EP2483576A1

EP2483576A1 - Arrangement of a gear and a coupling element for transmitting a rotational motion

Info

Publication number: EP2483576A1
Application number: EP10724309A
Authority: EP
Inventors: Andreas Zeller; Wolfgang Schiemenz; Rolf Schwarze
Original assignee: GKN Sinter Metals Holding GmbH
Current assignee: GKN Sinter Metals Holding GmbH
Priority date: 2009-09-29
Filing date: 2010-06-09
Publication date: 2012-08-08
Also published as: US20120210813A1; WO2011038790A1; IN2012DN03048A; DE102009043367A1; JP2013506101A; CN102648364A

Abstract

The invention relates to an arrangement (2), comprising: a gear (4) and a coupling element (6), which is connected to the gear (4) in a form-fitted manner in order to transmit a rotational motion. The gear (4) and the coupling element (6) each have a geometry G_z, G_κ on end faces (16, 28) facing each other, the geometry forming a form-fitted connection in connection with the geometry of the other element. The gear (4) and the coupling element (6) are designed as components produced by sintering, into which components the respective end-face geometries G_z, G_κ are impressed, by means of which end-face geometries the gear (4) and the coupling element (6) are positioned relative to each other.

Description

Arrangement of a gear and a coupling body for transmitting a rotary movement

The invention relates to an arrangement of a gear and a coupling body for transmitting a rotational movement and an associated torque, wherein the arrangement is used in particular in a manual transmission for a vehicle. The vehicle may be a land vehicle, aircraft, watercraft or a combination thereof. Such arrangements are carried out according to the prior art, in particular in the field of vehicle gearboxes, preferably in the form of a positive connection, wherein a coupling body may have a recess with a circumferential internal toothing, in which a bush-shaped portion or collar portion of a gear or gear wheel with a circumferential outer toothing can be used. In this case, these two mating bodies may additionally or alternatively also be welded together, for example by means of a selectively used fusion welding process or an at least partially continuous welding, for example in a circumferential direction of the arrangement, to prevent a relative movement between these two mating bodies. These two mating bodies and their respective form-fitting connection forming geometries are made as such by a machining of one blank each. For welding, the two mating bodies must be machined to ensure accurate positioning. In the aforementioned embodiment, therefore, the external toothing of the toothed wheel and the internal toothing of the coupling body would have to be machined.

Furthermore, these two mating bodies are also hardened. The curing can be done on the individual parts or in the assembled state of the items. The hardening itself also leads to unwanted dimensional distortion, which must be eliminated in the course of a span-removing post-processing in order to ensure the most accurate positioning.

In order for these two mating bodies to act centering one another and thereby ensure a correspondingly high positional accuracy, one also requires one Spanendenbeziehungsweise post-processing of the form-fitting forming associated geometries or elements.

The invention has for its object to simplify the manufacture of such arrangements and to improve. In addition, the object is a method and a. Use to provide a tailor-made production of parts to be joined, which are subjected to a torque.

This object is achieved with an arrangement having the features of claim 1. The features specified in the dependent claims are the subject of preferred embodiments and developments of the solution. In the following description further advantageous features are given, which may be the subject of further refinements and developments of the solution. These further features can be combined with one another and / or with the features of the claim form.

It is proposed an arrangement of a gear and a coupling body, wherein the coupling body is positively connected to the gear for transmitting a rotational movement. The toothed wheel and the coupling body each have a geometry on mutually facing end faces which, in conjunction with the geometry of the respective other body, form a positive connection, in particular a plug connection. In this case, a positive connection can be designated as a plug connection, which is formed from at least one depression contained in a first joining part and at least one elevation complementary to the depression which is contained in a second joining part. In this case, the gear and the coupling body are formed as sintered components, in which the respective end-face geometries are formed and / or pressed, through which the gear and the coupling body are mutually positionable. In a sintering production of these two mating bodies, in each case a pulverulent material is pressed into a compact to be sintered, also called a green compact. During sintering, the compact then obtains its final strength by virtue of the compressed powdery substance or compact or green compact forming a coherent crystal when passing through a sintering furnace by means of diffusion and recrystallization processes forms. The process of sintering is well known and will not be discussed here. The sintered materials used are preferably, but not exclusively, metallic materials. Particularly preferred materials are iron-based alloys. As metallic materials, the materials can be used, which have sufficient strength. Preference is given to the use of materials which are customary as gearwheels and in this sense enable safe torque transmission by means of the arrangement in a transmission.

