CN111828490A

CN111828490A - Plug toothing with a round or annular spring element

Info

Publication number: CN111828490A
Application number: CN202010300072.3A
Authority: CN
Inventors: N-T.阮; M.舒尔茨
Original assignee: Robert Bosch GmbH
Current assignee: Robert Bosch GmbH
Priority date: 2019-04-17
Filing date: 2020-04-16
Publication date: 2020-10-27
Also published as: DE102019205567A1; FR3095250A1; FR3095250B1

Abstract

The invention relates to a shaft connection (40) between a first shaft (12) having a first toothing (14) and a second shaft (22) having a second toothing (16). At least one spring element (42, 44, 80, 86, 88) in the form of a ring or a pin, which centers the first shaft (12) relative to the second shaft (22) or, conversely, the second shaft (22) relative to the first shaft (12), is accommodated on the first shaft (12). The invention further relates to a shaft-hub connection (76) between a shaft (72) having a gearing (84, 92) and a hub (74) having a groove (82) in the circumferential direction. The gearing (84, 92) is either wound by annular spring elements (42, 44, 86) or is provided with pin-shaped spring elements (80, 88) which support the gearing (84, 92) in the circumferential direction in a groove (82) of the hub (74).

Description

Plug toothing with a round or annular spring element

Technical Field

The invention relates to a plug toothing having a spring element of circular or annular design for centering and damping a force transmission via the plug toothing. The invention further relates to the use of the plug toothing for transmitting torque.

Background

In order to transmit or conduct the torque transmitted by the shaft through the gear, a good shaft-hub-connection is required. The possibility of connecting the shaft-hub connection is provided by the plug teeth with play. Such a standardized, positive-locking shaft-hub connection in the form of a plug-tooth system with play has the disadvantage of an undefined play and a defective centering. This results in tooth flank impact or tooth flank misalignment when torque is transmitted through the gear. This results in undesirable noise and an asymmetrical load pattern (trackbild) of the teeth and a punctiform transmission of the rotational load. As a further disadvantage, in such a plug toothing, an increase in the bearing load of approximately 25% is to be mentioned, and in addition, a significantly increased power loss and thus a reduced life expectancy of the participating force transmission elements and the bearing are to be mentioned.

DE 102015200661 a1 relates to a clutch device with an electromagnetic actuator. The clutch device comprises a rotatably driven transmission mechanism having at least one sleeve-type attachment for rotatable mounting in a stationary housing. Furthermore, an output part is provided which is rotatably arranged in the gear housing, and a clutch is also provided which is arranged in the power path between the gear housing and the output part. The clutch has a first clutch part, which is held in a rotationally fixed and axially movable manner relative to the gear mechanism housing, and a second clutch part, which is fixedly connected to the output part and is arranged in the gear mechanism housing. A controllable actuator is used for actuating the clutch in such a way that the first clutch part and the second clutch part can be selectively connected to each other for torque transmission. The actuator has an annular electromagnet arranged coaxially with the sleeve-like attachment of the gear housing, which electromagnet has a magnet housing and an axially movable piston.

DE 102015200465 a1 relates to a differential device for a vehicle. The differential device includes a first housing section, wherein the first housing section is configured to support the sun gear and/or the differential device on a surrounding structure. Furthermore, a second housing section is provided, in addition a drive wheel section and a fastening part are provided, wherein the fastening part, the second housing section and the drive wheel section are connected to one another by a screw connection and form a screwed assembly. The screwed assembly forms a form-fitting receptacle, wherein the first housing section is received in the form-fitting receptacle.

DE 102012213405 a1 relates to a bevel gear differential for a vehicle. The bevel gear differential comprises an outer wheel with a differential carrier, wherein the differential carrier is fixedly connected to the outer wheel via at least one connecting region. The differential carrier has at least one web region on which a compensating wheel is arranged, wherein the axis of rotation of the compensating wheel defines a compensating axis direction in an axial plan view of the bevel gear differential. In an axial plan view, a compensation angle range of at least +/-20 ° about the compensation axis is left free (freestellen) by at least one connecting region.

