WO2022256854A1

WO2022256854A1 - Component assembly, and planetary gear set in which the component assembly is installed

Info

Publication number: WO2022256854A1
Application number: PCT/AT2022/060191
Authority: WO
Inventors: Philipp Bergmann; Christian BRUNMAIR
Original assignee: Miba Gleitlager Austria Gmbh
Priority date: 2021-06-10
Filing date: 2022-06-08
Publication date: 2022-12-15
Also published as: DE112022003028A5; AT524540A4; AT524540B1

Abstract

The invention relates to a component assembly (15), comprising: - a carrier element (17, 8, 9) having a receiving bore (18); - a functional element (16, 13) having a through-hole (21), which functional element is fastened to the carrier element (17), a rear face (22) of the functional element (16) lying against a contact surface (23) of the carrier element (17); - a screw (14), which has a screw head (24) and a threaded portion (19), the threaded portion (19) being screwed, through the through-hole (21) in the functional element (16, 13), into the receiving bore (18) in the carrier element (17, 8, 9), and the screw head (24) lying against a screw-head bearing surface (25) of the functional element (16, 13). The functional element (16, 13) has a recess (26) in the rear face (22), in the region of the through-hole (21), which recess has a recess extent (27) that is at least as large as a screw-head bearing surface extent (28), and as a result, the screw-head bearing surface (25) is elastically resilient. The sleeve (35) is furthermore inserted in the through-hole (21).

Description

ASSEMBLY OF COMPONENTS, AS WELL AS A PLANETARY GEAR,

IN WHICH THE COMPONENT COMPOSITION IS BUILT IN

The invention relates to an assembly of components and a planetary gear in which the assembly of components is installed.

A planetary gear for a wind turbine is known from EP2383480B1. The planetary gear comprises a planet carrier with a first planet carrier cheek and a second planet carrier cheek, a planet wheel pin, which is accommodated in the planet carrier, a planet wheel, which is mounted on the planet wheel pin, and a planet wheel axial slide bearing, which is arranged between the planet wheel and the planet carrier cheek. Usually such planetary gear axial slide bearings are attached by means of a screw to the tarpaulin tenträgerwange.

Experience has shown that after a certain period of use, the planetary wheel axial plain bearings are no longer firmly attached to the planet carrier cheek and can therefore slip, which can lead to a malfunction of the planetary gear.

JP 2007182923 A discloses a combination of components with a carrier element and a functional element. The functional element is coupled to the carrier element by means of a screw. The functional element is designed to be flexible in the area of a contact surface of the screw. The screw has a shank through which the screw-in depth is limited.

The assembly of components in JP 2007182923 A has the disadvantage that the limitation of the screw-in depth by means of the shank has insufficient accuracy. Thus, the functional element can be held either too tightly or too loosely on the carrier element. In addition, the thread of the screw can be damaged by the limitation of the screw-in depth by means of the shank.

The object of the present invention was to overcome the disadvantages of the prior art and to create a combination of components or a planetary gear in which the individual parts fastened to one another by means of a screw are fastened sufficiently firmly to one another. This object is achieved by a device and a method according to the claims.

In the following, the effects of the invention are described using the exemplary embodiment of the tarpaulin transmission. However, the effects mentioned occur with every assembly of components formed according to the invention, even if this is not installed in a planetary gear or if it is not a planetary gear. The planetary gear claimed in the patent claims is a special version of the generally claimed component composition.

All features of the assembly of components can thus also be implemented in the special version of the planetary gear. The planet carrier cheek corresponds to the carrier element. The planetary gear axial plain bearing corresponds to the functional element.

The problems of the lack of permanently durable attachment can occur in particular when a thermal expansion coefficient of the material of the planetary wheel axial plain bearing, also called functional element material, is greater than a thermal expansion coefficient of the screw material.

In the production of the planetary gear, the screws are tightened with a predetermined torque to achieve a predetermined clamping force or preload between the planet wheel axial plain bearing and the planet carrier cheek. Research in the course of the invention has shown that during operation of the planetary gear there is massive heating of the interior of the planetary gear and thus of the components located in the interior of the planetary gear. Because the coefficient of thermal expansion of the material of the planetary wheel axial plain bearing, also known as the material of the functional element, is greater than the coefficient of thermal expansion of the material of the screw, the thermal expansion of the planetary wheel axial plain bearing is greater than that of the screw due to heating.

In the known from the prior art planetary gear is increased by this under different thermal expansion when heating the components, the clamping force of the screw on the planetary gear axial slide bearing, in which case the strength of the planetary gear wheel axial gleitla material is exceeded. This leads to a plastic deformation of the planetary gear axial plain bearing. Now, if the temperature in the interior of the planetary gear decreases again and the different thermal expansion of the planetary wheel axial plain bearing and the screw is reversed, the planetary gear axial plain bearing shrinks below its original size due to the above-described plastic deformation in the area of the screw head contact surface. As a result, the originally set preload of the screw can no longer be achieved, as a result of which the planetary gear axial plain bearing can no longer be adequately retained.

