DE102010023076A1 - Multi-speed gear for vehicle, has brake and coupling device comprising actuator for decelerating ring gear of planetary gears under release of planetary gear cage in shift position and coupling ring gear with cage in another shift position - Google Patents

Abstract

The gear (1) has a coupling device (6) for coupling a gear box input (7) to a motor output shaft. A transmission drive shaft (8) and a gear box driven shaft (9) accommodate spur gear pairs (4), and planetary gears (3) are arranged between the casing and input. A brake and coupling device (15) has an actuator (16) selectively holding the gears in a freewheeling condition in a shift position (17), decelerating a ring gear (20) of the planetary gears under release of a planetary gear cage (12) in another shift position (18) and coupling the ring gear with the cage in a third shift position (19).

Description

The application relates to a multi-speed transmission with torque split system via a planetary gear. The multi-speed transmission has a Stirnradpaarung for each gear, a clutch bell for receiving a coupling device for coupling a transmission input to an engine output shaft, at least one transmission input shaft and a transmission output shaft for receiving the Stirnradpaarungen the gears, and a transmission output with an output gear on the transmission output shaft. Between the clutch bell and the transmission input, the planetary gear is arranged, the Planetenradkäfig has a spur gear ring which meshes with the spur gear of the driven gear.

Such a multi-speed transmission with torque split system via a planetary gear is from the document EP 1 625 037 B1 As a transmission system for vehicles, which comprises an input shaft which can be coupled to a drive source known.

The known transmission system has for the ring gear of the planetary gear to a braking device to bridge when switching between low gears, for example, from first to second gear torque interruption by switching the planetary gear and deliver engine power to the chassis by the freewheeling ring gear of the planetary gear for this switching phase is blocked or braked and transmitted via the Stirnradzahnkranz the Planetenradkäfigs on the output gear of the transmission output shaft. As soon as the second gear engages, the brake is released for the ring gear, so that the planetary gear is in free-running.

To bridge in the lower gears of a gearbox, the torque interruptions during upshifting and thus to fill the torque gap, a reduction ratio, which corresponds almost to the reduction ratio of the third shift gear is an optimal option for the planetary gear. A disadvantage of the known transmission system of multi-speed transmission and planetary gear is that with the braking device for the ring gear further applications and reduction possibilities of the parallel-connected planetary gear can not be used.

The object of the application is to provide a multi-speed transmission with torque split system via a planetary gear, which overcomes the disadvantages of the prior art and has a braking and coupling device, which opens up further applications of the planetary gear.

This object is achieved with the subject matter of independent claim 1. Advantageous developments of the application will become apparent from the dependent claims.

According to the application, a multi-speed transmission with torque split system is provided via a planetary gear. The multi-speed transmission has a Stirnradpaarung for each gear, a clutch bell for receiving a coupling device for coupling a transmission input to an engine output shaft, at least one transmission input shaft and a transmission output shaft for receiving the Stirnradpaarungen the gears, and a transmission output with an output gear on the transmission output shaft.

Between the clutch bell and the transmission input, the planetary gear is arranged, the Planetenradkäfig has a spur gear ring which meshes with the spur gear of the driven gear. A brake and coupling device has an actuator which optionally holds the planetary gear in a freewheeling state in a first shift position, brakes a ring gear of the planetary gear in a second shift position releasing the Planetenradkäfigs and coupled in a third shift position, the ring gear with the Planetenradkäfig.

These three shift positions of the actuator have the advantage that in the first shift position the Mehrgangstirnradgetriebe without support of the planetary gear transmits torques in a conventional manner, in the second position torque interruptions can be bridged in the upshifts in the lower gears and thus can be done a torque filling between the lower gears , in the third shift position, the planetary gear is the high speed of the engine via the sun gear and rotating with the Planetenradkäfig ring gear in a ratio of 1: 1 to the spur of the Planetenradkäfigs on, so that in this third shift position and torque bridging the torque interruptions in upshifting in the upper courses becomes possible. The planetary gear is offset in the third switching position of the actuator in the so-called block cycle.

