit the scope of protection.

be understood kend, since they depend on the size of the eccentricity 31.

The rotation of the axis 21 can be carried out with an appropriate tool. To simplify this twisting, the second end region can be designed with a depression 34 that is polygonal in cross section. The indentation 34 can, for example, be square or hexagonal or octagonal, etc. The cross section of the tool is adapted accordingly, so that the tool can be inserted into the recess 34 in a form-fitting manner.

The mounting element 25 is connected to the axle 21 in a rotationally fixed manner, for example by means of a press fit and/or a positive connection. It can also be made in one piece with the axle 21, as has already been explained. Instead of locking/fixing the axle 21 in a specific position via the mounting element 25, a screw can also be guided through the axle 21, which is screwed to the machine housing or the motor housing in question. Other fixations of the relative position of the axle 21 are possible.

According to a further embodiment variant of the axle 21, it can be provided that a lubricant channel 35 for the supply of lubricant to the at least one bearing 27, 28, in particular the plain bearing(s), is arranged or formed in the axle 21, for example along the longitudinal center axis 22. Further channels can branch off from this lubricant channel 35 and lead into outlet openings 36 for the lubricant in the area of the at least one bearing 27, 28

flow.

7 shows an embodiment variant of the mounting element 25. This can be used instead of the mounting element 25 described above. However, it is also possible that, according to a further variant embodiment of the axle 21 , the second end area 24 of the axle 21 is also mounted. In this case, the assembly element 25 according to FIG. 7 can also be designed to accommodate the second end region 24 .

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The mounting element 25 according to FIG. 7, which is in particular plate-shaped, has a receptacle 37 for receiving the first or second end region 23, 24. This receptacle 37 can optionally be reinforced with a sleeve-shaped reinforcement element 38 . The reinforcement element 38 can be connected to the mounting element 25 by means of a press fit and/or form fit and/or material connection, in particular by welding. The respective end portion 23 or 24 of

Axle 21 is accommodated in this reinforcement element 38 .

According to a further embodiment variant of the axle 21, the mounting element 25 according to FIG. A plurality of bores 39 are preferably formed.

According to a further embodiment variant, it can be provided that a receiving element 40 for a fastener 41, in particular a screw, is arranged in at least one of the bores 39, preferably in all bores 39, as can also be seen in FIG. 8 . With this at least one screw, the mounting element 25 and thus possibly also the axle 21 can be fixed.

The backlash between the intermediate gear 11 and the first and second gear 6, 7 is set on the one hand via the coating which can be rubbed off during operation. For this purpose, the toothing of at least one of these gears is provided with this coating, at least in some areas, and the meshing gears are adjusted to one another in such a way that the backlash is zero. The desired backlash is determined by the layer thickness of the coating. During the first start-up, the coating rubs off due to the mechanical stress and the desired backlash is created. In addition, the axis 21 is used for at least one of the gears 6, 7, by rotating the axis distance of the axis 21 to the axis of the intermediate wheel 11 and thus the backlash can be changed and thus adjusted.

Finally, for the sake of order, it should be pointed out that for a better understanding of the structure, the axis 21, the gear wheel arrangement formed with it,

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the gear drive 12 and the engine 1, are not necessarily shown to scale.

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engine cylinder gear cylinder head

18

Reference List

31 eccentricity 32 distance

33 distance

34 deepening

Belt drive 35 lubricant channel

gear wheel gear wheel track gear track chain idler gear gear drive gear track gear tooth gear tooth gear tooth