According to the invention, a component assembly is formed. The assembly of components includes:

- A carrier element with a receiving bore;

- A functional element with a through hole, wherein the through hole has a through hole diameter, wherein the functional element is attached to the carrier element, wherein a rear side of the functional element rests against a contact surface of the Trä gerelementes;

- A screw with a screw head and a threaded section, the threaded section being fastened in the receiving bore of the carrier element and the screw head resting against a screw head bearing surface of the functional element in order to clamp the functional element on the carrier element, the screw head bearing surface having a screw head bearing surface extension, the Functional element in the area of the through hole on the back has a free position with a free extension, whereby the surface surface of the screw head is designed to be elastically resilient.

Furthermore, a sleeve can be formed, wherein a first face of the sleeve can bear against the screw head and wherein a second face of the sleeve can bear on the contact surface of the carrier element, wherein the sleeve has a first sleeve region with a first outer diameter, starting from the first face. wherein the first sleeve area has a first axial extension, wherein the first outer diameter is smaller than the through hole diameter and wherein the sleeve has a second sleeve area with a second outer diameter, wherein the second outer diameter is at least partially equal to or larger than the through hole diameter, wherein the sleeve has a sleeve bore through which the screw is inserted.

Surprisingly, the inventive design of the functional element allows a permanently durable connection to be established between the functional element and the carrier. achieve ger element. This permanently durable connection remains stable even with strong temperature fluctuations. In particular, it can be achieved by the assembly of components according to the invention that the prestressing of the screw is maintained over the service life of the assembly of components or decreases only slightly due to the creep effects of the individual components. This can be achieved in that due to the resilient nature of the functional element, even when the assembly of components heats up, there is no or only a justifiably small plastic deformation of the functional element, which does not mean that the functional element is no longer held sufficiently. In addition, no resilient sub-layers under the screw head, such as plate springs, etc., which would serve to compensate for the different elongation of the catch, are necessary in the assembly of components according to the invention. As a result, the structure of the assembly of components can be significantly simplified, which on the one hand significantly reduces the risk of incorrect assembly of the assembly of components and on the other hand brings with it economic advantages.

The design of the sleeve means that the screw can be tightened with the specified tightening torque without the screw head bearing surface of the functional element being subjected to excessive stress.

The fact that the second outer diameter is at least partially equal to or larger than the through hole diameter means that the sleeve can be accommodated in the functional element pre-assembled, so that it cannot be lost from the functional element. This can be achieved in particular by a press fit or pressing the second sleeve area into the through hole.

Alternatively, the second sleeve area can also be glued into the through hole. In this case, the adhesive can produce the diameter connection between the second sleeve area and the through hole.

In yet another alternative variant, provision can also be made for the second sleeve area to be fastened in the through hole by spot welding or by some other material connection. In this case, the spot weld or other material connection can produce the diameter connection between the second sleeve area and the through hole. In a state prior to assembly, in which the second sleeve area is received in the through hole of the functional element, the first end face of the sleeve can protrude in relation to the screw head contact surface of the functional element.

In a state after assembly, in which the carrier element and the functional element are firmly coupled to one another, the first end face of the sleeve and the screw head bearing surface can be arranged in one plane.

Furthermore, it can be provided that the functional element is formed from a functional element material and that the screw is formed from a screw material, with a thermal expansion coefficient of the functional element material being greater than a thermal expansion coefficient of the screw material.

Furthermore, it can be provided that the sleeve is formed from a sleeve material. In particular, it can be provided that the sleeve material is a steel material. Furthermore, it can be provided that the sleeve material and the screw material have similar material properties. In particular, it can be provided that the sleeve material and the screw material have a similar thermal expansion coefficient, in particular that the thermal expansion coefficients have a maximum deviation of the two thermal expansion coefficients of 2×10 ⁶ /K, in particular Ixl0 ⁶ /K, preferably 0.5×l0 ⁶ /K.

Furthermore, it can be expedient if an annular cantilever is formed between the screw head bearing surface and the exemption, which cantilever has a cantilever thickness where the first axial extent of the first sleeve region is greater than the cantilever thickness. This measure ensures that when the support element and the functional element are screwed together or when the support element and the functional element are screwed together, the sleeve is not clamped in the functional element, but that the sleeve can be moved relative to the functional element. This allows the sleeve and the functional element to function properly.

In addition, it can be provided that the thickness of the cantilever arm is between 10% and 99%, in particular between 50% and 95%, preferably between 60% and 90% of the first axial extent of the first sleeve area. With such a dimensioning in particular, an improved ability to assemble the assembly of components can be achieved. Furthermore, it can be provided that the sleeve has a sleeve length and that the screw head bearing surface is arranged at a distance from the contact surface, the sleeve length being smaller than the distance between the screw head bearing surface and the contact surface. This measure makes it possible for the screw head to rest against the screw head bearing surface in any case and for the functional element to be pressed against the carrier element before the screw head presses the sleeve against the carrier element.

