DE102015214935A1 - Electric machine with coupling device and actuating device - Google Patents

Abstract

The invention relates to an electric machine with a stator and a rotor and a coupling device and an actuating device, which are integrated in the rotor; in particular for a drive train of a motor vehicle, wherein the actuating device comprises a Wälzkörperrampensystem with an adjustable ramp means having a first ramp ring and a second ramp ring, wherein the first ramp ring first ramps with a slope and the second ramp ring second ramps with a slope, wherein the slope the ramps along the ramps changed, wherein the first ramp ring and the second ramp ring are rotatable relative to each other in a circumferential direction, wherein between each first ramp and second ramp each at least one rolling element is arranged, which moves with a rotation of the ramp rings to each other along the ramps in that when the ramp rings are rotated relative to each other there is a change in a distance in an axial direction between the ramp rings, wherein the actuating device further comprises a planetary gear with a ring gear, a sun gear, planetary gears and a m web, wherein the first ramps are fixedly connected to the ring gear and the second ramps are associated with the web.

Description

The invention relates to an electric machine with a stator and a rotor and a coupling device and an actuating device, which are integrated in the rotor; in particular for a drive train of a motor vehicle, wherein the actuating device comprises a Wälzkörperrampensystem with an adjustable ramp means having a first ramp ring and a second ramp ring, wherein the first ramp ring first ramp and the second ramp ring second ramp, wherein the first ramp ring and the second ramp ring in a circumferential direction are rotatable relative to each other, wherein between each first ramp and second ramp each at least one rolling element is arranged, which moves with a rotation of the ramp rings to each other along the ramps, so that when a rotation of the ramp rings to each other a change in a distance in an axial direction between the ramp rings, wherein the actuating device further comprises a planetary gear with a ring gear, a sun gear, planetary gears and a web, wherein the first ramps are fixedly connected to the ring gear and the second ramps the web zugege are orders.

In particular, the clutch device is a connection clutch (E-clutch) for a hybrid drive train or a booster clutch, wherein the Zuschaltkupplung is integrated in a rotor of an electric motor of the drive train. The Zuschaltkupplung is adapted to couple an internal combustion engine to the drive train or decouple from the drive train.

In the case of a pure electromotive drive, the connection clutch is open, so that the internal combustion engine is decoupled from the drive train. If a higher power is needed or the electrical energy supply is running low, the engine is started by partially closing the cut-in clutch by the Zuschlopkupplung goes into overrun mode.

For this purpose, an electric brake is closed, so that within the Zuschaltkupplung a speed difference between a lamellenseitigen ramp and a rohlradseitigen ramp is formed by means of a planetary gear / epicyclic gear (which is provided to increase the engagement force) the Wälzkörperrampensystem is rotated, which is the (dry) The multi-plate clutch of the connection clutch partially engages. The internal combustion engine is started by the electric motor. When the engine rotates faster than the electric motor (train operation), a freewheel closes, whereby the Zuschaltkupplung is fully engaged.

When the freewheel closes in traction, the engine transmits a portion of its torque via an associated with the freewheel, additional sun gear, and the planet and the ring gear on the ring gear ramp, so that the Zuschaltkupplung is fully engaged and then the entire torque of Internal combustion engine can transmit in train operation.

Such a coupling device with Wälzkörperrampensystem is from the DE 10 2013 210 451 A1 known, which is hereby incorporated by reference. In particular, reference is made to the statements and figures there, wherein like reference numerals in this application with the same reference numerals of the present invention match.

The axial displaceability of the ramp ring connected to the web is realized by leaf springs, which simultaneously bias the Wälzkörperrampensystem so that it rotates back to its zero position with open pilot clutch and thus opens the connection clutch.

As from the above DE 10 2013 210 451 A1 As can be seen, the e-clutch is a rotor-integrated connecting clutch, which connects the internal combustion engine with the electric machine and the drive train. To start the internal combustion engine, the electric machine is used. If the vehicle is already being driven electrically, then the electric machine must increase the currently provided torque by the starting torque of the internal combustion engine at the time of engine start, at the same time the e-clutch is closed. So that no longitudinal accelerations occur on the vehicle while the transmittable torque of the e-clutch must be set very precisely to the starting torque.