An advantage of this proposed arrangement is that the front-side geometries forming the form-fit require no subsequent machining. This circumstance advantageously saves time and money. This circumstance also advantageously requires a simplification of a production of the two mating bodies. In addition, these geometries are advantageously coordinated with each other so that a corresponding caused by a hardening unwanted dimensional distortion of the geometries during sintering production can be kept, so that eliminates the reworking of the geometries as an advantage. Another advantage of the frontal geometries is that they give considerable freedom in terms of a geometric design. It should be noted that the term "positive connection" was chosen because any kind of form-fitting connection between the joining partners is possible. Important for the design of the positive connection here is that by means of the positive connection, a transmission of torque allows and / or supported. In one exemplary embodiment, a gearwheel and a clutch body in a transmission serve as joining partners. It is conceivable here that the components to be joined by means of the positive connection are available such that their central axes fall into each other, so that solely due to the positive connection, a force and / or moment transfer is possible. In a preferred embodiment, these geometries of the two mating bodies each have an orientation on at least one associated longitudinal axis, so that the mating bodies advantageously center each other. As a longitudinal axis in this case, for example, a central axis or a center line or in the case of rotationally symmetrical parts, a symmetry and / or central axis can be labeled. Preference is given to ing components used in the transmission rotationally symmetric components. In addition, the gear and the coupling body may be arranged coaxially with each other and form at least one common longitudinal axis, wherein their longitudinal axes coincide with each other, so that a common center of rotation or a common axis of rotation is formed by the longitudinal axis. This common longitudinal axis can be, for example, at least the central axis of the proposed arrangement.

In a further preferred embodiment, the geometries forming a plug connection are configured such that preferably at least the geometry of the toothed wheel is provided with a multiplicity of depressions into which a projection or an increase in the geometry of the coupling body respectively engages. Alternatively or additionally, also the coupling body may be provided with a plurality of depressions, in each of which engages a complementarily formed projection of the gear. The connector is preferably formed in a preferred embodiment in the form of a spline, wherein preferably the gear on a front side preferably in a region between a root diameter and a bush-shaped portion has a plurality of recesses in the circumferential direction, which are spaced by individual web portions of each other , wherein the individual web portions preferably extend from a circumferential projection to the sleeve-shaped portion. The web sections are preferably evenly spaced from each other. On the other hand, the coupling body has, on a front side associated with the toothed wheel, a multiplicity of toothed elements which are arranged in the circumferential direction and extend in each case from the end face into one of the recesses of the toothed wheel. These tooth elements correspond in their geometric configuration to the recesses of the coupling body, so that the gear and the coupling body are available without backlash. These recesses are aligned with a gear axis associated with the longitudinal axis, whereas the toothed elements are aligned with a coupling body associated longitudinal axis, so that the gear and the coupling body with each other advantageously centering effect.

Alternatively or additionally, the coupling body may be provided with a plurality of depressions, for example in an analogous manner in the circumferential direction, in the depending engages a correspondingly formed tooth and / or a differently shaped projection of the gear.

In a further preferred embodiment, the gear and the coupling body are additionally bonded cohesively. The cohesive connection is formed at least selectively. Such a punctual cohesive connection has the advantage that its underlying effort for their production is minimal. In addition, a punctual cohesive connection such as a selective fusion welding method offers the advantage of minimal heat input into the components to be joined. Alternatively or additionally, the cohesive connection can also be designed to be continuous at least in regions, for example in the circumferential direction. For cohesive connection while the gear can be welded to the coupling body and / or soldered and / or glued. According to a further preferred embodiment, the gear and the coupling body are additionally caulked against each other, so that a relative movement, preferably in the longitudinal direction of the two mating body between the gear and the coupling body advantageously omitted. Calking offers the advantage of a safe torque transmission, since the mating body or joining parts are permanently connected to each other.

Preferably, the sleeve-shaped portion or collar portion of the gear protrudes through a corresponding recess of the coupling body through, wherein the sleeve-shaped portion at the end caulked at least selectively for the purpose of caulking, preferably rolled ein.Ein conditional bead ensures a physical connection between the gear and the coupling body, wherein the connection allows positioning of the gear relative to the coupling body in the longitudinal direction of the arrangement. It is further proposed a use of an arrangement of a gear and a coupling body of the type described above for a manual transmission of a vehicle, wherein the vehicle may be formed as a land vehicle, aircraft, watercraft or a combination thereof. Here, the manual transmission as a conventional manual transmission or preferably be designed as an automated transmission.