In particular, it can be provided that the sleeve length is between 1 μm and 2 mm, in particular between 10 μm and 500 μm, preferably between 50 μm and 100 μm shorter than the distance between the screw head bearing surface and the contact surface. As a result, the functional element can be securely clamped.

In addition, it can be provided that the first sleeve area has a cylindrical outer lateral surface. In particular, a sleeve designed in this way can be produced easily.

Also advantageous is an embodiment according to which it can be provided that a surface structuring, in particular in the form of knurls, is formed in the second sleeve area. This brings with it the advantage that in the uninstalled state the second sleeve area of the sleeve can be easily accommodated in a through bore of the functional element and that the sleeve can be easily pushed out of the functional element.

According to a development, it is possible for the second sleeve area to have a cylindrical outer lateral surface. This has the advantage that a sleeve designed in this way is easy to manufacture.

In an alternative embodiment, it can be provided that the second sleeve area tapers, in particular conically, at least in sections towards the first sleeve area. A sleeve designed in this way places only low demands on manufacturing tolerances, with good connectivity being able to be achieved between the second sleeve area of the sleeve and the through hole of the functional element. In particular, it can be provided that a counter-shape corresponding to the taper is formed in the through bore of the functional element. Furthermore, it can be provided that the extent of the release is at least as large as the extent of the screw head bearing surface. Particularly with such a design of the functional element, it can be achieved that the prestressing of the screw is maintained over the life of the component assembly.

Furthermore, it can be provided that the extension of the screw head bearing surface is between 30% and 100%, in particular between 50% and 95%, preferably between 70% and 80% of the extension of the release area. This measure allows sufficient elasticity of the screw head support surface to be achieved, while at the same time it can offer sufficient stability to be able to absorb the necessary clamping force of the screw.

In addition, it can be provided that the functional element is formed from an AlSn alloy and the screw is formed from a steel material. Particularly with such a combination of the material of the functional element and the material of the screw, the positive effects of the long-term durable clamping of the functional element can be achieved.

An AlSn alloy is an alloy that includes aluminum and tin and has outstanding properties, particularly as a plain bearing material. Such an alloy has a high coefficient of thermal expansion.

In an alternative embodiment, it can also be provided that the functional element is formed from a copper material or a copper alloy and the screw is formed from a steel material.

Of course, the functional element can also be formed from another material with high thermal expansion.

Furthermore, it can be expedient if the carrier element is formed from a steel material.

An embodiment is also advantageous according to which it can be provided that an annular cantilever is formed between the screw head bearing surface and the clearance, with a cantilever arm thickness between 20% and 100%, in particular between 30% and 80%, preferably between 40% and 60% of a through hole diameter. In particular, a cantilever arm with such a cantilever arm thickness can have sufficient elasticity combined with sufficient stability.

According to a further development, it is possible for the screw head bearing surface to be designed countersunk in a recess in the functional element. This is particularly advantageous when the functional element is designed as a sliding bearing and has a sliding surface. In particular, it can be provided that the countersink is dimensioned in such a way that the screw head can be accommodated completely within the countersink.

With this measure, the attachment of the functional element does not interfere with its sliding properties.

Furthermore, it can be expedient if the screw is designed as an expansion screw. Be particularly when the screw is designed as an expansion screw, a long-term bare connection between the functional element and the support element can be achieved. When using an expansion screw, a specified tightening torque can also be deviated from without this leading to a major change in the clamping force, as a result of which the tolerances can be better maintained.

In addition, it can be provided that the screw head bearing surface is elastically prestressed at an ambient temperature of 20°C. In particular, the design of the component or the specification of the tolerance is selected such that when a predetermined tightening torque of the screw is reached in the assembly of the component combination, an elastic prestressing of the screw head contact surface is achieved. With this measure, it can be achieved that even if the ambient temperature drops and the individual components of the assembly of components suffer negative thermal expansion, adequate clamping of the functional element on the carrier element can still be achieved. The elastic prestressing of the screw head contact surface at an ambient temperature of 20 °C can be selected in such a way that even with a minimum ambient temperature at the installation site of the component assembly and thus negative thermal expansion for this assembled state, a sufficient clamping force of the screw is still applied to the functional element. According to the invention, a planetary gear is formed. The planetary gear includes:

- A planetary carrier with a first planetary carrier cheek and a second planetary carrier cheek, in at least one of the planetary carrier cheeks a receiving bore is ausgebil det;

- At least one planet wheel bolt, which is accommodated in the planet carrier, in particular in the two planet carrier cheeks;

- At least one planet wheel, which is mounted on the planet wheel bolt;

- At least one planet gear axial plain bearing with a through hole, which is arranged between the planet gear and the planet carrier cheek and which is attached to the planet carrier cheek, with a rear side of the planetary gear axial plain bearing resting against a contact surface of the planet carrier cheek,

- At least one screw with a screw head and a threaded section, the threaded section being fastened in the receiving bore of the planetary carrier cheek and the screw head resting against a screw head bearing surface of the planetary gear axial plain bearing in order to clamp the planetary gear axial plain bearing on the planetary gear carrier cheek, the screw head bearing surface having a screw head bearing surface extension.