Disclosure of Invention

According to the invention, a shaft connection between a first shaft with a first toothing and a second shaft with a second toothing is proposed, wherein at least one spring element in the form of a ring or a pin is accommodated on the first shaft, which spring element centers the first shaft relative to the second shaft or vice versa.

Furthermore, according to the invention, a shaft-hub connection is proposed between a first shaft having a gearing and a hub having a groove in the circumferential direction, wherein the gearing is either wound by an annular spring element or is alternatively provided with a pin-shaped spring element which supports the gearing in the groove of the hub in the circumferential direction.

In an advantageous manner, both embodiments of the solution proposed according to the invention make it possible to realize such shaft connections, in particular plug-tooth connections and shaft-hub connections, in such a way that the occurrence of tooth flank impacts is significantly reduced as a result of the centering guidance. By appropriate dimensioning of both the annularly configured spring element and the pin-shaped spring element, an optimization with respect to load and assembly force can be achieved in dependence on the individual load situation.

In both variants of the solution proposed according to the invention, the shaft connection or the shaft/hub connection can be designed in such a way that the spring element is designed as a wound-up spring ring in which the spring ring start and the spring ring end are coupled to one another at the coupling point. This embodiment variant of the spring element is characterized by the possibility of any desired dimensioning, which allows particularly simple production.

In a further development of the solution proposed according to the invention, the spring element can be designed as a rolled-up spring ring made of spring wire having a diameter in the range between 0.2mm and 0.5 mm and having a spring diameter of between 1.2 mm and 5 mm. The spring element as a wound-up spring ring is preferably made of spring steel wire, stainless steel spring steel wire or from the material EN 10270-3-14310.

In a further development of the solution proposed according to the invention, the spring element can alternatively be produced as a stamped spring ring from a spring steel sheet. When the spring element is produced as a stamped spring ring, the first cross section and the second cross section are formed in the spring element in an alternating sequence, as viewed in the circumferential direction. After the spring element has been stamped out of the spring steel sheet, the resulting stamped spring steel sheet is bent, so that an annular hollow body is formed, on which the first and second cross sections extend in alternating sequence in the circumferential direction. In the shaft connection or shaft/hub connection proposed according to the invention, longitudinal grooves for receiving pin-shaped spring elements in the form of helical springs (Wurmfeder) or clamping pins can be formed on the gearing teeth in the root region.

In order to impart elasticity to the inserted pin-shaped spring element, which is designed as a clamping pin, the clamping pin is provided with longitudinal slits on its circumference, which serve to ensure the spring action.

In the shaft connection proposed according to the invention or in the shaft-hub connection, the spring element on the first shaft or on the second shaft, which are centered relative to one another at the shaft connection, can be accommodated in a groove which extends in the circumferential direction on the first shaft or on the second shaft.

In an advantageous embodiment of the shaft connection according to the invention or of the shaft-hub connection according to the invention, the longitudinal grooves can be formed in the root regions of both flanks of the gearing. In this case, it is advantageously possible to center the assembly of the shaft-hub connection on the shaft-hub connection between the shaft on which the transmission teeth are accommodated with the pin-shaped spring element introduced into the longitudinal groove and the hub having the groove in the circumferential direction without play, wherein there is no play both in the first rotational direction and in the second rotational direction opposite thereto.

The invention further relates to the use of the shaft connection as a plug-in toothing of two shafts in a transmission of an E-shaft module of an electrically driven vehicle. The invention further relates to the use of the shaft-hub connection between the shaft and the hub in an E-shaft module of an electrically driven vehicle. The invention further relates to the use of a shaft connection or an identical hub connection in a drive train of a vehicle driven by an internal combustion engine, a Hybrid Electric Vehicle (HEV) or a plug-in hybrid electric vehicle (PHEV).