36 exit port

37 recording

38 reinforcement element 39 hole

40 pick-up element

41 fasteners

idler gearing

Intermediate wheel tooth axis longitudinal center axis end area end area mounting element length

warehouse

Bearing outer surface breakthrough

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Claims (13)

patent claims 1. Gear arrangement comprising an axle (21) and a gear which is rotatably mounted on the axle (21), the axle (21) having a longitudinal extension along a longitudinal central axis (22) and a first end region (23) and a second end region ( 24) which lie opposite one another along the longitudinal central axis (22), and the first end area (23) forms a bearing area for the axle (21), and with at least one bearing (27, 28) for a gear wheel (6, 7), which is arranged or formed at a distance from the first end area (23), and wherein teeth of the gear wheel are provided with a coating that can be rubbed off during operation of the gear wheel, characterized in that the first end area (23) of the axle (21) in relation to the longitudinal center axis (22 ) an eccentricity (31) having. 2. Gear arrangement according to claim 1, characterized in that the bearing for the first or second gear (6, 7) is designed as a coating on an axle surface (29). 3. Gear arrangement according to claim 1 or 2, characterized in that a mounting element (25) is arranged on the axis (21). 4. Gear arrangement according to claim 3, characterized in that an axial plain bearing is formed on the mounting element (25). 5. Gear arrangement according to one of claims 1 to 4, characterized in that in the second end region (24) has a polygonal in cross section Depression (34) is formed. 6. Gear arrangement according to one of claims 1 to 5, characterized in that in the axis (21) a lubricant channel (35) for supplying lubricant to the bearing (27, 28) is arranged. A2021/50511-AT-00 7. Gear arrangement according to one of claims 1 to 6, characterized in that the second end area (24) is designed as a further bearing area of the axle (21). 8. Gear arrangement according to one of claims 3 to 7, characterized in that the mounting element (25) for fastening the axle to an engine block exclusively has a bore (39) or exclusively several Has bores (39). 9. Gear arrangement according to claim 8, characterized in that in at least one of the bores a receiving element for a fastener is arranged. 10. Gear drive (12) comprising a first gear (6) with a first toothing (15), a second gear (7) with a second toothing (17) and an intermediate wheel (11) with an intermediate wheel toothing (19), the intermediate wheel (11) is in meshing engagement with the first and the second gear (6, 7), and the first and/or the second gear (6, 7) is rotatably mounted on an axle (21), characterized in that the first and /or the second gear (6, 7) is designed as a gear arrangement according to one of Claims 1 to 9. 11. Gear drive (12) according to claim 10, characterized in that the first toothing (15) of the first toothed wheel (6) and/or the second toothing (17) of the second toothed wheel (7) and/or the intermediate wheel toothing (19) of the Intermediate wheel (11) is or are provided with the coating which can be abraded during operation of the gear drive (12). 12. Engine (1) with several rows of cylinders (2), in particular a V-engine, in which several reciprocating pistons are arranged, the reciprocating pistons being connected to a gear drive (12) via a crankshaft, characterized in that the gear drive (12) is formed according to claim 10 or 11. A2021/50511-AT-00 13. A method for adjusting the backlash of meshing gears of a gear drive (12), wherein the gear drive (12) has a first gear (6) with a first toothing (15), a second gear (7) with a second toothing (17) and an intermediate wheel (11) with an intermediate wheel toothing (19), and the intermediate wheel (11) is in meshing engagement with the first and the second gear wheel (6, 7), comprising the steps of: - Coating the first toothing (15) and/or the second toothing (17) and/or the intermediate gear toothing (19) with a coating that can be abraded during operation of the gear arrangement (12), - Establishing the meshing engagement of the intermediate wheel toothing (19) with the first toothing (15) of the first gear (6) and setting the backlash between the intermediate wheel toothing (19) and the first toothing (15) to zero - Formation of a gear arrangement according to one of claims 1 to 9 by arranging the second gear (7) on the axis (21), - Establishing the meshing engagement of the second toothing (17) of the second gear (7) with the intermediate wheel toothing (19) - Setting the backlash between the intermediate wheel toothing (19) and the second toothing (17) to a predefined value by turning the axle (21) on which the second gear wheel (7) is arranged and locking the axle (21) after reaching the predefined value of the backlash, - Driving the gear drive (12) so that the abradable coating of the first toothing (15) and/or the second toothing (17) and/or the intermediate wheel toothing (19) rubs off at least partially. A2021/50511-AT-00