In the following, embodiments of the invention will be explained in detail with reference to the drawings. The resulting from the drawings and the accompanying descriptions features are not limited to the respective embodiments. Nor are these features to be construed restrictively. Rather, these features are illustrative of an exemplary implementation. In addition, the individual features with regard to possible further refinements and developments of the solution with each other and with the features of the above description can be combined, these further embodiments and further developments are not shown in detail. 1 shows a three-dimensional view of a proposed arrangement of a toothed wheel and a coupling body and a cross-sectional representation of the arrangement along a section line B-B,

Fig. 2 is a two-dimensional view of the gear shown in Fig. 1 and a cross-sectional view of the gear along a section line C-C;

3 shows a two-dimensional representation of the coupling body shown in FIG. 1 and a cross-sectional view of the coupling body along the section line D-D, FIG.

4 shows the gear in a three-dimensional representation, in a view showing the side to be joined with the coupling body,

5 shows the coupling body in a three-dimensional representation, in a view showing the side to be joined with the gear,

Fig. 6 shows the coupling body in a three-dimensional view, in a view showing the side facing away from the gear

7 shows a further embodiment of a coupling body in a three-dimensional representation in a view showing the side to be joined with the gear,

7 shows the coupling body according to FIG. 7 in a three-dimensional representation in a view showing the side facing away from the gear, and FIG Fig. 9 is a gear in a three-dimensional view in a view showing the with the coupling body according to FIGS. 7 and 8 to be joined side.

The same reference numerals refer to the same or similar components below.

The arrangement 1 shown in FIG. 1 comprises a gear 2 as a spur gear with a preferred helical gearing and a coupling body 3, which is positively connected to the gear 2 for transmitting a rotary motion and thereby forms a plug connection. The plug connection is preferably designed in the form of a plug-in toothing. The gear 2 and the coupling body 3 in this case have on facing end faces 4, 5 each have a geometry G _z , G _K (see Fig. 2 and 3), which in conjunction with the geometry G _z , G _K of the other body. 2 , 3 forms the spline. The gear 2 and the coupling body 3 are formed as sintered and each preferably one-piece components 2, 3, in which the respective end-face geometries G _z , G _{K are} pressed and / or molded, through which the gear 2 and the coupling body 3 to each other are positionable. Alternatively, the gearwheel 2 and the coupling body 3 can also each be a component joined together at least in two parts. The training as a sintered component justified a significant improvement over the aforementioned prior art, which is due to the fact that a machining for the production of the splines forming geometries G _z , G _K advantageously eliminated.

In a sintering production of the two mating bodies 2, 3, in each case a pulverulent material is pressed into a compact to be sintered, also called a green compact. During sintering, the compact then obtains its final strength, in that the compressed powdery substance or compact or green body forms a coherent crystal structure when passing through a sintering furnace through primarily diffusion, but also recrystallization processes. In addition to a conventional sintering technique, said sintering production should also be understood as meaning sintering forging technology which is intended to represent a subordinate idea to conventional sintering technology in order to provide sintered components 2, 3 with a higher density and strength. Fig. 2 shows a view of a gear 2 and a section through the gear 2 along the line CC. The top view in FIG. 2 shows a view of the gear wheel 2, which shows the face 4 to be joined with the coupling body 3. Preferably, the gear wheel 2 has at an end face 4 in a region between preferably a root diameter D _F K (see FIG. 9) and a bush-shaped section or collar section 6 a plurality of depressions 7 in the circumferential direction, which are separated by individual web sections 8 are spaced. These individual web portions 8 are preferably evenly spaced from each other and preferably extend from a circumferential projection 9 to the sleeve-shaped portion 6, wherein the circumferential projection 9 is located on a diameter which is greater than an outer diameter of the collar portion 6 and smaller as the root diameter D _{FK of} the gear 2.

Fig. 3 shows a view of a preferred embodiment of the coupling body 3 and a section through the coupling body 3 along the line D-D. The upper illustration in FIG. 3 shows a view of the coupling body 3, which shows the face 5 to be joined with the gear 2. The coupling body 3, however, preferably has on a gear 2 associated end face 5 a plurality of tooth elements 10 which are arranged in the circumferential direction and each extending from the end face 5 into one of the recesses 7, to which they correspond in their geometric configuration. In this case, the recesses 7 are preferably aligned with a gearwheel 2 associated longitudinal axis 11, whereas the toothed elements 10 are preferably aligned with the coupling body 3 associated longitudinal axis 12. Both in the longitudinal axis 11 and in the longitudinal axis 12 are each an associated central axis, these two central axes 11, 12 are preferably arranged coaxially to one another and thereby form a common longitudinal axis 13 of the assembly 1.