To close the connection coupling a torque is applied to the freely rotatable ramp ring of the ball ramp system shown there, via a pilot element, whereby the two ramps rotate relative to each other and so the connection is closed. In this case, the leaf spring is further deflected due to the axial movement of the ramp ring, whereby the leaf spring force increases. With increasing lamellar wear, the ramp system must be further rotated starting from the new state of the connection clutch, whereby the leaf spring force increases again. This has the consequence that the Wirkanpresskraft in the Zuschaltkupplung and thus the transmittable torque (despite the same pilot torque) changes over the wear range.

On this basis, the present invention, the object of the prior art At least partially overcome the disadvantages known to the art.

The object is solved by the features of independent claim 1. Advantageous developments are the subject of the dependent claims.

In particular, a Wälzkörperrampensystem a clutch device is proposed comprising at least one adjustable ramp device with a first ramp ring and a second ramp ring, wherein the first ramp ring first ramps with a slope and the second ramp ring second ramps with a slope, wherein the first ramp ring and the second ramp ring in a circumferential direction are rotatable relative to each other, wherein between each first ramp and second ramp each have a rolling body is arranged, which moves in a rotation of the ramp rings to each other along the ramps, so that when a rotation of the ramp rings to each other a change in a distance in an axial Direction between the ramp rings takes place, with the slope of the ramps changing along the ramps.

In particular, a slope is chosen for the ramps to compensate for a change in leaf spring force over the engagement path. Preferably, the ramp slope is less than before after passing through a home position (when new). In particular, therefore, a clutch device with a constant ratio (pilot torque to torque clutch) is proposed over the entire wear range of the clutch device.

In particular, it is proposed to adjust the slope of the ramps so that a predetermined ratio (pilot torque to torque clutch) over the entire wear range is adjustable.

In particular, the pitch of the first ramp and the second ramp are each identical.

In particular, each ramp ring comprises in each case three ramps which are arranged distributed uniformly in the circumferential direction as pairs of the first ramp and the second ramp, each having a rolling element between them (for example a ball).

According to a preferred development, in a first region of the ramps, in which the ramp rings are arranged in close proximity to one another in the axial direction, there is in each case a first slope having a first value, wherein in at least a second region of the ramps (which are located in FIG Circumferential direction to the first region immediately adjoins), in which the ramp rings are arranged in the axial direction at a greater distance from each other, there is a second slope having a second value, wherein the first value and the second value are different.

In particular, the second value is less than the first value. Especially with such an embodiment of the coupling device can be realized over the entire wear area of the coupling device a constant translation (pilot torque to moment clutch).

In particular, in the (immediate) connection to the second region, there is a third region with a third slope, in which the ramp rings are arranged in the axial direction at a further increased distance from one another, the third slope having a smaller third value than the first value and the second value.

The slope preferably has a constant value in at least one area.

In particular, only the first slope in the first region has a constant first value.

Preferably, the pitch has a constant value in each area.

Preferably, the slope is steadily smaller. Ie. in particular, that the value of the slope steadily decreases. The value of the slope can also remain constant over a certain range or a subrange of a range, but can not become larger again.

In particular, the invention also relates to an assembly of the coupling device and the actuating device; in particular for a drive train of a motor vehicle having an internal combustion engine, an electric machine with a stator and a rotor and a transmission device, wherein the coupling device in the drive train between the internal combustion engine on the one hand and the electric machine and the transmission device on the other can be arranged, wherein the coupling device and the actuating device are integrated in the rotor; wherein the actuating device comprises a Wälzkörperrampensystem according to the invention and comprises a planetary gear with a ring gear, a sun gear, planetary gears and a web, wherein the first ramps are fixedly connected to the ring gear and the second ramps are associated with the web and rotatably via leaf springs with the web and in are connected biased axial direction, wherein the ring gear and the web and thus the ramps through the planetary gear in the circumferential direction relative to each other and against the spring force of the leaf springs are rotatable so that increases distance between the ramp rings, wherein in a starting position, the distance between the ramp rings is minimal and the rolling elements are arranged in a first region of the ramps.

Also in this context is on the DE 10 2013 210 451 A1 which is fully referenced. There, a coupling device is proposed, wherein, however, the ramps have a constant slope.

The features listed individually in the claims can be combined with one another in any technologically meaningful manner and can be supplemented by explanatory facts from the description and details from the figures, wherein further embodiments of the invention are shown.

The invention and the technical environment will be explained in more detail with reference to FIGS. The figures show particularly preferred embodiments, to which the invention is not limited. In particular, it should be noted that the figures and in particular the illustrated proportions are only schematic. Like reference numerals designate like objects. Show it:

1 a powertrain of a motor vehicle with a parallel full hybrid drive and arranged in the drive train coupling device;

2 an integrated into the rotor of an electric machine coupling device for a motor vehicle with a hybrid drive;

3 a rolling element ramp system; and

4 a ramp.