The advantage of the centered, play-free shaft connection, which is preferably designed as a plug toothing, and of the centered, play-free shaft/hub connection, which is proposed according to the invention, lies in the improved load-bearing diagram of the toothing with respect to the plug toothing and with respect to the play-free capability achievable with the solution proposed according to the invention, which applies both to the shaft connection and to the play-free, non-centered shaft/hub connection. The inserted spring elements of annular and pin-shaped design serve as dampers and can be assembled with relatively low assembly and disassembly forces. The transmission power losses can be reduced and imbalances avoided by using spring elements of annular or pin-shaped configuration. In addition, transmission shocks can be eliminated and the operational stability of the respective shaft connection, in particular of the plug toothing, and of the shaft-hub connection can be significantly improved, resulting in a low-noise operation. By reducing the vibrations and correcting the load map, a significantly longer service life duration is expected. Furthermore, the solution proposed according to the invention provides a very economical solution by using spring wire for producing a helical spring or a resting spring (simmering retainer) or a spring ring as a stamped and bent piece made of spring steel sheet.

By selecting the respective spring material, whether it be a spring steel plate or a spring wire, and the variability of the diameter of the spring wire, which may vary between 0.2mm and 5 mm, and the spring diameter being in the range of 1.2 mm to 5 mm, optimization of the load and assembly forces in terms of the spring element may be achieved. By means of the materials used, the spring steel plates and the wound spring wire can be used in a wide variety of possible applications in terms of the geometric and dimensional design of the spring element.

Drawings

Embodiments of the invention are further elucidated with the aid of the drawings and the following description. In which is shown:

figure 1 shows the occurring oblique position of the plug-tooth connection and the two shafts relative to each other without a centering device,

figure 2 shows a first embodiment variant of the shaft connection proposed according to the invention,

figure 3 shows a spring element configured as a ring spring,

figure 3.1 shows the coupling between the beginning of the spring ring and the end of the spring ring of the ring spring,

figure 3.2 shows the stretched arrangement of the coiled spring wire,

figure 3.3 shows an enlarged view of the beginning and end of the annular spring,

figure 3.4 shows a schematic view of a ring spring,

figure 4 shows a top view of a spring element stamped from a spring steel sheet,

figure 4.1 shows an enlarged view of a part according to figure 4,

figure 4.2 shows a first cross-section,

FIG. 4.3 shows a second cross section

Figure 5 shows a representation of the shaft-hub connection between a shaft with gearing teeth and a hub designed as a gear,

figure 5.1 shows a perspective view of the placement of the helical spring,

figure 5.2 shows a perspective view of a shaft with gearing teeth each with a wound helical spring,

fig. 6 shows a schematic representation of the forces occurring on the gear teeth, which engage in the groove in the circumferential direction of the hub,

figure 7 shows an enlarged view of the shaft end with the gearing teeth and the longitudinal groove for receiving the clamping pin,

FIG. 8 shows a representation of a clamping pin with a longitudinal slit, and

fig. 9 shows an enlarged plan view of the end face of the shaft end according to fig. 7.

Detailed Description

In the following description of embodiments of the invention, identical or similar elements are denoted by identical reference numerals, wherein the description of these elements is not repeated in individual cases. The figures only schematically show the subject matter of the invention.

Fig. 1 shows a shaft connection configured as a plug tooth connection with play. According to fig. 1, the first shaft 12 is provided with a first toothing 14 configured as an external toothing. On the second shaft 22, which is designed as a hollow shaft, there is a second toothing 16, which is designed here as an internal toothing. A gear 18 is received on the first shaft 12, while a rotor 20 is provided on the second shaft 22. The plug toothing 10 with play is supported in the triple bearing 24. The axis of symmetry is provided with reference numeral 26. Reference numeral 28 denotes the inclined position of the first shaft 12 relative to the second shaft 22, which occurs as a result of the play of the plug teeth 10 shown in fig. 1. The inclined position 28 means the occurrence of vibrations, an inclined bearing pattern with respect to the tooth flanks of the teeth of the first tooth system 14 and of the second tooth system 16, and leads to increased noise generation during the service life, which is detrimental to the service life of the plug tooth system 10 shown with play. For a good arrangement, it is mentioned that the triple bearing arrangement 24 comprises a first bearing 30, a second bearing 32 and a third bearing 34, which are all designed as ball bearings.