In the area of the through hole, the planetary gear axial plain bearing has a clearance on the back with a clearance extension that is at least as large as a screw head bearing surface extension, as a result of which the screw head bearing surface is designed to be elastically resilient, with a sleeve being formed, which rests with a first end face on the screw head and with a second end face resting against the contact surface of the planet carrier cheek, wherein the sleeve, starting from the first end face, has a first sleeve area with a first outer diameter, the first sleeve area having a first axial extension, the first outer diameter being smaller than the through hole diameter and wherein the sleeve has a second sleeve portion with a second outer diameter, wherein the second outer diameter is at least partially equal to or greater than the through hole diameter, wherein the sleeve is a sleeve Has a bore through which the screw is inserted.

The planetary gear according to the invention brings with it the advantage that the planetary gear axial plain bearing is held sufficiently firmly and sufficiently durable on the planetary carrier cheek over the entire life of the planetary gear can. Particularly in the case of planetary gears, there are large temperature fluctuations in the internal components of the planetary gear during operation, which means that it is necessary for the planetary gear axial plain bearing, which is made of a plain bearing material with high thermal expansion, not to be plastically deformed by the temperature fluctuations in the area of the screw head contact surface and is thus damaged.

It can also be provided that the planetary wheel axial plain bearing is formed from a planetary wheel axial plain bearing material and that the screw is made from a screw material, with a thermal expansion coefficient of the planetary wheel axial plain bearing material being greater than a thermal expansion coefficient of the screw material.

According to the invention, a wind power plant is designed with a planetary gear, the planetary gear being designed in accordance with the above statements.

According to the invention, a method for assembling a component assembly is provided. The process comprises the process steps:

- Providing a carrier element with a receiving bore, wherein the carrier element has a contact surface;

- providing a functional element with a through-hole, the through-hole having a through-hole diameter, a rear side of the functional element being designed to rest against a bearing surface of the carrier element, the functional element having a screw-head bearing surface and a sleeve being accommodated in the through-hole, which sleeve has a has a first sleeve area and a second sleeve area, the sleeve being accommodated in the through hole in such a way that the sleeve has a firm seat in the through hole by means of the second sleeve area, a first end face of the sleeve protruding relative to the screw head bearing surface of the functional element;

- providing a screw with a screw head and a threaded section,

- Insert the screw through the sleeve bore of the sleeve;

- Create the back of the functional element on the contact surface of the support element;

- Pick up and tighten the screw in the receiving bore of the carrier element, where in a first step of tightening the screw, the screw head rests on a first end face of the sleeve and with further tightening of the screw, the sleeve by means of The screw head is displaced axially towards the carrier element, so that the second sleeve area is loosened from the through hole and axially removed and the first sleeve area of the sleeve is accommodated in the through hole in a freely displaceable manner, with further tightening of the screw, the screw head resting on a screw head bearing surface of the functional element rests in order to clamp the functional element on the support element, with further tightening of the screw, the sleeve between the screw head and the contact surface of the support element is clamped.

The method according to the invention has the advantage that the sleeve can be accommodated preassembled in the functional element, so that it cannot be lost from the functional element. When assembling or attaching the functional element to the carrier element, the sleeve is automatically released by tightening the screw. Overall, a simplified assembly can be achieved by the method according to the invention, since the sleeve does not have to be used separately, but is already pre-assembled in the functional element.

For the essence of the invention, it is not necessary for the screw head to rest directly on a screw head support. Of course, it is also conceivable and is also covered by the patent claims that a washer, a lock washer, a snap ring, a spring ring and the like can be arranged between the screw head and the screw head support.

In a first embodiment, it is conceivable that the receiving bore is designed as a threaded bore. Here, a threaded portion of the screw can be screwed into the receiving hole. In a further embodiment, it is also conceivable that the mounting hole is designed as a through hole and the screw is inserted through the mounting hole and a threaded nut is arranged on a rear side of the carrier element, which is screwed onto the threaded portion of the screw. The use of a threaded rod instead of a screw has the same effect, with a threaded nut being formed instead of the screw head, which is coupled to the threaded rod.