In addition, in the first and / or the second switching position, additional intermediate gears can be realized by means of the planetary gear, so that a multi-speed transmission having four forward gears can be operated with six forward gears by the second and the third shift position are used to Zwischenuntersetzungen or To realize translations. It is even possible to realize an overdrive in the third shift position when the number of teeth of the spur gear ring of the Planetenradkäfigs is selected to be larger than the number of teeth of the spur gear ring of the output gear.

Finally, it is also possible to offer a reduction ratio of the planetary gear with the second switching position of the actuator, which corresponds to a previous third gear of a Stirnradpaarung, so that a Stirnradpaarung can be saved and thus the space for the transmission can be reduced. In all three switching positions, the sun gear of the planetary gear is preferably coupled to the engine output shaft by the sun gear is mechanically connected to the flywheel of the clutch.

In one embodiment of the application, the brake and coupling device has a plurality of ring elements. A first middle ring element in this case has an adjusting ring. A central brake disk with brake linings arranged on both sides is axially displaced by the middle ring element in cooperation with the adjusting ring. The central brake disc is axially displaceable and rotationally fixed with an outer ring gear of the ring gear in engagement. Another ring element forms a first pressure ring, which is rigidly fixed to the clutch bell against which the brake disc is pressed to brake the ring gear in the second switching position of the actuator. Finally, a second pressure ring forms a third ring element, wherein the second pressure ring is rotatably mounted relative to the clutch bell and against the coupling of the ring gear with the Planetenradkäfig the brake disc is pressed by the first ring member in the third shift position.

For this purpose, the actuator is preferably actuated electrically and the adjusting ring has in annular segments extending, axially displaceable acting, double-sided arranged on the adjusting ring ramps. These ramps move during rotation of the adjusting ring, the first ring element having a Kugelanornung, roll the pairs of balls on the ramps and cause the axial displacement of the first ring segment and thus the brake disc.

The adjusting ring also has an outer sprocket segment, in which engages a worm drive spindle, which can be moved by an electric servomotor in the three switching positions. Instead of the sprocket segment in cooperation with the worm drive spindle can also be arranged on an adjusting ring articulated shift linkage which moves the adjusting ring electromagnetically via a multi-stage solenoid in the three switching positions, which advantageously allows rapid switching to the Drehmomentauffüllmodus.

The subject of the application will now be explained in more detail with reference to the accompanying figures.

1 shows a schematic cross-sectional view of a portion of a multi-speed transmission with an additional torque split system;

2 shows a schematic cross-sectional view of the torque split system in detail;

3 shows a schematic cross-sectional view of a braking and coupling device in an enlarged scale;

4 shows with the 4A . 4B and 4C schematic cross-sectional views of the brake and coupling device in three switching positions of an actuator;

5 shows a schematic plan view of an adjusting ring with three axially acting on both sides of ramps;

6 shows a schematic, partially sectioned side view of the adjusting ring according to 5 with a ball arrangement for axially displacing a first middle ring segment.

1 shows a schematic cross-sectional view of a portion of a multi-gear transmission 1 with an additional torque split system 2 via a planetary gear 3 , The multi-speed transmission 1 has a Stirnradpaarung 4 for every gear, a clutch bell 5 for receiving a coupling device 6 for coupling a transmission input 7 to an engine output shaft, not shown, at least one transmission input shaft 8th and a transmission output shaft 9 for receiving the Stirnradpaarungen 4 the gears and a transmission output 10 with a driven gear 11 on the transmission output shaft 9 on.

Between the clutch bell 5 and the transmission input 7 is the planetary gear 3 arranged. A sun wheel 25 of the planetary gear 3 is coaxial with the gear drive shaft 8th on an axle tube 39 stored and a flywheel of the coupling device 6 connected to the engine output shaft, not shown here. A planetary cage 12 has a spur gear ring 13 that rotates on the axle tube 39 is stored up. The spur gear ring 13 of the planet wheel cage 12 meshes with a spur gear wreath 14 of the output gear 11 ,

A brake and coupling device 15 that the planetary gear 3 annular surrounds, has an actuator 16 on, which optionally in a first switch position 17 , like it 1 shows the planetary gear 3 holds in a freewheeling state, in a second switching position 18 a ring gear 20 of the planetary gear 3 under release of the planetary gear cage 12 einbremst and in a third switching position 19 the ring gear 20 with the planetary gear cage 12 to a so-called block cycle of the planetary gear 3 coupled.