In addition to this positive connection, the toothed wheel 2 and the coupling body 3 can also be connected to one another in a material-locking manner by the toothed wheel 2 being welded to the coupling body 3 and / or soldered and / or glued, in order to produce a relative movement between the two mating bodies 2, 3 to prevent. In this case, the cohesive connection is preferably formed at least selectively. additionally or alternatively, such a cohesive connection may also be formed at least in regions continuously, for example in the circumferential direction.

Furthermore, as an alternative or in addition to the cohesive connection, the toothed wheel 2 and the coupling body 3 can also be caulked against one another. In this case, the bushing-shaped section 6 of the toothed wheel 2 preferably protrudes through a corresponding recess 14 of the coupling body 3, wherein the bush-shaped section 6 is at least punctually rolled, so that a bead produced by a plastic deformation of the bush-shaped section 6 forms a physical connection between the toothed wheel 2 and ensures the coupling body 3, which prevents a relative movement between the two joining parts 2, 3.

This proposed arrangement 1 is preferably used as part of a so-called locking and synchronization device in a manual transmission for a vehicle use, with the locking and synchronization device a gear can be easily and silently switched, provided a shift sleeve and the coupling body 3, the form-fitting cooperates with the shift sleeve over its toothing or gear teeth 15 to the circuit of a corresponding gear, have an equal speed. In the formed in the coupling body 3 preferably rectangular recesses 16, which are preferably uniformly spaced in the circumferential direction of the coupling body 3, engages a so-called intermediate synchronizing ring. This intermediate synchronizing ring comprises a number of recesses 16 corresponding number of so-called foot plates, which engage in the recesses 16. A basic structure and a basic mode of operation of such a blocking and synchronization device is evident from the literature. In this context, reference may be made, for example, to the technical textbook for automotive engineering of the European textbook series (25th edition) (see page 372) or to the motor vehicle technical handbook by Bosch (23rd edition), their respective descriptions of the locking and synchronization device hereby made the disclosure of the invention. The manual transmission may preferably also be an automated manual transmission.

4, a three-dimensional representation of a gear 2 is shown. The gear has a bore 17 through which the gear 2 on a shaft or axle se is positionable. On the outer circumference, the gear 2 has a toothing 18 in the form of a helical gear with a helical toothing. About the teeth 18 is a torque or a force absorbable or transferable. The gear 2 is formed in the illustrated embodiment as a one-piece sintered part. The sintered part 2 is thereby formed so accurately during production, pressed and sintered that can be dispensed with a post-processing or post-processing is at least minimized.

As a means for axial power transmission 2 recesses 7 are formed in the gear, which correspond in shape to a negative form of tooth elements. The recesses 7 are circumferentially introduced at the collar portion 6 on a uniform diameter in the gear 2. The recesses 7 are part of the positive connection for transmitting a torque of the arrangement of coupling body 3 and gear 2. The indentations 8 in the gear 2 form recesses 7 in the end face 4. The collar portion 6 has an outer diameter D _A , with the recess 14 corresponds in the coupling body 3, wherein the gutter 6 can be inserted into the recess 14. When joining the gear 2 and the coupling body 3, the recess 14 is pushed over the gutter 6. The displacement takes place until the tooth elements 10 come to rest in the depressions 7. By the concerns of the tooth elements 10 in the recesses 7 of the gear 2, a positive connection for transmitting a torque is produced. For example, if a torque is introduced into the toothed wheel 2 via the helical toothing 18 and the coupling body 3 sits positively on the toothed wheel 2, then the torque can be dissipated by means of the toothed toothing 15. FIG. 6 shows the coupling body 3 in a three-dimensional view and in a view showing the side 19 facing away from the gear 2. By sliding the coupling body 3 on the gutter 6 and joining the tooth elements 10 in the recesses 7, the gear 2 and the coupling body 3 are aligned such that the central axes 11, 12 of the gear 2 and the coupling body 3 fall into each other and form a central axis 13 of the arrangement 1.