1 shows a drive train 100 a motor vehicle not otherwise shown here with a parallel full hybrid drive and one in the drive train 100 arranged coupling 102 , The powertrain 100 has an internal combustion engine 104 , a dual-mass flywheel 106 , the coupling 102 , an electric machine 108 , a gearbox 110 and at least one drivable wheel 112 on. The electric machine 108 is operable as a motor. The coupling 102 is in the drive train 100 between the dual mass flywheel 106 and the electric machine 108 arranged. The coupling 102 is in the drive train 100 between the dual mass flywheel 106 and the transmission 110 arranged. The coupling 102 has an entrance part 114 and an output part 116 on. The entrance part 114 the clutch 102 is with the dual mass flywheel 106 connected. The starting part 116 the clutch 102 is with the electric machine 108 connected. The electric machine 108 has a stator 118 and a rotor 120 on. The starting part 116 the clutch 102 is with the rotor 120 the electric machine 108 connected. The starting part 116 the clutch 102 is with the gearbox 110 connected. The electric machine 108 is with the gearbox 110 connected. The rotor 120 the electric machine 108 is with the gearbox 110 connected.

2 shows one, in a rotor 200 (like rotor 120 according to 1 ) of an electric machine not otherwise shown here (such as electric machine 108 according to 1 ) integrated clutch 202 (like clutch 102 according to 1 ), with an actuating device 204 for a motor vehicle with a hybrid drive. The coupling 202 is in the direction of extension of the axis of rotation 206 and in the radial direction within the rotor 200 arranged. The actuating device 204 is in the direction of extension of the axis of rotation 206 and in the radial direction within the rotor 200 arranged. The coupling 202 and the actuator 204 are arranged nested inside each other. The coupling 202 is arranged on the engine side. The actuating device 204 is arranged on the transmission side.

The coupling 202 has an input part and an output part. The entrance part has a shaft 208 , a moment sensor 210 and clutch discs, like 212 , on. The output part of the coupling 202 has a pressure plate 214 , Intermediate printing plates, such as 216 , and a printing plate 218 on. The clutch discs 212 are rotatable with the shaft 208 connected. The pressure plate 214 , the intermediate printing plates 216 and the pressure plate 218 are non-rotatable with the rotor 200 connected. The pressure plate 214 is in the direction of extension of the axis of rotation 206 limited axially displaceable.

The actuating device 204 has a planetary gear with a ring gear 220 a sun wheel 222 , Planetary gears and a bridge 224 on. The ring gear 220 has an internal toothing. The sun wheel 222 has an external toothing. The planetary gears each have an outer toothing. The epicyclic gearbox has first epicyclic gears, such as 226 , on, with the sun wheel 222 to form a first translation. The epicyclic gearbox has second epicyclic gears, such as 228 , on, with the ring gear 220 to form a second translation. There are each a first planetary gear 226 and a second planetary gear 228 rotatably connected with each other. The planetary gears 226 . 228 are in the jetty 224 stored.

The actuating device 204 has a ramp device 2 with a first ramp ring 3 and a second ramp ring 4 on. The first ramp ring 3 has first ramps 230 on. The second ramp ring 4 has second ramps 232 on. The first ramp ring 3 and the second ramp ring 4 are in the circumferential direction 6 rotatable relative to each other. Between the first ramp ring 3 and the second ramp ring 4 are rolling elements, like 234 arranged. A twist of the ramp rings 3 . 4 relative to each other causes a change in the distance 7 between the ramp rings 3 . 4 , The ramp rings 3 . 4 are connected to each other via the epicyclic gearing. The first ramp ring 3 is with the ring gear 220 firmly connected. The second ramp ring 4 is with the jetty 224 rotatable and to the bridge 224 in the axial direction 8th relocatable connected. The second ramp ring 4 is with the jetty 224 using ring-shaped leaf springs, such as 236 , connected. The leaf springs 236 act as tension springs between the bridge 224 and the second ramp ring 4 , The jetty 224 is with the rotor 200 firmly connected.