For a better understanding of the invention, it is explained in more detail with reference to the following figures. They each show in a greatly simplified, schematic representation:

1 shows a first exemplary embodiment of a planetary gear in a schematic sectional view;

Fig. 2 shows a first exemplary embodiment of a component assembly in the assembled state;

3 shows a representation of a first method step for assembling the assembly of components;

4 shows an illustration of the first method step for assembling a further exemplary embodiment of the assembly of components.

As an introduction, it should be noted that in the differently described embodiments, the same parts are provided with the same reference numbers or the same component designations, and the disclosures contained throughout the description can be transferred to the same parts with the same reference numbers or the same component designations. The position information selected in the description, such as top, bottom, side, etc., refers to the figure directly described and shown and these position information are to be transferred to the new position in the event of a change in position.

Fig. 1 shows an embodiment of a planetary gear 1 in a sectional view according to a cross section along a center line 2 of the planetary gear 1.

As is known, wind turbines include a tower at the upper end of which a gondola is arranged, in which the rotor is mounted with the rotor blades. This rotor is via the Pla designated gear 1 with a generator, which is also located in the nacelle, effektver connected, with the planetary gear 1, the low speed of the rotor is translated into a higher speed of the generator rotor. Since such designs of wind turbines belong to the state of the art, reference is made to the relevant specification at this point.

The planetary gear 1 has a sun gear 3 which is coupled for movement to a shaft 4 leading to the generator rotor. The sun gear 3 is surrounded by several planetary gears 5, for example two, preferably three, surrounded. Both the sun gear 3 and the plane tenräder 5 have external spur gears, which are in meshing engagement miteinan, these spur gears are shown in Fig. 1 schematically.

The planet wheels 5 are each mounted in a planet carrier 7 by means of a planet wheel bolt 6 . Furthermore, it can be provided that the planetary gear pin 6 is fixed or accommodated in a non-positive or form-fitting manner in a first planetary carrier cheek 8 and a second planetary carrier cheek 9 . In particular, it can be provided that the planet wheel bolt 6 is secured against rotation by any securing element that is not explicitly shown. The two planet carrier cheeks 8, 9 are part of the planet carrier 7.

Surrounding the planetary gears 5 is a ring gear 10 which has internal gearing which is in meshing engagement with the face gearing of the planetary gears 5 . The ring gear 10 can be formed in a one-part or multi-part planetary gear housing 11 or be coupled to it.

Furthermore, it can be provided that for the storage of the planetary gears 5 on the planetary gear bolts 6 per planetary gear 5, at least one planetary gear radial plain bearing 12 is provided.

Furthermore, it can be provided that for mounting the planetary gears 5 on the planetary gear bolts 6 for each planetary gear 5, at least one planetary gear axial slide bearing 13 is provided. The plane tenradaxialgleitlager 13 can be fastened by means of a screw 14 on the planet carrier cheek 8, 9 be.

2 shows a detailed view of a further and possibly independent embodiment of the bearing situation of the planetary wheel axial plain bearing 13, again using the same reference numbers or component designations as in the previous FIG. 1 for the same parts. In order to avoid unnecessary repetitions, reference is made to the detailed description in the preceding FIG. 1 .

In the following, this storage situation is referred to as an assembly of components 15, since such an assembly of components 15 can be used not only in the planetary gear 1, but also in other applications. The individual features of the component composition 15 must of course be assigned to the planetary gear 1 . As can be seen from FIG. 2, the planetary gear axial plain bearing 13, which can generally also be referred to as the functional element 16, is fastened to the second planet carrier cheek 9, which can also generally be referred to as the carrier element 17, by means of the screw 14. In particular, it can be provided that a receiving bore 18 is formed in the carrier element 17, into which a threaded portion 19 of the screw 14 is screwed.

The screw 14, in particular a screw shank 20 of the screw 14 can be passed through a sleeve 45 senbore 35 of a sleeve. In particular, it can be provided that the sleeve 35 is received in a through hole 21 arranged in the functional element 16 . The sleeve 35 can have a sleeve length 36 .

As can also be seen from FIG. 2, a rear side 22 of the functional element 16 rests against a contact surface 23 of the carrier element 17 in the assembled state. The functional element 16 is pressed against the carrier element 17 by means of the screw 14 . In particular, it is provided here that a screw head 24 of the screw 14 bears against a screw head bearing surface 25 of the functional element 16 .

Furthermore, an opening 26 can be formed on the rear side 22 of the functional element 16 , which is formed in the area of the screw head bearing surface 25 . In particular, it is provided that the release 26 has a release extension 27 . The screw head bearing surface 25 has a screw head bearing surface extension 28 . In the present embodiment, the screw 14 is formed as a hexagon socket screw out, the screw head bearing surface 25 is formed as a circular ring surface. The extension of the screw head bearing surface 28 thus corresponds to a diameter in the present exemplary embodiment.