Because in this third shift position 19 in a block cycle of the planetary gear 3 the engine speed over the sun gear 25 directly on the spur gear ring 13 of the planet wheel cage 12 is transmitted, determines the ratio of the number of teeth of the spur gear ring 13 of the planet wheel cage 12 to the number of teeth of the spur gear ring 14 of the output gear 11 a gear ratio or a reduction ratio. This can also be an overdrive with a suitable ratio of the number of teeth of the spur gear ring 13 to the number of teeth of the spur gear ring 14 to the transmission output 10 and thus to a differential 40 be delivered.

In the second switching position 18 the brake and coupling device 15 becomes the ring gear 20 of the planetary gear 3 braked, so that a reduction ratio between sun gear speed and speed of Planetenradkäfigs 12 occurs, which can be designed such that it is in the vicinity of the third gear of the multi-speed transmission and thus there is the possibility of bridging the torque interruptions occurring in a higher speed gearshift in the lower gears, preferably from the first to the second gear, or these Torque interruptions replenish, so that the multi-speed transmission 1 In these critical phases, drive power via the torque split system 2 transmits to the chassis.

With the third switching position 19 of the actuator 16 On the other hand, torque interruptions can be bridged accordingly when upshifting in the higher gears, as already mentioned above, the speed of the output gear in the block cycle of the planetary gear up to the overdrive depending on the ratio of Stirnradzahnkränze 13 and 14 can be driven.

With this multi-speed transmission 1 with torque split system 2 via a planetary gear 3 It is therefore possible to bridge the torque interruptions occurring when switching the multi-speed transmission both in the lower gear range and in the upper gear range. For this purpose, an actuator-ball mechanism is provided with double-sided effective ramps, with the following 2 to 6 is explained in more detail. In addition, the actuator ball mechanism allows the planetary gear 3 can be designed so that it is the multi-speed transmission 1 supplemented by two more gears, namely once in the lower gear range and once in the upper gear range up to an overdrive gear.

On the other hand, it is also possible, for example, to the third gear and thus on the Stirnradpaarung for the third gear in multi-speed transmission 1 to dispense with this function through the planetary gear 3 with the second switching position 18 of the actuator 16 provided.

2 shows a schematic cross-sectional view of the torque split system 2 with the brake and coupling device 15 in detail. The brake and coupling device 15 has several ring elements 21 . 22 and 23 on, wherein a first middle ring element 21 an adjusting ring 24 owns and a central brake disc 26 with brake pads arranged on both sides 36 and 37 moves axially. The brake disc 26 stands with the ring gear 20 axially displaceable via an outer ring gear 34 of the ring gear 20 engaged and is rotatable relative to the middle ring segment 21 stored.

A second ring segment 32 forms a first pressure ring 22 , who is rigidly attached to the clutch bell 5 is fixed and against the brake disc 26 with a brake pad 38 for braking the ring gear 20 in the second switching position 18 of the actuator 16 through the first ring element 21 can be pressed. As the third ring segment 33 has the brake and coupling device 15 a second pressure ring 23 on, opposite the clutch bell 5 rotatable for example by means of a needle bearing 41 is stored. The brake disc 26 is with her brake pad 37 in the third switching position 19 of the actuator 16 against this third ring element 33 pressed and thus becomes the ring gear 20 of the planetary gear 3 with the planetary gear cage 12 coupled and a block cycle of the planetary gear 3 in which the gear ratio between sun gear 25 and planetary gear cage 12 1: 1 is produced.

3 shows a schematic cross-sectional view of a brake and coupling device 15 on an enlarged scale. The drive of the actuator 16 is here for example with a worm drive spindle 29 achieved with an outer sprocket segment 28 the adjusting ring 24 combs. Instead of a worm drive spindle 29 However, a three-stage solenoid can be used to the three switching positions of the actuator 16 to realize. When turning the adjusting ring 24 becomes a ball arrangement 38 that in takeaway rings 27 of the first middle ring element 21 or in depressions of the first middle ring element 21 are stored axially by means of a ramp 30 on which the ball arrangement 38 on both sides of the adjusting ring 24 rolls off, moved.