The actuating device 204 has the moment sensor 210 and a freewheel 238 on. The moment sensor 210 used for controlled adjustment of the ramp device 2 , The moment sensor 210 has an input part and an output part. The input part of the momentary sensor 210 is with the wave 208 rotatably connected. The output part of the momentary sensor 210 is with the clutch discs 212 rotatably connected. Between the input part and the output part of the momentary sensor 210 are helical compression springs, like 240 , effective. The freewheel 238 has an inner ring and an outer ring. The freewheel 238 has clamp body. The inner ring of the freewheel 238 is with the wave 208 rotatably connected. The outer ring of the freewheel 238 is with a sleeve-shaped component 242 rotatably connected, with the second planetary gears 228 corresponds. The moment sensor 210 and the freewheel 238 are in the direction of extension of the axis of rotation 206 arranged side by side. The moment sensor 210 and the freewheel 238 overlap in the radial direction. The helical compression springs 240 and the freewheel 238 overlap in sections in the radial direction. The input part of the momentary sensor 210 and the inner ring of the freewheel 238 have at least approximately the same inner diameter. The moment sensor 210 and the freewheel 238 are in the direction of extension of the axis of rotation 206 inside the clutch 202 arranged. The moment sensor 210 and the freewheel 238 are radially inside the coupling 202 arranged.

The actuating device 204 has an eddy current brake 244 on. The eddy current brake 244 has a brake stator and a brake rotor. The brake stator and the brake rotor are arranged one above the other in the radial direction. The brake stator is arranged radially on the outside of the brake rotor. The brake stator has several coils and armatures. The anchors each have a staple-like shape with a back portion and two finger portions. The coils are each arranged on the back portion of an armature. The coils each have a winding axis, which is the axis of rotation 206 is arranged in parallel. The back sections of the anchors each extend parallel to the axis of rotation 206 , The brake stator is with the rotor 200 firmly connected. The brake rotor has a disc-like shape. The brake rotor has a disk-like metal plate. The brake rotor is non-rotatable with the sun gear 222 connected. The armatures of the brake stator enclose the brake rotor in a clamp-like manner. The armatures of the brake stator enclose the brake rotor with the finger sections. This can be done via the sun gear 222 a pilot torque for actuating the clutch 202 be initiated. The planetary gear is arranged so that the pilot torque is increased.

In purely electric driving is the clutch 202 open. ring gear 220 , Footbridge 224 , Planetary gears 226 . 228 and sun gear 222 run at the same speed (electric motor speed), the epicyclic gearbox is so to speak "blocked". This will twist the ramp rings 3 . 4 and the actuation of the clutch 202 prevented. In addition, an influence of rotational accelerations is almost eliminated by those with the ring gear 220 rotating components on the one hand and those with the sun gear 222 On the other hand, rotating components each have approximately the same moment of inertia.

If the internal combustion engine is to be started now, the eddy current brake is used 244 on the Sonnerad 222 a pilot torque for the clutch 202 generated. This moment is a braking torque and counteracts the original rotational movement. The sun wheel 222 is rotated relative to the previously existing planetary gear. About the function of the epicyclic gear is the ring gear 220 and thus also the ramp ring 3 relative to the jetty 224 twisted, which at the same time a twisting of the ramp device 2 and closing the clutch 202 equivalent.

The pilot torque of the eddy current brake 244 is due to the translation on the epicyclic gearbox and on the ramp rings 3 . 4 translated so that the internal combustion engine can be started with the required torque. The pre-control torque can be via the power supply to the eddy current brake 244 controlled and set up in the shortest possible time. The starting time of the internal combustion engine is a few milliseconds. Due to the high translation of the moment and the short operating time results for starting the Internal combustion engine a low actuation energy. Furthermore, the eddy current brake 244 wear-free and can use the magnetic field of the e-magnet any intermediate stages of the required torque, without torque fluctuations and Reibwertabhängigkeiten realize.

When the internal combustion engine is running, the pilot torque on the internal combustion engine itself and the freewheel 238 generated. The wave 208 serves to connect the internal combustion engine. In this operating state, the clutch transmits 202 a moment in the direction of pulling. A certain part of this tensile torque is over the freewheel 238 as pre-control torque for the component 242 used. This will be the clutch 202 by a part of the moment of the internal combustion engine on the ramp rings 3 . 4 operated via the epicyclic gearing. The clutch discs 212 and be between the pressure plate 214 , the intermediate printing plates 216 and the printing plate 218 clamped and transmit the required moment. The angle of rotation of the ramp rings 3 . 4 is about the moment sensor 210 regulated. This also enables the clutch 202 opens again as soon as no more moment is transmitted. By this arrangement of the components is the coupling 202 in this state self-regulating and requires no further external energy for actuation. In this state, operating states such as load shifting, boosting and driving with the internal combustion engine are possible. An overrun operation of the internal combustion engine is also possible for the system. In the process, the eddy current brake becomes 244 operated in continuous operation.