FIG. 7 shows a further embodiment of the invention and in particular another geometry G "of a coupling body 20. The view shows a three-dimensional representation in a view that the to be joined with the gear 21 end face 22nd shows. The coupling body 20 is identical except for the formation of the geometry G _K to the coupling body 3. The elevations 23 on the end face 22 of the coupling body 20 form in contrast to the coupling body 3 is not a tooth shape, but are undulating. The elevations 23 are arranged on an identical diameter and regularly around the recess 24 on the coupling body 20. The elevations 23 project out of the end face 22 and are spaced apart by webs 24, wherein the webs 24 lie in a plane to the end face 22. The ridges 23 may have a width B that is uniform from the inner diameter Di to an outer diameter. In this exemplary embodiment according to FIG. 7, the elevations 23 are formed cubically. Conical here means that the width B increases, starting from an inner diameter Di to the outer gear teeth 15 out. The conical broadening of the elevations 23 is characterized by the conical lines 26 on the undulating elevations 23. FIG. 8 shows a three-dimensional view of the coupling body 20 according to FIG. 7 in a view showing the end face 27 facing away from the tooth rim. To the coupling body 20, a gutter 28 is also formed. The coupling body 20 is integrally formed in this embodiment. However, it is also conceivable according to the invention to design the coupling body 20 as well as the associated toothed wheel 21 in multiple parts. The gutter 28 serves to further stabilize the positive connection between the coupling body 20 and gear 21st

FIG. 9 shows a three-dimensional view of an alternative embodiment of a toothed wheel 21. The gear 21 has circumferentially a toothing 29, which is formed as a helical toothing in involute. The gutter 30 protrudes beyond the toothing 29 and forms a guide for the recess 24 of the coupling body 20. At the outer diameter D _{A of} the gutter 30 recesses 31 are introduced, which are formed as complementary recesses 31 to the elevations 23, that is, the Ridges 23 cooperate with the recesses 31 in such a way that the ridges 23 interlock positively on the circumference. The recesses 31 extend here from the outer diameter D _{A of} the gutter 30 to a diameter D _{v of} the recesses 31, wherein the diameter D _{v of} the recesses 31 is always smaller than the diameter D _F «of the root circle of the toothing 29 of the gear 21st The depressions 31 lie in an end face 32 of the toothed wheel 21 and are from a diameter D _A to a diameter D _v , wherein the diameter D _{v of} the recesses 31 is greater than the diameter D _{A of} the guide bush 30 and smaller than the diameter D _{FK of} the root circle of the toothing 29. After joining the Gear 2, 21 with a coupling body 3, 20 results in a relative position of the joined components 2, 3, 20, 21, as shown by way of example in FIG. After joining, the components 2, 3, 20, 21 can be materially or mechanically connected. In the case of a cohesive connection, for example, a welding of the components 2, 3, 20, 21 in the region 33, shown in Fig. 1, take place. In the area 33 but would also be caulking of the components 2, 3, 20, 21 and in particular the collar webs 6, 28, 30 possible. Calking and / or cohesive bonding increases safety in transmitting a force or torque.

As shown, the geometric configuration of the positive connection between see the gear 2, 21 and the coupling body 3, 20 is not fixed. Thus, it is conceivable to form geometric shapes between the gear 2, 21 and the coupling body 3, 20, which cooperate and can have any shape. For example, it is conceivable that the elevations 10, 23 and / or depressions 7, 31 are trapezoidal, tooth-shaped, curved, sinusoidal, wavy in the gear 2, 21 and / or coupling body 3, 20. It is of course also conceivable that the elevations 10, 23 and recesses 7, 31 in the gear 2, 21 and / or coupling body 3, 20 are formed alternately, that is in the gear 2, 21 and / or coupling body 3, 20 are consecutively increases 10, 23 and recesses 7, 31 formed. Also conceivable is an asymmetrical arrangement of elevations 10, 23 and / or depressions 7, 31 on the circumference of the toothed wheel 2, 21 and / or coupling body 3, 20. It is also conceivable for the elevations 10, 23 and / or depressions 7, 31 in the gear 2, 21 and / or coupling body 3, 21 for producing a positive connection with the gutter 6, 28, 30 of the gear 2, 21 and the recess in the coupling body 3, 20 cooperate. The positive connection is then formed by a combination of fit between the recess on the coupling body 3, 20 and gutter of the gear 2, 21 and the elevations 10, 23 and / or recesses 7, 31 in the gear 2, 21 and / or coupling body 3, 20 ,

Claims

claims:

1. Arrangement (1) comprising a gear (2, 21) and a coupling body (3, 20) which is positively connected to the gear (2, 21) for transmitting a rotational movement, characterized in that the gear (2, 21 ) and the coupling body (3, 20) on mutually facing end faces (4, 5, 27, 32) each have a geometry (G _z , G _K ) which in conjunction with the geometry of the respective other component (2, 3, 20 , 21) forms a positive connection, wherein the toothed wheel (2, 21) and the coupling body (3, 20) is in each case designed as a sintered component and, wherein in the gear (2, 21) and the coupling body (3, 20) the respective end-face geometry (G _z , G ") is pressed, by which the gear (2, 21) and the coupling body (3, 20) are mutually positionable.