In contrast, fig. 2 shows a variant embodiment of the centered, play-free shaft connection 40 proposed according to the invention.

As can be seen from fig. 2, a first spring element 42 is accommodated on the circumference of the first shaft 12 and a second spring element 44 is accommodated at a distance from the first spring element. The two spring elements 42, 44 are each designed as a spring ring 46. The two spring elements 42, 44, which are designed in an annular manner as spring rings 46, are dimensioned such that their outer circumference presses against the tip circle of the second toothing 16, i.e. against the second shaft 22, i.e. the tip circle of the internal toothing on the hollow shaft, and thus centers the latter relative to the first shaft 12. Furthermore, the spring elements 42, 44, which are accommodated at a distance from one another in circumferential grooves on the first shaft 12, press a play out of the shaft connection 40, as a result of which the running stability and the load profile between the teeth of the first toothing 14 and the teeth of the second toothing 16 are significantly improved. As can be seen from the illustration according to fig. 2, a first spring element 42, which is embodied as a spring ring 46, and a second spring element 44, which is likewise embodied as a spring ring 46, are located next to the first toothing 14 of the first shaft 12. Thus, the two spring elements 42, 44, which are designed as spring rings 46, are positioned such that they lie alongside the tooth flank contact between the first tooth 14 and the second tooth 16.

As can be seen from fig. 3, a spring ring 46 is accommodated on the circumference of the first shaft 12. The spring ring 46 is designed as a helical spring; the spring ring start 48 and the spring ring end 50 (see the illustration according to fig. 3.1) are coupled to one another at a coupling point 52.

In the illustration according to fig. 3.1, the spring ring 46 is shown in a curved geometry, whereas in fig. 3.2 the spring ring start 48 and the spring ring end 50 are in a stretched position. As can be seen from the illustration according to fig. 3.1, the spring ring start 48 is inserted into the spring ring end 50 and a coupling point 52 between the spring ring start 48 and the spring ring end 50 is obtained thereby.

As can be seen from fig. 3.3, the spring ring 46 is made of a coiled spring wire. The spring wire, which may be referred to as a stainless steel spring wire or a material called EN 10270-3-14310, has a wire diameter 54 in the order of between 0.2mm and 0.5 mm. The spring diameter 56 is in the order of between 1.2 mm and 5 mm. Depending on the choice of the wire diameter 54 and the spring diameter 56, the elasticity or damping characteristics and the force to be applied for mounting and dismounting can be adapted to the respective application.

The reference numeral 57 designates a spring length which the coiled spring wire (as can be taken from the illustration according to fig. 3) occupies over its longitudinal extent before it can be converted into the shape of the spring ring 46 over its extended length by the mutual engagement of the spring ring start 48 and the spring ring end 50 at the coupling point 52.

The substantially rectangular contour of the rolled-up spring ring 58 can be seen from fig. 3.4. Such a member may be circularly curved or may also have a substantially rectangular extending profile as shown in fig. 3.4.