The first middle ring element 21 is taken along in the axial direction and can the brake disc 26 connected to the outer ring gear of the ring gear 20 achsverschieblich is engaged, from this first switching position shown here 17 in which the planetary gear 3 is released, move axially to a second or a third position, as the following 4 with the 4A . 4B and 4C shows.

4 shows with the 4A . 4B and 4C schematic cross-sectional views of the brake and coupling device 15 in three switching positions 17 . 18 and 19 of the actuator 16 , Components having the same functions as in the previous figures are identified by the same reference numerals and will not be discussed separately.

In addition shows 4A the first switching position 17 in which the planetary gear 3 is released. The ball arrangement 38 holds the first ring segment 21 and thus the brake disc 26 in a middle neutral position.

In 4B reaches the actuator 16 its second switching position 18 in which the ball assembly 38 through the ramp 30 on the adjusting ring 24 axially shifted so far that the brake pad 36 the brake disc 26 to a first pressure ring 22 holding the clutch bell 5 is fixed, is pressed. This is the ring gear 20 of the planetary gear 3 braked and can over the spur gear of the Planetenradkäfigs 12 transmit torque to the output gear during torque interruption of the lower gears of the multi-speed spur gear.

In 4C is after twisting the adjusting ring 24 the ball arrangement 38 on the two-sided effective ramps 30 shifted axially so that now on the brake pad 37 the brake disc 26 on the second pressure ring 23 with which the planetary gear cage 12 is mechanically connected, is pressed, and thus the ring gear 20 with the planetary gear cage 12 is coupled, so that the planetary gear 3 operated in a block cycle and only determine the ratio of the spur gears and the Planetenradkäfigs and the output gear ratio.

5 shows a schematic plan view of the adjusting ring 24 with three axially acting ramps on both sides 30 , These ramps 30 are in this case in three ring segments 31 . 32 and 33 the adjusting ring 24 incorporated and each have a ball assembly, as in the preceding 3 and 4 will be shown. The adjusting ring 24 itself has in this embodiment of the invention on its outer periphery an outer sprocket segment 28 on, with the above-mentioned worm drive spindle 29 meshes with the worm drive spindle 29 from a servomotor 35 is driven.

In order to achieve a rapid deceleration of the ring gear or a quick switching and coupling of the ring gear with the Planetenradkäfig, instead of the worm drive spindle 29 with electric servomotor 35 also a hinged to the outer circumference of the adjusting ring 24 articulated mounted shift linkage, which is driven by a multi-stage solenoid.

6 shows a schematic, partially cross-sectional side view of the Verstelirings 24 according to 5 along the section line CC with a ball arrangement 38 for axial displacement in the directions of arrows A '' and B ''. The ball arrangement rolls 38 held by the first middle ring segment along the double-acting ramp 30 in the ring segments shown here with dashed lines 31 and 32 , For example, the worm drive spindle 29 of the actuator 16 rotated in the direction of arrow A, then rolls the ball assembly 38 in the direction of arrow A ', whereby an axial displacement in A''takes place. In contrast, the worm drive spindle 29 of the actuator 16 rotated in the direction of arrow B, then rolls the ball assembly 38 in the direction of arrow B ', whereby an axial displacement of the first ring segment in the direction of arrow B''takes place.

LIST OF REFERENCE NUMBERS

1

Multi-speed transmission

2

Torque split system

3

planetary gear

4

spur gear pairing

5

clutch bell

6

coupling device

7

transmission input

8th

Transmission input shaft

9

Gearbox output shaft

10

transmission output

11

output gear

12

planet cage

13

Spur gear of the planetary gear cage

14

Spur gear of the output gear

15

Brake and coupling device

16

Actuator (with ball ramp mechanism)

17

first switching position (freewheeling state of the planetary gear)

18

second shift position (ring gear braked)

19

third shift position

20

ring gear

21

first middle ring element

22

first pressure ring

23

second pressure ring

24

adjusting

25

sun

26

brake disc

27

driver ring

28

outer sprocket segment

29

Worm drive spindle

30

ramp

31

ring segment

32

ring segment

33

ring segment

34

Outer ring gear of the ring gear

35

electric servomotor

36

brake lining

37

brake lining

38

ball arrangement

39

axle tube

40

differential

41

needle roller bearings

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

• EP 1625037 B1 [0002]