In an alternative embodiment, it can of course also be provided that the extension of the screw head bearing surface 28 is not rotationally symmetrical but, for example, polygonal or in some other form. Similarly, in the present exemplary embodiment, the clearance 26 is also designed as a cylindrical element, as a result of which the clearance extension 27 is also a diameter. Of course, the exemption 26 can also have any other shape. As can also be seen from FIG. 2, the through-hole 21 has a diameter 29 through-hole. The screw head bearing surface 25 is thus formed between the screw head bearing surface extension 28 and the through hole diameter 29 .

As can also be seen from FIG. 2, a cantilever arm 30 is formed by the cutout 26, which in the present exemplary embodiment is designed in the shape of a circular ring. The cantilever 30 has a cantilever thickness 31 which essentially determines the rigidity or the strength of the cantilever 30 . Through the formation of the exemption 26 and thus hanging together of the cantilever 30, the screw head bearing surface 25 can be formed from elastically flexible.

As can also be seen from FIG. 2 , the cutout 26 has a cutout depth 32 . The clearance depth 32 is preferably selected to be large enough so that the cantilever arm 30 does not come into contact with the contact surface 23 of the carrier element 17 when the maximum deformation of the screw head contact surface 25 occurs. In the present exemplary embodiment, the clearance depth 32 is exaggerated for the sake of clarity compared to the proportions of the remaining components. The relief depth 32 can be between 0.1 mm and 10 mm, in particular between 0.5 mm and 5 mm, preferably between 1 mm and 3 mm. It can also be provided that the relief depth 32 is between 1% and 300%, in particular between 2% and 200%, preferably between 50% and 120% of the cantilever thickness 31 is.

As can also be seen from FIG. 2 , provision can be made for a countersink 33 to be formed in the functional element 16 , which serves to accommodate the screw head 24 . Sensing effect 33 can have a countersink diameter 34 . Furthermore, it can be provided that the countersink diameter 34 is between 50% and 200%, in particular between 70% and 120%, preferably between 80% and 90% of the extent 27 of the release area.

As can also be seen from FIG. 2, it can be provided that a first end face 37 of the sleeve 35 rests on the screw head 24 and a second end face 38 of the sleeve 35 rests on the contact surface 23 of the carrier element 17, 8, 9. The distance between the first end face 37 and the second end face 38 to one another define the sleeve length 36. Starting from the first end face 37 , the sleeve 35 can have a first sleeve region 39 with a first outer diameter 41 . The first sleeve area 39 has a first axial extent 42 .

Furthermore, the sleeve 35 can have a second sleeve area 40 with a second outer diameter 43 . The second sleeve portion may have a second axial extent 44 .

In particular, the sleeve 35 can have a sleeve bore 45 through which the screw 14 is inserted. The sleeve 35 has a sleeve length 36, which is preferably chosen so that when the screw 14 is screwed in, the screw head 24 is pressed against the screw head bearing surface 25 such that the screw head bearing surface 25 is elastically deformed. In this way, a clamping or a pre-tensioning of the screw situation can be achieved. In particular, it can be provided that, taking into account the manufacturing tolerances, the sleeve length 36 of the sleeve 35 is less than the sum of the cantilever arm thickness 31 and the clearance depth 32, which can also be referred to as the distance 46 between the screw head bearing surface 25 and the contact surface 23.

Furthermore, it can be provided that the first axial extension 42 of the first sleeve area 39 is greater than the cantilever arm thickness 31.

3 shows the assembly of components 15 in a position ready for assembly, the same reference numerals or component designations as in the preceding FIGS. 1 and 2 being used again for the same parts. In order to avoid unnecessary repetitions, reference is made to the detailed description in the preceding FIGS.

As can be seen from FIG. 3, it can be provided that for the assembly of the functional element 16 and the carrier element 17 the sleeve 35 can be accommodated in the through bore 21 of the functional element 16 already preassembled. In particular, it can be provided that the second sleeve area 40 is pressed into the through bore 21 . In this case, the sleeve 35 does not have to be be kept or used separately, but can be placed together with the functional element 16. This entails substantial simplifications when assembling the assembly of components 15 .

As can be seen particularly clearly from FIG.

In a first method step for assembling the functional element 16 and the carrier element 17, the functional element 16 can now be placed against the carrier element 17 and the screw 14 can be screwed through the sleeve bore 45 into the receiving bore 18 of the carrier element 17. The screw head 24 first comes to rest on the first end face 37 of the sleeve 35 and presses the sleeve 35 axially out of its position, so that the second sleeve area 40 is removed from the cantilever arm 30 or from the through hole 21 of the functional element 16. As soon as the second sleeve area 40 is completely removed from the area of the through hole 21 and the sleeve 35 is located with its first sleeve area 39 inside the through hole 21, the sleeve 35 is detached from the functional element 16 and can be moved axially. Within the sleeve bore 45, the sleeve can also be moved slightly radially.