Fig. 4 shows a representation of a stamped spring ring 60. The spring ring 60 shown here is stamped from a spring steel plate 62. For shaping the stamped spring ring 60, the spring tongues stamped out of the first cross section 66 and the spring sections according to the second cross section 68 are viewed in an alternating sequence in the circumferential direction. The material of the spring steel plate 62, which is illustrated in fig. 4.1 as an expansion (abbicklung) 64 in the X/Y plane, is then bent into a circular shape, so that the first cross section 66 illustrated in fig. 4.2 is obtained in relation to the first cross section 66 and a second cross section 68 according to the illustration in fig. 4.3 is formed between the two first cross sections 66. The first cross-section 66 and the second cross-section 68 extend in an alternating sequence along the circumferential direction of the stamped spring ring 60. Since the stamped ends of the tongues do not touch, as is the case with the opening remaining on the first cross section 66 according to fig. 2, the stamped spring ring 60 according to the illustration in fig. 4.2, i.e. in the bent state, acquires an elasticity which imparts a damping or spring characteristic to it.

Instead of the first and second spring elements 42, 44 shown in fig. 2 and designed as a rolled-up spring ring 58, which are designed as a spring ring 46, a stamped spring ring 60 according to the embodiment in fig. 4, 4.1, 4.2 and 4.3 can also be used instead.

Fig. 5 shows a shaft-hub connection 76 between the hub 74 and the shaft 72, on the circumference of which a plurality of projections, in this case four projections (Nocken) 84 or projections in the form of drive teeth 92, are formed. In the illustration according to fig. 5, four projections 84 or four drive teeth 92 are formed on the shaft 72 in a 90 ° indexing manner.

In fig. 5.2, it is shown that each of the projections 84 or the gearing 92 is wound by a wound helical spring 86, which is configured here as a ring. The wound helical spring 86 is introduced into a longitudinal groove 94 which extends into its root region at each of the projections 84 or the drive teeth 92, that is to say at the circumference of the outer circumference of the shaft 72. The longitudinal groove 94 extends in the axial direction parallel to the axis of symmetry of the shaft 72, as shown in the illustration according to fig. 5.2. Fig. 5.1 shows an enlarged view of a detail of the projection 84 or of the transmission teeth 92 with the helical spring 80 introduced into the longitudinal groove 94. As can be seen from the illustration according to fig. 5.1, the helical spring 80 is made of a rolled-up spring wire material. The flank gap 78 is pressed out by the helical spring 80 introduced into the longitudinal groove 94, which would otherwise occur between the contact surface 96 of the circumferentially extending groove 82 of the hub 74 and the drive teeth 92 engaged therein. In fig. 5.1, a helical spring 80 is accommodated on the gearing teeth 92, whereas, as shown in fig. 5.2, a wound helical spring 86 can be accommodated on each of the gearing teeth 92, which is wound around the respective gearing tooth 92 in the form of a ring and manufactured as the sole component.

The individual wound coil springs 86 can be produced from the pin-shaped coil springs 80 (see illustration according to fig. 3.4) in a rectangular shape with a corresponding length and simply can be slipped from the top onto the projections 84 or the transfer teeth 92 before the shaft/hub connection 76 is built up. The wound helical spring 86 is applied by pressing it into a corresponding longitudinal groove 94 in the region of the base of the gearing 92 and is permanently locked there as a result of the spring tension. This results in a region of the wound helical spring 86 on each side of the gear teeth 92.

Fig. 6 shows the force relationships that occur between the wound coil springs 86 that are received in longitudinal grooves 94 on both flanks of the boss 84. The wound helical spring 86 bears on the one hand against a longitudinal groove 94 of the gearing 92 and extends in the plane of the drawing according to fig. 6 and on the other hand on an abutment surface 96 of the groove 82 in the circumferential direction of the hub 74. By determining the angles α or α/2 and β, the required support force requirements can be designed and determined, depending on the desired mechanical load, not only in the radial direction but also in the tangential direction, depending on the case. By F_ANIndicating the driving force driving portion, by F_AEINBShowing the installation force portion. Which is divided into radial portions FR_1…And a tangential component FT_F1…. As shown in the illustration according to fig. 6. Furthermore, it can be seen from the illustration according to fig. 6 that the wound helical spring 86 is designed in the form of a ring which engages without play on an abutment surface 96 of the groove 82 extending in the circumferential direction on the hub 74.