Claims (9)

Multi-speed transmission with torque split system ( 2 ) via a planetary gear ( 3 ), - the multi-speed transmission ( 1 ) a spur gear pairing ( 4 ) for each gear, a clutch bell ( 5 ) with coupling device ( 6 ) for coupling a transmission input ( 7 ) to an engine output shaft, at least one transmission input shaft ( 8th ) and a transmission output shaft ( 9 ) for receiving the spur gear pairs ( 4 ) of the gears, and a transmission output ( 10 ) with an output gear ( 11 ) on the transmission output shaft ( 9 ), wherein between the clutch bell ( 5 ) and the transmission input ( 7 ) the planetary gear ( 3 ) is arranged, the Planetenradkäfig ( 12 ) a spur gear ring ( 13 ) which is connected to the spur gear ( 14 ) of the driven gear meshes, and wherein a braking and coupling device ( 15 ) an actuator ( 16 ), which is optionally in a first switching position ( 17 ) the planetary gear ( 3 ) holds in a freewheeling state, in a second switching position ( 18 ) a ring gear ( 20 ) of the planetary gear ( 3 ) releasing the Planetenradkäfigs ( 12 ) and in a third switching position ( 19 ) the ring gear ( 20 ) with the Planetenradkäfig ( 12 ) couples. Multi-speed transmission according to claim 1, wherein a sun gear ( 25 ) of the planetary gear ( 3 ) is coupled to the engine output shaft. Multi-speed transmission according to claim 1 or claim 2, wherein the brake and coupling device ( 15 ) a plurality of ring elements ( 21 . 22 . 23 ), a first middle ring element ( 21 ), which has an adjusting ring ( 24 ) and a central brake disc ( 26 ) with brake linings arranged on both sides ( 36 . 37 ) axially displaced with the ring gear ( 20 ) is axially displaceable engageable, a first pressure ring ( 22 ), which is rigidly attached to the clutch bell ( 5 ) is fixed, against which the brake disc ( 26 ) for braking the ring gear ( 20 ) in the second switching position ( 18 ) through the first ring element ( 21 ), a second pressure ring ( 23 ), which is opposite the clutch bell ( 5 ) is rotatably mounted and against the coupling of the ring gear ( 20 ) with the Planetenradkäfig ( 12 ) the brake disc ( 26 ) through the first ring element ( 21 ) in the third switching position ( 19 ) is pressed. Multi-speed transmission according to claim 1, wherein the actuator ( 16 ) while rotating the adjusting ring ( 24 ) the first ring element ( 21 ) axially in the three switching positions ( 17 . 18 . 19 ) shifts. Multi-speed transmission according to claim 3 or claim 4, wherein the adjusting ring ( 24 ) extending in ring segments, axially displaceable acting, double-sided on the collar arranged ramps ( 30 ), which during the rotation of the adjusting ring ( 24 ) the first ring element ( 21 ) move axially. Multi-speed transmission according to claim 4, wherein the adjusting ring ( 24 ) an outer sprocket segment ( 28 ) into which a worm drive spindle ( 29 ) engaged by an electric servomotor ( 35 ) into the three switching positions ( 17 . 18 . 19 ) is movable. Multi-speed transmission according to claim 4, wherein in the first switching position ( 17 ) of the planetary gear ( 3 ) the multi-speed transmission ( 1 ) according to the spur gear pairs ( 4 ) is switchable. Multi-speed transmission according to claim 4, wherein in the second switching position ( 18 ) the multi-speed transmission ( 1 ) in the reduction ratio between Sonnerad ( 25 ) and Planetenradkäfig ( 12 ) with fixed ring gear ( 20 ) is operable. Multi-speed transmission according to one of the preceding claims, wherein in the third shift position ( 19 ) the multi-speed transmission ( 1 ) in the transmission ratio between the spur gear ring ( 13 ) of the planetary gear cage ( 12 ) and the spur gear ring ( 14 ) of the output gear ( 11 ) with rotating ring gear ( 20 ) is operable.

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