3 shows a Wälzkörperrampensystem 1 , The rolling element ramp system 1 includes an adjustable ramp device 2 with a first ramp ring 3 and a second ramp ring 4 , where the first ramp ring 3 first ramps 230 with a slope 5 and the second ramp ring 4 second ramps 232 with a slope 5 having, wherein the first ramp ring 3 and the second ramp ring 4 in a circumferential direction 6 (about the axis of rotation 206 ) are rotatable relative to each other, wherein between each first ramp 230 and second ramp 232 each a rolling element 234 is arranged, which is at a rotation of the ramp rings 3 . 4 to each other along the ramps 230 . 232 moves, so that at a rotation of the ramp rings 3 . 4 to each other a change of a distance 7 in an axial direction 8th between the ramp rings 3 . 4 he follows.

4 shows a ramp 230 . 232 (in developed form), where in a first area 9 the ramp 230 . 232 in which the ramp rings 3 . 4 in the axial direction 8th at a small distance 7 arranged in each case a first slope 10 present, the first value 11 having, in at least a second area 12 the ramp 230 . 232 in which the ramp rings 3 . 4 in the axial direction 8th at a greater distance 7 are arranged to each other, each a second slope 13 present, which has a second value 14 , wherein the first value 11 and the second value 14 are different, here the second value 14 less than the first value 11 , Furthermore, following the second area 9 a third area 15 with a third slope 16 provided in which the ramp rings 3 . 4 in the axial direction 8th in a further enlarged distance 7 are arranged to each other, wherein the third slope 16 a lower third value 17 has as the first value 11 and the second value 14 ,

The preceding embodiments relate to an electrical machine 108 with a stator 118 and a rotor 120 . 200 and a coupling device 102 . 202 and an actuator 204 in the rotor 120 . 200 are integrated; especially for a drive train 100 a motor vehicle, wherein the actuating device 204 a Wälzkörperrampensystem 1 with an adjustable ramp device 2 with a first ramp ring 3 and a second ramp ring 4 having, wherein the first ramp ring 3 first ramps 230 with a slope 5 . 10 . 13 . 16 and the second ramp ring 4 second ramps 232 with a slope 5 . 10 . 13 . 16 has, where the slope 5 . 10 . 13 . 16 the ramps 230 . 232 along the ramps 230 . 232 changed, with the first ramp ring 3 and the second ramp ring 4 in a circumferential direction 6 are rotatable relative to each other, wherein between each first ramp 230 and second ramp 232 in each case at least one rolling element 234 is arranged, which is at a rotation of the ramp rings 3 . 4 to each other along the ramps 230 . 232 moves, so that at a rotation of the ramp rings 3 . 4 to each other a change of a distance 7 in an axial direction 8th between the ramp rings 3 . 4 takes place, wherein the actuating device 204 Furthermore, a planetary gear with a ring gear 220 a sun wheel 222 , Planetary gears 226 . 228 and a jetty 224 having, wherein the first ramps 230 with the ring gear 220 are firmly connected and the second ramps 232 the jetty 224 assigned.

LIST OF REFERENCE NUMBERS

1

 Wälzkörperrampensystem

2

 ramp means

3

 first ramp ring

4

 second ramp ring

5

 pitch

6

 circumferentially

7

 distance

8th

 axial direction

9

 first area

10

 first climb

11

 first value

12

 second area

13

 second climb

14

 second value

15

 third area

16

 third slope

17

 third value

100

 powertrain

102

 coupling device

104

 Internal combustion engine

106

Dual Mass Flywheel

108

electric machine

110

 transmission

112

 wheel

114

 introductory

116

 output portion

118

 stator

120

rotor

200

rotor

202

 clutch

204

 actuator

206

 axis of rotation

208

 wave

210

 torque sensor

212

 clutch disc

214

 pressure plate

216

 Between the pressure plate

218

printing plate

220

 ring gear

222

 sun

224

 web

226

 first planetary gear

228

 second planetary gear

230

 first ramp

232

second ramp

234

 rolling elements

236

 leaf spring

238

freewheel

240

Helical compression spring

242

component

244

 Eddy current brake

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• DE 102013210451 A1 [0006, 0008, 0025]

Claims (9)