Fig. 7 shows a perspective view of a journal constructed on the shaft 72. As can be seen from the illustration according to fig. 7, a plurality of gearing teeth 92 are formed on the shaft journal of the shaft 72, said gearing teeth being present here in a 90 ° graduation. On each tooth flank 102 of the gearing 92 there is a longitudinal groove 94 extending in the axial direction. One clamping pin 88 is introduced into each of the longitudinal grooves 94, as it is shown on an enlarged scale in fig. 8. The clamping pin 88 has a substantially pin-shaped appearance, wherein the circumference of the clamping pin is interrupted by a longitudinal slit 90. The clamping pin 88 is preferably made of a spring steel plate 62, as is also the previously mentioned stamped spring ring 60. After stamping, the clamping pins 88 are bent such that their ends lie opposite one another along the longitudinal slit 90 without touching one another. Thus, the clamp pin 88 made of the spring steel plate 62 obtains elasticity. If the clamping pin 88 according to the illustration in fig. 8 is now introduced into each longitudinal groove 94 on the tooth flank 102 of the gearing 92 on each side, the shaft 72 can be journalled in the hub 74.

As can be seen from the plan view shown in fig. 9, in the assembled state of the shaft-hub connection 76, the hub 74 engages with the shaft 72 or the journal shown in fig. 7. In this case, all the gear teeth 92 move into corresponding grooves 82 of the hub 74 which extend in the circumferential direction. This brings the outer circumferential surfaces of the clamping pins 88 into contact with contact surfaces 96, which contact the grooves 82 extending in the circumferential direction in the hub 74. Since the clamping pin 88 is arranged in the longitudinal groove 94 on each of the flanks 102 of each drive tooth 92, the shaft 72 or its journal is accommodated without play in the hub 74 and centered relative thereto due to the elasticity of the clamping pin 88. When the shaft 72 is rotated both in the first rotational direction 98 and in the opposite second rotational direction 100, it is ensured that the outer circumference of the clamping pin 88 makes contact on one of the tooth flanks 102, depending on the

rotational direction

98, 100, with the corresponding abutment face 96 of the groove 82 extending in the circumferential direction. The gearless alternating operation of the shaft-hub connection 76, shown in top view in fig. 9, is ensured in the first rotational direction 98 and in the second rotational direction 100. As is apparent from the illustration according to fig. 9, the clamping pin 88 accommodated in a longitudinal groove 94 extending in the plane of the drawing does not have a closed circumferential surface in a plan view according to the drawing, but rather is formed on its circumference with a longitudinal slit 90 which imparts elasticity to the clamping pin 88.

Fig. 9 shows that in this embodiment variant of the shaft 72, four gearing teeth 92 are formed with a 90 ° graduation. On each of its flanks 102, there is a longitudinal groove 94 extending in the plane of the drawing, into which a clamping pin 88, shown in perspective in fig. 8, which in the illustration can be rolled from the spring steel sheet 62 and has a longitudinal slit 90 extending in the longitudinal direction, is introduced.

Both with the shaft connection 40 according to fig. 4.3 and with the shaft-hub connection 76 according to fig. 5 to 9, a play-free and centered connection of the two drive assemblies, for example of the first shaft 12 and the second shaft 22, is possible for the shaft connection 40 and a play-free and centered connection between the shaft 72 and the hub 74 is possible for the shaft-hub connection 76. In both variants, good centering and defined positioning and vibration damping can be achieved within the shaft connection 40 and the shaft/hub connection 76. The solution proposed according to the invention results in significantly lower transmission power losses and outstanding damping characteristics in both embodiments thereof. Unbalance and transmission of shocks and the consequent reduction of noise and operational smoothness are other features of the shaft connection 40 proposed according to the invention. In this way, the oblique bearing diagram is again omitted with respect to the first toothing 14 meshing with the second toothing 16, with respect to the shaft connection 40, which is designed, for example, as a plug toothing connection. The service life of the proposed play-free shaft connection 40 and of the centered and play-free shaft-hub connection 76 can be considerably more highly estimated due to the mechanically lower stresses.