As the screw 14 is screwed in further, the screw head 24 comes into contact with the screw head bearing surface 25 and presses the functional element 16 against the carrier element 17. When the screw 14 is tightened further, the screw head bearing surface 25 or the cantilever arm 30 deforms flexibly, as a result of which the Functional element 16 is pressed against the element 17 carrier element. This deformation extends until the screw head 24 rests against the first end face 37 of the sleeve 35 and the second end face 38 of the sleeve 35 rests on the bearing surface 23 of the carrier element 17 . Upon further tightening of the screw 14, the screw 14 can be tightened or adjusted to the desired torque and thus the desired bias voltage.

4 shows a further embodiment of the assembly of components 15, which may be independent of itself, with the same reference numerals or component designations as in the preceding FIGS. 1 to 3 being used again for the same parts. In order to avoid unnecessary repetitions, reference is made to the detailed description in the preceding FIGS. As can be seen from FIG. 4, provision can be made for the second sleeve region 40 to be designed conically at least in sections, with the cone being able to taper towards the first end face 37 . Correspondingly, the through hole 21 can also be formed conically.

The exemplary embodiments show possible variants, it being noted at this point that the invention is not limited to the specifically illustrated variants of the same, but rather that various combinations of the individual variants are also possible with one another and these possible variations are based on the teaching of technical action the present invention is within the skill of a person skilled in the art working in this technical field.

The scope of protection is determined by the claims. However, the description and drawings should be used to interpret the claims. Individual features or combinations of features from the different exemplary embodiments shown and described can represent independent inventive solutions. The task on which the independent inventive solutions are based can be found in the description.

All information on value ranges in the present description is to be understood in such a way that it also includes any and all sub-ranges, e.g. the information 1 to 10 is to be understood as including all sub-ranges, starting from the lower limit 1 and the upper limit 10 i.e. all sub-ranges start with a lower limit of 1 or greater and end with an upper limit of 10 or less, e.g. 1 to 1.7, or 3.2 to 8.1, or 5.5 to 10.

Finally, for the sake of clarity, it should be pointed out that some elements are shown not to scale and/or enlarged and/or reduced in order to better understand the structure. list of reference numbers

29 through hole diameter planetary gear

30 cantilever centerline

31 cantilever thickness sun wheel

32 depth of relief wave

33 lowering planet gear

34 counterbore diameter planetary pinion

35 planet carrier sleeve

36 sleeve length first planet carrier cheek

37 first face second planet carrier cheek

38 second face ring gear

39 first sleeve area planetary gear case

40 second sleeve area planetary gear radial plain bearing

41 first outer diameter planet gear axial plain bearing

42 first axial screw

43 second outer diameter assembly of components

44 second axial extension functional element

45 sleeve bore carrier element

46 distance locating hole threaded section screw shank through-hole rear contact surface screw head screw head bearing surface release release extension screw head bearing surface extension

Claims

P atentClaims

1. Assembly of components (15) comprising:

- A carrier element (17, 8, 9) with a receiving bore (18);

- A functional element (16, 13) with a through hole (21), the through hole (21) having a through hole diameter (29), the functional element (16, 13) being fastened to the carrier element (17), with a rear side ( 22) of the functional element (16) on a bearing surface (23) of the carrier element (17);

- A screw (14) with a screw head (24) and a threaded section (19), the threaded section (19) being fastened in the receiving bore (18) of the carrier element (17, 8, 9) and the screw head (24). a screw head bearing surface (25) of the functional element (16, 13) in order to clamp the functional element (16, 13) on the carrier element (17, 8, 9), the screw head bearing surface (25) having a screw head bearing surface extension (28), wherein the functional element (16, 13) has a clearance (26) with a clearance extension (27) in the region of the through bore (21) on the rear side (22), as a result of which the screw head bearing surface (25) is designed to be elastically resilient, characterized in that a sleeve (35) is formed, with a first face (37) of the sleeve (35) bearing against the screw head (24) and with a second face (38) of the sleeve (35) on the bearing surface (23) of the carrier element (17, 8, 9) rests, whereby the sleeve (3 5) starting from the first end face (37), has a first sleeve area (39) with a first outer diameter (41), the first sleeve area (39) having a first axial extension (42), the first outer diameter (41) being smaller , as the through-hole diameter (29) and wherein the sleeve (35) has a second sleeve area (40) with a second outer diameter (43), the second outer diameter (43) being at least partially the same size or larger than the through-hole diameter ( 29), where in the sleeve (35) has a sleeve bore (45) through which the screw (14) is pushed through.

2. Assembly of components (15) according to claim 1, characterized in that an annular cantilever (30) is formed between the screw head bearing surface (25) and the clearance (26), which has a cantilever arm thickness (31), the first axial extension (42 ) of the first sleeve area (39) is greater than the cantilever thickness (31).