Electric machine ( 108 ) with a stator ( 118 ) and a rotor ( 120 . 200 ) and a coupling device ( 102 . 202 ) and an actuating device ( 204 ), which are in the rotor ( 120 . 200 ) are integrated; especially for a drive train ( 100 ) of a motor vehicle, wherein the actuating device ( 204 ) a rolling body ramp system ( 1 ) with an adjustable ramp device ( 2 ) with a first ramp ring ( 3 ) and a second ramp ring ( 4 ), wherein the first ramp ring ( 3 ) first ramps ( 230 ) with a slope ( 5 . 10 . 13 . 16 ) and the second ramp ring ( 4 ) second ramps ( 232 ) with a slope ( 5 . 10 . 13 . 16 ), wherein the slope ( 5 . 10 . 13 . 16 ) of the ramps ( 230 . 232 ) along the ramps ( 230 . 232 ), the first ramp ring ( 3 ) and the second ramp ring ( 4 ) in a circumferential direction ( 6 ) are rotatable relative to each other, wherein between each first ramp ( 230 ) and second ramp ( 232 ) each at least one rolling element ( 234 ) is arranged, which in a rotation of the ramp rings ( 3 . 4 ) to each other along the ramps ( 230 . 232 ), so that upon rotation of the ramp rings ( 3 . 4 ) to each other a change of a distance ( 7 ) in an axial direction ( 8th ) between the ramp rings ( 3 . 4 ), the actuating device ( 204 ) further comprises a planetary gear with a ring gear ( 220 ), a sun wheel ( 222 ), Planetary gears ( 226 . 228 ) and a jetty ( 224 ), the first ramps ( 230 ) with the ring gear ( 220 ) and the second ramps ( 232 ) the bridge ( 224 ) assigned. Electric machine ( 108 ) according to claim 1, wherein the second ramps ( 232 ) via leaf springs ( 236 ) with the bridge ( 224 ) rotationally fixed and in the axial direction ( 8th ) are biased, wherein the ring gear ( 220 ) and the jetty ( 224 ) and thus the ramps ( 230 . 232 ) by the epicyclic gear in the circumferential direction ( 6 ) relative to each other and against the spring force of the leaf springs ( 236 ) are rotatable so that distance ( 7 ) between the ramp rings ( 3 . 4 ), wherein in an initial position ( 18 ) the distance ( 7 ) between the ramp rings ( 3 . 4 ) is minimal and the rolling elements ( 234 ) in a first area of the ramps ( 230 . 232 ) are arranged. Electric machine ( 108 ) according to claim 1 or 2, wherein in a first region ( 9 ) of the ramps ( 230 . 232 ), in which the ramp rings ( 3 . 4 ) in the axial direction ( 8th ) at close range ( 7 ) are arranged in each case a first slope ( 10 ), which has a first value ( 11 ), wherein in at least a second area ( 12 ) of the ramps ( 230 . 232 ), in which the ramp rings ( 3 . 4 ) in the axial direction ( 8th ) at a greater distance ( 7 ) are arranged to each other, in each case a second slope ( 13 ), which has a second value ( 14 ), the first value ( 11 ) and the second value ( 14 ) are different. Electric machine ( 108 ) according to claim 3, wherein the second value ( 14 ) is less than the first value ( 11 ). Electric machine ( 108 ) according to claim 4, wherein following the second area ( 9 ) a third area ( 15 ) with a third slope ( 16 ) is present, in which the ramp rings ( 3 . 4 ) in the axial direction ( 8th ) at a further increased distance ( 7 ) are arranged to each other, wherein the third slope ( 16 ) a lower third value ( 17 ) than the first value ( 11 ) and the second value ( 14 ). Electric machine ( 108 ) according to one of claims 3 to 5, wherein the slope ( 5 . 10 . 13 . 16 ) in at least one area ( 9 . 12 . 15 ) each have a constant value ( 11 . 14 . 17 ) having. Electric machine ( 108 ) according to one of claims 3 to 6, wherein only the first slope ( 10 ) in the first area ( 9 ) has a constant first value ( 11 ) having. Electric machine ( 108 ) according to one of claims 3 to 6, wherein the slope ( 5 . 10 . 13 . 16 ) in every sector ( 9 . 12 . 15 ) each have a constant value ( 11 . 14 . 17 ) having. Electric machine ( 108 ) according to one of claims 4 to 8, wherein the slope ( 5 . 10 . 13 . 16 ) becomes steadily smaller.

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