By selecting the respective spring steel plate 62 and the high deformation possibilities with regard to the configuration of the wire diameter 54 and the spring diameter 56, the spring element 42 or 44, whether manufactured as a rolled spring ring 58 or a stamped spring ring 60, can be manufactured with virtually any geometric and dimensional design.

The present invention is not limited to the embodiments described herein and the aspects emphasized therein. On the contrary, many modifications are possible within the scope of the appended claims, within the reach of a person skilled in the art.

Claims

1. A shaft connection (40) between a first shaft (12) with a first toothing (14) and a second shaft (22) with a second toothing (16), characterized in that at least one spring element (42, 44, 80, 86, 88) in the shape of a ring or a pin, which centers the first shaft (12) relative to the second shaft (22) or, conversely, the second shaft (22) relative to the first shaft (12), is accommodated on the first shaft (12).

2. A shaft-hub connection (76) between a shaft (72) having a gearing (84, 92) and a hub (74) having a groove (82) in the circumferential direction, characterized in that the gearing (84, 92) is either wound by an annular spring element (42, 44, 86) or is provided with a pin-shaped spring element (80, 88) which supports the gearing (84, 92) in the circumferential direction in the groove (82) of the hub (74).

3. The shaft connection (40) or shaft-hub-connection (76) according to claim 1 or 2, characterized in that the spring element (42, 44) is configured as a rolled-up spring ring (58) in which a spring ring start (48) and a spring ring end (50) are coupled at a coupling point (52).

4. Shaft connection (40) or shaft-hub-connection (76) according to claim 1 or 2, characterized in that the spring element (42, 44) is configured as a rolled-up spring ring (58) made of spring wire having a wire diameter (54) of between 0.2mm and 0.5 mm and made of spring steel wire, stainless steel spring wire or of EN 10270-3-14-310 with a spring diameter (56) of between 1.2 mm and 5 mm.

5. Shaft connection (40) or shaft-hub-connection (76) according to claim 1 or 2, characterized in that the spring element (42, 44) is made as a stamped spring ring (60) from a spring steel plate (62).

6. Shaft connection (40) or shaft-hub-connection (76) according to claim 1 or 2, characterized in that the spring elements (42, 44) of the stamped spring ring (60) have a first cross section (66) and a second cross section (68) in an alternating sequence.

7. The shaft connection (40) or shaft-hub-connection (76) according to claim 1 or 2, characterized in that the gearing (84, 92) has a longitudinal groove (94) in the root region for accommodating a helical spring (80) or a clamping pin (88).

8. Shaft connection (40) or shaft-hub-connection (76) according to claim 7, characterized in that the clamping pin (88) has a longitudinal slit (90) on its circumference.

9. Shaft connection (40) or shaft-hub-connection (76) according to claim 1 or 2, characterized in that the spring elements (42, 44) on the first shaft (12) or the second shaft (22) are accommodated in grooves which extend in the circumferential direction on the shafts (12, 22).

10. Shaft connection (40) or shaft-hub-connection (76) according to claim 7, characterized in that the longitudinal groove (94) is configured in the root region of both flanks (102) of the gearing (84, 92).

11. Use of a shaft connection (40) or a shaft-hub-connection (76) according to any one of claims 1 to 10 for connecting two shafts (12, 22) in a transmission of an electrically driven vehicle.

12. Use of a shaft-hub-connection (76) according to any one of claims 1 to 10 between a shaft (72) and a hub (74) in an E-shaft module of an electrically driven vehicle.

13. Use of a shaft connection (40) or a shaft-hub-connection (76) according to any one of the preceding claims in a transmission mechanism of a vehicle driven with an internal combustion engine, a Hybrid Electric Vehicle (HEV) or a plug-in hybrid electric vehicle (PHEV).