2. Arrangement (1) according to claim 1, characterized in that the geometries (G _z , G _K ) each have an orientation on at least one associated longitudinal axis (11, 12).

3. Arrangement (1) according to claim 1 or 2, characterized in that the gear (2, 21) and the coupling body (3, 20) are arranged coaxially to each other and form at least one common longitudinal axis (13).

4. Arrangement (1) according to one of claims 1 to 3, characterized in that the plug-in connection forming geometries (G _z , G _K ) are designed such that preferably at least the geometry (G _z ) of the gear (2, 21) is provided with a plurality of depressions, in each of which a projection of the geometry (G _K ) of the coupling body (3, 20) engages.

5. Arrangement (1) according to claim 4, characterized in that the plug-in connection is designed in the form of a spline, wherein the gear (2, 21) on an end face (4, 32) in a region between a Fußkreisdurchmesser (D _FK ) and a bush-shaped section (6, 30) has a plurality of recesses (7, 31) in the circumferential direction, which are spaced from each other by individual web sections (8), wherein the individual web sections te (8) extending from a diameter (D _v ) of the recesses (7, 31) to a diameter (D _A ) of the bush-shaped portion (18), and wherein the coupling body (3, 20) on a the gear (2, 21) associated with the end face (19, 22) has a plurality of elevations (10, 23) which are arranged in the circumferential direction and each extend from the end face (19, 22) into one of the recesses (6, 30), wherein the Recesses (6, 30) on a gear (2, 21) associated longitudinal axis (1 1) are aligned, whereas the number elements (10, 23) on a coupling body (3, 20) associated longitudinal axis (12) are aligned.

Arrangement (1) according to claim 5, characterized in that the web portions (8) are evenly spaced from each other.

Arrangement (1) according to one of claims 1 to 6, characterized in that the gear (2, 21) and the coupling body (3, 20) are materially interconnected.

8. Arrangement (1) according to claim 7, characterized in that the cohesive connection is at least selectively formed.

9. Arrangement (1) according to claim 8, characterized in that the cohesive connection is formed pointwise and / or continuously in the circumferential direction.

10. Arrangement (1) according to one of claims 7 to 9, characterized in that the gear (2, 21) to the coupling body (3, 20) welded and / or soldered and / or glued.

11. Arrangement (1) according to one of claims 1 to 10, characterized in that the gear (2, 21) and the coupling body (3, 20) are caulked against each other.

12. Arrangement (1) according to claim 1 1, characterized in that the bush-shaped portion (6, 30) of the toothed wheel (2, 21) by a corresponding recess (14, 24) of the coupling body (3, 20) protrudes, the sleeve-shaped portion (6, 30) is at least partially rolled on the front side, so that a conditional bead ensures a physical connection between the gear (2, 21) and the coupling body (3, 20).

13. A method for producing an arrangement (1) comprising a gear (2, 21) and a coupling body (3, 20), wherein the coupling body (3, 20) with the gear (2, 21) for transmitting a rotational movement positively connected is characterized in that the gear (2, 21) and the coupling body (3, 20) as sintered components produced by means of mutually facing end faces (4, 5, 27, 32) formed geometries form-fit, wherein in the Gear (2, 21) and the coupling body (3, 20) in an upstream process step, the respective end face geometry (G _z , G _K ) is pressed, so that the gear (2, 21) and the coupling body (3, 20 ) are positionable to each other.

14. The method according to claim 13, characterized in that the gear (2, 21) and the coupling body (3, 20) are inseparably connected after the joining. Use of an arrangement (1) of a gear (2, 21) and a coupling body (3, 20) according to one of claims 1 to 12 for a manual transmission of a vehicle, the vehicle being designed as a land vehicle, aircraft, watercraft or a combination thereof is. Use according to claim 15, characterized in that the manual transmission is designed as an automated transmission.