3. Assembly of components (15) according to claim 1 or 2, characterized in that the sleeve (35) has a sleeve length (36) and that the screw head bearing surface (25) is arranged at a distance (46) from the contact surface (23), wherein the sleeve length (36) is less than the spacing (46).

4. assembly of components (15) according to any one of the preceding claims, characterized in that the first sleeve region (39) has a cylindrical surface Außenmantelflä.

5. Assembly of components (15) according to one of the preceding claims, characterized in that a surface structure, in particular in the form of knurls, is formed in the second sleeve region (40).

6. assembly of components (15) according to any one of claims 1 to 4, characterized in that the second sleeve region (40) has a cylindrical outer surface.

7. Assembly of components (15) according to one of claims 1 to 5, characterized in that the second sleeve region (40) is designed to taper, in particular conically, at least in sections towards the first sleeve region (39).

8. Planetary gear (1), the planetary gear (1) comprising:

- A planet carrier (7) with a first planet carrier cheek (8) and a second tarpaulin tenträgerwange (9), wherein in at least one of the planet carrier cheeks (8, 9) a Aufnah mebohr (18) is formed;

- At least one planet wheel bolt (6), which is accommodated in the planet carrier (7), in particular in the two planet carrier cheeks (8, 9);

- At least one planet wheel (5) which is mounted on the planet wheel pin (6);

- at least one planet wheel axial plain bearing (13) with a through hole (21), which is arranged between the planet wheel (5) and the planet carrier cheek (8, 9) and which is fastened to the planet carrier cheek (8, 9), with a rear side (22) of the planetary gear bearing (13) rests against a contact surface (23) of the planet carrier cheek (8, 9), - At least one screw (14) with a screw head (24) and a threaded section (19), the threaded section (19) being fixed in the receiving bore (18) of the planetary carrier cheek (8, 9) and the screw head (24) being fixed on a screw head bearing surface (25) of the planetary wheel axial plain bearing (13) in order to clamp the planetary wheel axial plain bearing (13) on the planet carrier cheek (8, 9), the screw head bearing surface (25) having a screw head bearing surface extension (28), characterized in that the planetary wheel axial plain bearing (13) in the area of the through hole (21) on the rear side (22) has a clearance (26) with a clearance extension (27) which is at least as large as a screw head bearing surface extension (28), whereby the screw head bearing surface (25) is designed to be elastically resilient , wherein a sleeve (35) is formed, which rests with a first end face (37) on the screw head (24) and with a two-th Sti rnseite (38) on the contact surface (23) of the planet carrier cheek (8, 9), wherein the sleeve (35) starting from the first end face (37) has a first sleeve area (39) with a first outer diameter (41), wherein the first sleeve area (39) has a first axial extension (42), the first outer diameter (41) being smaller than the through bore diameter (29) and the sleeve (35) having a second sleeve area (40) with a second outer diameter (43) has, wherein the second outer diameter (43) is at least partially the same size or larger than the through hole diameter (29), wherein the sleeve (35) has a sleeve bore (45) through which the screw (14) is inserted.

9. Wind power plant with a planetary gear (1), characterized in that the planetary gear (1) is designed according to claim 8.

10. A method for assembling a component assembly (15) comprising the method steps:

- Providing a carrier element (17, 8, 9) with a receiving bore (18), wherein the carrier element (17, 8, 9) has a contact surface (23);

- providing a functional element (16, 13) with a through-bore (21), the through-bore (21) having a through-bore diameter (29), a rear side (22) of the functional element (16) for laying against a contact surface (23) of the Support element (17) is formed, wherein the functional element (16, 13) has a screw head bearing surface (25) and wherein in the through hole (21) a sleeve (35) is accommodated, which has a first sleeve area (39) and a second sleeve area ( 40). ) the sleeve (35) relative to the screw head bearing surface (25) of the functional element (16, 13) protrudes;

- Provide a screw (14) with a screw head (24) and a threaded section (19),

- inserting the screw (14) through the sleeve bore (45) of the sleeve (35);

- Create the back (22) of the functional element (16) on the contact surface (23) of the Trä gerelementes (17);

- Pick up and tighten the screw (14) in the receiving bore (18) of the carrier element (17, 8, 9), wherein in a first step of tightening the screw (14), the screw head (24) on a first end face (37 ) of the sleeve (35) is in contact and when the screw (14) is tightened further, the sleeve (35) is displaced axially towards the carrier element (17, 8, 9) by means of the screw head (24), so that the second sleeve area (40 ) is detached from the through bore (21) and removed axially and the first sleeve region (39) of the sleeve (35) is received in the through bore (21) in a freely displaceable manner, with further tightening of the screw (14) causing the screw head (24 ) rests against a screw head bearing surface (25) of the functional element (16, 13) in order to clamp the functional element (16, 13) on the carrier element (17, 8, 9), with further tightening of the screw (14), the sleeve (35) clamped between the screw head (24) and the contact surface (23) of the carrier element (17). becomes.